[Federal Register Volume 82, Number 3 (Thursday, January 5, 2017)]
[Rules and Regulations]
[Pages 1426-1591]
From the Federal Register Online via the Government Publishing Office [www.gpo.gov]
[FR Doc No: 2016-30004]
[[Page 1425]]
Vol. 82
Thursday,
No. 3
January 5, 2017
Part II
Department of Energy
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10 CFR Parts 429 and 430
Energy Conservation Program: Test Procedures for Central Air
Conditioners and Heat Pumps; Final Rule
Federal Register / Vol. 82 , No. 3 / Thursday, January 5, 2017 /
Rules and Regulations
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DEPARTMENT OF ENERGY
10 CFR Parts 429 and 430
[Docket No. EERE-2016-BT-TP-0029]
RIN 1904-AD71
Energy Conservation Program: Test Procedures for Central Air
Conditioners and Heat Pumps
AGENCY: Office of Energy Efficiency and Renewable Energy, Department of
Energy.
ACTION: Final rule.
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SUMMARY: On August 24, 2016, the U.S. Department of Energy (DOE)
published a supplemental notice of proposed rulemaking (SNOPR) to amend
the test procedure for central air conditioners and heat pumps. That
SNOPR serves as the basis for this final rule. This final rule amends
the test procedure and specific certification, compliance, and
enforcement provisions related to this product. In this final rule, DOE
makes two sets of amendments to the test procedure: Amendments to
appendix M that would be required as the basis for making efficiency
representations starting 180 days after final rule publication and a
new appendix M1 that would be the basis for making efficiency
representations as of the compliance date for any amended energy
conservation standards. The new appendix M1 establishes new efficiency
metrics SEER2, EER2, and HSPF2 that are based on the current efficiency
metrics for cooling and heating performance, but generally have
different numerical values than the current metrics. Broadly speaking,
the amendments address off-mode test procedures, test set-up and fan
delays, external static pressure conditions for testing, represented
values for CAC/HP that are distributed in commerce with multiple
refrigerants, the methodology for testing and calculating heating
performance, and testing of variable-speed systems.
DATES: The effective date of this rule is February 6, 2017. The final
rule changes of appendix M will be mandatory for representations of
efficiency starting July 5, 2017. Representations using appendix M1
will be mandatory starting January 1, 2023. The incorporation by
reference of certain publications listed in Appendix M1 is approved by
the Director of the Federal Register on February 6, 2017 February 6,
2017. The incorporation by reference of certain publications listed in
Appendix M was approved by the Director of the Federal Register as of
July 8, 2016.
ADDRESSES: The docket, which includes Federal Register notices, public
meeting attendee lists and transcripts, comments, and other supporting
documents/materials, is available for review at regulations.gov. All
documents in the docket are listed in the regulations.gov index.
However, some documents listed in the index, such as those containing
information that is exempt from public disclosure, may not be publicly
available.
The docket Web page can be found at https://www.regulations.gov/docket?D=EERE-2016-BT-TP-0029. The docket Web page will contain simple
instruction on how to access all documents, including public comments,
in the docket.
FOR FURTHER INFORMATION CONTACT:
Ashley Armstrong, U.S. Department of Energy, Office of Energy
Efficiency and Renewable Energy, Building Technologies Program, EE-2J,
1000 Independence Avenue SW., Washington, DC 20585-0121. Telephone:
(202) 586-6590. Email: [email protected].
Johanna Jochum, U.S. Department of Energy, Office of the General
Counsel, GC-33, 1000 Independence Avenue SW., Washington, DC, 20585-
0121. Telephone: (202) 287-6307. Email: [email protected].
For further information on how to review public comments and the
docket contact the Appliance and Equipment Standards Program staff at
(202) 586-6636 or by email: [email protected].
SUPPLEMENTARY INFORMATION: This final rule incorporates by reference
into part 430 specific sections, figures, and tables in the following
industry standards:
(1) ANSI/AHRI 210/240-2008 with Addenda 1 and 2, (``AHRI 210/240-
2008''): 2008 Standard for Performance Rating of Unitary Air-
Conditioning & Air-Source Heat Pump Equipment, ANSI approved October
27, 2011;
(2) ANSI/AHRI 1230-2010 with Addendum 2, (``AHRI 1230-2010''): 2010
Standard for Performance Rating of Variable Refrigerant Flow (VRF)
Multi-Split Air-Conditioning and Heat Pump Equipment, ANSI approved
August 2, 2010.
Copies of AHRI 210/240-2008 and AHRI 1230-2010 can be obtained from
the Air-Conditioning, Heating, and Refrigeration Institute, 2111 Wilson
Boulevard, Suite 500, Arlington, VA 22201, USA, 703-524-8800, or by
going to http://www.ahrinet.org/site/686/Standards/HVACR-Industry-Standards/Search-Standards.
(3) ANSI/ASHRAE 23.1-2010, (``ASHRAE 23.1-2010''): Methods of
Testing for Rating the Performance of Positive Displacement Refrigerant
Compressors and Condensing Units that Operate at Subcritical
Temperatures of the Refrigerant, ANSI approved January 28, 2010;
(4) ANSI/ASHRAE Standard 37-2009, (``ANSI/ASHRAE 37-2009''),
Methods of Testing for Rating Electrically Driven Unitary Air-
Conditioning and Heat Pump Equipment, ANSI approved June 25, 2009;
(5) ANSI/ASHRAE 41.1-2013, (``ANSI/ASHRAE 41.1-2013''): Standard
Method for Temperature Measurement, ANSI approved January 30, 2013;
(6) ANSI/ASHRAE 41.6-2014, (``ASHRAE 41.6-2014''): Standard Method
for Humidity Measurement, ANSI approved July 3, 2014;
(7) ANSI/ASHRAE 41.9-2011, (``ASHRAE 41.9-2011''): Standard Methods
for Volatile-Refrigerant Mass Flow Measurements Using Calorimeters,
ANSI approved February 3, 2011;
(8) ANSI/ASHRAE 116-2010, (``ASHRAE 116-2010''): Methods of Testing
for Rating Seasonal Efficiency of Unitary Air Conditioners and Heat
Pumps, ANSI approved February 24, 2010;
(9) ANSI/ASHRAE 41.2-1987 (Reaffirmed 1992), (``ASHRAE 41.2-1987
(RA 1992)''): ``Standard Methods for Laboratory Airflow Measurement'',
ANSI approved April 20, 1992.
Copies of ASHRAE 23.1-2010, ANSI/ASHRAE 37-2009, ANSI/ASHRAE 41.1-
2013, ASHRAE 41.6-2014, ASHRAE 41.9-2011, ASHRAE 116-2010, and ASHRAE
41.2-1987 (RA 1992) can be purchased from ASHRAE's Web site at https://www.ashrae.org/resources--publications.
(10) ANSI/AMCA 210-2007, ANSI/ASHRAE 51-2007, (``AMCA 210-2007'')
Laboratory Methods of Testing Fans for Certified Aerodynamic
Performance Rating, ANSI approved August 17, 2007.
Copies of AMCA 210-2007 can be purchased from AMCA's Web site at
http://www.amca.org/store/index.php.
For a further discussion of these standards, see section IV.M.
Table of Contents
I. Authority and Background
A. Authority
B. Background
II. Synopsis of the Final Rule
III. Discussion
A. Testing, Rating, and Compliance of Basic Models of Central
Air Conditioners and Heat Pumps
1. Representation Accommodation
2. Highest Sales Volume Requirement
3. Determination of Represented Values for Multi-Split, Multi-
Circuit, and Multi-Head Mini-Split Systems
4. Service Coil Definition
[[Page 1427]]
5. Efficiency Representations of Split-Systems for Multiple
Refrigerants
6. Representation Limitations for Independent Coil Manufacturers
7. Reporting of Low-Capacity Lockout for Air Conditioners and
Heat Pumps With Two-Capacity Compressors
8. Represented Values of Cooling Capacity
9. New Efficiency Metrics
B. Amendments to Appendix M Testing To Determine Compliance With
the Current Energy Conservation Standards
1. Measurement of Off Mode Power Consumption: Time Delay for
Units With Self-Regulating Crankcase Heaters
2. Refrigerant Pressure Measurement Instructions for Cooling and
Heating Heat Pumps
3. Revised EER and COP Interpolation Method for Units Equipped
With Variable-Speed Compressors
4. Outdoor Air Enthalpy Method Test Requirements
5. Certification of Fan Delay for Coil-Only Units
6. Normalized Gross Indoor Fin Surface Area Requirements for
Split Systems
7. Modification to the Test Procedure for Variable-Speed Heat
Pumps
8. Clarification of the Requirements of Break-In Periods Prior
to Testing
9. Modification to the Part Load Testing Requirement of VRF
Multi-Split Systems
10. Modification to the Test Unit Installation Requirement of
Cased Coil Insulation and Sealing
11. Correction for the Calculation of the Low-Temperature Cut-
Out Factor for Single-Speed Compressor Systems
12. Clarification of the Refrigerant Liquid Line Insulation
C. Amendments to Appendix M1
1. Minimum External Static Pressure Requirements
2. Default Fan Power for Rating Coil-Only Units
3. Revised Heating Load Line Equation
4. Revised Heating Mode Test Procedure for Units Equipped With
Variable-Speed Compressors
D. Effective Dates and Representations
1. Effective Dates
2. Comment Period Length
3. Representations From Appendix M1 Before Compliance Date
E. Comments Regarding the June 2016 Final Rule
1. Determination of Represented Values for Single-Split Systems
2. Alternative Efficiency Determination Methods
3. NGIFS Limit for Outdoor Unit With No Match
4. Definitions
5. Inlet Plenum Setup
6. Off-Mode Power Consumption
IV. Procedural Issues and Regulatory Review
A. Review Under Executive Order 12866
B. Review Under the Regulatory Flexibility Act
C. Review Under the Paperwork Reduction Act of 1995
D. Review Under the National Environmental Policy Act of 1969
E. Review Under Executive Order 13132
F. Review Under Executive Order 12988
G. Review Under the Unfunded Mandates Reform Act of 1995
H. Review Under the Treasury and General Government
Appropriations Act, 1999
I. Review Under Executive Order 12630
J. Review Under Treasury and General Government Appropriations
Act, 2001
K. Review Under Executive Order 13211
L. Review Under Section 32 of the Federal Energy Administration
Act of 1974
M. Description of Materials Incorporated by Reference
N. Congressional Notification
V. Approval of the Office of the Secretary
I. Authority and Background
A. Authority
Title III, Part B \1\ of the Energy Policy and Conservation Act of
1975 (``EPCA'' or ``the Act''), Public Law 94-163 (42 U.S.C. 6291-6309,
as codified) sets forth a variety of provisions designed to improve
energy efficiency and established the Energy Conservation Program for
Consumer Products Other Than Automobiles.\2\ These products include
central air conditioners and central air conditioning heat pumps,\3\
(single-phase \4\ with rated cooling capacities less than 65,000
British thermal units per hour (Btu/h)), which are the focus of this
Final Rule. (42 U.S.C. 6291(1)-(2), (21) and 6292(a)(3))
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\1\ For editorial reasons, Part B was codified as Part A in the
U.S. Code.
\2\ All references to EPCA in this document refer to the statute
as amended through the Energy Efficiency Improvement Act of 2015,
Public Law 114-11 (Apr. 30, 2015).
\3\ This rulemaking uses the term ``CAC/HP'' to refer
specifically to central air conditioners (which include heat pumps)
as defined by EPCA. 42 U.S.C. 6291(21.)
\4\ Where this rulemaking uses the term ``CAC/HP'', they are in
reference specifically to central air conditioners and heat pumps as
defined by EPCA.
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Under EPCA, DOE's energy conservation program generally consists of
four parts: (1) Testing; (2) labeling; (3) Federal energy conservation
standards; and (4) certification, compliance, and enforcement. The
testing requirements consist of test procedures that manufacturers of
covered products must use as the basis of: (1) Certifying to DOE that
their products comply with applicable energy conservation standards
adopted pursuant to EPCA, and (2) making other representations about
the efficiency of those products. (42 U.S.C. 6293(c); 42 U.S.C.
6295(s)) Similarly, DOE must use these test procedures to determine
whether covered products comply with any relevant standards promulgated
under EPCA. (42 U.S.C. 6295(s))
EPCA sets forth criteria and procedures DOE must follow when
prescribing or amending test procedures for covered products. (42
U.S.C. 6293(b)(3)) EPCA provides, in relevant part, that any test
procedures prescribed or amended under this section shall be reasonably
designed to produce test results which measure the energy efficiency,
energy use, or estimated annual operating cost of a covered product
during a representative average use cycle or period of use, and shall
not be unduly burdensome to conduct. Id.
In addition, if DOE determines that a test procedure amendment is
warranted, it must publish proposed test procedures and offer the
public an opportunity to present oral and written comments on them. (42
U.S.C. 6293(b)(2)) Finally, in any rulemaking to amend a test
procedure, DOE must determine to what extent, if any, the amended test
procedure would alter the measured energy efficiency of any covered
product as determined under the existing test procedure. (42 U.S.C.
6293(e)(1))
The Energy Independence and Security Act of 2007 (EISA 2007),
Public Law 110-140, amended EPCA to require that, at least once every 7
years, DOE must review test procedures for all covered products and
either amend the test procedures (if the Secretary determines that
amended test procedures would more accurately or fully comply with the
requirements of 42 U.S.C. 6293(b)(3)) or publish a notice in the
Federal Register of any determination not to amend a test procedure.
(42 U.S.C. 6293(b)(1)(A))
DOE's existing test procedures for CAC/HP adopted pursuant to these
provisions appear under Title 10 of the Code of Federal Regulations
(CFR) part 430, subpart B, appendix M (``Uniform Test Method for
Measuring the Energy Consumption of Central Air Conditioners and Heat
Pumps''). These procedures establish the currently permitted means for
determining energy efficiency and annual energy consumption for CAC/HP.
The procedures established in the new appendix M1 include new
efficiency metrics to represent cooling and heating performance whose
values will be altered as compared to the current metrics. The new
metrics include seasonal energy efficiency ratio 2 (SEER2), energy
efficiency ratio 2 (EER2), and heating seasonal performance factor 2
(HSPF2). Use of the test procedures of appendix M1 will become
mandatory to demonstrate compliance on the compliance date of revised
energy conservation standards.
Section 310 of EISA 2007 established that the Department's test
procedures for all covered products must account for standby mode and
off mode energy consumption. (42 U.S.C. 6295(gg)(2)(A)) For CAC/HP,
standby mode is
[[Page 1428]]
incorporated into the SEER and HSPF metrics, while off mode power
consumption is separately regulated. This final rule includes changes
relevant to the determination of both SEER and HSPF (including standby
mode) and off mode power consumption.
B. Background
DOE initiated a round of test procedure revisions for CAC/HP by
publishing a notice of proposed rulemaking in the Federal Register on
June 2, 2010 (June 2010 NOPR; 75 FR 31223). Subsequently, DOE published
several supplemental notices of proposed rulemaking (SNOPRs) on April
1, 2011 (April 2011 SNOPR; 76 FR 18105), on October 24, 2011 (October
2011 SNOPR: 76 FR 65616), and on November 9, 2015 (November 2015 SNOPR;
80 FR 69277) in response to comments received and to address additional
needs for test procedure revisions. The June 2010 NOPR and the
subsequent SNOPRs addressed a broad range of test procedure issues. On
June 8, 2016, DOE published a test procedure final rule (June 2016
final rule) that finalized test procedure amendments associated with
many but not all of these issues. 81 FR 36991.
On November 5, 2014, DOE published a request for information for
energy conservation standards (ECS) for CAC/HP (November 2014 ECS RFI).
79 FR 65603. In response, several stakeholders provided comments
suggesting that DOE amend the current test procedure. The November 2015
SNOPR addressed those test procedure-related comments, but, as
mentioned in this preamble, not all of the related issues were resolved
in the June 2016 final rule.
On July 14, 2015, DOE published a notice of intent to form a
Working Group to negotiate a NOPR for energy conservation standards for
CAC/HP and requested nominations from parties interested in serving as
members of the Working Group. 80 FR 40938. The Working Group, which
ultimately consisted of 15 members in addition to one member from
Appliance Standards and Rulemaking Federal Advisory Committee (ASRAC)
and one DOE representative, identified a number of issues related to
testing and certification. The term sheet summarizing the Working Group
recommendations included several recommendations associated with test
procedures. (CAC ECS: ASRAC Term Sheet, No. 76) \5\
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\5\ This final rule addresses proposals and comments from two
rulemakings: (1) Stakeholder comments and proposals regarding the
CAC test procedure (CAC TP: Docket No. EERE-2009-BT-TP-0004); and
(2) stakeholder comments and proposals regarding the CAC energy
conservation standard from the Working Group (CAC ECS: Docket No.
EERE-2014-BT-STD-0048). Comments received through documents located
in the test procedure docket are identified by ``CAC TP'' preceding
the comment citation. Comments received through documents located in
the energy conservation standard docket (EERE-2014-BT-STD-0048) are
identified by ``CAC ECS'' preceding the comment citation. Further,
comments specifically received during the CAC/HP ECS Working Group
meetings are identified by ``CAC ECS: ASRAC Public Meeting''
preceding the comment citation.
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On August 24, 2016 DOE published a SNOPR (August 2016 SNOPR)
proposing several amendments to the test procedure and to
certification, compliance, and enforcement provisions, including a
proposal to establish a new appendix M1 to be used for testing under
any new energy conservation standard. 81 FR 58164. That SNOPR addressed
issues not resolved by the June 2016 final rule and also proposed test
procedure amendments to implement several of the items summarized in
the ASRAC Working Group Term Sheet.
II. Synopsis of the Final Rule
In this final rule, DOE revises the certification requirements and
test procedure for CAC/HP based on public comment on various published
materials and the ASRAC negotiation process discussed in section I.B.
This final rule establishes two sets of test procedure changes: One set
of changes to appendix M (effective 30 days after publication of a
final rule and required for testing and determining compliance with
current energy conservation standards); and another set of changes to
create a new appendix M1 that would be used for testing to demonstrate
compliance with any amended energy conservation standards (agreed
compliance date of January 1, 2023, by the Working Group in the CAC
rulemaking negotiations (CAC ECS: ASRAC Term Sheet, No. 76)). With the
exceptions discussed in sections III.B.3 and III.B.7, the changes to
appendix M do not alter measured efficiency. However, the new appendix
M1 establishes new efficiency metrics for cooling and heating
performance, SEER2, EER2, and HSPF2.
In this final rule, DOE makes the following changes to
certification requirements:
(1) Codifying the CAC/HP ECS Working Group's recommendation
regarding delayed implementation of testing to demonstrate compliance
with amended energy conservation standards;
(2) Relaxing the requirement that a split system's tested
combination be a high sales volume combination;
(3) Revising requirements for certification of multi-split systems
in light of the adoption of multiple categories of duct pressure drop
that the indoor units can provide;
(4) Making explicit certain provisions of the service coil
definition;
(5) Revising the certification of separate individual combinations
within the same basic model for each refrigerant that can be used in a
model of split system outdoor unit and certification of details
regarding the indoor units with which unmatched outdoor units are
tested;
(6) Revising representation limitations for independent coil
manufacturers;
(7) Revising the certification of low-capacity lockout for air
conditioner and heat pumps with two capacity compressors;
(8) Revising the requirements for represented values of cooling and
heating capacity; and
(9) Adding new efficiency metrics SEER2, EER2, and HSPF2 to reflect
the changes in the test procedure that result in significant change in
the efficiency metric values.
DOE implements the following changes to appendix M:
(1) Requiring a limit on the internal volume of lines and devices
connected to measure pressure at refrigerant circuit;
(2) Revising the method to calculate EER and coefficient of
performance (COP) for variable-speed units for calculating performance
at intermediate compressor speeds;
(3) Requiring a 30-minute test without the outside-air apparatus
connected (a ``free outdoor air'' test) to be the official test as part
of all cooling and heating mode tests which use the outdoor air
enthalpy method as the secondary measurement;
(4) Relaxing the requirement for secondary capacity checks,
requiring instead use of a secondary capacity measurement that agrees
with the primary capacity measurement to within 6 percent only for the
cooling full load test and, for heat pumps, for the heating full load
test;
(5) Revising the certification of the indoor fan off delay used for
coil-only tests;
(6) Modifying the test procedure for variable-speed heat pumps; and
(7) Modifying the part load testing requirement of VRF multi-split
systems and test unit installation requirement of cased coil insulation
and sealing.
DOE adopts the following provisions for new appendix M1:
[[Page 1429]]
(1) New higher external static pressure requirements for all units,
including unique minimum external static pressure requirements for
mobile home systems, ceiling-mount and wall-mount systems, low- and
mid-static multi-split systems, space-constrained systems, and small-
duct, high-velocity systems;
(2) A unique default fan power for rating mobile home coil-only
units and new default fan power for all other coil-only units;
(3) Revisions to the heating load line equation in the calculation
of the heating mode efficiency metric, HSPF2;
(4) Amendments to the test procedures for variable-speed heat pumps
that change speed at lower ambient temperatures and add a
5[emsp14][deg]F heating mode test option for calculating full-speed
performance below 17[emsp14][deg]F; and
(5) Establishment of a 4-hour or 8-hour delay time before the power
measurement for units that require the crankcase heating system to
reach thermal equilibrium after setting test conditions.
The test procedure amendments to appendix M for subpart B to 10 CFR
part 430 established in this final rule pertaining to the efficiency of
CAC/HP will be effective 30 days after publication in the Federal
Register (referred to as the ``effective date''). Pursuant to EPCA,
manufacturers of covered products are required to use the applicable
test procedure as the basis for determining that their products comply
with the applicable energy conservation standards. (42 U.S.C. 6295(s))
180 days after publication of a final rule, any representations made
with respect to the energy use or efficiency of CAC/HPs are required to
be made in accordance with the results of testing pursuant to the
amended test procedures. (42 U.S.C. 6293(c)(2))
The test procedures established in this final rule for appendix M1
to subpart B of 10 CFR part 430 pertaining to the efficiency of CAC/HP
are effective 30 days after publication in the Federal Register. The
appendix M1 procedures will be required as the basis for determining
that CAC/HP comply with any amended energy conservation standards (if
adopted in the concurrent CAC/HP energy conservation standards
rulemaking) and for representing efficiency as of the compliance date
for those amended energy conservation standards.
DOE revises the test procedure and requirements for certification,
compliance, and enforcement in this final rule effective on February 6,
2017. The amended test procedure of appendix M is mandatory for
representations of efficiency as of July 5, 2017. The new test
procedure of appendix M1 is mandatory for representations of efficiency
as of January 1, 2023.
III. Discussion
This section discusses the revisions to the certification
requirements and test procedure that DOE adopts in this final rule.
A. Testing, Rating, and Compliance of Basic Models of Central Air
Conditioners and Heat Pumps
1. Representation Accommodation
In the August 2016 SNOPR, DOE proposed to implement the following
recommendations from the CAC/HP ECS Working Group regarding
representations for split systems in 10 CFR 429.16 and 429.70:
[cir] DOE will implement the following accommodation for
representative values of split system air conditioners and heat pumps
based on the M1 methodology:
[cir] By January 1, 2023, manufacturers of single-split systems
must validate an AEDM that is representative of the amended M1 test
procedure by:
[ssquf] Testing a single-unit sample for 20-percent of the basic
models certified.
[ssquf] The predicted performance as simulated by the AEDM must be
within 5 percent of the performance resulting from the test of each of
the models.
[ssquf] Although DOE will not require that a full complement of
testing be completed by January 1, 2023, manufacturers are responsible
for ensuring their representations are appropriate and that the models
being distributed in commerce meet the applicable standards (without a
5% tolerance).
[cir] By January 1, 2023, manufacturers must either determine
representative values for each combination of single-split-system CAC/
HP based on the M1 test procedures using a validated AEDM or through
testing and the applicable sampling plan.
[cir] By January 1, 2023, manufacturers of multi-split, multi-
circuit, or multi-head mini-split systems must determine representative
values for each basic model through testing and the applicable sampling
plan.
[cir] By July 1, 2024, each model of condensing unit of split
system CAC/HP must have at least 1 combination whose rating is based on
testing using the M1 test procedure and the applicable sampling plan.
81 FR at 58167 (Aug. 24, 2016)
Lennox and AHRI commented that they supported DOE's proposal,
although AHRI noted it supported DOE's proposal with certain
exceptions. (Lennox, No. 25 at p. 2; AHRI, No. 27 at p. 1) While AHRI
did not note the exceptions, DOE assumes these may be related to their
comments regarding test requirements for two-stage air conditioners (Id
at p. 2), effective dates for appendix M in the June 2016 Final Rule
and this final rule (Id at p. 8), and AEDM options for multi-split
systems (Id at p. 20). These issues are discussed separately in III.D
and III.E. As these exceptions are tangential to the original proposal,
DOE has adopted the accommodations as proposed.
2. Highest Sales Volume Requirement
In the August 2016 SNOPR, based on recommendations by the CAC/HP
ECS Working Group, DOE proposed removing the requirement for single-
split-system air conditioners that the individual combination required
for testing be the highest sales volume combination (HSVC).
Specifically, DOE proposed that for every basic model, a manufacturer
must test the model of outdoor unit with a model of indoor unit.\6\ 81
FR at 58202 (Aug. 24, 2016)
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\6\ As adopted in the June 2016 Final Rule, for single-split-
system air conditioners with single-stage or two-stage compressors,
the model of indoor unit must be coil-only.
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ACEEE, NRDC, ASAP, and NEEA supported DOE's proposal to adopt the
CAC/HP ECS Working Group recommendations regarding removing the HSVC,
as described in the SNOPR. (ACEEE, NRDC, and ASAP, No. 33 at p. 8;
NEEA, No. 35 at p. 1) DOE received no other comment on this issue.
Therefore, DOE adopts this proposal in this final rule. DOE notes that
some stakeholders commented on related items that were finalized in the
June 2016 Final Rule. These are discussed in section III.E.1.
3. Determination of Represented Values for Multi-Split, Multi-Circuit,
and Multi-Head Mini-Split Systems
In the August 2016 SNOPR, DOE proposed that multi-split, multi-head
mini-split, and multi-circuit systems could be tested and rated with
five kinds of indoor units: Non-ducted, low-static ducted, mid-static
ducted, conventional ducted, or small-duct, high velocity (SDHV). DOE
proposed that when determining represented values (including certifying
compliance with amended energy conservation standards), at a minimum, a
manufacturer must test and rate a ``tested combination'' composed
entirely of non-ducted units. Under the proposed rule, if a
manufacturer were to offer the model of outdoor unit with
[[Page 1430]]
models of low-static, mid-static, and/or conventional ducted indoor
units, the manufacturer would be required, at a minimum, also to test
and rate a second ``tested combination'' with the highest static
variety of indoor unit offered. The manufacturer would also be allowed
to choose to test and rate additional ``tested combinations'' composed
of the lower static varieties. In each case, the manufacturer would
test with the appropriate external static pressure. DOE did not propose
use of AEDMs for these systems. 81 FR at 58169 (Aug. 24, 2016)
DOE also proposed to maintain its requirement from the June 2016
final rule that, if a manufacturer also sells a model of outdoor unit
with SDHV indoor units, the manufacturer must test and rate the SDHV
system (i.e., test a combination with indoor units that all have SDHV
pressure capability). DOE also proposed to continue to allow mix-match
ratings across any two of the five varieties by taking a straight
average of the ratings of the individual varieties, and to allow
ratings of individual combinations through testing. 81 FR at 58169
(Aug. 24, 2016)
NEEA commented that they supported DOE's proposals regarding
certification of multi-split, multi-circuit, and multi-head mini-split
systems. (NEEA, No. 35 at p. 1-2) Lennox and Nortek commented that they
supported DOE's proposals regarding tested combinations for multi-
split, multi-head mini-split, and multi-circuit systems. (Lennox, No.
25 at p. 3-4; Nortek, No. 22 at p. 3) AHRI commented that they
supported DOE's proposals regarding tested combinations for multi-split
and multi-circuit systems. (AHRI, No. 27 at p. 2)
AHRI and Mitsubishi commented that they were concerned with DOE's
proposal to add low-static and mid-static testing requirements to
appendix M. They commented that the ``low-static'' and ``mid-static''
terminology and the associated testing requirements were negotiated for
appendix M1, and implementing this requirement before the effective
date of the 2023 standard would not be in alignment with the Working
Group's recommendation. (AHRI, No. 27 at p. 2-3; Mitsubishi, No. 29 at
p. 2)
DOE notes that it intended the low-static and mid-static
requirements to apply to appendix M1 only. In the August 2016 SNOPR, 10
CFR 429.16(a)(1) and (b)(2)(i) included tables regarding determining
represented values and minimum testing requirements. In both of these
tables, DOE only discussed the static variety in regards to testing in
accordance with M1 or making representations on and after January 1,
2023. In addition, the definitions for the static varieties are only
found in appendix M1. However, DOE acknowledges that 10 CFR
429.16(c)(3) may have included unclear language on this topic. DOE has
modified this language in this final rule.
AHRI and Mitsubishi commented that multi-head mini-split systems do
not belong in the requirements for multi-split and multi-circuit
systems because they operate as 1-to-1 combinations, and it is not
possible to turn off one indoor unit for testing. In addition, they
stated that these systems do not have multiple-ducted and non-ducted
combinations. AHRI and Mitsubishi requested that DOE remove multi-head
mini-split systems from non-applicable testing requirements and other
sections and instead include multi-head mini-split in the same line as
``Single-Split-System'' in the table in 10 CFR 429.16(b)(2). (AHRI, No.
27 at p. 2; Mitsubishi, No. 29 at p. 1-2; Mitsubishi, Public Meeting
Transcript, No. 20 at p. 113-114)
In response, DOE notes that, though the August 2016 SNOPR proposed
additional requirements regarding tested combinations, the
certification and testing requirements for multi-head mini-split
systems became associated with the testing requirements for multi-split
and multi-circuit systems in the June 2016 final rule, and were not
proposed in the August 2016 SNOPR. The only related change proposed in
the August 2016 SNOPR pertains to requirements for different static
varieties. Furthermore, although multi-head mini-split systems are
grouped with multi-split and multi-circuit systems in the certification
requirements, appendix M and M1 do not require this equipment to turn
off any indoor units during testing. In addition, DOE does not believe,
based on the information provided by AHRI and Mitsubishi, that the
proposed language in 10 CFR 429.16 presents a problem for multi-head
mini-split systems. The certification and testing requirements allow
only non-ducted representations if that is all that is sold, or
representations of only one kind of ducted combination, if that is all
that is sold. The fact that multi-head mini-split systems are sold in
few combinations should not preclude manufacturers from meeting these
requirements. For these reasons, DOE is not removing multi-head mini-
splits from its grouping with multi-split and multi-circuit systems in
10 CFR 429.16.
DOE received no other comment on the proposals in the August 2016
SNOPR for determining represented values for multi-split, multi-
circuit, and multi-head mini-split systems and DOE adopts all of the
proposed requirements in this final rule. DOE also notes that in the
August 2016 SNOPR, DOE omitted mention in 10 CFR 429.16(a)(1) that non-
SDHV multi-split, multi-circuit, and multi-head mini-split systems may
also include space-constrained units, so DOE has clarified that in this
final rule.
4. Service Coil Definition
In the June 2016 final rule, to distinguish newly installed cased
and uncased coils from replacement cased and uncased coils, DOE added a
definition for service coils and explicitly excluded them from indoor
units in the indoor unit definition.
In the August 2016 SNOPR, DOE proposed to modify the adopted
definition of service coil to more explicitly define what ``labeled
accordingly'' meant. Specifically, DOE proposed that a manufacturer
must designate a service coil as ``for indoor coil replacement only''
on the nameplate and in manufacturer product and technical literature.
In addition, DOE proposed that the model number for any service coil
must include some mechanism (e.g., an additional letter or number) for
differentiating a service coil from a coil intended for an indoor unit.
81 FR at 58169-58170 (Aug. 24, 2016)
AHRI, Nortek, and Ingersoll Rand commented that they support DOE's
proposal. (AHRI, No. 27 at p. 3, Nortek, No. 22 at p. 3, Ingersoll
Rand, No. 38 at p. 2) DOE received no other comments on this issue.
Therefore, DOE is adopting this proposal in this final rule.
5. Efficiency Representations of Split-Systems for Multiple
Refrigerants
DOE made numerous proposals in the August 2016 SNOPR regarding
efficiency representations for multiple refrigerants, and they elicited
voluminous and multi-faceted responses. The proposals themselves can be
divided into three broad categories, including (1) representations for
multiple refrigerants, (2) certification report requirements for
outdoor units with no match, and (3) clarifying what outdoor units must
have no-match efficiency representations. By far most of the responses
addressed the third category--discussion thereof has been divided up
into the following sub-topics: DOE authority, altering the measured
efficiency, specific no-match criteria, and normalized gross indoor fin
surface (NGIFS) (addressed in sections III.A.5.c through III.A.5.f).
[[Page 1431]]
a. Representations for Multiple Refrigerants
In the August 2016 SNOPR, to address instances in which the
manufacturer indicates that more than one refrigerant is acceptable for
use in a unit, DOE proposed that a split-system air conditioner or heat
pump, including an outdoor unit with no match, must be certified as a
separate individual combination for every acceptable refrigerant.
Specifically, each individual combination would be certified under the
same basic model. DOE's existing requirements for basic models would
continue to apply; therefore, if an individual combination or an
outdoor unit with no match fails to meet DOE's energy conservation
standards using any refrigerant indicated by the manufacturer to be
acceptable, then the entire basic model would fail. DOE also proposed
that manufacturers must certify the refrigerants for every individual
combination that is distributed in commerce. For models where the
manufacturer only indicates one acceptable refrigerant, this proposal
would simply entail certifying to DOE the refrigerant for which the
model is designed. Finally, DOE proposed that any outdoor unit model
that has certain characteristics (e.g., if it is distributed in
commerce without a specific refrigerant), a manufacturer must determine
the represented value as an outdoor unit with no match. For some
outdoor units, the proposal called for representations both as an
outdoor unit with no match and as part of a combination, both as part
of the same basic model. 81 FR at 58170 (Aug. 24, 2016).
The August 2016 SNOPR proposed that a refrigerant's acceptability
for use in an outdoor unit would be based on its being covered under
the unit's warranty, either explicitly or based on refrigerant
characteristics. Id. at 58201.
AHRI, Nortek, Ingersoll Rand, and Carrier/UTC supported DOE's
proposal that manufacturers should be required to certify efficiency
ratings for all refrigerants that they have designed their equipment to
use. (AHRI, No. 27 at p. 3; Nortek, No. 22 at p. 3; Ingersoll Rand, No.
38 at p. 2; Carrier/UTC, No. 36 at p. 3) AHRI, Nortek, and JCI
suggested that DOE revise the requirement so that, if a manufacturer
approves an air conditioner or heat pump for multiple refrigerants by
listing them on the nameplate, such a product is subject to DOE
certification and enforcement requirements for each approved
refrigerant. AHRI, Nortek, and JCI commented that manufacturers should
have the option to rate all compatible refrigerants as one basic model
with the same efficiency rating, or to list different efficiencies for
different refrigerants as separate basic models. AHRI, Nortek, and JCI
contend that the determination of different efficiency ratings for
different refrigerants should be allowed based on testing, or the
appropriate use of AEDMs. (AHRI, No. 27 at p. 6; Nortek, No. 22 at p.
6; JCI, No. 24 at p. 9) Ingersoll Rand commented similarly. (Ingersoll
Rand, No. 38 at p. 2)
ACEEE, NRDC, and ASAP commented that they support the proposed
requirement to assign separate model numbers to systems designed for
more than one refrigerant. (ACEEE, NRDC, and ASAP, No. 33 at p. 4;
Lennox, No. 25 at p. 5)
Goodman commented that they agreed with DOE's proposal in
principle, but were concerned that clarification regarding the
refrigerants that are approved for use in a product may not always be
clear, and that a refrigerant may be used in the field if information
about approved refrigerants is weak or not readily identifiable.
Goodman proposed regulatory text to address this issue, emphasizing
reliance on a product's nameplate to indicate which refrigerants are
approved. Specifically, the suggestion was that any refrigerant listed
on the unit nameplate of any portion of the basic model be considered
to be approved. Further, Goodman's suggestion also includes as
``approved for use'' those non-zero ozone-depleting refrigerants with
similar thermophysical properties to a refrigerant listed on the
nameplate, (Goodman, No. 39, p. 2-3)
In response to these comments DOE has revised the requirements so
that indication of which refrigerants require certification of
performance is based on the unit nameplate that is required by safety
standards (e.g., UL 1995) to list all approved refrigerants (see newly
designated paragraph (a)(3) of section 10 CFR 429.16).
DOE does not understand Goodman's reference to ``any portion of the
basic model''. If an individual combination of a basic model includes
an indoor unit whose nameplate lists a refrigerant that is not listed
on the outdoor unit's nameplate, such listing on the indoor unit's
nameplate would not make the refrigerant approved for use in the
outdoor unit. The refrigerant would therefore not be approved for use
with that individual combination and presumably would not be required
for certification with the basic model. Hence, if listing on the unit's
nameplate is a sufficiently strong indication of which refrigerants are
approved for use, it is not clear that any refrigerant listed on the
indoor unit's nameplate but not on the outdoor unit's nameplate should
be considered approved for use with the outdoor unit. Consequently, DOE
has not included the ``any portion of the basic model'' language in its
requirements. DOE has not adopted this language due to manufacturers'
representations that the refrigerant listings on the nameplate are
respected sufficiently that installers would not use a refrigerant in a
system if it is not listed on the outdoor unit's nameplate.
DOE also is not convinced that the ``approved refrigerants'' need
to include any non-zero ozone depletion potential refrigerant that has
similar thermophysical properties to a refrigerant approved for use on
the unit nameplate. DOE is only aware of HCFC-22 as a non-zero ozone
depletion refrigerant that is used for split system air conditioners--
no such alternatives are approved in the EPA SNAP list for residential
and light commercial air conditioning and heat pumps.\7\ HCFC-22 and
refrigerants with properties similar to HCFC-22, whether non-zero ozone
depletion or not, are addressed separately in the no-match requirements
(see section III.A.5.e).
---------------------------------------------------------------------------
\7\ https://www.epa.gov/snap/acceptable-substitutes-residential-and-light-commercial-air-conditioning-and-heat-pumps.
---------------------------------------------------------------------------
Additionally, in the August 2016 SNOPR, DOE did not intend to
require testing of each refrigerant. In this final rule, DOE is
clarifying the requirement to allow the manufacturer to test the unit
with one refrigerant and to use an AEDM for other refrigerants. This
clarification appears in paragraph (a)(3) of Sec. 429.16, but DOE has
also modified paragraph (c)(2) of this section to emphasize this
clarification for outdoor units with no match. Additionally, in this
final rule, DOE is adding a provision in paragraph (a)(3) of Sec.
429.16 to allow grouping of refrigerants in reporting provided that the
representative values represent the least efficient refrigerant. In
response to ACEEE, NRDC, and ASAP, DOE does not believe the additional
reporting burden of requiring that each refrigerant have its own model
number and efficiency representation is justified if the rating
represents the least efficient refrigerant. In response to AHRI and
Nortek, DOE is requiring that all of the refrigerants for the given
model of outdoor unit be part of the same basic model. This is
consistent with the basic model definition adopted in the June 2016
final rule, which groups all combinations with a given model of
[[Page 1432]]
outdoor unit into the same basic model. 81 FR at 37053 (June 8, 2016).
b. Certification Report Requirements for Outdoor Units With no Match
DOE proposed to require reporting of additional non-public
information for the indoor unit that is tested with an outdoor unit
with no match. This would include the indoor coil face area, depth in
the direction of airflow, fin density (fins per inch), fin material,
fin style (e.g., wavy or louvered), tube diameter, tube material, and
numbers of tubes high and deep. These additional requirements would
apply to outdoor units with no match, whether or not the outdoor unit
was also certified as part of an individual combination. 81 FR at 58172
(Aug. 24, 2016).
Unico, Goodman, ACEEE, NRDC, and ASAP supported DOE in requiring
that specific indoor coil descriptions be specified for outdoor units
with no match. (Unico, Inc., No. 30 at p. 2; Goodman, No. 39 at p. 5;
ACEEE, NRDC, and ASAP, No. 33 at p. 4)
AHRI generally did not support DOE's proposals for outdoor units
with no match, but noted that the following fin styles are available as
options in the AHRI Directory: Flat corrugated, high performance,
lanced, louvered, and N/A. (AHRI, No. 27 at p. 7) Rheem commented that
the proposed list of indoor unit details are insufficient as a measure
of indoor coil performance. Rheem opposed reporting of additional non-
public information for the indoor unit that is tested with an outdoor
unit with no match. (Rheem, No. 37 at p. 2) Nortek similarly commented
that DOE's attempt to have manufacturers describe a fin style and tube
diameter is obsolete and that with the varying materials and
technologies in the market, the burden of characterizing fins as
``lanced, flat, corrugated'', etc. is of no value. (Nortek, No. 22 at
p. 7)
In response to the comments from AHRI, DOE will include options
noted by AHRI for fin style in the certification template. In response
to the comments from Rheem and Nortek, DOE notes that the reporting of
information on the indoor unit is necessary for DOE's assessment and
enforcement testing. DOE notes that, although Rheem indicated that the
listed information is insufficient, they provided no recommendations
regarding alternative ways that DOE can verify performance claimed for
outdoor units with no match. Therefore, DOE adopts this requirement in
this final rule.
c. DOE Authority
Per DOE's regulations in Appendix M established in the June 2016
final rule, the model of outdoor unit must be tested with an indoor
unit meeting specified criteria. 81 FR at 37051 (June 8, 2016). 81 FR
at 58171 (Aug. 24, 2016). Under the certification requirements proposed
in the August 2016 SNOPR, DOE expanded the scope of outdoor units that
would be required to be tested as outdoor units with no match. The
specific criteria proposed to require such a rating are discussed in
greater detail in section III.A.5.e, but they include having no
designated refrigerant, a warranty that specifies refrigerant
properties similar to those of HCFC-22 to define refrigerant
acceptability (rather than or in addition to specific refrigerants),
shipping without refrigerant or with a charge that requires addition of
more than a pound of charge during setup, and shipping with any amount
of R-407C. As proposed, any such unit would need to be certified as an
outdoor unit with no match.
Multiple stakeholders commented on various aspects of DOE's
authority to establish such requirements.
AHRI and Nortek commented that DOE has authority over
manufacturers, but that DOE cannot expand that authority to make the
manufacturer selling a legal product liable for the conduct of a
distributor, contractor or individual consumer. They emphasized that an
objective standard that could be the basis of DOE's certification and
enforcement requirements will capture the conduct through which the
manufacturer is distributing in commerce and marketing the equipment.
(AHRI, No. 27 at p. 4; Nortek, No. 22 at p. 3-4)
DOE agrees that DOE has authority over manufacturers but notes that
EPCA defines manufacture as ``to manufacture, produce, assemble, or
import.'' (42 U.S.C. 6291(10))
AHRI and Nortek commented that the test requirements for outdoor
units with no match represent design requirements and that DOE does not
have authority to impose design requirements for central air
conditioners. They noted that EPCA clearly states for some products
that a standard may be a design requirement or a performance standard,
but not both, and that EPCA does not even give DOE the option of
considering design requirements for central air conditioners. AHRI and
Nortek commented that when the use of a component with specific design
requirements is mandated by the test procedure, it is in fact a design
requirement for the product, since that test procedure must be used to
determine the product's efficiency. (AHRI, No. 27 at p. 4-5; Nortek,
No. 22 at p. 4)
In response, DOE does not agree that the test procedure imposes a
design requirement as DOE does not impose any design restrictions on
the outdoor unit. However, DOE must establish test procedures that are
reasonably designed to measure energy efficiency during a
representative average use cycle as determined by DOE (42 U.S.C. 6293
(b)(3)), which is why the indoor unit characteristics are specified.
This requirement is analogous to the requirement to use higher external
static pressure (ESP) when testing an SDHV system. DOE also notes that
its delineation of outdoor units with no match is for units that are
predominantly used to replace failed HCFC-22 outdoor units. As such,
DOE has developed a straightforward approach to defining the
characteristics of an indoor unit which is representative of such
applications in order to allow the test procedure for these units to be
representative of field installation. The extension of this concept to
additional categories of outdoor units with no match (other than those
designed for HCFC-22) does not invalidate this premise. For example,
DOE has no evidence that outdoor units designed for use with R-407C are
installed to a significant extent with new indoor units. Further
discussion regarding the specific criteria to identify outdoor units
with no match is in section III.A.5.e.
AHRI and Nortek commented that DOE's proposal for outdoor units
with no match would be an expansion into technical and policy issues
that are outside of DOE's authority under EPCA, were not within
Congress' intent in granting DOE authority over energy efficiency
standards, and are the jurisdiction of the EPA. They assert that the
proposed approach would effectively ban the sale of otherwise legal
products by requiring the very restrictive no match testing. (AHRI, No.
27 at p. 5; Nortek, No. 22 at p. 4-5) Similarly, JCI commented that
DOE's R-407C proposal effectively bans the use of R-407C in split-
system CACs and HPs by proposing to burden R-407C units with more
stringent testing requirements than units designed for use with any
other EPA-SNAP approved refrigerant, requiring testing with an
inefficient indoor unit, and thus requiring outdoor unit efficiency
that is either technically impossible or economically inviable to meet.
JCI commented that this refrigerant-specific test procedure requirement
constitutes back-door regulation of R-407C by DOE even though R-407C is
already subject to
[[Page 1433]]
direct regulation by EPA under the Clean Air Act, and EPA has permitted
the use of R-407C in split system CAC/HPs. In proposing to manipulate
the CAC/HP test procedure in a way that would eliminate the use of R-
407C in split-system CAC/HPs, JCI stated that DOE is acting beyond its
legal authority under EPCA. (JCI, No. 24 at p. 3-4)
Ingersoll Rand agrees with AHRI's position that these proposed
requirements exceed DOE's statutory authority. (Ingersoll Rand, No. 38
at p. 3)
On the other hand, ACEEE, NRDC, and ASAP commented that DOE
regulates energy efficiency and has a legal obligation to ensure that
manufacturers comply with its standards. According to ACEEE, NRDC, and
ASAP, the August 2016 test procedure SNOPR does precisely that by
ensuring that units intended as replacement units have to meet the same
rules regardless of the refrigerant they are designed to use. ACEEE,
NRDC, and ASAP commented that in the SNOPR, DOE clearly set out to
close a loophole in its own regulations that, if left unaddressed,
would result in the sale of units that do not meet existing standards,
resulting in higher energy consumption. ACEEE, NRDC, and ASAP commented
that closing that loophole is the purpose of DOE's ``no-match''
requirements for certifying these units. ACEEE, NRDC, and ASAP further
commented that DOE is not banning the sale of R-407C units and that
selling outdoor unit replacements using R-407C is and will continue to
be perfectly legal--in fact, manufacturers may produce and sell outdoor
units with no match using any refrigerant they want, including R-22 and
R-407C. They commented that these units will need to meet the
efficiency of DOE's existing minimum standards, rather than skate by
with a certified value not achieved in the real world. They expressed
the view that DOE's SNOPR effectively addresses the efficiency
performance of products on the market today. (ACEEE, NRDC, and ASAP,
No. 33 at p. 11) ACEEE, NRDC, and ASAP also indicated that some
products, including the R-407C products introduced to the market in
2016, can only meet the existing standards by pairing the outdoor unit
with an oversized indoor unit, even though the units are sold as
replacements for outdoor units in which the existing indoor unit is not
replaced. They further stated that other combinations in which the
outdoor and indoor units are mismatched are unlikely to be sold in
these combinations in any significant quantity. (ACEEE, NRDC, and ASAP,
No. 33 at p. 4) Lennox also commented that ``a manufacturer'' rated an
outdoor unit for R-407C by matching the outdoor unit with an unusually
large indoor coil and sold it with one pound of refrigerant charge as a
replacement for HCFC-22 units. (Lennox, No. 25 at p. 4)
Contrary to the comments of AHRI, JCI, Nortek, and Ingersoll Rand,
EPCA requires DOE to establish appropriate test procedures with which
to measure product efficiency for a representative average use cycle.
(42 U.S.C. 6293(b)(3)) DOE's proposals regarding outdoor units with no
match are based on efficiency considerations and supported by DOE's
authority granted by EPCA to regulate product efficiency and to
establish appropriate test procedures with which to measure product
efficiency. JCI commented that when consumers are offered the option to
use R-407C, as opposed to HCFC-22, they take advantage of it, citing
that sales of R-407C are rising proportionately with JCI's sales of R-
407C units, and pointing out that they are giving customers the
opportunity to avoid HCFC-22 refrigerant without entirely replacing
their CAC/HP systems. (JCI, No. 24 at p. 7) These statements support
DOE's expectation that the sales of these R-407C units are primarily,
if not entirely, for no-match installations in which the indoor unit is
not replaced. Although JCI claims that DOE cannot extend its arguments
made for HCFC-22 outdoor units (i.e., that they are clearly no-match
installations because there is no valid EPA-approved combination that
includes an HCFC-22 outdoor unit (JCI, No. 24 at p. 5)), DOE asserts
that the possibility that there are or could be a few valid R-407C
combinations sold does not in itself make sales of combinations (rather
than no-match sales) the representative efficiency value for R-407C.
JCI also claimed that DOE has no authority to regulate outdoor
units with no match because they are not a central air conditioner or a
heat pump as defined by EPCA. (JCI, No. 24 at p. 4) DOE notes that in
the June 2016 Final Rule, DOE reasonably interpreted the statutory
definition to specify the following: ``A central air conditioner or
central air conditioning heat pump may consist of: a single-package
unit; an outdoor unit and one or more indoor units; an indoor unit
only; or an outdoor unit with no match. In the case of an indoor unit
only or an outdoor unit with no match, the unit must be tested and
rated as a system (combination of both an indoor and an outdoor
unit).'' 81 FR at 37056 (June 8, 2016). In that rule, DOE noted that
this interpretation did not change the scope of DOE's product coverage
and is in line with the current certification requirements for CAC/HP.
81 FR at 36999.
d. Altering the Measured Efficiency
In the August 2016 public meeting, JCI commented that they offer a
matched combination with R-407C, and that the tested combination is
available in the AHRI database. JCI noted that the product has been
available since spring 2016, and it is too early to say that there is
no tested combination of this product. JCI also questioned how long
after introduction of an outdoor unit product an assessment can be made
whether there is or is not a highest sales volume combination. (JCI,
Public Meeting Transcript, No. 20 at pp. 124-132) In written comments,
JCI cited EPCA requirements that when amending test procedures, DOE
must consider to what extent the amendments alter the measured
efficiency of covered products, and then amend the applicable energy
conservation standards if a determination is made that the test
procedure amendment alters the measurement. (42 U.S.C. 6293(e)(1-2))
JCI commented that DOE has not done this for its amendments associated
with no-match R-407C products. JCI explained that the no-match
proposals would force manufacturers to re-test previously certified
compliant products using a new testing standard that is technically
impossible to meet, which would render the previously-compliant R-407C
systems non-compliant. (JCI, No. 24 at p. 6)
This test procedure provides a mechanism of assessing the
performance of no-match products, such as those that use R-407C, which
can then be used to provide a reasonable level of assurance that all
field-match combinations of the new, unmatched outdoor units will
achieve the established efficiency levels. The current test procedure
requires that single-stage split system air conditioners be tested
using the highest sales volume tested combination. 10 CFR 429.16. It is
DOE's understanding that condensing units utilizing R407C typically do
not have a highest sales volume indoor unit that satisfy the
requirements of the test procedure and thus, could not be tested under
the current regulatory regime. Further, if the condensing units were to
have a highest sales volume indoor unit for testing, DOE believes the
results of such testing would overstate the performance of R407C
systems as installed. DOE believes this is the case because R407C
systems typically get installed with existing indoor units, which are
not properly sized, in order
[[Page 1434]]
to achieve the system efficiency that would result from a new matched
pair system. Thus, DOE believes that manufacturers of R407C condensing
units should have sought a waiver for the current test procedure
requirements pursuant to the procedures at 10 CFR 430.27. EPCA requires
DOE to adopt test procedures that are reasonably designed to produce
test results which measure energy efficiency of a covered product
during a representative average use cycle or period of use. (42 U.S.C.
6293(b)(3)) To meet this requirement for outdoor units with no match,
DOE is now adopting an alternative approach similar to the proposal
with modification for testing and determining represented values for
no-match R407C products based on stakeholder comments. DOE notes that
under the approach adopted in this final rule, the testing method for
no-match systems does not consider HSVC. In this rulemaking, the only
proposal regarding HSVC was to remove the requirement for single-split
system air conditioners, which DOE adopts as discussed in section
III.A.2. The application of HSVC to current applicable regulations is
not within the scope of this rulemaking. Therefore, DOE will not
address its application in this rule.
JCI also questioned whether DOE performed any analysis on how the
new requirements for units with R-407C refrigerant impact consumers.
(JCI, Public Meeting Transcript, No. 20 at pp. 137-139)
In response, DOE does not evaluate impacts on consumers for test
procedure amendments. The test procedure amendments are developed to
provide efficiency representations for representative average use
cycles. (42 U.S.C. 6293(a)(3)) As discussed in section III.A.5.d, DOE
developed the test approach for outdoor units with no match on this
basis. Thus, the energy conservation standard rulemaking's
consideration of consumer impacts accounts for the impacts that might
be associated with specific test procedure changes.
e. Specific No-Match Criteria
DOE proposed in the August 2016 SNOPR that manufacturers must
determine efficiency representations for outdoor units as outdoor units
with no match if they meet any of the following criteria: Having no
designated refrigerant, a warranty that specifies refrigerant
properties similar to those of HCFC-22 to define refrigerant
acceptability (rather than or in addition to specific refrigerants),
shipping without refrigerant or with a charge that requires addition of
more than a pound of charge during setup, and shipping with any amount
of R-407C. 81 FR at 58170-58172 (Aug. 24, 2016).
JCI and Goodman commented that there are other refrigerants,
including MO-99 and NU-22, that are used as replacements for HCFC-22.
JCI questioned why those refrigerants were not specifically called out
in the proposed test procedure as R-407C was, while Goodman indicated
that the proposal would do nothing to address these other HCFC-22
replacement refrigerants. (JCI, Public Meeting Transcript, No. 20 at p.
140; Goodman, No. 39 at p. 3)
JCI also stated that they have competitors that have published
guidelines around the application of R-410A units into existing indoor
applications, and questioned why those units would not have to be held
to the same test approach for outdoor units with no match.
In response, it has always been the case that some outdoor units
are installed as replacements for failed outdoor units. However, in
most cases an outdoor unit model would also be sold in substantial
numbers as a combination with indoor units. This is in contrast to R-
407C units, which are predominantly sold in scenarios in which the
outdoor unit is replaced, and the indoor unit is not replaced. Hence
the test procedure is representative of an average use cycle for R-410A
units without requiring that it be tested as a unit with no match.
JCI also commented that the benefits of R-407C will increase over
time if products designed for this refrigerant based on ``additional
valid matches'' are allowed to be sold, but that the proposed
requirements would significantly limit any such possibility. JCI
asserted that it can create a larger market for complete R-407C systems
and that DOE should not limit the potential for such innovation. (JCI,
No. 24 at p. 7)
ACEEE, NRDC, and ASAP and Lennox supported the proposed requirement
that an outdoor unit distributed without a designated refrigerant must
be tested and certified as an outdoor unit with no match. (ACEEE, NRDC,
and ASAP, No. 33 at p. 4; Lennox, No. 25 at p. 5)
AHRI and Nortek commented that DOE's categorization of dry-ship
units is overly-broad and does not necessarily equate to outdoor units
with no match. AHRI and Nortek commented that units with long line sets
require more than one pound of charge to be added in the field. AHRI
and Nortek contended that it is also very realistic that manufacturers
will not be able to ship units with mildly flammable refrigerants
factory charged which will require adding refrigerants in the field
during installation. (AHRI, No. 27 at p. 6; Nortek, No. 22 at p. 6)
JCI, Ingersoll Rand, Goodman, Carrier/UTC also disagreed with DOE's
proposal for similar reasons. Ingersoll Rand, Goodman, and Carrier/UTC
gave examples of situations in which the entire charge required for a
system could not be contained within the outdoor unit by itself as
shipped from the factory, and would require more than a pound of
refrigerant to be added, including for MicroChannel Heat Exchangers and
long line sets. (JCI, No. 24 at p. 7-8; Ingersoll Rand, No. 38 at p. 2;
Goodman, No. 39 at p. 3-4; Carrier/UTC, No. 36 at p. 3; JCI and
Ingersoll Rand, Public Meeting Transcript, No. 20 at pp. 140-141)
Goodman further commented that the regulatory text should restrict the
one pound rule to laboratory tests and suggested regulatory text to
address this issue as well as the small diameter tubing issue.
(Goodman, No. 39 at p. 3-4) Lennox supported the intent of DOE's
proposal but found it to be too restrictive because of the existence of
products in which the internal volume of the product does not allow it
to be fully charged from the factory. (Lennox, No. 25 at p. 5) Goodman,
Lennox, and JCI were particularly concerned with potential unintended
consequences and potentially impeding innovation as the industry moves
toward lower global warming potential (GWP) refrigerants, in which
cases the manufacturer may choose to ship split-system units designed
for use with A2L refrigerants without the refrigerant factory-
installed. (Goodman, No. 39 at p. 4) Lennox commented that the safety
requirements and codes and standards required for a transition to A2L
\8\ refrigerants are not developed and that there is a high probability
that some form of mitigation to ensure product safety will be required,
for example, requiring that such units be dry-shipped, i.e. with a dry
nitrogen charge rather than with refrigerant. Lennox commented that DOE
should maintain a path that allows dry-shipping products (DOE
understands this to mean not requiring no-match testing for these
products) to ensure the most efficient transition to low-GWP products
with the least
[[Page 1435]]
negative consumer impacts. (Lennox, No. 25 at p. 5)
---------------------------------------------------------------------------
\8\ A2L is a safety classification for refrigerants that have
low toxicity and lower flammability. See https://www.epa.gov/snap/refrigerant-safety. Most refrigerants in current use (e.g. R-410A)
have an A1 classification, indicating both low toxicity and no flame
propagation.
---------------------------------------------------------------------------
First Co. objected to the requirement to test an outdoor unit as a
no-match outdoor unit if more than a pound of refrigerant would have to
be added during set up. First Co. commented that the proposals are
based on a single charge value when there are multiple charge values
for different coils. First Co. requested DOE drop this requirement
entirely. (EERE-2016-BT-TP-0029, No. 21 at p. 5)
In response to these comments DOE has revised the criteria for
outdoor units with no match. Specifically, manufacturers must determine
efficiency representations, and certify such representations, for
outdoor units as an outdoor unit with no match if:
The outdoor unit is approved for use with, determined by
listing on the outdoor unit nameplate, HCFC-22 or refrigerants with
similar thermophysical properties, as specified in Sec. 429.16(a)(3)
(the discussion below addresses similarity);
There are no designations of approved refrigerants on the
outdoor unit nameplate; or.
The outdoor unit is shipped requiring more than two pounds
of charge when tested according to the test procedure (e.g., with 25
feet of interconnecting lines), unless (a) an A2L refrigerant is listed
as approved on the nameplate, or (b) the factory charge listed on the
nameplate is 70 percent or more of the outdoor unit's internal
refrigerant circuit volume times the density for 95 [deg]F refrigerant
liquid.
DOE agrees with JCI and Goodman that outdoor units approved for use
with refrigerants similar to HCFC-22 (other than R-407C) are likely to
be intended for no-match use in the field. Hence, DOE is changing the
criteria so that approval for use of any such refrigerant similar to
HCFC-22 would make the outdoor unit subject to the no-match
requirements. DOE does not find it likely that a large market for
complete systems based on R-407C or other refrigerants similar to HCFC-
22 would likely emerge in the near future given the initial trends
associated with introduction of R-407C products, as discussed section
III.A.5.c. As suggested by ACEEE, NRDC, and ASAP (ACEEE, NRDC, and
ASAP, No. 33 at p. 3), R-410A is nearly universally used as the
refrigerant that has replaced HCFC-22 in CAC/HP systems. Other
refrigerants approved by the EPA in its SNAP listing for acceptable
substitutes in residential and light commercial air conditioning and
heat pumps \9\ are rarely used in new split systems. DOE considered the
approved refrigerants in the SNAP list and refrigerants understood to
be suitable for use in HCFC-22 systems (``Refrigerants for R-22
Retrofits'', No. 46 at p. 1) and developed an HCFC-22 similarity
criterion that would apply for these likely replacement options. DOE
determined that the HCFC-22 replacement refrigerants would be selected
and no other refrigerant that is likely to be approved for use in new
split systems would be selected if the saturation pressure associated
with 95 [deg]F refrigerant temperature is within 18 percent of the
pressure for HCFC-22. Hence, DOE adopts this as a criterion for no-
match status of an outdoor unit. DOE recognizes that there may be A2L
refrigerants that would themselves have similar pressures that in
future may be approved on EPA's SNAP list for these products. To ensure
that transition from global warming refrigerants is not restricted, DOE
acknowledges that some revisions to these requirements may need to be
developed as manufactures start to adopt such refrigerants in new split
systems. DOE will consider such testing and certification revisions and
propose options in a future rulemaking.
---------------------------------------------------------------------------
\9\ https://www.epa.gov/snap/acceptable-substitutes-residential-and-light-commercial-air-conditioning-and-heat-pumps.
---------------------------------------------------------------------------
DOE is also revising the no-match criteria regarding dry shipping
and required refrigerant addition as indicated above in response to
manufacturer comments and additional research. First, DOE recognizes
that where an installation requires long line sets, that a higher
quantity of refrigerant may have to be added. DOE agrees with Goodman's
suggestion to base this limit on a standardized scenario, specifically
the addition of charge in a DOE test, for which 25 feet of refrigerant
lines are specified. Second, DOE has adopted the exception associated
with small-volume outdoor coils (factory charge 70 percent or more than
the coil internal volume times refrigerant density) suggested by
Goodman. However, DOE reviewed its own available test data for CAC/HP
systems and determined that, for tests in which the added charge
quantities were clearly recorded, a large percentage of tests required
addition of 1 pound or more of refrigerant. Review of the data showed
that nearly all of the tests could be conducted with the addition of
less than 2 pounds of refrigerant. Hence, DOE is revising the charge
addition requirement accordingly. First Company's comments addressed
differences in indoor coil volumes, but did not provide specific
information regarding the potential differences in charge that could be
associated with different coil sizes--the additional pound doubles the
allowed charge addition for a unit before requiring a no-match test
and, based on DOE test experience, is sufficient to address nearly all
tested systems. Because these systems were charged without
consideration of this new requirement and would likely have required
less charge addition if pre-charged with the limit in mind, and also
considering that at least one manufacturer (Goodman) agreed with the
one-pound limit on the basis of additional clarifications that DOE has
adopted (the low-coil-volume exclusion and clarification that the limit
applies for ratings testing), DOE believes that the finalized criteria
are sufficiently flexible to avoid requiring no-match testing for any
outdoor units that should not be tested this way.
DOE also acknowledges the issues associated with A2L refrigerants
and small-volume heat exchanger technologies. DOE agrees with Goodman's
suggestions for providing exceptions to the no-match requirements in
these cases and has adopted the suggestions in this final rule.
f. NGIFS
In the July 2016 final rule, DOE set requirements for the indoor
units that are used in tests of outdoor units with no match. 81 FR at
37065 (June 8, 2016). The August SNOPR proposed extension of this
requirement to additional types of outdoor units with no match. 81 FR
at 58170 (Aug. 24, 2016).
AHRI and Nortek commented that it will not always be the case that
outdoor units with no match are a result of the phase-out of R-22
refrigerant and that in the future there will be a transition between
nonflammable and mildly flammable refrigerants. They further suggested
that when higher GWP refrigerants, such as R-410A are phased out, there
will likely be a period of time when R-410A condensing units will be
sold as outdoor units with no match, and that they will likely be
shipped dry. AHRI and Nortek commented that while a NGIFS no higher
than 1.0 sq.in./Btu/hr may be representative of R-22 units circa 2006,
NGIFS of 1.0 makes no sense for R-410A, resulting in energy
measurements that are not representative of the unit in the field.
(AHRI, No. 27 at p. 5-6; Nortek, No. 22 at p. 5) Ingersoll Rand
commented similarly. (Ingersoll Rand, No. 38 at p. 2) Ingersoll Rand
further commented that the NGIFS definition is only appropriate for \3/
8\'' tube coils and cannot be used for coils with smaller
[[Page 1436]]
diameter tubes or with microchannel heat exchangers. Ingersoll Rand
commented that NGIFS does not account for fin design or tube pattern
which affects heat transfer, and its adoption will create the potential
for testing loopholes in the future. Ingersoll Rand commented that it
would be better to set a limit on coil cabinet volume based on coils
sold in the 5 years prior to the elimination of a refrigerant.
(Ingersoll Rand, No. 38 at p. 2)
DOE acknowledges that the old indoor units that are matched with
no-match outdoor units in field installations will not always be old
HCFC-22 indoor units. DOE will consider adjustments to the no-match
requirements consistent with available information in a future
rulemaking. However, DOE does not necessarily agree that a phaseout of
high GWP refrigerants will by itself mean a step change of the existing
population of indoor units to characteristics typical of more recent R-
410A systems. Consideration will have to be given to whether the NGIFS
value is allowed to rise to reflect representative field conditions or
whether there are alternative approaches that would be more effective
in addressing issues associated with installation of no-match outdoor
units.
In response to Ingersoll Rand's comment regarding applicability of
NGIFS, DOE responds that the vast majority of indoor units that are
field-matched with no-match outdoor units have \3/8\-in OD tubing.
Further, DOE selected the NGIFS value based on the assumption that
manufacturers would use enhanced fin surfaces (e.g., lanced, louvered,
wavy) for such tests. DOE also notes that such surfaces were in general
use during the time period before phaseout of HCFC-22 for new systems.
(See, e.g., page 1-11 of the 1997 technical support document for room
air conditioners, which indicates that such surfaces were in use for
central air conditioners at the time, https://www1.eere.energy.gov/buildings/appliance_standards/pdfs/tsdracv2.pdf.)
6. Representation Limitations for Independent Coil Manufacturers
In the June 2016 final rule, DOE adopted language in 10 CFR 429.16
specifying that a basic model may only be certified as compliant with a
regional standard if all individual combinations within that basic
model meet the regional standard for which that basic model would be
certified and that an ICM cannot certify a basic model containing a
representative value that is more efficient than any combination
certified by an OUM containing the same outdoor unit. 81 FR at 37050
(June 8, 2016).
Based on letters submitted by several stakeholders (Docket No.
EERE-2016-BT-TP-0029-0006, -0005, and -0003), in the August 2016 SNOPR,
DOE proposed to remove the sentence: ``An ICM cannot certify a basic
model containing a representative value that is more efficient than any
combination certified by an OUM containing the same outdoor unit.'' and
replace it with the following language in 10 CFR 429.16(a)(4)(i): An
ICM cannot certify an individual combination with a rating that is
compliant with a regional standard if the individual combination
includes a model of outdoor unit that the OUM has certified with a
rating that is not compliant with a regional standard. Conversely, an
ICM cannot certify an individual combination with a rating that is not
compliant with a regional standard if the individual combination
includes a model of outdoor unit that an OUM has certified with a
rating that is compliant with a regional standard. 81 FR at 58172 (Aug.
24, 2016)
AHRI, Nortek, Unico, First Co., ADP, ACEEE, NRDC, and ASAP,
Ingersoll Rand, Rheem, Carrier, Lennox, and JCI supported DOE's
proposal. (AHRI, No. 27 at p. 7; Nortek, No. 22 at p. 7; Unico, Inc.,
No. 30 at p. 2; First Co, No. 21 at p. 3; ADP, No. 23 at p. 3; ACEEE,
NRDC, and ASAP, No. 33 at p. 5; Ingersoll Rand, No. 38 at p. 3; Rheem,
No. 37 at p. 2; Carrier/UTC, No. 36 at p. 4; Lennox, No. 25 at p. 11;
JCI, No. 24 at p. 9; ADP, Public Meeting Transcript, No. 20 at p. 143)
Therefore, in this final rule, DOE is adopting this language as
proposed.
7. Reporting of Low-Capacity Lockout for Air Conditioners and Heat
Pumps With Two-Capacity Compressors
In the August 2016 SNOPR, DOE proposed to require that the lock-out
temperatures for both cooling and heating modes for CAC/HPs with two-
capacity compressors be provided in the certification report. 81 FR
58163, 58172 (Aug. 24, 2016).
NEEA commented that they strongly support the proposed reporting
requirement. (NEEA, No. 35 at p. 2) AHRI, Nortek, Ingersoll Rand, JCI,
and Carrier/UTC commented that low-capacity lockout for air
conditioners and heat pumps with two-capacity compressors is considered
intellectual property, and that they are concerned about the
possibility of reverse engineering products if this information is
publicly reported. (AHRI, Public Meeting Transcript, No. 20 at p. 101;
AHRI, No. 27 at p. 7; Nortek, No. 22 at p. 8; Ingersoll Rand, No. 38 at
p. 3; JCI, No. 24 at p. 17-18; Carrier/UTC, No. 36 at p. 3)
In the existing requirements and the requirements proposed in the
August 2016 SNOPR, DOE lists product-specific items that needs to be
included in certification reports in 10 CFR 429.16(e), with subsection
(2) listing public items, and subsection (4) listing additional items
that would not be posted to DOE's public certification database. DOE
notes that it included the proposal to require reporting the outdoor
temperature(s) at which the unit locks out low capacity operation
(where applicable) in proposed Sec. 429.16(e)(4) of the August 2016
SNOPR. Because, under the proposal, the item would not be posted to
DOE's public certification database, DOE is maintaining this
requirement in this final rule.
8. Represented Values of Cooling Capacity
In the August 2016 SNOPR, DOE proposed to revise the regulatory
text in three locations (10 CFR 429.16(b)(3), 10 CFR 429.16(d), 10 CFR
429.70(e)(5)(iv)) to allow a one-sided tolerance on cooling and heating
capacity that allows underrating of any amount, but only overrating up
to 5 percent (i.e., the certified capacity must be no greater than 105
percent of the mean measured capacity or the output of the AEDM), as
intended in the June 2016 final rule. As adopted in the June 2016 final
rule, DOE would still use the mean of the measured capacities in its
enforcement provisions.
AHRI, Mitsubishi, Rheem, Carrier, JCI, Nortek, Ingersoll Rand, ADP,
Lennox, and Goodman opposed DOE's proposal for tolerance on cooling
capacity. They commented that the same rules that apply to efficiency
should be applied to capacity, where manufacturers should be permitted
to rate cooling and heating capacity only as high as the tested value
or AEDM output. (AHRI, No. 27 at p. 7; Mitsubishi, No. 29 at p. 2;
Rheem, No. 37 at p. 2; Carrier/UTC, No. 36 at p. 4; JCI, No. 24 at p.
9; Nortek, No. 22 at p. 8; Ingersoll Rand, No. 38 at p. 3; ADP, No. 23
at p. 3-4; Lennox, No. 25 at p. 6; Goodman, No. 39 at p. 12; Carrier/
UTC and Lennox, Public Meeting Transcript, No. 20 at p. 145)
Additionally, Carrier commented that de-rating capacity would result in
a consumer getting more capacity than expected but that overrating
capacity as suggested in this proposal would result in a loss to the
consumer. In addition, the double sided tolerance would statistically
result in much higher risk for manufacturers. (Carrier/UTC, No. 36
[[Page 1437]]
at p. 4; Carrier/UTC, Public Meeting Transcript, No. 20 at p. 144)
ACEEE, NRDC, ASAP supported the use of one-sided tolerance tests
where possible, stating that there may be legitimate business reasons
to label and sell units that are more efficient than their certified
values and that consumers can only be pleased if a product does better
than claimed. (ACEEE, NRDC, and ASAP, No. 33 at p. 5)
Unico commented that they strongly support one-sided tolerance for
capacity, without which a manufacturer cannot rate conservatively.
Unico stated that it recognizes that, for some product classes other
than small-duct high-velocity, there is a very small chance that a
manufacturer could conservatively rate a system with the express intent
to avoid testing with a slightly higher external static pressure. Unico
believes the advantage that this provides is insignificant. (Unico,
Inc., No. 30 at p. 2)
NEEA commented that they do not necessarily support the proposal,
stating that they were not able to ascertain if DOE's one-sided
tolerance for capacity reporting would result in a system being rated
with a lower building load as a result of reporting an overly
conservative value, and thus an overrated cooling and/or heating
performance. (NEEA, No. 35 at p. 2)
First Co. agreed with DOE's proposal to allow one sided tolerance
on represented values of cooling and heating capacity, but commented
that the proposed language in Sec. 429.70(e)(5)(iv) does not
accurately reflect DOE's intention. First Co. believes that in the
first sentence after the words ``. . . by more than 5 percent'' the
text should read ``or tests worse than its certified cooling capacity
by more than 5 percent.'' (First Co, No. 21 at p. 3)
DOE understands that overrating capacity could result in a loss to
the consumer and could put the manufacturer at risk. In response to the
comments received, in this final rule DOE is revising the tolerance on
cooling capacity to be similar to the tolerance on efficiency, where
the cooling capacity should be less than or equal to the lower of: (1)
The mean of the sample and (2) the lower 90 percent confidence limit of
the true mean divided by 0.95; or less than or equal to the AEDM
output. DOE agrees with Unico that conservatively rating to gain some
advantage is not a significant risk. In response to NEEA, DOE notes
that the building loads, calculated by sections 4.1 and 4.2 of both
appendix M and appendix M1 of the August 2016 SNOPR, use the tested
heating and cooling capacities, not the rated capacities. Therefore,
there is no concern of overrating cooling or heating performance.
In response to First Co.'s comments, DOE notes that the August 2016
SNOPR, Sec. 429.70(e)(5)(iv), regarding AEDM verification testing,
inadvertently stated that DOE would notify a manufacturer that a unit
fails to meet its certified rating if the tested cooling capacity is
greater than 105 percent of its certified cooling capacity. In this
final rule, the section has been revised to indicate DOE will notify a
manufacturer that a unit fails to meet its certified rating if the
tested cooling capacity is lower than its certified cooling capacity.
This is consistent with DOE's revisions to its tolerance on cooling
capacity.
9. New Efficiency Metrics
During the August 2016 Public Meeting, EEI, PG&E, Goodman, Rheem,
and Unico recommended renaming the efficiency metrics whose values will
be altered as compared to the current metrics, which includes HSPF,
SEER, and EER. The purpose of this would be to help avoid confusion in
the marketplace and to allow more relevant utility incentive programs.
(EEI, PG&E, Goodman, Rheem, and Unico, Public Meeting Transcript, No.
20 at pp. 85-91)
Additionally, EEI submitted a written comment suggesting that a new
efficiency acronym be used under the revised test procedure in order to
avoid market confusion and to ensure that consumers are aware that
significant changes have been made in how heat pumps are tested and
rated. EEI suggested the use of several specific acronyms. (EEI, No.
34, page 6) The California IOUs similarly commented that the proposed
changes to appendix M1 efficiency ratings are so substantial that they
should be given new descriptors. The California IOUs stated that value
changes will cause confusion in the marketplace unless they are re-
labeled as ``EER2,'' ``SEER2,'' and ``HSPF2,'' or with other labels
determined by DOE to be appropriate. (California IOUs, No. 32 at p. 5)
In response to the comments, in this final rule, DOE is creating
new efficiency metrics to represent cooling and heating performance
whose values will be altered as compared to the current metrics. The
new metrics include seasonal energy efficiency ratio 2 (SEER2), which
will replace seasonal energy efficiency ratio (SEER); energy efficiency
ratio 2 (EER2), which will replace energy efficiency ratio (EER); and
heating seasonal performance factor 2 (HSPF2), which will replace
heating seasonal performance factor (HSPF). These labels are consistent
with those used in the CAC/HP ECS Working Group Term Sheet. New
efficiency metrics SEER2, EER2, and HSPF2 reflect the changes in the
test procedure in appendix M1 that result in change in the measured
efficiency values. The definitions for these metrics are identical to
those for the original metrics except that they are determined in
accordance with appendix M1 instead of in accordance with appendix M.
B. Amendments to Appendix M Testing To Determine Compliance With the
Current Energy Conservation Standards
Under EPCA, any test procedure that DOE prescribes or amends shall
be reasonably designed to produce test results which measure energy
efficiency and energy use of a covered product during a representative
average use cycle or period of use. (42 U.S.C. 6293(b)(3)) In the
August 2016 SNOPR, DOE proposed several revisions to appendix M to
subpart B of 10 CFR part 430 to improve the test representativeness and
repeatability. 81 FR 58164 (Aug. 24, 2016) In addition, DOE held a
public meeting at DOE headquarters in Washington, DC, on August 26,
2016 (Public Meeting Transcript, Docket No. EERE-2016-BT-TP-0029-0020).
Based on the comments DOE received from the August 2016 Public Meeting
and from the August 2016 SNOPR comment period, DOE is modifying its
approach and adopting revisions to its procedures in Appendix M, which
is independent of Appendix M1.
1. Measurement of Off Mode Power Consumption: Time Delay for Units With
Self-Regulating Crankcase Heaters
In the August 2016 SNOPR, DOE proposed revisions to the off-mode
test procedure imposing time delays to allow self-regulating crankcase
heaters to approach equilibrium before making measurements. DOE
proposed a 4-hour time delay for units without compressor sound
blankets and an 8-hour time delay for units with compressor sound
blankets. 81 FR at 58173 (Aug. 24, 2016)
In the SNOPR public meeting, JCI commented that adding four or
eight hour time delays is a substantial testing burden and requested
that DOE consider developing an approach to predict the final values
without much extra test time. They reiterated this request in written
comments and suggested that a time-based correlation developed by
manufacturers could be built into the AEDM for the off-mode metric.
(JCI, Public Meeting Transcript, No. 20 at p. 31; JCI, No. 24 at p. 10)
[[Page 1438]]
AHRI and Nortek commented that they generally support establishing
delay time but were concerned that manufacturers would have to retest
all units again within 180 days of the publication of the final rule so
soon after initiating off-mode testing after the June 2016 final rule
first established the off-mode test procedures. AHRI asserted that this
revision represents a significant and unnecessary testing burden. AHRI
suggested that DOE should either allow the off-mode rating to be based
on appendix M modifications finalized in the June 2016 Final Rule (DOE
assumes this is a request to clarify that products tested within 180
days of the June 8 final rule need not be retested again using the time
delays) or move this revision to appendix M1 (AHRI, No. 27 at p. 8;
Nortek, No. 22 at pp. 8-9). Carrier commented that the estimated time
to implement this change would be at least six additional months
(Carrier, No. 36 at p. 5). Rheem disagreed with the implementation time
frame because this change will double the testing time and supported
moving the change to appendix M1 (Rheem, No. 37 at p. 2). Ingersoll
Rand commented that completing all the required testing would extend
beyond the effective date (Ingersoll Rand, No. 38 at p. 3).
ACEEE, NRDC, and ASAP commented that DOE's approach to the thermal
response delay issue for self-regulating crankcase heaters seems
reasonable and responsive, but also sub-optimal considering that the
measured self-regulating heater's power at the end of the specified
delay times could be higher or lower with compressors having more or
less thermal mass. ACEEE, NRDC, and ASAP recommended that DOE allow
manufacturers to select alternative delay times if shorter or longer
delays are required for specific models. (ACEEE, NRDC, and ASAP, No. 33
at p. 6).
Lennox, the CA IOUs and NEEA supported DOE's proposal. (Lennox, No.
25 at p. 11; CA IOU, No. 32 at p. 4; NEEA, No. 35 at p. 2)
DOE agrees that this additional delay time requirement could change
the off-mode power measurement for some tested combinations that
manufacturers may have already tested using the test procedure of the
June 2016 Final Rule. DOE does not intend to introduce unnecessary test
burden due to the close timing between the June 2016 Final Rule and
this final rule. Therefore, DOE has decided to remove this requirement
from appendix M and adopt it only in appendix M1. As for JCI's
suggestion to develop a time-based correlation to allow prediction of
the final measurement based on the trend in the measurement over a
limited time period, DOE does not have sufficient test data to be
confident that such an approach would provide a predictable result. In
fact, depending on the equation used to fit the curve created by the
first few data points, the details of the particular compressor design,
and the history of testing just prior to conducting an off-mode test,
DOE is concerned that a wide range of results might be obtained for any
given unit, including a prediction of infinite wattage. DOE understands
JCI's concern and agrees that such an approach could be considered in
the future with more analysis and testing to validate an approach.
Hence, DOE will not adopt a shortened test using curve fitting to
predict ultimate off-mode power input. Regarding JCI's mention of an
AEDM for off-mode, DOE does not regulate what analytic evaluation can
be used in an AEDM--there is nothing in the AEDM requirements that
would prevent a manufacturer from adopting an AEDM that uses the
results of a shortened test as its input, as long as the requirements
in 10 CFR 429.16 and 429.70 are satisfied. Thus, this notice does not
adopt a shortened test procedure using curve fitting and prediction to
determine off-cycle power input for systems with self-regulating
crankcase heaters.
DOE received no comment suggesting different time delays than those
proposed by DOE. Hence, DOE has adopted in appendix M1 the proposed
time delays for measurement of off-mode power for units with self-
regulating crankcase heaters or heater systems in which the crankcase
heater control is affected by the heater's heat.
In addition, DOE notes that the August 2016 SNOPR inadvertently
included in the regulatory text a certification requirement for the
duration of the crankcase heater time delay for the shoulder season and
heating season, if such time delay is employed. DOE does not actually
require this information and has not adopted this requirement in the
final rule.
2. Refrigerant Pressure Measurement Instructions for Cooling and
Heating Heat Pumps
In the August 2016 SNOPR, DOE proposed limiting the internal volume
of the pressure measurement system (i.e. the pressure gauge or
transducer and the capillary tube and tube fittings connecting the
transducer to the refrigerant lines) at pressure measurement locations
that may switch from liquid to vapor state when changing operating
modes and for all locations for systems undergoing cyclic tests for
cooling/heating heat pumps. Specifically, DOE proposed the limit to be
0.25 cubic inch per 12,000 Btu/h. DOE also proposed the default
internal volumes to be assigned to pressure transducers and gauges of
0.1 and 0.2 cubic inches, respectively, if transducer or gauge
datasheets do not provide their internal volume. 81 FR at 58174 (Aug.
24, 2016)
During the 2016 August Public Meeting, Carrier commented that
manufacturers typically test with up to six pressure transducers and
the proposed limit would prohibit the level of testing during
manufacturers' development stage and limit the number of pressure
transducers to two. Carrier requested a reconsideration of the
tolerance. (Carrier, Public Meeting Transcript, No. 20 at pp. 70-75)
AHRI requested clarification of ``locations where the refrigerant
state changes from liquid to vapor for different parts of the test.''
AHRI commented that it is standard industry practice to place pressure
taps with capillary tubes at six locations and advised that one of its
members reported that, in their test chambers, the average internal
volume of each pressure line is 0.91 cubic inches. Hence, AHRI asserts
that DOE's proposed limit is too tight, such that the allowed number of
pressure transducers would be zero for a unit that has a capacity less
than 3 tons, and only one for larger-capacity units. In addition, AHRI
commented that, for a cyclic test, the refrigerant state change occurs
so quickly during transient startup that the effects (if any) will be
within the tolerance of the measuring equipment. According to AHRI, for
steady-state tests of units with the cooling mode restrictor located in
the outdoor unit, there are at most two locations where the refrigerant
state changes from liquid to two-phase between heating and cooling.
AHRI's comment provided a table showing the refrigerant states at the
six typical measurement locations for a cooling/heating heat pump
having two expansion devices (one each in the indoor and outdoor units)
for four test scenarios: Cooling steady-state, cooling transient start-
up, heating steady-state, and heating transient start-up. The comment
provided a similar table showing the refrigerant states for a heat pump
with a single expansion device in the outdoor unit. In these tables,
the transient startup scenario entries were all ``two-phase''. In
addition, the only differences in refrigerant state between steady-
state heating and steady-state cooling were highlighted in the single-
expansion-device table for the liquid
[[Page 1439]]
service valve and indoor coil inlet locations. AHRI commented that the
refrigerant weight difference (e.g., associated with transfer of
refrigerant in and out of the pressure lines) is extremely small
(particularly considering standard charging conditions in the field),
and would have a negligible effect on the system performance. AHRI
requested that DOE eliminate restrictions on pressure transducer
internal volume or increase them significantly in order to ensure
proper system analysis. (AHRI, No. 27 at pp. 8-11) JCI, Carrier,
Ingersoll Rand and Goodman concurred with AHRI's comment. (JCI, No. 24
at p. 10-12; Carrier/UTC, No. 36 at p. 5-6; Ingersoll Rand, No. 38 at
p. 3; Goodman, No. 39 at p. 9) Ingersoll Rand further requested that
there be clarification that this requirement would apply only to
assessment and enforcement testing, not for developmental testing.
(Ingersoll Rand, No. 38 at p. 3)
Lennox commented that this proposal is not practical or in
alignment with current practice for either manufacturer or audit
testing, and requested DOE remove or extensively revise this
requirement to align with current practices. (Lennox, No. 25 at p. 12)
Rheem disagreed with DOE's proposal, and commented that the amount of
refrigerant trapped in pressure measuring devices can be adequately
accounted for through proper refrigerant charging instructions. (Rheem,
No. 37 at p. 3) Unico agreed there should be volume limits but did not
have a comment on the value. Unico commented that most systems have a
high tolerance for charging while some systems, particularly systems
with microchannel coils, have a very low tolerance. (Unico, No. 30 at
p. 3) ACEEE, NRDC, and ASAP appreciated DOE's interest but stated that
it could not judge whether the proposed volumetric limits are the right
ones. (ACEEE, NRDC, and ASAP, No. 33 at p. 6) The CA IOUs agreed with
DOE's proposal (CA IOU, No. 32 at p. 4)
DOE has considered all of the comments received and is making
revisions based on those comments. First, DOE agrees that the transient
startup phase of a cyclic test may be sufficiently short that any
transfer of refrigerant in or out of the pressure lines at this time
could have very little impact on measured cyclic performance. The
scenario for cyclic test performance enhancement at the end of the on
cycle discussed in the August 2016 SNOPR could still occur (see 81 FR
at 58174 (Aug. 24, 2016)), but there is no data available to
demonstrate that this effect is significant.
DOE notes that the tables provided in the AHRI comment showing
refrigerant states at different refrigerant circuit locations represent
states in the refrigerant lines and not in the pressure measurement
systems, which could be different. For example, while the refrigerant
state is always vapor at the discharge location during steady-state
operation, the pressure measurement system is at a lower temperature
than the saturation temperature associated with the prevailing pressure
level. Hence, the vapor in the pressure line will condense. The
condensed liquid may flow out of the capillary line back into the
system, but this is unlikely if the pressure measurement system is
lower than the measurement location. Also, it is somewhat unclear
whether surface tension inside a small-diameter capillary tube would
impede the flow of condensed liquid back into the system, or whether
the vapor flowing into the system to replace the liquid would hold up
the liquid's return flow. DOE considered the potential states within
the pressure measurement systems rather than at the measurement
locations when evaluating the potential for refrigerant transfer
between steady-state operating modes. DOE made some reasonable
assumptions for this assessment, making liberal assumptions where there
is some doubt about what will occur--specifically, DOE did not assume
that for the above scenario that liquid return flow to the system would
be impeded. DOE's assessment of likely refrigerant states for a single-
expansion-valve heat pump is summarized in Table III-1. The table adds
a seventh potential refrigerant circuit location, between the outdoor
coil and the expansion valve, which DOE expects that some manufacturers
may monitor during developmental testing to determine subcooling
achieved during cooling mode operation.
Table III-1--Refrigerant States in Pressure Measurement Systems for a Single-Expansion-Valve Heat Pump
--------------------------------------------------------------------------------------------------------------------------------------------------------
Operating mode Steady-state cooling Steady-state heating
--------------------------------------------------------------------------------------------------------------------------------------------------------
Pressure measurement system above or
below tap location Above Below Above Below
--------------------------------------------------------------------------------------------------------------------------------------------------------
1. Compressor Discharge............. Vapor...................... Liquid **.................. Vapor...................... Liquid **.
2. Between Outdoor Coil and Liquid..................... Liquid..................... Vapor *.................... Two-phase.
Expansion Valve.
3. Liquid Service Valve............. Vapor *.................... Two-phase.................. Liquid..................... Liquid.
4. Indoor Coil Inlet................ Vapor *.................... Two-phase.................. Liquid..................... Liquid.
5. Indoor Coil Outlet............... Vapor...................... Vapor...................... Vapor...................... Liquid **.
6. Common Suction Port (i.e. vapor Vapor...................... Vapor...................... Vapor...................... Liquid **.
service valve).
7. Compressor Suction............... Vapor...................... Vapor...................... Vapor...................... Vapor.
--------------------------------------------------------------------------------------------------------------------------------------------------------
* Any liquid that enters the pressure measurement system will evaporate because the system is at a warmer temperature than the saturation temperature
associated with the pressure.
** Liquid will condense in the pressure measurement system because the system is at a cooler temperature than the saturation temperature associated with
the pressure, and will not drain back into the refrigeration circuit.
DOE notes that the liquid that might transfer out of one pressure
measurement system as the operating mode switches from cooling to
heating may transfer into another pressure measurement system and
therefore not affect total charge operating within the refrigerant
circuit. Also, because of the large density difference between liquid
and vapor, DOE believes that the charge in the pressure measurement
system would be negligible if the refrigerant within it is two-phase or
vapor. Hence, the likely transfer of refrigerant out of the
refrigeration circuit as the system switches from cooling to heating
would be equal to the liquid density (calculated for 100 [deg]F bubble
point conditions) multiplied by the volume differential obtained by
adding the volumes of the downward-run pressure measurement systems at
locations 5 and 6 (as designated in Table III-1) to the volumes of any
pressure measurement systems at locations 3 and 4 and subtracting the
volume of any pressure measurement system at location 2. For
[[Page 1440]]
a system with two expansion valves, the transferred refrigerant would
represent only the volumes of downward-run pressure measurement systems
at locations 5 and 6.
DOE realizes the refrigerant transfer could be mitigated by complex
phenomena occurring within the pressure measurement systems, some of
which, for example surface tension, are mentioned above. Another
mitigating phenomenon would be the filling of the pressure measurement
system with compressor oil, which would displace any refrigerant that
might transfer into it. Hence, DOE is relaxing the requirement proposed
in the August 2016 SNOPR in new section 2.2.g (see 81 FR at 58207 (Aug.
24, 2016)) that the volume differentials listed above represent no more
than 0.5 percent of refrigerant charge. DOE is instead adopting a
requirement in section 2.2.g that the volume differential represent no
more than 2 percent of the charge listed on the outdoor unit nameplate.
Basing the limit on the outdoor unit nameplate charge will provide more
flexibility for pressure measurement systems for those heat pumps that
have more charge and would hence be less sensitive to this issue.
However, due to the uncertainty regarding the actual potential behavior
regarding refrigerant transfer, DOE also is imposing a pressure
measurement system volume limit of 1 cu. in. for location 2 for single-
expansion-device heat pumps, in order to prevent a test laboratory from
using a very large volume for this location to offset the volumes of
locations 3, 4, 5, and 6.
For a two-expansion-device heat pump with pressure measurement
systems at locations 5 and 6 above the pressure tap locations, this
approach imposes no volume limits. Also, for single-expansion-valve
heat pumps with pressure measurement systems at locations 5 and 6 above
the pressure tap locations and the volume at locations 2 offsetting the
volumes at locations 3 and 4, there will also be no volume limit, other
than the 1 cu. in. limit at location 2. DOE believes that these
revisions to the proposal will allow manufacturers to make pressure
measurements at the locations typically used for development and
ratings testing while also providing some assurance that unforeseen
impacts associated with refrigerant transfer between operating modes
will be mitigated. However, DOE notes that the test procedure is for
determining the performance of the product for the purpose of
efficiency representations, not for development testing. DOE does not
require pressure measurements installed at all 7 locations indicated in
Table III-1. If manufacturers require use of pressure lines for
development testing that exceed the volume requirements, they have the
option of using isolation valves to isolate the tap locations not
needed for ratings tests as the test transitions from development to
determination of ratings for purposes of certifying compliance with
applicable standards. Another option is to use pressure transducers
that are more resistant to the temperature changes that occur in the
test chamber. In any case, DOE may consider revisions to the
requirements in the future if testing shows that they can be revised
further to both improve test repeatability and allow more flexibility
in making pressure measurements.
3. Revised EER and COP Interpolation Method for Units Equipped With
Variable-Speed Compressors
In the August 2016 SNOPR, DOE proposed to require use of bin-by-bin
interpolations for all variable-speed units (including variable-speed
multi-split and multi-head mini-split systems), to calculate
performance when operating at an intermediate compressor speed to match
the building cooling or heating load. This method consists of using
interpolation of EER or COP for each temperature bin based on the
estimates of capacity and power input for the specific bin temperature.
(EER is equal to cooling capacity divided by power input, while COP is
proportional to heating capacity divided by power input.) 81 FR at
58175 (Aug. 24, 2016)
Nortek, JCI, Mitsubishi, Carrier, Rheem, Ingersoll Rand and AHRI
expressed support for DOE's proposal but stated concerns that it would
impact ratings and would, as a result, be more appropriate for
inclusion in appendix M1 as opposed to Appendix M. (Nortek, No. 22 at
p. 9; JCI, No. 24 at p. 12; Mitsubishi, No. 29 at p. 2; Carrier, No. 36
at p. 6; Rheem, No. 37 at p. 3; Ingersoll Rand, No. 38 at p. 4; AHRI,
No. 27 at p. 11) AHRI also commented that its members were in the
process of collecting data on the impact this proposed change would
have on ratings and committed to providing additional information to
the Department within 30 days of the close of the comment period.
(AHRI, No. 27 at p. 11) DOE notes that the additional data were not
provided. Goodman also requested DOE implement this change as part of
appendix M1. (Goodman, No. 39 at p. 6) Unico recommended that this
proposal be moved to appendix M1, and if it remains as an appendix M
change, DOE should allow that the higher rating of both methods be
used, but only if the bin-by-bin method results in a failure. (Unico,
No. 30 at p. 3-4) Lennox, CA IOU, ACEEE, NRDC, and ASAP, and NEEA all
supported DOE's proposal. (Lennox, No. 25 at p. 12; CA IOU, No. 32 at
p. 4; ACEEE, NRDC, and ASAP, No. 33 at p. 6; NEEA, No. 35 at p. 2)
Central air conditioning heat pumps include single-speed, two-
speed, and variable-speed products, all within the same product class
that when tested in accordance with the DOE test procedure will have
different measured efficiencies. Pursuant to 42 U.S.C. 6293(e), DOE is
required to determine to what extent, if any, the proposed test
procedure would alter the measured efficiency of the covered product.
DOE proposed changes to the interpolation method for variable speed
units only. For single-speed and two-speed products there would be no
change in measured efficiency because they would not be impacted by
this change in test procedure. However, variable-speed products would
be impacted by this change in test procedure, so the measured
efficiency would change.
Where an amended test procedure would alter measured efficiency,
EPCA requires DOE to amend an energy conservation standard by
measuring, under the amended test procedure, a sample of representative
products that minimally comply with the standard. In this case,
minimally compliant units are those with single-speed technology.
Consistent with the statute, DOE has tested a representative sample of
covered products that minimally comply with the existing standard. EPCA
requires that the amended standard should constitute the average of the
energy efficiency of those units, determined under the amended test
procedure. As a result of that testing, DOE has determined that there
is no change in measured average energy efficiency for single-speed
units between the current test procedure and the amended test
procedure. Thus, under 42 U.S.C. 6293(e)(2), the amended standard
applicable to the amended test procedure and the current standard
applicable to the amended test procedure are the same. As a result, DOE
does not need to amend the existing standard to require that
representations of variable-speed heat pumps be based on the amended
test procedure in appendix M.
If DOE were to include this change in appendix M, Goodman requested
that DOE allow industry up to two years to re-test and re-calculate
SEER and HSPF, by either modifying the implementation date for this
provision or by issuing a policy of non-enforcement for this provision.
(Goodman, No. 39 at p. 6) DOE notes that this proposal would not
[[Page 1441]]
require additional testing. The proposed change only impacts how
ratings are calculated based on the new interpolation method, not the
data that is measured or how it is measured. If manufacturers have test
data that is otherwise valid under the amended test procedure, there
would be no reason to retest solely because of the change in the way
represented values for variable speed heat pumps are calculated.
Several commenters suggested that because the change to bin-by-bin
interpolation for variable speed heat pumps might cause changes in
ratings, DOE should not require the new method in Appendix M.
Commenters did not explain why a simple change in ratings would warrant
a decision to postpone the change in method, but DOE has considered
three possibilities. First, commenters may be concerned about the work
to comply with the new method. However, as noted above, the new
interpolation method is only a matter of calculation; it will require
no new tests. DOE believes that the burden of recalculation using
existing test data will be minimal; Appendix M will specify how to
perform the bin-by-bin interpolation, and relatively simple revision to
a spreadsheet would suffice to implement this method as a substitute
for the quadratic method required under the prior test procedure.
Second, commenters may be concerned about the cost of revising labels
and other representation documents to reflect the new ratings. Third,
some commenters may object because if the new method results in a
decreased rating, that change will make the affected models appear less
efficient to potential buyers.
With respect to these second and third concerns, DOE believes that
the inaccuracy of the current method warrants the change. As the August
2016 SNOPR explained, the quadratic interpolation method can produce
inaccurate results. For HSPF the quadratic method can produce a value
up to 7.9% different from what the bin-by-bin method produces (and DOE
regards the latter as more accurate). Thus, for some equipment the
rated HSPF is overstated, with respect to a fair measure of efficiency,
by as much as 7.9%. A buyer using such equipment would consume 7.9%
more energy, at 7.9% more cost, than expected based on the rating. DOE
believes that amount is a significant difference. By contrast, the
regulation requires a represented cooling capacity to be within 5% of
the average measured cooling capacities, and it permits rounding of
figures to approximately 1% precision (200 Btu/h for a 20,000 Btu/h
system). Using 1% and 5% as indicators of what amount of error in a
rating is significant, DOE believes it is important to correct an
interpolation method that generates, for some models, larger errors. Of
course, if a rating based on the old method is still valid--including
by being within the regulation's tolerances with respect to
recalculated values--a manufacturer could choose whether or not to
revise the rating.
For these reasons, DOE is adopting this proposal both in appendix M
and appendix M1 in this final rule.
4. Outdoor Air Enthalpy Method Test Requirements
In the August 2016 SNOPR, DOE proposed modifications to
requirements when using the outdoor air enthalpy method as the
secondary test method, including that the official test be conducted
without the outdoor air-side test apparatus connected. 81 FR at 58175-
58176 (Aug. 24, 2016)
During the August 26, 2016 public meeting, Carrier suggested that
the proposal to require a heat balance only for the full-load cooling
test and, for a heat pump, the full-load heating test be extended to
other secondary capacity measurement methods, including to use of the
refrigerant enthalpy method. Carrier contended that it can be difficult
to get an energy balance for some operating conditions, particularly
for variable-speed systems, when there is insufficient subcooling or
superheat.\10\ (Carrier, Public Meeting Transcript, No. 20 at pp. 38-
39) Ingersoll Rand agreed with this suggestion; Goodman also agreed and
indicated that the issue applies for tests of single-stage, two-stage,
and variable-speed systems for the heating mode test conducted in 17
[deg]F outdoor temperature. (Ingersoll Rand, Public Meeting Transcript,
No. 20 at p. 39; Goodman, Public Meeting Transcript, No. 20 at p. 40)
---------------------------------------------------------------------------
\10\ In this context, subcooling refers to the difference
between the saturated temperature associated with the pressure of
the refrigerant liquid exiting the outdoor unit (in cooling mode)
and the temperature of the liquid. Similarly, superheat refers to
the difference between the temperature of the refrigerant exiting
the indoor unit (in cooling mode) and the saturated temperature
associated with the pressure of this refrigerant. The enthalpy of
the refrigerant at these locations generally cannot be determined if
these values are zero.
---------------------------------------------------------------------------
JCI, Lennox, Carrier, Ingersoll Rand, Goodman and AHRI agreed with
DOE on this proposal but recommended that the ducted test be a 30-
minute test. (JCI, No. 24 at p. 12; Lennox, No. 25 at p. 12; Carrier,
No. 36 at p. 7; Ingersoll Rand, No. 38 at p. 4; Goodman, No. 39 at p.
13; AHRI, No. 27 at p. 11-12) Carrier, Ingersoll Rand, Goodman and AHRI
also suggested DOE similarly only require balance checks for the
A2 and H12 (or H1N) tests for the
refrigerant enthalpy method. (Carrier, No. 36 at p. 7; Ingersoll Rand,
No. 38 at p. 4; Goodman, No. 39 at p. 13; AHRI, No. 27 at p. 11-12) In
addition, AHRI and Ingersoll Rand suggested DOE eliminate the five
consecutive readings for verifying the primary capacity measurements.
(AHRI, No. 27 at p. 11-12; Ingersoll Rand, No. 38 at p. 4) CA IOU and
Rheem agreed with DOE's proposal. (CA IOU, No. 32 at p. 4; Rheem, No.
37 at p. 3)
DOE agrees that validation of proper capacity measurement for
cooling and heating modes for full-load operation is sufficient to show
that the indoor air enthalpy method is being applied properly and gives
an accurate measurement. Hence, use of the secondary method and
achieving an energy balance for all load levels in each operating mode
is not necessary. DOE notes that systems with capacity greater than
135,000 Btu/h are tested without any requirement for a secondary
capacity check. (American Society of Heating Refrigeration, and Air-
Conditioning Engineers (``ASHRAE'') Standard 37-2009 (``ASHRAE 37-
2009''), which is incorporated by reference into the DOE test
procedures for both residential and commercial air conditioners,
indicates in Table 1 that a single method is used for systems with a
cooling capacity greater than 135,000 Btu/h.) Further, DOE believes
this modification will help to reduce test burden. The situation
discussed in the public meeting and written comments, in which, when
using the refrigerant enthalpy method as the secondary test method, a
heat balance cannot be calculated for some conditions due to subcooling
or superheat being too low, would technically make completion of a
valid test impossible, according to the current test procedure, without
resorting to an alternative secondary method. DOE recognizes that use
of different secondary methods for different parts of the test would
significantly increase test burden. Hence, DOE is modifying the test
procedure to require use of a secondary capacity measurement that
agrees with the primary capacity measurement to within 6 percent only
for the cooling full load test and, for heat pumps, for the heating
full load test.
DOE has decided to change the names for ``ducted'' and ``non-
ducted'' outdoor air enthalpy methods to avoid confusion with certain
product types. Specifically, DOE is adopting the new name ``free
outdoor air test'' for non-ducted outdoor air enthalpy test, and
``ducted outdoor air test'' for ducted outdoor air enthalpy test. In
this final rule, DOE is also
[[Page 1442]]
adopting a 30-minute ducted outdoor air test with measurements at five-
minute intervals, and eliminating from section 3.11.1.2 the requirement
of five consecutive readings for verifying primary capacity
measurements.
DOE's proposed changes to outdoor air enthalpy method requirements
in the August 2016 SNOPR included revision to section 3.11.1.2 that
removed the reference to section 8.6.2 of ASHRAE 37-2009. 81 FR at
58209 (Aug. 24, 2016). However, the key points of section 8.6.2 still
apply for the revised approach for the outdoor air enthalpy method. The
finalized test procedure retains the reference to this section.
5. Certification of Fan Delay for Coil-Only Units
In the August 2016 SNOPR DOE proposed to amend its certification
report requirements to require coil-only ratings to specify whether a
time delay is included, and if so, the duration of the delay used. DOE
proposed to use the certified time delay for any testing to verify
performance. 81 FR at 58176 (Aug. 24, 2016)
Nortek, Ingersoll Rand, Carrier, JCI, Rheem, Goodman and AHRI
suggested that the certification of the indoor fan off delay should not
be public information. (Nortek, No. 22 at p. 2; Ingersoll Rand, No. 38
at p. 3; Carrier, No. 36 at p. 7; JCI, No. 24 at p. 13; Rheem, No. 37
at p. 3; Goodman, No. 39 at p. 12; AHRI, No. 27 at p. 12) ADP agreed
that the duration of the indoor fan time delay needs to be specified
but should be a part of the public product-specific information. ADP
commented that making this information public improves the accuracy of
ICM AEDM ratings. (ADP, No. 23 at p. 4) Lennox and ACEEE, NRDC, and
ASAP supported DOE's proposal. (Lennox, No. 25 at p. 12; ACEEE, NRDC,
and ASAP, No. 33 at p. 6)
DOE understands that manufacturers want to keep fan delay setting
information private. Given that DOE proposed to require this
information in the section of additional product-specific information
that would not be posted to DOE's public certification database, DOE
has decided to adopt this proposal in this final rule. In response to
ADP, DOE will address concerns regarding reporting for ICMs through a
separate process.
6. Normalized Gross Indoor Fin Surface Area Requirements for Split
Systems
To help ensure that the test procedure results in ratings that are
representative of average use, in the August 2016 SNOPR DOE, proposed
to include a provision that would prevent testing certain combinations
that are not representative of single-split systems with coil-only
indoor units that are commonly distributed in commerce. Specifically,
DOE proposed to limit the normalized gross indoor fin surface (NGIFS)
for the indoor unit used for single-split-system coil-only tests to no
greater than 2.0 square inches per British thermal unit per hour
(sq.in./Btu/hr). NGIFS is equal to total fin surface multiplied by the
number of fins and divided by system capacity. 81 FR at 58177 (Aug. 24,
2016)
In the August 2016 Public Meeting, Ingersoll Rand commented that it
did a rough calculation for a micro channel heat exchanger and
determined the NGIFS to be 0.81. Ingersoll Rand commented that this
indicates that there are problems with looking at today's technology
and coming up with a value for NGIFS. Ingersoll Rand further commented
that in coming up with a value for NGIFS, it needs to be ensured that
doing so does not create issues or loopholes. (Ingersoll Rand, Public
Meeting Transcript, No. 20 at p. 45) Rheem commented that there needs
to be further study on the 2.0 value of NGIFS before making a decision
in order to not limit future efficiencies. (Rheem, Public Meeting
Transcript, No. 20 at p. 46) Carrier/UTC similarly commented that there
may be unforeseen consequences of limiting design options that
manufacturers will have to comply with the efficiency standards.
(Carrier/UTC, Public Meeting Transcript, No. 20 at pp. 47-48) Rheem
also commented that due to the complexity of the issue, the NGIFS
criteria should go in appendix M1, not in appendix M. (Rheem, Public
Meeting Transcript, No. 20 at p. 46) Johnson Controls commented that
units that are above 2.0 today would need to be retested, and the
ratings for these units would most likely change. JCI commented that
for this reason, they believe that the proposal for NGIFS belongs in
appendix M1, not in appendix M. (JCI, Public Meeting Transcript, No. 20
at pp. 50-51) Allied commented that the values that DOE is proposing
are reasonable, but that there are further considerations associated
with the different technologies that apply. Allied also commented that,
based on their review, future standard levels could be even more
stringent and still allow some latitude in design approaches. (Allied,
Public Meeting Transcript, No. 20 at pp. 49-50) JCI also commented that
usually normalized values do not have dimensions and questioned whether
the proposal takes into account fin and tube spacing. (JCI, Public
Meeting Transcript, No. 20 at pp. 56-59)
Nortek and AHRI opposed DOE's proposal and commented that DOE does
not have the authority to regulate the design of residential central
air-conditioners and heat pumps, so all NGIFS restrictions should be
removed from both appendix M and M1. AHRI commented that AHRI would
like to aid the Department to address this ``golden blower'' issue in a
way which does not put restrictions on design and is both refrigerant
and technology neutral. AHRI proposed to develop a solution within 30
days of the close of the August 2016 SNOPR comment period, but they did
not provide additional input. (Nortek, No. 22 at p. 10; AHRI, No. 27 at
p. 12)
JCI commented that while DOE stated in the SNOPR that the 2.0 limit
of NGIFS does not affect 95% of tested combinations, this also showed
there are current systems that will not be compliant. JCI expressed
concern that if such changes are made to appendix M, standards
adjustments would be required. JCI recommended that DOE limit NGIFS in
M1 only and the DOE recommended value of 2.5 appears to be a valid
target. (JCI, No. 24 at p. 13)
Lennox commented that while it is reasonable to use \3/8\'' round
tube, plate fin coil in the NGIFS definition for outdoor units with no
match, DOE must revise the definition for other split system products
because there are other tube diameters and technologies used across the
industry. Lennox recommended that DOE expand the definition to include
all tube types and fin surfaces. Lennox supported DOE's proposal on the
NGIFS calculation and proposed limit. (Lennox, No. 25 at p. 6-8)
Carrier opposed DOE's proposal to limit NGIFS for the indoor unit and
preferred DOE not restrict design options as that could impact consumer
choices when different refrigerants are used in the future or lessen a
manufacturer's ability to optimize for hot dry climates. Additionally,
Carrier commented that this proposal does not address microchannel
coils or any other coil tube diameter besides \3/8\''. (Carrier, No. 36
at p. 7)
Rheem objects to the limitation of a fixed value for NGIFS and
proposed that indoor coil area should be determined by balancing with
the outside coil area. (Rheem, No. 37 at p. 3-4) Ingersoll Rand opposed
the proposed NGIFS limit because it is only appropriate for 3/8'' tube
coils. Ingersoll Rand commented that it would be better to set a limit
on coil cabinet volume based on coils sold in the 5 years prior to the
elimination of a refrigerant. (Ingersoll Rand, No. 38
[[Page 1443]]
at p. 4) Goodman also expressed concern that this requirement on the
tested combination may inhibit future designs and did not support the
proposed restrictions. Goodman suggested that some requirements in
cabinet width might be appropriate and that DOE and AHRI should work
together to develop a reasonable restriction. (Goodman, No. 39 at p. 7-
8)
ACEEE, NRDC, and ASAP supported DOE's proposal and also suggested
DOE should consider the input of manufacturers who may have a few
models designed for hot, dry climates where the apparent evaporator
surface oversizing can improve rated performance. (ACEEE, NRDC, and
ASAP, No. 33 at p. 6) CA IOU and NEEA agreed with DOE's proposal. (CA
IOU, No. 32 at p. 4; NEEA, No. 35 at p. 3)
In response to JCI, valid normalized values may have units. For
example, energy efficiency ratio is a normalized value representing
capacity per electric power input with units of British thermal units
(Btu) per Watt-hour (Btu/W-h). Additionally, the NGIFS does take into
consideration the fin spacing--the number of fins, Nf, is a
parameter in the equation to determine NGIFS. As an example, consider
two indoor coils with the same finned length--the coil with the higher
fin density will have more fins and thus a higher NGIFS. It is true,
however, that NGIFS does not include the impact of tube spacing.
Addressing the Ingersoll Rand and Allied comments, DOE acknowledges
that NGIFS does not provide as good a representation of the heat
transfer performance of microchannel indoor coils as that of
conventional tube-fin indoor coils, and the development of an
appropriate equivalent value for this newer technology will be
important in order to prevent loopholes in the requirement. However,
DOE is not aware of any significant current market share of systems
using microchannel indoor coils, and so good information to use as the
basis for development of NGIFS limits for this technology is not yet
available. Further, the likely lower value of NGIFS for microchannel
coils will mean that imposing a limit based on conventional coil
technology would not limit use of microchannel coils before a better
approach is developed. DOE has not developed an appropriate approach at
the moment, but could consider adopting an NGIFS approach for
microchannel indoor coils in a future rulemaking.
Because DOE's NGIFS analysis for coil-only systems does not
consider tube diameters other than \3/8\ inches and fin types other
than plate fins, as well as the units currently on the market that
would not meet the 2.0 NGIFS limit (e.g. as indicated by the JCI
comment), the proposed approach does not resolve DOE's concern while
maintaining a reasonable test procedure for units with different
designs. Accordingly, DOE is not adopting the NGIFS requirement in this
final rule for either appendix M or appendix M1. DOE will consider how
best to address this issue in the future.
7. Modification to the Test Procedure for Variable-Speed Heat Pumps
The August 2016 SNOPR proposed changes to the test procedure of
appendix M for variable-speed heat pumps to allow more flexibility in
the design and testing of these products. 81 FR at 58177-79 (Aug. 24,
2016). The June 2016 final rule imposed restrictions on the compressor
speeds that could be used in testing, indicating that full speed must
be the same speed for all heating mode operating conditions. DOE
adopted this approach based on the observation that extrapolation of
performance outside of the range of conditions used for testing can
lead to unreasonable results if the speeds are allowed to be different
for the different test conditions. 81 FR at 37029 (June 8, 2016).
However, the final rule discussed stakeholder comments regarding heat
pumps that improve heating mode performance by using different
compressor speeds at lower ambient temperatures, and indicated that
consideration would be given in the future to test procedure revisions
that would better address their operation. Id. In the August SNOPR, DOE
proposed a test procedure revision that would allow testing of heat
pumps whose compressors operate at higher speeds in lower ambient
temperatures. 81 FR at 58177-58179 (Aug. 24, 2016). Specifically, DOE
proposed the following amendments for appendix M.
A 47[emsp14][deg]F full-speed test used to represent the
heating capacity would be required and designated as H1N.
However, the 47[emsp14][deg]F full-speed test would not have to be
conducted using the same compressor speed (determined based on
revolutions per minute (RPM) or power input frequency) as the full-
speed tests conducted at 17[emsp14][deg]F and 35[emsp14][deg]F ambient
temperatures, nor at the same compressor speeds used for the full-speed
cooling test conducted at 95[emsp14][deg]F. For appendix M, the
compressor speed for the 47[emsp14][deg]F full-speed test would be at
the manufacturer's discretion, except that it would have to be no lower
than the speed used in the 95[emsp14][deg]F full-speed cooling test.
Prior to the June 2016 final rule amendments, the heating capacity was
represented either by the H12 test (for which the compressor
speed guidance was not explicit), or, if a manufacturer chose to
conduct what was then the optional H1N test, this latter
test (using the same compressor speed as the full-speed cooling mode
test) represented the heating capacity. Under the proposal in the
August SNOPR, heating capacity would be represented only by the
H1N test, which would be mandatory, while the compressor
speed would be at the manufacturer's discretion within a range from the
speed used for the 95[emsp14][deg]F full-speed cooling test to the
speed used for the full-speed 17[emsp14][deg]F test.
The full-speed tests conducted at 17[emsp14][deg]F and
35[emsp14][deg]F ambient temperatures would still have to use the same
speed, which would be the maximum speed at which the system controls
would operate the compressor in normal operation in a 17[emsp14][deg]F
ambient temperature, although the 35[emsp14][deg]F full-speed test
would remain optional.
It would be optional to conduct a second full-speed test
at 47[emsp14][deg]F ambient temperature at the same compressor speed as
used for the 17[emsp14][deg]F test, if this speed is higher than the
speed used for the H1N test described in this preamble. This
test would be designated the H12 test. Because DOE does not
expect that an H1N test would ever use a higher compressor
speed than used for the full-speed 17[emsp14][deg]F test, the proposed
test procedure would not provide for this situation.
If no 47[emsp14][deg]F full-speed test were conducted at
the same speed as used for the 17[emsp14][deg]F full-speed test,
standardized slope factors for capacity and power input would be used
to estimate the performance of the heat pump for the 47[emsp14][deg]F
full-speed test point for the purpose of calculating HSPF.
The capacity measured for the H1N test would be
used in the calculation to determine the design heating requirement.
In addition, DOE proposed that the H1N test, at
47[emsp14][deg]F ambient temperature, be conducted to represent nominal
heat pump heating capacity, but that there would be no specific
compressor speed requirement associated with it for appendix M, except
that it be no lower than the speed used for the 95[emsp14][deg]F full-
speed cooling test. Under the proposal, if the H1N test did
not use the same speed as is used for the 17[emsp14][deg]F full-speed
heating test, it would affect the HSPF calculation only through its
influence on the design heating requirement, since the standardized
slope factors would be used to represent full-speed heat pump
performance. 81 FR at 58179 (Aug. 24, 2016)
[[Page 1444]]
A number of manufacturers and AHRI recommended the proposed changes
should be part of appendix M1 rather than appendix M. (Rheem, Public
Meeting Transcript, No. 20 at pp. 54-55; Rheem, No. 37 at p. 4;
Carrier, No. 36 at p. 2; Nortek, No. 22 at p. 11; AHRI, No. 27 at p.
13; Mitsubishi, No. 29 at p. 2-3) Carrier commented at the public
meeting that the proposals may be good, but that there had not been
sufficient time to thoroughly review them, adding that a key concern is
avoiding any potential need to retest products. (Carrier/UTC, Public
Meeting Transcript, No. 20 at pp. 55). Unico recommended moving the
slope factor change and the proposal for compressor speed at
47[emsp14][deg]F test to appendix M1. (Unico, No. 30 at p. 4)
JCI recommended the proposal that the H12 test be
conducted at maximum speed should be made optional, and the use of
slope factors should be permitted if the test is not run. JCI commented
that the standardized slope factors predict performance fairly closely,
but can lower the HSPF by as much as 0.5 HSPF, and requested to move
this change to M1. Additionally, JCI objected to DOE's proposal on
H1N test and commented that if a manufacturer wishes to rate
the heating capacity of their units at 47[emsp14][deg]F at a speed
above the A2 speed, they should be permitted to do so. (JCI,
No. 24 at p. 14)
Goodman supported DOE's proposal to require a full-speed test at
47[emsp14][deg]F to be designated H1N. However, Goodman does
not support the proposal to mandate that the compressor speed for this
test be equal to or higher than the cooling full compressor speed. In
addition, although Goodman generally supported DOE's proposal regarding
the standardized slope factors to be used if no 47[emsp14][deg]F test
is run using the same compressor speed as the H32 test,
Goodman commented that the datasets DOE's contractor have used to set
the standardized slopes are not appropriate. According to Goodman,
developing ratios of capacity based on certified heating capacities can
lead to errors because ratings might be conservative. Further, Goodman
asserted that it would be possible for models to be counted more than
once, or that a limited number of an appropriate cross section of
representative models would be included. Additionally, according to
Goodman, varying technologies could have different slopes. Goodman
suggested that DOE work with AHRI and manufacturers to review real test
data. Goodman also supported the optional 5[emsp14][deg]F test and
suggested DOE to take a further step to provide an optional
5[emsp14][deg]F test for two-speed and single-speed heat pumps.
(Goodman, No. 39 at p. 5-7)
AHRI suggested that a test procedure similar to triple-capacity
heat pumps should be made an optional procedure for variable-speed heat
pumps. (AHRI, No. 27 at p. 13)
EEI strongly recommended that the 5[emsp14][deg]F test and any
additional considered test should remain optional. EEI also suggested
that DOE should require tests and information be published for all
furnaces and boilers at the same temperatures as for heat pumps. (EEI,
No. 34 at p. 2)
Carrier supported DOE's modification to allow the H1N
speed to be any speed between the 17[emsp14][deg]F full heating speed
and 95[emsp14][deg]F full cooling speed. (Carrier, No. 36 at p. 8)
Lennox, ACEEE, NRDC, and ASAP, and NEEA supported DOE's proposals
for revising the variable-speed heat pump test methods in appendix M.
(Lennox, No. 25 at p. 13; ACEEE, NRDC, and ASAP, No. 33 at p. 7; NEEA,
No. 35 at p. 3)
DOE considered the requests to move the proposed variable-speed
heat pump test method amendments to appendix M1 and other detailed
comments regarding specific aspects of the amendments. DOE revised part
of its proposal as discussed later in this section. DOE's intention
with the changes to the variable-speed heat pump test procedure of
appendix M was to allow the tests conducted previously (i.e., prior to
the effective date of the June 2016 final rule) to still be used to
represent heat pump performance, while preventing use of extrapolation
of the performance below 17[emsp14][deg]F using the results of tests
conducted at different speeds at 17[emsp14][deg]F and 47[emsp14][deg]F.
For this reason, DOE is not finalizing some aspects of its proposal for
appendix M, and instead is finalizing them only for appendix M1.
DOE believes that the standardized slope factors (or use of same-
speed tests, if a manufacturer does prefer to retest rather than use
the standardized slope factors) would provide more accurate
representation of heat pump performance. As discussed in section
III.B.3, pursuant to 42 U.S.C. 6293(e), DOE is required to determine to
what extent, if any, the proposed test procedure would alter the
measured efficiency of the covered product. DOE proposed changes to
heating mode test procedure for variable speed units only. For single-
speed and two-speed products there would be no change in measured
efficiency because they would not be impacted by this change in test
procedure. However, variable-speed products would be impacted by this
change in test procedure, so the measured efficiency may change.
Where an amended test procedure would alter measured efficiency,
EPCA requires DOE to amend an energy conservation standard by
measuring, under the amended test procedure, a sample of representative
products that minimally comply with the standard. In this case,
minimally compliant units are those with single-speed technology.
Consistent with the statute, DOE has tested a representative sample of
covered products that minimally comply with the existing standard. EPCA
requires that the amended standard should constitute the average of the
energy efficiency of those units, determined under the amended test
procedure. As a result of that testing, DOE has determined that there
is no change in measured average energy efficiency for single-speed
units between the current test procedure and the amended test
procedure. Thus, under 42 U.S.C. 6293(e)(2), the amended standard
applicable to the amended test procedure and the current standard
applicable to the amended test procedure are the same. As a result, DOE
does not need to amend the existing standard to require representations
of variable-speed heat pumps to be based on the amended test procedure
in appendix M. Therefore, DOE is finalizing aspects of its proposal for
appendix M, including the use of standardized slope factors, which
might require recalculation of HSPF for variable-speed unit.
DOE believes that Unico's comment about the ``changing the slope
factors'' may have been a comment regarding the heating load line
equation slope factor rather than the standardized slope factors
associated with the appendix M variable speed heat pump proposal. If
so, the change was proposed only for appendix M1. If not, DOE's
discussion regarding the standardized slope factors in the above
paragraph responds to Unico's comment.
Based on the comments received, DOE concluded that the proposal
details that commenters believed would lead to a need to retest are (a)
requiring the compressor speed for the H32 and
H22 tests to be the maximum speed at which the system
controls would operate the compressor in normal operation in a
17[emsp14][deg]F ambient temperature, and (b) requiring the compressor
speed for the H1N test to be no lower than the for the
A2 test.
To resolve the first of these issues, DOE is adopting this
requirement in appendix M1, but not appendix M. However, for appendix
M, DOE is amending the proposal to require that
[[Page 1445]]
the compressor speeds used for the H32 and H22
tests be the same (if the optional H22 test is conducted),
and will require that the compressor frequency that corresponds to
maximum speed at which the system controls would operate the compressor
in normal operation in a 17[emsp14][deg]F ambient temperature be
provided in the certification reports. However, DOE will not post this
information to DOE's public certification database. DOE has added this
reporting requirement in 10 CFR 429.16(e).
To resolve the second issue, DOE is revising its proposal to allow
the compressor speed used for the H1N test to be lower than
used for the A2 test, provided that the H1N
capacity is no lower than the A2 cooling capacity. Goodman's
comment regarding this issue states that it is normally the case that
products on the market today have heating full compressor speed equal
to or higher than the cooling full compressor speed, but Goodman
believes this does not necessarily have to be the case. (Goodman, No.
39 at p. 6) While DOE agrees that such a possibility could exist, this
is not a very strong statement regarding the existence of heat pumps
with lower heating speed. Goodman's comment continues with an
explanation that achieving roughly equivalent capacity in heating mode
at 47[emsp14][deg]F as in cooling mode at 95[emsp14][deg]F would likely
provide better performance at lower ambient temperatures. Id. These
statements suggest that a reasonable compromise would be to allow lower
H1N speed than A2 speed as long as the
H1N capacity is no lower, which is the approach that DOE has
adopted in this final rule.
Similarly, JCI's comment that the compressor speed for the
H1N test be allowed to be higher than the A2
speed is consistent with the previously-stated approach that DOE is
adopting in this final rule.
As for Goodman's suggestion regarding an optional 5[emsp14][deg]F
test for two-speed and single-speed heat pumps, DOE discusses this in
section III.C.4, as part of its discussion of amendments to appendix
M1.
With regard to AHRI's suggestion to add an optional test procedure
for variable-speed heat pumps that is similar to the test for triple-
capacity heat pumps, DOE considered this suggestion, but is declining
to adopt these optional tests in this final rule because stakeholders
have not been given an opportunity to comment on them. However, DOE may
consider such an option in the future. In response to EEI's comment on
making the proposed 5[emsp14][deg]F test and any additional test points
optional, DOE notes that it has not proposed nor adopted any new
heating mode tests for heat pumps that are not optional, either in the
June 2016 final rule, the August 2016 SNOPR, or this rulemaking.
In response to JCI's comment that conducting the H12
test at maximum speed should be made optional, DOE notes that this was
optional as proposed and is optional in the test procedure adopted in
this final rule.
In response to Goodman's comment about rigorous review of test data
to develop the standardized slope factors, DOE requested data or
suggestions regarding how they should be changed. 81 FR at 58179 (Aug.
24, 2016). However, such data were not provided. DOE notes that the
standardized slope factors, which DOE derived from different data
sources, some of which must have represented test data, were remarkably
consistent. Further, if capacities reported for both 17[emsp14][deg]F
and 47[emsp14][deg]F test points are conservative, it is not clear that
there would be a dramatic difference in the calculated slope.
Therefore, DOE has adopted the standardized slope factors proposed in
the August 2015 SNOPR.
Regarding EEI's comment that furnace performance should be provided
at the same temperatures and for at least two temperatures for both
furnaces and CAC/HP, DOE is reluctant to impose that additional
reporting burden at this time. The capacity and steady-state efficiency
for furnaces does not vary significantly as a function of outdoor
temperature. Thus, DOE is not convinced that the additional information
would be of significant value to consumers.
8. Clarification of the Requirements of Break-In Periods Prior to
Testing
In the August 2016 SNOPR, DOE proposed modifications to the test
procedure to clarify the use of break-in, generalizing the requirement
so that it applies regardless of who conducts the test, indicating that
the break-in requirement applies for each compressor of the unit, and
clarifying that the compressor(s) must undergo the certified break-in
period (which may not exceed 20 hours) prior to any test period used to
measure performance. 81 FR at 58179 (Aug. 24, 2016)
During the August 2016 Public Meeting, Ingersoll Rand commented
that DOE's proposed rule was unclear about whether a compressor change-
out is required if the compressor of a unit operates longer than the
certified break-in period during product development or operation
associated with test set-up prior to making the first measurement used
to determine an efficiency representation. (Ingersoll Rand, Public
Meeting Transcript, No. 20 at pp. 27-29).
Many stakeholders commented that changing out compressors during
testing is a significant burden. Nortek suggested that DOE extend the
break-in period to 50 hours and allow the break-in to be conducted at
ambient conditions. (Nortek, No. 22 at p. 11) ADP and Lennox commented
that the 20 hour maximum should remain in place for any verification,
enforcement or other non-development testing. ADP also suggested that
the break-in period should be part of the public product-specific
information so that ICMs can use this information for more accurate
AEDM ratings. (ADP, No. 23 at p. 4; Lennox, No. 25 at p. 13) JCI
suggested DOE allow up to 72 hours of break-in time and recommended
allowing break ins to be conducted before installing the compressor in
the unit, or to break in a system outside of the test cell. (JCI, No.
24 at p. 14) AHRI provided data from two compressor manufacturers and
suggested DOE extend the allowed break-in period to 72 hours and permit
the break-in to be conducted at ambient conditions. Rheem supported
AHRI. (AHRI, No. 27 at p. 13-15; Rheem, No. 37 at p. 4) Unico supported
a 72-hour minimum break-in period and commented that it is easy to run
the unit outside the test chamber. (Unico, No. 30 at p. 5) Emerson
commented that longer break-in will ensure repeatability and improve
stability of compressor performance. Emerson also included data for
several compressors. (Emerson, No. 31 at pp. 1-2) Carrier suggested
that DOE allow a 72-hour break-in period and allow break in outside of
test chamber while running tests on other units. (Carrier, No. 36 at p.
8-9) Ingersoll Rand, Goodman and the Joint Advocates commented that
there is no technical reason to establish an upper limit for break-in.
Goodman suggested to permit 72 hours of break-in. (Ingersoll Rand, No.
38 at p. 4; Goodman, No. 39 at p. 8-9; Joint Advocates, No. 33 at p.7)
NEEA supported DOE's proposed modification of the test procedure.
(NEEA, No. 35 at p. 3)
DOE does not intend to require a compressor change-out in the
development test. Rather, the establishment of the 20-hour limit is to
maintain test repeatability among labs regardless of who conducts the
test. DOE notes that there is no requirement in the test procedure that
the break-in has to be conducted in the psychrometric chamber, so
manufacturers and technicians have an option, if needed, as to where
break-in
[[Page 1446]]
is conducted. Finally, DOE adopted the 20-hour break-in limit in the
June 2016 Final Rule, and the proposal in the August 2016 SNOPR was
intended to clarify how this requirement applies for manufacturers and
third party testing. Accordingly, DOE will not change the 20-hour limit
in this final rule.
In response to ADP's comments, DOE will discuss concerns about
reporting requirements for ICMs through a separate process.
9. Modification to the Part Load Testing Requirement of VRF Multi-Split
Systems
In the August 2016 SNOPR, DOE proposed to remove the 5 percent
tolerance for part load operation from section 2.2.3.a of appendix M
when comparing the sum of nominal capacities of the indoor units and
the intended system part load capacity for VRF multi-split units. 81 FR
at 58179 (Aug. 24, 2016)
DOE received no objections on this proposal, and adopts it in this
final rule.
10. Modification to the Test Unit Installation Requirement of Cased
Coil Insulation and Sealing
In the August 2016 SNOPR, DOE proposed to remove the statement
about insulating or sealing cased coils from appendix M, section 2.2.c,
in order to avoid confusion regarding whether sealing of duct
connections is allowed. 81 FR at 58180 (Aug. 24, 2016)
DOE received no objections on this proposal, and adopts it in this
final rule.
11. Correction for the Calculation of the Low-Temperature Cut-Out
Factor for Single-Speed Compressor Systems
Equation 4.2.1-3 in section 4.2.1 of appendix M, used for
calculating the low-temperature cut-out factor for a blower coil system
heat pump having a single-speed compressor and either a fixed-speed
indoor blower or a constant-air-volume-rate indoor blower, or for a
single-speed coil-only system heat pump, was incorrectly modified in
the June 2016 final rule, in that the ``or'' initially in the equation
was changed to an ``and''. 81 FR at 37107 (June 8, 2016). DOE was
alerted to this issue in comments received in response to the notice of
data availability (NODA) associated with the CAC/HP energy conservation
standard rulemaking published October 27, 2016. 81 FR 74727. (Docket
Number EERE-2014-BT-STD-0048, AHRI, No. 94 at p. 2; Unico, No. 95 at p.
1) The equation originally used ``or''. This modification could have
changed the range of temperature bins for which it is assumed that the
heat pump function has cut out. DOE has corrected this issue in this
rulemaking in appendix M and also has adopted the correct equation in
appendix M1.
12. Clarification of the Refrigerant Liquid Line Insulation
In the June 2016 Final Rule, DOE adopted clarifications for
insulation requirements for the refrigerant lines in section 2.2(a) of
appendix M. 81 FR at 37027 (June 8, 2016). In some cases, these
requirements may indicate that the refrigerant lines should be
uninsulated, exposed to the air. However, DOE notes that this
requirement is not appropriate to apply for every inch of refrigerant
line, particularly where it would conflict with the requirements in
ASHRAE 41.1-1986 (RA 2006) (referenced in section 5.1.1 of ASHRAE 37-
2009, which is incorporated by reference, see Sec. 430.3). ASHRAE
41.1-1986 (RA 2006) requires in sections 8.2 and 8.3 that it is
acceptable to use surface temperature measurement for the refrigerant
liquid temperature, but that insulating material extending to at least
6 in. on each side of a surface temperature-measuring element should be
installed on the line. The liquid temperature measurement may be
essential, e.g. when the refrigerant enthalpy method is used as the
secondary method (see section 2.10.3 of appendix M). Therefore, DOE has
decided to clarify in the test procedure (in both appendices M and M1)
that the refrigerant insulation requirement in section 2.2(a) does not
apply for portions of the lines insulated according to the ASHRAE 41.1-
1986 (RA 2006) requirements for temperature measurement.
Because this clarification simply addresses DOE's intention on how
to correctly conduct the test procedure, DOE finds that there is good
cause under 5 U.S.C. 553(b)(B) to not issue a separate notice to
solicit public comment on this change.
C. Amendments to Appendix M1
The November 2015 SNOPR proposed to establish a new appendix M1 to
Subpart B of 10 CFR part 430, which would be required to demonstrate
compliance with any new energy conservation standards. 80 FR at 69397
(Nov. 9, 2015) In the August SNOPR, DOE continued to propose
establishing a new appendix M1. Under DOE's proposal, the appendix
would include all of the test procedure provisions in appendix M as
finalized in the June 2016 final rule, all of the changes to appendix M
that are finalized in this rulemaking as discussed in section III.B,
and all of the additional changes discussed in this section III.C,
which would be included only in the new appendix M1. DOE proposed to
make appendix M1 mandatory for representations of efficiency starting
on the compliance date of any amended energy conservation standards for
CAC/HP (however, note the phase-in of testing requirements for certain
proposed new requirements for split systems discussed in section
III.A.1).
1. Minimum External Static Pressure Requirements
Most of the residential central air conditioners and heat pumps in
the United States use ductwork to distribute air in a residence, using
either a fan inside the indoor unit or housed in a separate component,
such as a furnace, to move the air. External static pressure (ESP) for
a CAC/HP is the static pressure rise between the inlet and outlet of
the indoor unit that is needed to overcome frictional losses in the
ductwork. The external static pressure imposed by the ductwork affects
the power consumed by the indoor fan, and therefore also affects the
SEER and/or HSPF of a CAC/HP.
a. Conventional Central Air Conditioners and Heat Pumps
The current DOE test procedure \11\ stipulates that certification
tests for ``conventional'' CACs and heat pump blower coil systems
(i.e., CACs and heat pump blower coil systems which are not small-duct,
high-velocity systems) must be performed with an external static
pressure at or above 0.10 in. wc. if cooling capacity is rated at
28,800 Btu/h or less; at or above 0.15 in. wc. if cooling capacity is
rated from 29,000 Btu/h to 42,500 Btu/h; and at or above 0.20 in. wc.
if cooling capacity is rated at 43,000 Btu/h or more.
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\11\ Table 3 of 10 CFR part 430 subpart B appendix M.
---------------------------------------------------------------------------
DOE did not propose revisions to minimum external static pressure
requirements for conventional blower coil systems in the June 2010 test
procedure NOPR, stating that new values and a consensus standard were
not readily available.\12\ 75 FR 13223, 31228 (June 2, 2010). However,
between the June 2010 test procedure NOPR and the November 2015 test
procedure SNOPR, many stakeholders submitted comments citing data that
suggested the minimum external static pressure requirements were too
low and a value
[[Page 1447]]
of 0.50 in. wc. would be more representative of field conditions. These
comments are summarized in the November 2015 test procedure SNOPR. 80
FR at 69317-69318 (Nov. 9, 2015). Ultimately, in the November 2015
SNOPR, DOE proposed to adopt, for inclusion into 10 CFR part 430,
subpart B, appendix M1, for systems other than multi-split systems and
small-duct, high-velocity systems, minimum external static pressure
requirements of 0.45 in. wc. for units with a rated cooling capacity of
28,800 Btu/h or less; 0.50 in. wc. for units with a rated cooling
capacity from 29,000 Btu/h to 42,500 Btu/h; and 0.55 in. wc. for units
with a rated cooling capacity of 43,000 Btu/h or more. DOE reviewed
available field data to determine the external static pressure values
it proposed in the November 2015 test procedure SNOPR. DOE gathered
field studies and research reports, where publically available, to
estimate field external static pressures. DOE previously reviewed most
of these studies when developing test requirements for furnace fans.
The 20 studies, published from 1995 to 2007, provided 1,010 assessments
of location and construction characteristics of CAC and/or heat pump
systems in residences, with the data collected varying by location,
representation of system static pressure measurements, equipment's age,
ductwork arrangement, and air-tightness.\13\ 79 FR 500 (Jan. 3, 2014).
DOE also gathered data and conducted analyses to quantify the pressure
drops associated with indoor coil and filter foulants.\14\ The November
2015 test procedure SNOPR provides a detailed overview of the analysis
approach DOE used to determine an appropriate external static pressure
value using these data. 80 FR at 69318-69319 (Nov. 9, 2015). DOE did
not consider revising the minimum external static pressure requirements
for SDHV systems in the November 2015 test procedure SNOPR. DOE did,
however, propose to establish a new category of ducted systems, short
duct systems, which would have lower external static pressure
requirements for testing. DOE proposed to define ``short duct system''
to mean ducted systems whose indoor units can deliver no more than 0.07
in. wc. external static pressure when delivering the full load air
volume rate for cooling operation. 80 FR at 69314. DOE proposed in the
November 2015 SNOPR to require short duct systems to be tested using
the minimum external static pressure previously proposed in the June
2010 NOPR for ``multi-split'' systems: 0.03 in. wc. for units less than
28,800 Btu/h; 0.05 in. wc. for units between 29,000 Btu/h and 42,500
Btu/h; and 0.07 in. wc. for units greater than 43,000 Btu/h. 75 FR at
31232 (June 2, 2010)
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\12\ In the June 2010 NOPR, DOE proposed lower minimum ESP
requirements for ducted multi-split systems: 0.03 in. wc. for units
less than 28,800 Btu/h; 0.05 in. wc. for units between 29,000 Btu/h
and 42,500 Btu/h; and 0.07 in. wc. for units greater than 43,000
Btu/h. 75 FR at 31232 (June 2, 2010).
\13\ DOE has included a list of citations for these studies in
the docket for the furnace fan test procedure rulemaking. The docket
number for the furnace fan test procedure rulemaking is EERE-2010-
BT-TP-0010.
\14\ Siegel, J., Walker, I., and Sherman, M. 2002. ``Dirty Air
Conditioners: Energy Implications of Coil Fouling'' Lawrence
Berkeley National Laboratory report, number LBNL-49757.
ACCA. 1995. Manual D: Duct Systems. Washington, DC, Air
Conditioning Contractors of America.
Parker, D.S., J.R. Sherwin, et al. 1997. ``Impact of evaporator
coil airflow in air conditioning systems'' ASHRAE Transactions
103(2): 395-405.
---------------------------------------------------------------------------
In response to the November 2015 SNOPR, the CAC/HP ECS Working
Group members weighed in on appropriate minimum external static
pressure requirements. (CAC ECS: CAC/HP ECS Working Group meeting, No.
86 at pp. 31-128) Recommendation #2 of the CAC/HP ECS Working Group
Term Sheet states that the minimum required external static pressure
for CAC/HP blower coil systems other than mobile home systems, ceiling-
mount and wall-mount systems, low and mid-static multi-split systems,
space-constrained systems, and small-duct, high-velocity systems should
be 0.50 in. wc. for all capacities. (CAC ECS: ASRAC Term Sheet, No. 76
at p. 2)
In the August 2016 SNOPR, DOE proposed to adopt a minimum external
static pressure requirement of 0.50 in. wc. for systems other than
mobile home, ceiling-mount and wall-mount systems, low and mid-static
multi-split systems, space-constrained systems, and small-duct, high-
velocity systems based on DOE's analysis and consistent with the CAC/HP
ECS Working Group Term Sheet. 81 FR at 58181 (Aug. 24, 2016)
During the August 2016 SNOPR public meeting and in written
comments, many stakeholders expressed support for the new minimum
external static requirements that DOE proposed. JCI, Goodman, Unico,
AHRI, NEEA, Carrier/UTC, Lennox, Ingersoll Rand, and Nortek expressed
support for DOE's proposal to require conventional systems to be tested
at a minimum external static pressure of 0.5 in. wc. consistent with
Recommendation #2 of the Term Sheet. (JCI, No. 24 at p. 15; Goodman,
No. 39 at p. 13; Unico, No. 30 at p. 6; AHRI, No. 27 at p. 16; NEEA,
No. 35 at p. 3; Carrier/UTC, No. 36 at p. 9; Lennox, No. 25 at p. 10;
Ingersoll Rand, No. 38 at p. 5; Nortek, No. 22 at p. 11)
In light of DOE's analysis results, the Term Sheet recommendation,
and support expressed in written comments, DOE is adopting a minimum
external static pressure of 0.50 in. wc. for all capacities of
conventional CAC/HP products in this final rule.
b. Non-Conventional Central Air Conditioners and Heat Pumps
In response to the November 2015 SNOPR and during the CAC/HP ECS
Working Group negotiations, DOE also received comment regarding the
minimum external static pressure requirements for mobile home systems,
ceiling-mount and wall-mount systems, low and mid-static multi-split
systems, space-constrained systems, and small-duct, high-velocity
systems. 81 FR at 58181 (Aug. 24, 2016). The CAC/HP ECS Working Group
included in its Final Term Sheet Recommendation #2, which is summarized
in Table III-2. (CAC ECS: ASRAC Term Sheet, No. 76 at p. 2)
Table III-2--CAC/HP ECS Working Group Recommended Minimum External
Static Static Pressure Requirement
------------------------------------------------------------------------
Minimum external static
Product description pressure (in. wc.)
------------------------------------------------------------------------
All central air conditioners and heat pumps 0.50.
except (2)-(7) below.
(2) Ceiling-mount and Wall-mount Blower Coil TBD by DOE.
System.
(3) Manufactured Housing Air Conditioner Coil 0.30.
System.
(4) Low-Static System.......................... 0.10.
[[Page 1448]]
(5) Mid-Static System.......................... 0.30.
(6) Small Duct, High Velocity System........... 1.15.
(7) Space-Constrained.......................... 0.30.
------------------------------------------------------------------------
Recommendation #1 of the CAC/HP ECS Working Group included
suggested definitions for distinguishing the CAC/HP varieties included
in Recommendation #2 (Table III-2) to enable the proper administration
of the CAC/HP ECS Working Group's recommended minimum external static
pressure requirements.
DOE agrees with the intent of Recommendation #1 and #2 of the CAC/
HP ECS Working Group Term Sheet because DOE recognizes that the CAC/HP
varieties included in these recommendations have unique installation
characteristics that result in different field external static pressure
conditions, and in turn, indoor fan power consumption in the field.
Consequently, in the August 2016 test procedure SNOPR, DOE proposed to
adopt definitions similar to those that the CAC/HP ECS Working Group
recommended for space-constrained systems, low-static systems, and mid-
static systems, as well as the recommended minimum external static
pressure requirements for those products, to be more reflective of
field conditions.
In the August 2016 SNOPR, DOE proposed to adopt the following
definitions for the CAC/HP varieties included in Recommendations #1 and
#2 in the CAC/HP ECS Working Group Term Sheet, which are slightly
modified versions of those suggested in the Term Sheet, but reflect the
same intent:
Ceiling-mount blower coil system means a split system for
which the outdoor unit has a certified cooling capacity less than or
equal to 36,000 Btu/h and the indoor unit is shipped with manufacturer-
supplied installation instructions that specify to secure the indoor
unit only to the ceiling of the conditioned space, with return air
directly to the bottom of the unit (without ductwork), having an
installed height no more than 12 inches (not including condensate drain
lines) and depth (in the direction of airflow) of no more than 30
inches, with supply air discharged horizontally.
Low-static blower coil system means a ducted multi-split
or multi-head mini-split system for which all indoor units produce
greater than 0.01 in. wc. and a maximum of 0.35 in. wc. external static
pressure when operated at the cooling full-load air volume rate not
exceeding 400 cfm per rated ton of cooling.
Mid-static blower coil system means a ducted multi-split
or multi-head mini-split system for which all indoor units produce
greater than 0.20 in. wc. and a maximum of 0.65 in. wc. when operated
at the cooling full-load air volume rate not exceeding 400 cfm per
rated ton of cooling.
Mobile home blower coil system means a split system that
contains an outdoor unit and an indoor unit that meet the following
criteria: (1) Both the indoor and outdoor unit are shipped with
manufacturer-supplied installation instructions that specify
installation only in a mobile home with the home and equipment
complying with HUD Manufactured Home Construction Safety Standard 24
CFR part 3280; (2) the indoor unit cannot exceed 0.40 in. wc. when
operated at the cooling full-load air volume rate not exceeding 400 cfm
per rated ton of cooling; and (3) the indoor unit and outdoor unit each
must bear a label in at least \1/4\ inch font that reads ``For
installation only in HUD manufactured home per Construction Safety
Standard 24 CFR part 3280.''
Wall-mount blower coil system means a split-system air
conditioner or heat pump for which the outdoor unit has a certified
cooling capacity less than or equal to 36,000 Btu/h and the indoor unit
is shipped with manufacturer-supplied installation instructions that
specify to secure the back side of the unit only to a wall within the
conditioned space, with the capability of front air return (without
ductwork) and not capable of horizontal airflow, having a height no
more than 45 inches, a depth of no more than 22 inches (including
tubing connections), and a width no more than 24 inches (in the
direction parallel to the wall). 81 FR at 58181-58183 (Aug. 24, 2016)
In response to the August 2016 test procedure SNOPR, NEEA, Lennox,
AHRI, Ingersoll Rand, Goodman, Nortek and UTC/Carrier expressed support
for DOE's proposed minimum external static pressure requirements and
definitions for all product types. (NEEA, No. 35 at p. 3; Lennox, No.
25 at p. 14; AHRI, No. 27 at p. 16; IR, No. 38 at p. 5; Goodman, No. 39
at p. 13; Nortek, No. 22 at p. 12; UTC/Carrier, No. 36 at p. 9)
In written comments, JCI, ADP and First Co. suggested that DOE
modify its proposed definition for wall-mount blower coil system. JCI,
ADP, and First Co. pointed out that these systems have common
installations that do not meet DOE's proposed definition. JCI, ADP and
First Co. stated that wall-mount units are not exclusively installed by
securing the back of the unit to a wall within the conditioned space.
Instead, wall-mount units are often mounted to adjacent wall studs or
within an enclosure (e.g., a closet) such that the front side of the
unit is flush with the wall of the conditioned space. JCI, ADP, and
First Co. recommended that DOE modify the definition of wall-mount
blower coil system to allow for these types of installations. (JCI, No.
24 at p. 15; ADP, No. 23 at pp. 4-5; First Co., No. 21 at p. 4-5) ADP
provided an example installation manual for an ADP wall-mount blower
coil that provided instructions for the installation options mentioned.
ADP suggested adding ``the ability'' and remove ``only'' from the
proposed definition. (ADP, No. 23 at p 4) Mortex echoed ADP's suggested
modifications to DOE's proposed definition for wall-mount blower-coil
systems. (Mortex, No. 26 at p. 4)
DOE recognizes that wall-mount units are often installed as JCI,
ADP, Mortex, and First Co. describe in their comments. In this final
rule, DOE is modifying the definition proposed in the August 2016 test
procedure SNOPR to maintain the intent of the Term Sheet but also allow
for the ``flush-mount'' installations described by JCI, ADP, Mortex and
First Co. DOE is adopting the following modified definition for ``wall-
mount blower coil system'':
[[Page 1449]]
Wall-mount blower coil system means a split-system air conditioner
or heat pump for which (a) the outdoor unit has a certified cooling
capacity less than or equal to 36,000 Btu/h; (b) the indoor unit(s) is/
are shipped with manufacturer-supplied installation instructions that
specify mounting only by (1) securing the back side of the unit to a
wall within the conditioned space, or (2) securing the unit to adjacent
wall studs or in an enclosure, such as a closet, such that the indoor
unit's front face is flush with a wall in the conditioned space; (c)
has front air return without ductwork and is not capable of horizontal
air discharge; and (d) has a height no more than 45 inches, a depth
(perpendicular to the wall) no more than 22 inches (including tubing
connections), and a width no more than 24 inches (parallel to the
wall).
In response to the August 2016 test procedure SNOPR, DOE received
comment on its proposed definition for ceiling-mount blower coil
system. In its comments, First Co. stated that these systems have
common installations that do not meet DOE's proposed definition.
According to First Co., ceiling-mount indoor units are often installed
in a furred down space, which requires that return air comes into the
back of the unit either through a duct or through the furred down
space. DOE understands a furred down space to be an area below ceiling
level that is enclosed and finished (e.g., using drywall and paint).
First Co. also identified another common installation practice for
ceiling-mount indoor units used in applications with dropped ceilings
in which the indoor unit is equipped with an insulated box that is
suspended such that the bottom of the unit is flush with the ceiling
and return air comes into the bottom of the unit. First Co. recommended
modifications to DOE's proposed definition for ceiling-mount blower
coil system to allow for these other common installation types. (First
Co., No. 21 at pp. 4-5)
DOE recognizes that ceiling-mount units are often installed as
First Co. describes. In this final rule, DOE is modifying the
definition proposed in the August 2016 test procedure SNOPR to maintain
the intent of the Term Sheet but also allow for the installations
described by First Co. DOE is adopting the following modified
definition for ``ceiling-mount blower coil system'':
Ceiling-mount blower coil system means a split system for which (a)
the outdoor unit has a certified cooling capacity less than or equal to
36,000 Btu/h; (b) the indoor unit(s) is/are shipped with manufacturer-
supplied installation instructions that specify to secure the indoor
unit only to the ceiling, within a furred-down space, or above a
dropped ceiling of the conditioned space, with return air directly to
the bottom of the unit without ductwork, or through the furred-down
space, or optional insulated return air plenum that is shipped with the
indoor unit; (c) the installed height of the indoor unit is no more
than 12 inches (not including condensate drain lines) and the installed
depth (in the direction of airflow) of the indoor unit is no more than
30 inches; and (d) supply air is discharged horizontally.
The CAC/HP ECS Working Group tasked DOE with determining the
appropriate minimum external static pressure for ceiling-mount and
wall-mount systems. During the CAC/HP ECS Working Group meetings,
manufacturers of these systems suggested a minimum external static
pressure requirement of 0.30 in. wc. (CAC ECS: CAC/HP ECS Working Group
meeting, No. 88 at p. 31) However, the CAC/HP ECS Working Group did not
adopt this as a recommendation primarily due to lack of time to
thoroughly review the subject. In the August 2016 test procedure SNOPR,
DOE proposed to specify a minimum external static pressure requirement
of 0.30 in. wc. for ceiling-mount and wall-mount systems, consistent
with manufacturers' recommendations.
In response to the August 2016 SNOPR, First Co. disagreed with
DOE's proposed minimum external static pressure requirements for
ceiling-mount and wall-mount blower coil systems. First Co. claimed
that the minimum external static pressure requirement for these
products should be no greater than 0.20 in. wc. According to First Co.,
ceiling-mount and wall-mount systems typically use limited length or
short run duct work, which produces lower static pressure. First Co.
contested that 0.30 in. wc. is unreasonably high for representing such
ductwork and that the requirement will result in reductions in product
ratings and negative impacts on small manufacturers and product
availability. (First Co., No. 21 at pp. 3-4) NEEA, Lennox, AHRI,
Ingersoll Rand, Goodman, and UTC/Carrier expressed support for DOE's
proposed minimum external static pressure requirement of 0.30 in. wc.
for these products. (NEEA, No. 35 at p. 3; Lennox, No. 25 at p. 14;
AHRI, No. 27 at p. 16; IR, No. 38 at p. 5; Goodman, No. 39 at p. 13;
UTC/Carrier, No. 36 at p. 9).
DOE recognizes that ceiling-mount and wall-mount systems use
shorter duct runs than conventional systems, which will result in lower
static pressure. For this reason, DOE proposed a lower minimum external
static pressure requirement for these products relative to its proposed
minimum external static pressure requirement for conventional systems.
DOE disagrees with First Co. that 0.30 in. wc. is not representative of
field-installed ceiling-mount and wall-mount systems because
manufacturers of these products recommended 0.30 in. wc. during the
CAC/HP ECS Working Group Negotiations. (Docket EERE-2014-BT-STD-0048,
CAC/HP ASRAC Working Group Meeting, October 13, 2015, No. 88 at p. 21)
In addition, publicly-available product literature for these products
include airflow data tables that include performance at 0.30 in. wc.
(Wall Mount Blower Coil Literature Example, No. 41 at p. 3) DOE
understands that higher minimum external static pressure requirements
will result in reductions to rated performance. These impacts will be
considered and accounted for in the energy conservation standard levels
set by the concurrent energy conservation standard rulemaking.
Therefore, DOE is adopting 0.30 in. wc. as the minimum external static
pressure requirement for ceiling-mount and wall-mount blower coil
systems in this final rule.
Recommendation #2 of the Term Sheet includes a recommended minimum
external static pressure for ``space-constrained'' products. The Term
Sheet does not differentiate between space-constrained outdoor units
paired with conventional indoor units from those paired with non-
conventional indoor units. In the August 2016 SNOPR, DOE proposed that
when space-constrained outdoor units are paired with conventional
indoor units, the minimum external static pressure requirement for
space-constrained systems recommended by the CAC/HP ECS Working Group,
0.30 in. wc., would not be appropriate. Consequently, DOE proposed to
apply the minimum external static pressure requirement included for
space-constrained products in the Term Sheet only to single- package
space-constrained products or space-constrained outdoor units paired
with space-constrained indoor units. 81 FR at 58163, 58182 (Aug. 24,
2016).
In written comments, AHRI and Nortek expressed concern with DOE's
proposal to modify the external static pressure requirements when
space-constrained outdoor units are paired with conventional indoor
units. AHRI and Nortek stated that there is no definition of a ``space-
constrained indoor unit'' (air handler). AHRI and Nortek added that a
space-constrained
[[Page 1450]]
condensing unit rated using a conventional air handler at 0.5 in. wc
would not be able to meet existing efficiency standards. According to
AHRI and Nortek, size restrictions of space-constrained products
require rating with an efficient conventional air handler as a matched
system to meet existing standards. AHRI and Nortek submit that, by
definition, space-constrained condensing units are all under 30,000
Btu/h, with limited applications. AHRI and Nortek concluded that the
minimum external static pressure requirement for space-constrained
systems recommended by the CAC/HP Working Group, 0.30 in. wc., was not
only appropriate for these installations; they are required in order
for manufacturers to offer these niche products, i.e. that DOE should
not require use of 0.5 in. wc. for space-constrained system
combinations using conventional air handlers. (AHRI, No. 27 at pp. 16-
17; Nortek, No. 22 at p. 13).
In response to AHRI's and Nortek's comments, DOE understands that
split-system space-constrained systems that comprise a space-
constrained outdoor unit and conventional indoor unit are typically
installed in homes with size restrictions that are different than homes
in which conventional split-systems (i.e., conventional outdoor and
indoor unit) are typically installed. Space-constrained systems
(regardless of whether paired with a conventional or non-conventional
indoor unit) are more commonly installed in homes in which the system
is installed in closer proximity to the conditioned space. Ductwork is
typically shorter and less restrictive as a result. As such, the CAC/HP
ECS Working Group recommended minimum external static pressure of 0.30
in. wc. is more representative. DOE is adopting 0.30 in. wc. for all
space-constrained products in this final rule. DOE is adopting this
provision because it will result in a test procedure that produces test
results that measure the energy efficiency, energy use, or estimated
annual operating cost of space-constrained products during a
representative average use cycle. DOE is adopting this provision
irrespective of comments regarding its implications on products'
ability to meet standards. DOE will account for impacts to rated values
in the concurrent energy conservation standard rulemaking.
In the August 2016 SNOPR, DOE proposed to adopt the CAC/HP ECS
Working Group recommendations for minimum external static pressure
requirements for low-static and mid-static systems. 81 FR at 58182-
58183 (Aug. 24, 2016).
As mentioned, many stakeholders agreed with DOE's proposed minimum
external static pressures and definitions for all product types. (NEEA,
No. 35 at p. 3; Lennox, No. 25 at p. 14; AHRI, No. 27 at p. 16; IR, No.
38 at p. 5; Goodman, No. 39 at p. 13; Nortek, No. 22 at p. 12; UTC/
Carrier, No. 36 at p. 9) Unico supported DOE's proposal, but voiced one
concern. Unico recommended that DOE eliminate the mid-static product
class, change the range for low static from 0.01 to 0.49 in. wc. so as
not to overlap with the range for normal ducted systems, and to test
those products as low-static (unless DOE would plan to establish a
separate standard for mid-static systems). According to Unico, the mid-
static products would be able to meet the low-static requirements
without difficulty, so Unico would not separate these products into a
separate class. Unico recommended that DOE add a requirement to the
test procedure that both low and mid-static products should be labeled
as ``low static'' with the maximum static clearly written on the
product rating label, so that a manufacturer would be able to list the
mid-static pressure on their literature and labels, while the product
would still considered a low-static system (Unico, No. 30 at p. 5).
DOE does not agree with Unico's recommendation. Based on
discussions during the CAC/HP ASRAC Working Group Negotiations, and as
reflected in the Term Sheet recommendations, DOE understands that there
are ducted multi-split and multi-head mini-split systems that are
designed and installed to produce between 0.20 in. wc. and 0.65 in. wc.
Testing these systems at 0.10 in. wc., as Unico recommends, would not
be representative of field performance because they are typically
installed in more restrictive applications, which results in higher fan
energy consumption. In addition, testing these ``mid-static'' systems,
at the same external static pressure as ``low-static,'' would not
produce results reflective of relative performance. In the field, a
``mid-static'' system, which is typically installed in more restrictive
applications, is expected to have higher fan energy consumption than a
``low-static'' system. Testing both types of systems at the same
external static pressure would ignore this difference and would not
reflect the increased fan energy consumption of the ``mid-static''
system compared to the ``low-static'' system. DOE is not establishing a
separate product class or a separate standard for ``mid-static''
systems, as Unico infers. DOE is only establishing a differing test
conditions for ``low-static'' and ``mid-static'' systems to reflect the
differences in their application and resulting differences in field
performance.
The CAC/HP ECS Working Group did not recommend changing the current
minimum external static pressure required (1.15 in. wc.) for SDHV
systems with a cooling or heating capacity between 29,000 to 42,500
Btu/h. However, the CAC/HP ECS Working Group recommended that 1.15 in.
wc. also be used as the minimum external static pressure requirement
for SDHV systems of all other capacities. Using a single minimum
external static pressure value for all capacities of a given CAC/HP
variety is consistent with the approach recommended by the Working
Group for all CAC/HP varieties. In the August 2016 SNOPR, DOE proposed
to adopt the Working Group recommendation for the minimum external
static pressure requirement for SDHV systems. 81 FR at 58183 (Aug. 24,
2016).
DOE did not receive any negative comments regarding its August 2016
test procedure SNOPR proposed minimum external static pressure
requirements for SHDV systems, and DOE is adopting these requirements
in this final rule.
Table III-3 summarizes the minimum external static pressure
requirements that DOE is adopting in this final rule.
Table III-3--Minimum External Static Pressure Requirements
------------------------------------------------------------------------
Minimum external
CAC/HP variety static pressure (in.
wc.)
------------------------------------------------------------------------
Conventional (i.e., all central air 0.50
conditioners and heat pumps not otherwise
listed in this table).
Ceiling-mount and Wall-mount................... 0.30
Mobile Home.................................... 0.30
[[Page 1451]]
Low-Static..................................... 0.10
Mid-Static..................................... 0.30
Small Duct, High Velocity...................... 1.15
Space-Constrained (indoor and single-package 0.30
units only).
------------------------------------------------------------------------
c. Certification Requirements
In the August 2016 SNOPR, DOE proposed to establish the
certification requirements for appendix M1 to require manufacturers to
certify the kind(s) of CAC/HP associated with the minimum external
static pressure used in testing or rating (i.e., ceiling-mount, wall-
mount, mobile home, low-static, mid-static, small duct high velocity,
space-constrained, or conventional/not otherwise listed). In the case
of mix-match ratings for multi-split, multi-head mini-split, and multi-
circuit systems, manufacturers would be allowed to select two kinds. In
addition, models of outdoor units for which some combinations
distributed in commerce meet the definition for ceiling-mount and wall-
mount blower coil system, would still be required to have at least one
coil-only rating (which uses the 441W/1000 scfm default fan power
value) that is representative of the least efficient coil distributed
in commerce with the particular model of outdoor unit. Mobile home
systems would also be required to have at least one coil-only rating
that is representative of the least efficient coil distributed in
commerce with the particular model of outdoor unit. Further, DOE
proposed to specify a default fan power value of 406W/1000 scfm, rather
than 441W/1000 scfm, for mobile home coil-only systems. Details of this
proposal are discussed in detail in section III.C.2. 81 FR at 58183
(Aug. 24, 2016).
DOE did not receive any comments on the certification requirements
regarding minimum external static pressure or default fan power.
Comments on the minimum external static pressure requirements and
default fan power are included in sections III.C.1 and III.C.2,
respectively.
d. External Static Pressure Reduction Related to Condensing Furnaces
In the November 2015 SNOPR, DOE requested comment on its proposal
to implement a 0.10 in. wc. reduction in the minimum external static
pressure requirement for air conditioning units tested in blower coil
(or single-package) configuration in which a condensing furnace is in
the airflow path during the test. This issue was also discussed as part
of the CAC/HP ECS Working Group negotiation process. In response to the
November 2015 SNOPR, stakeholders commented that they did not support
DOE's proposed reduction in the minimum external static pressure
requirement because it would result in test results that are less
representative of field energy use. (CAC TP: ADP, No. 59 at p. 12;
Lennox, No. 61 at p. 20; NEEA and NPCC, No. 64 at p. 8; California
IOUs, No. 67 at p. 6; Rheem, No. 69 at p. 17; ACEEE, NRDC, ASAP, No. 72
at p. 4) Recommendation #2 of the CAC/HP ECS Working Group Term Sheet
reflects this sentiment, stating that DOE should not adopt its proposed
reduction in minimum external static pressure required for units paired
with condensing furnaces. (CAC ECS: CAC/HP ECS Working Group Term
Sheet, No. 76 at p. 2).
In the August 2016 SNOPR, in light of public comments and the
consensus of the CAC/HP ECS Working Group, DOE did not propose to adopt
a reduced minimum external static pressure requirement for air
conditioning units tested in blower coil (or single-package)
configuration in which a condensing furnace is in the airflow path
during the test. 81 FR at 58184 (Aug. 24, 2016).
In response to the August 2016 SNOPR, ADP agreed with removing the
reduced ESP as it is not representative of actual installed
performance. ADP also commented there were other more suitable means to
drive the adoption of condensing furnaces. (APD, No. 23 at p. 4) NEEA,
the Joint Advocates, UTC, Goodman, JCI, and Ingersoll Rand also
supported this proposal. (NEEA, No. 35 at p. 3; Joint Advocates, No. 33
at p. 7; UTC, No. 36 at p. 10; Goodman, No. 39 at p. 11; JCI, No. 24 at
p. 15; Ingersoll Rand, No. 38 at p. 5) Rheem also agreed with removing
the reduced ESP, stating that its use could cause the representation of
cooling efficiency to become similar to that with a non-condensing
furnace, which would not reflect how the system would operate in the
field. (Rheem, No. 37 at p. 5).
DOE did not receive any comments in favor of a reduced minimum
external static pressure for systems tested with a condensing furnace.
In light of stakeholder comments, DOE did not include a reduced minimum
external static pressure requirement for these products in this final
rule.
2. Default Fan Power for Rating Coil-Only Units
The default fan power value (hereafter referred to as ``the default
value'') is used to represent fan power input when testing coil-only
air conditioners, which do not include their own indoor fans.\15\ In
the current test procedure, the default value is 365 Watts (W) per
1,000 cubic feet per minute of standard air (scfm) and there is an
associated adjustment to measured capacity to account for the fan heat
equal to 1,250 British Thermal Units per hour (Btu/h) per 1,000 scfm
(10 CFR part 430, subpart B, appendix M, section 3.3.d). The default
value was discussed in the June 2010 NOPR, in which DOE did not propose
to revise it due to uncertainty on whether higher default values would
better represent field installations. 75 FR 31227 (June 2, 2010). In
the November 2015 SNOPR, DOE proposed to update the default value to be
more representative of field conditions (i.e., consistent with indoor
fan power consumption at the minimum required external static pressures
proposed in the November 2015 SNOPR). In the November 2015 SNOPR, DOE
used indoor fan electrical power consumption data from product
literature, testing, and exchanges with manufacturers collected for the
furnace fan rulemaking (79 FR 506, January 3, 2014) to determine an
appropriate default value for coil-only products.\16\ (80 FR 69318) DOE
calculated the adjusted default fan power to be 441 W/1000 scfm. In the
November 2015
[[Page 1452]]
SNOPR, DOE proposed to use this value in appendix M1, while keeping the
current default fan power of 365 W/1000 scfm in appendix M.
---------------------------------------------------------------------------
\15\ See 10 CFR part 430, subpart B, appendix M, section 3.3.d.
\16\ For a complete explanation of DOE's methodology, see 80 FR
at 69319-69320 (Nov. 9, 2015).
---------------------------------------------------------------------------
In response to the November 2015 SNOPR, many stakeholders supported
raising the coil-only test default fan power to 441 W/1000 scfm to
allow for more representative ratings of units. (CAC TP: NEEA and NPCC,
No. 64 at p. 8; ACEEE, NRDC, and ASAP, No. 72 at p. 4; California IOUs,
No. 67 at p. 2)
The CAC/HP ECS Working Group also discussed the default value as
part of the negotiation process. Ultimately, the Working Group came to
a consensus on a recommendation for the default value. Recommendation
#3 of the CAC/HP ECS Working Group Term Sheet states that the default
fan power for rating the performance of all coil-only systems other
than manufactured housing products be 441W/1000 scfm. (CAC ECS: ASRAC
Working Group Term Sheet, No. 76 at p. 3)
Consistent with the CAC/HP ECS Working Group Term Sheet, DOE
maintained its previous proposal to use a default value of 441 W/1000
scfm for split-system air conditioner, coil-only tests in the August
2016 SNOPR. DOE also proposed to adjust measured capacity to account
for the fan heat by 1,505 Btu/h per 1,000 scfm, consistent with 441W/
1000 scfm. 81 FR at 58184 (Aug. 24, 2016). DOE proposed to use these
values in appendix M1 of 10 CFR part 430 subpart B in place of the
default fan power of 365 W/1000 scfm that had been used previously in
appendix M.
Recommendation #3 of the CAC/HP ECS Working Group Term Sheet also
stated that DOE should calculate an alternative default fan power for
rating mobile home air conditioner coil-only units based on the minimum
external static pressure requirement for blower coil mobile home units
(0.30 in. wc.) suggested in recommendation #2 of the Term Sheet. (CAC
TP: ASRAC Working Group Term Sheet, No. 76 at p. 3) As discussed in
section III.C.1, the CAC/HP ECS Working Group included this
recommendation because HUD requires less restrictive ductwork for
mobile homes than for other types of housing, which reduces electrical
energy consumption of the indoor fan. The default value used to rate
coil-only mobile home systems should reflect this difference in field
energy consumption to improve the field representativeness of the test
procedure.
In the August 2016 test procedure SNOPR, DOE used the same
aforementioned furnace fan power consumption data and methodology to
calculate the appropriate default value for mobile home fan power
consumption, which DOE found to be 406 W/1000 scfm. DOE proposed to use
406 W/1000 scfm and adjust cooling capacity by 1,385 Btu/h per 1,000
scfm for mobile home coil-only tests in the August 2016 test procedure
SNOPR. 81 FR at 58163, 58183 (Aug. 24, 2016).
In response to the August 2016 SNOPR, AHRI, Nortek, Lennox,
Ingersoll Rand, JCI, ACEEE, NRDC, ASAP, and Rheem supported DOE's
proposal to use a default value of 441 W/1000 scfm for split-system air
conditioner, coil-only tests. These stakeholders also supported a
unique default fan power of 406 W/1000 scfm for rating mobile home
coil-only units. (AHRI, No. 27 at p. 17; Nortek, No. 22 at p. 13;
Lennox, No. 25 at p. 8; Ingersoll Rand, No. 38 at p. 5; JCI, No. 24 at
p. 16; ACEEE, NRDC, and ASAP, No. 33 at p7; Rheem, No. 37 at p. 3)
Carrier/UTC also expressed support for a default fan power value of 441
W/1000 scfm for split-system air conditioner, coil-only tests.
(Carrier/UTC, No. 36 at p. 10) ADP and Lennox also expressed support
for 406 W/1000CFM as a default fan power value for coil-only mobile
home applications. (ADP, No., 23 at p.5, Lennox, No. 25 at p. 8) DOE
did not receive any negative comments regarding the use of 441 W/1000
scfm or 406 W/1000 scfm as the default fan power values for
conventional split-system or mobile home coil-only tests, respectively.
DOE also did not receive any additional data to validate these values.
In light of stakeholder support and no adverse comments, DOE is
adopting a default fan power value of 441 W/1000 scfm and capacity
adjustment of 1,505 Btu/h/1000 scfm for non-mobile home coil-only
systems and a default fan power value of 406 W/1000 scfm and capacity
adjustment of 1,385 Btu/h/1000 scfm for mobile home coil-only systems.
In the August 2016 test procedure SNOPR, DOE proposed a definition
for a mobile home coil-only system to appropriately apply the proposed
default value for these kinds of CAC/HP. DOE proposed the following:
Mobile home coil-only system means a coil-only split
system that includes an outdoor unit and coil-only indoor unit that
meet the following criteria: (1) The outdoor unit is shipped with
manufacturer-supplied installation instructions that specify
installation only for mobile homes that comply with HUD Manufactured
Home Construction Safety Standard 24 CFR part 3280, (2) the coil-only
indoor unit is shipped with manufacturer-supplied installation
instructions that specify installation only in a mobile home furnace,
modular blower, or designated air mover that complies with HUD
Manufactured Home Construction Safety Standard 24 CFR part 3280, and
(3) the coil-only indoor unit and outdoor unit each has a label in at
least \1/4\ inch font that reads, ``For installation only in HUD
manufactured home per Construction Safety Standard 24 CFR part 3280.''
81 FR at 58163, 58185 (Aug. 24, 2016).
In written comments, Rheem, JCI, ACEEE, NRDC, and ASAP expressed
support for DOE's proposed definition for mobile home coil-only system.
(Rheem, No. 37 at p.5; JCI, No. 24 at p.16, ACEEE, NRDC, and ASAP, No.
33 at p.7)
Some stakeholders offered suggested improvements to the definition
to better differentiate mobile home coil-only systems from other types
of systems. ADP explained that indoor units are often installed in
attics, basements, closets and other areas of limited access, so most
consumers would not see a label, limiting the usefulness of a label.
(ADP, No., 23 at p.6) Lennox and ADP recommended that DOE add the
following physical indoor coil characteristics to the definition of
mobile home coil-only system in addition to labeling requirements to
limit the definition to products exclusively manufactured for mobile
homes:
(1) Downturned refrigerant connections
(2) refrigerant connections on left hand side of coil (when viewed from
the front)
(3) down-flow capable
(4) maximum size of 20'' wide, 32'' high and 21'' deep (Lennox, No. 25
at p. 8; ADP, No., 23 at p.6)
ADP added that these features are shared by products marketed as
mobile home coils and collectively are not present in coils marketed
for other applications. Mortex commented that mobile home furnaces have
a unique footprint and are only compatible with indoor coils that have
a drain pan footprint of 18.5'' wide by 21'' long. Mortex suggests that
the definition for mobile home coil-only should include these dimension
restrictions for indoor coils. (Mortex, No. 26 at p. 3)
DOE appreciates the suggestions from ADP, Lennox, and Mortex. DOE
agrees that a definition that includes descriptions of physical
characteristics unique to indoor and outdoor units and combinations
that are installed in mobile homes will better distinguish mobile home
coil-only systems from other systems. DOE reviewed public product
literature for mobile home indoor coils to evaluate the additional
criteria suggested by stakeholders.
[[Page 1453]]
DOE's search confirmed many of the suggestions, but not all. DOE could
not confirm with confidence that all mobile home indoor coils include
downturned refrigerant connections on the left hand side when viewed
from the front. DOE also found mobile home indoor units that slightly
exceeded the height limit that ADP and Lennox recommend. For these
reasons, DOE is modifying its proposed definition to include some, but
not all, of the physical characteristics that interested parties
recommend. In this final rule, DOE is adopting the following definition
for mobile home coil-only system:
Mobile home coil-only system means a coil-only split system that
includes an outdoor unit and coil-only indoor unit that meet the
following criteria: (1) The outdoor unit is shipped with manufacturer-
supplied installation instructions that specify installation only for
mobile homes that comply with HUD Manufactured Home Construction Safety
Standard 24 CFR part 3280, (2) the coil-only indoor unit is shipped
with manufacturer-supplied installation instructions that specify
installation only in or with a mobile home furnace, modular blower, or
designated air mover that complies with HUD Manufactured Home
Construction Safety Standard 24 CFR part 3280, and has dimensions no
greater than 20'' wide, 34'' high and 21'' deep, and (3) the coil-only
indoor unit and outdoor unit each has a label in at least \1/4\ inch
font that reads ``For installation only in HUD manufactured home per
Construction Safety Standard 24 CFR part 3280.''
As discussed in detail in section III.C.1.b, in response to
stakeholder comment, DOE is adopting a lower minimum external static
pressure requirement for space-constrained products to better reflect
their field-installed conditions. Similar to mobile home coil-only
units, space-constrained coil-only tests should use a default fan power
value and capacity adjustment representative of operation at the
minimum external static pressure. Recommendation #2 of the Term Sheet
includes 0.30 in. wc. as the suggested minimum external static pressure
for both mobile home and space-constrained products. As discussed
earlier in this section, DOE has determined, with stakeholder support,
that a default fan power value of 406 W/1000 scfm and capacity
adjustment of 1,385 Btu/h/1000 scfm are consistent with operation at
0.30 in. wc. For this reason, DOE is adopting a default fan power value
of 406 W/1000 scfm and capacity adjustment of 1,385 Btu/h/1000 scfm for
space-constrained products in this final rule.
3. Revised Heating Load Line Equation
a. Revision of the Heating Load Line Analysis and Proposals
DOE initially proposed revisions to the heating load line equation
used in the calculation of heating season performance factor (HSPF) in
the November 2015 SNOPR. 80 FR at 69320-69322 (Nov. 9, 2015) The
proposals were based on a 2015 Oak Ridge National Laboratory (ORNL)
study \17\ that examined the heating load line equation for cities
representing the six climate regions of the HSPF test procedure in
appendix M. DOE received comments on its heating load line equation
proposals both in written form in response to the November 2015 SNOPR
and verbally during the CAC/HP ECS Working Group meetings. DOE
considered the comments received, worked with ORNL on re-examination of
certain aspects of the analysis described in the 2015 study, and
revised its proposals for revision of the heating load line equation.
The revised proposal presented in the August 2016 SNOPR included the
following test procedure amendments.
---------------------------------------------------------------------------
\17\ ORNL, Rice, C. Keith, Bo Shen, and Som S. Shrestha, 2015.
An Analysis of Representative Heating Load Lines for Residential
HSPF Ratings, ORNL/TM-2015/281, July. (Docket No. EERE-2009-BT-TP-
0004-0046).
---------------------------------------------------------------------------
The zero-load temperature would vary by climate region
according to the values provided in Table III-4, but remain at 55
[deg]F (as proposed in the November 2015 SNOPR) for Region IV;
The heating load line equation slope factor for single-
and two-stage heat pumps would vary by climate region, as shown in
Table III-4, and be 1.15 for Region IV; and
For variable-speed heat pumps, the heating load line
equation slope factor would be 7 percent less than for single- and two-
stage heat pumps. It would vary by climate region, as shown in Table
III-4, and be 1.07 for Region IV; 81 FR at 58189 (Aug. 24, 2016)
DOE also revised the heating load hours based on the new zero-load
temperatures of each climate region. The revised heating load hours are
also given in Table III-4.
Table III-4--Climate Region Information Proposed in the August 2016 SNOPR Notice
----------------------------------------------------------------------------------------------------------------
Region Number
-----------------------------------------------------------------------------
I II III IV V VI *
----------------------------------------------------------------------------------------------------------------
Heating Load Hours................ 493 857 1247 1701 2202 1842
Zero-Load Temperature, Tzl, [deg]F 58 57 56 55 55 57
Heating Load Line Equation Slope 1.10 1.06 1.30 1.15 1.16 1.11
Factor, C........................
Variable-speed Slope Factor, CVS.. 1.03 0.99 1.21 1.07 1.08 1.03
----------------------------------------------------------------------------------------------------------------
* Pacific Coast Region.
Note: Some of the values in this table for Region III differ from those presented in the SNOPR. See discussion
of these corrections below.
Following from this proposed heating load line equation change, DOE
also proposed in the August 2016 SNOPR to require cyclic testing for
variable-speed heat pumps be run at 47 [deg]F, rather than using the 62
[deg]F ambient temperature that is required by the current test
procedure (see appendix M, section 3.6.4 Table 11). The test would
still be conducted using minimum compressor speed. The modified heating
load line cyclic test at 47 [deg]F would be more representative of the
conditions for which cycling operation is considered in the HSPF
calculation. 81 FR at 58190 (Aug. 24, 2016)
In addition, for variable-speed heat pumps, the SEER would be
calculated using a building load that is adjusted downwards by 7
percent, consistent with the heating load adjustment.
Heating Load Line Zero-Load Temperature and Slope Factor
A number of commenters disagreed with the zero-load temperature
and/or the slope factor proposed for the heating load line equation.
EEI commented that the zero-load temperatures appeared to be too
low in light of the predominance of older houses in the building stock,
and that the approach may be missing many
[[Page 1454]]
heating load hours between 55 [deg]F and 65 [deg]F outdoor
temperatures. (EEI, Public Meeting Transcript, No. 20 and pp. 82-83) In
written comments, EEI reiterated objection to a 55 [deg]F zero-load
temperature, asserting that house temperature would fall to 55 [deg]F
if the heating system provided no heat at warmer temperatures. They
stated most houses are not insulated as well as newer houses, and
assuming zero heating system operation between 55 [deg]F and the indoor
thermostat settings (e.g., 68 [deg]F) is not realistic and results in
lowering the estimated seasonal efficiency of heat pumps. EEI suggested
using a zero-load temperature of 65 [deg]F. EEI suggested using a slope
of 0.77 or 1.02. (EEI, No. 34 at pp. 2-6)
In its comments, AHRI did not agree with the zero load point of 55
[deg]F. AHRI commented that DOE's proposal was solely based on computer
modeling and that AHRI members had submitted real world data from
across the entire country during the negotiations to support AHRI's
position. AHRI recommended keeping the existing zero-load temperature
as 65 [deg]F, and a single heating load line for all products with a
1.02 slope. (AHRI, No. 27 at p. 18) Mitsubishi, Carrier, Lennox,
Nortek, Ingersoll Rand, and Goodman all submitted comments agreeing
with AHRI's recommendation to use a 65 [deg]F zero-load temperature and
a 1.02 slope factor. (Mitsubishi, No. 29 at pp. 3-4; Carrier, No. 36 at
p. 10; Lennox, No. 25 at pp. 9-10; Nortek, No. 22 at p. 14; Ingersoll
Rand, No. 38 at p. 5; Goodman, No. 39 at p. 9-10)
JCI commented that the ORNL analysis was flawed in that it did not
measure the heating load in homes in which human occupants were
present. JCI expressed belief that a good survey would find heating
load occurring even into the 70 [deg]F-75 [deg]F range in certain
regions of the country for certain demographics, and recommended DOE
use the 65 [deg]F value for the zero-load temperature.
Bruce Harley Energy Consulting (BHEC) provided field monitoring
data and analysis of heating loads conducted at the request of PG&E.
The work addressed heating load data of seven homes covering regions I/
II,\18\ IV, and V that were monitored to measure heating system
operation. The data sets and analysis for these houses were not
explained extensively in the BHEC comment, but DOE understands that
average heating loads were determined by 5 [deg]F-wide temperature bins
for hours representing at least a full heating season for each
location. Linear curve fits to the binned loads as a function of
temperature were determined. The zero-load temperatures for the linear
fits lie within a range between 57 [deg]F and 61 [deg]F. Based on this
study, BHEC suggested DOE use a value of 60 [deg]F for the zero-load
temperature for all climate regions. BHEC also pointed out that these
homes are likely to be somewhat less efficient than the 2006 IECC.
(BHEC, No. 28 at pp. 2-3)
---------------------------------------------------------------------------
\18\ The comment indicates that three of the monitored homes are
located in Stockton, CA and are in Region ``I/II''. Based on
comparison of the location of Stockton with the climate zone map
(Figure 1 in Appendix M), it is not clear that ``I/II'' clearly
represents Stockton's climate zone--it would appear to be more
likely in Region III. In contrast, the other locations mentioned in
the comment are much more clearly in their listed zones, e.g. V for
Southern Vermont, and IV for New York/New Jersey.
---------------------------------------------------------------------------
BHEC's initial comparison of the regional heating load lines with
the load lines determined for the seven monitored locations led to the
conclusion that the heating load line equation in the August 2016 SNOPR
incorrectly included the term TOD (the regional outdoor
design temperature) in the denominator. The comment provided analysis
showing that the value TOD should be replaced with 5 [deg]F,
which is the outdoor design temperature for Region IV. (BHEC, No. 28 at
pp. 3-6) With this change, and use of 60 [deg]F as the zero-load
temperature, the comment showed that the field data provided good
agreement with the calculated heating load lines using the 1.15 slope
factor proposed in the August 2016 SNOPR for all but one of the seven
monitored locations. This location, ``Site W'', has an unusually high
heating load, as indicated by the comment. BHEC concluded that DOE
should consider adopting a heating load line with a 60 [deg]F zero-load
temperature and a 1.15 slope factor. (BHEC, No. 28 at pp. 6-8)
PG&E commented during the public meeting that the August 2016 SNOPR
proposals were not consistent with recent field data not available
during the CAC/HP ECS negotiations, and that more details would be
provided later. (PG&E, Public Meeting Transcript, No. 20 at p. 84)
These additional details presumably are provided by the BHEC comment.
The CA-IOUs (which includes PG&E) reiterated some of the discussion of
the BHEC comment and supported the 60 [deg]F zero-load temperature and
the 1.15 slope factor, although indicating that the selection of zero-
load temperature has less impact on measured efficiency. (CA IOU, No.
32 at pp. 1-4)
NEEA supported BHEC's comments on zero-load temperature and slope
factor. (NEEA, No. 35 at p. 3)
ACEEE, ASAP, and NRDC supported the heating load line equation
proposal of the August 2016 SNOPR but suggested that a more thorough
review and revision of the test method for determining heat pump
efficiency should be conducted in future. (ACEEE, NRDC, and ASAP, No.
33 at pp. 2, 7-8)
DOE agrees with BHEC's comment regarding appearance of
TOD in the denominator of the heating load line equation.
This is a mistake that initially appeared in the November 2015 SNOPR.
The correct form of the equation, shown in the initial ORNL Report,
indicates that the TOD should be replaced with 5 [deg]F
(Docket No. EERE-2009-BT-TP-0004, An Analysis of Representative Heating
Load Lines for Residential HSPF Ratings, No. 46 at p. B-1).
Regarding several comments pointing to operation of heating systems
in temperatures well above 55 [deg]F, DOE does not dispute that this
occurs. The ORNL analysis, in fact, shows that heating loads exist at
higher temperatures, as illustrated in Figure 2 of the initial report
(Docket No. EERE-2009-BT-TP-0004, An Analysis of Representative Heating
Load Lines for Residential HSPF Ratings, No. 46 at p. 5) The zero-load
temperature is not intended to be the highest temperature at which the
heating system would operate. Instead, it is the zero-load intercept of
the best-fit line representing the average loads calculated for each
bin. The field data that were provided during the CAC/HP ECS
negotiations, cited in the AHRI comment and also provided in the
Ingersoll Rand comment (Ingersoll Rand, No. 38 at p. 6), represent many
locations and likely represent a wide range of house characteristics
and occupancy patterns. DOE does not believe that this type of
aggregation of the data of all of the monitored locations is very
useful to provide an understanding of building heating loads. For
example, much of the operation of the heating systems above 55 [deg]F
outdoor temperature could be associated with recovery from night
setback. Also, it is not known how the supplemental electric resistance
heat compares with the heat pump capacity, or whether any of the
locations have supplemental heat other than the electric resistance
heat built into the monitored heat pumps--to the extent that such
alternative supplemental heating (e.g. supplied by a separate space
heater, furnace, or wood stove) occurs at different temperatures than
heating provided by the heat pump--would affect the results by
flattening the apparent load line slope. DOE initially requested
additional details of this
[[Page 1455]]
study to allow more careful analysis, but such information was not
readily available. DOE points out similar issues associated with the
aggregation of the field data provided by Lennox. (Lennox, No. 25 at p.
9) In contrast, the data provided by BHEC provides a clearer indication
of how the load varies with ambient temperature for specific locations,
because the data were provided separately for each location and the
heating loads were more directly measured than for the data sets
provided by Ingersoll Rand and Lennox.
DOE reviewed the work by BHEC, and believe that, while these data
suggest use of a zero-load temperature higher than 55 [deg]F, they do
not show that DOE's 55 [deg]F proposal is inappropriate. First, the
best-fit zero-load temperatures of the monitored locations ranges from
57 [deg]F to 61 [deg]F. However, the 61 [deg]F value is associated with
Site W, which has unusually high loads, suggesting that this location
is an outlier not consistent with most houses. Second, as suggested by
the comment, these homes are likely less efficient than the 2006 IECC
housing characteristics used in the ORNL analysis. During the CAC/HP
ECS negotiations, Working Group members commented that, in developing
test procedures, DOE should be looking further towards the future than
represented by IECC 2006 (see, e.g., Docket EERE-2014-BT-STD-0048,
2015-09-28 Working Group Meeting Transcript; Ingersoll Rand, No. 86 at
p. 187; Carrier, No. 85 at p. 112) Hence, DOE believes consideration of
house models representative of earlier building codes is not
appropriate and maintains its selection of the IECC 2006 building
models. DOE notes that there is variation in the existing housing stock
and that some houses may have higher zero load slopes than others.
Also, when considering all of the locations of the BHEC comment other
than Site W, the heating load calculated using the 60 [deg]F zero
temperature is slightly higher than the field-correlated line for 5
locations. For these locations, reducing the zero-load temperature to
60 [deg]F would slightly improve the fit of the calculated heating load
line to the field data. DOE also considered the impact of a 60 [deg]F
zero-load temperature as opposed to the proposed 55 [deg]F zero-load
temperature on the differentiation between variable-speed and two-stage
products. Using data provided by AHRI during the CAC/HP Working Group
meetings, DOE determined that use of 60 [deg]F would make little change
to the differences in HSPF values calculated for heat pumps with
different characteristics. The HSPF is roughly 2.4 percent higher when
using the 60 [deg]F zero-load temperature, and there are no significant
difference in trends for products with different characteristics. For
all these reasons, DOE has decided not to revise the heating load line
using a 60 [deg]F zero-load temperature.
In response to JCI's comment suggesting that the heating loads of
the ORNL study did not include the impacts of human occupants, this is
not true--the load analysis did include load contributions for human
occupants. In response to EEI's comment that the house temperature
would fall to 55 [deg]F if the heating system did not operate at warmer
temperature, DOE reiterates that the 55 [deg]F zero-load temperature
does not imply that there is no heating system operation at warmer
temperatures and that the EEI statement ignores the impacts of internal
heat loads and solar gain that raise the internal temperature above the
exterior temperature even when there is no heating system operation.
Heat Pump and Furnace Load Lines
Ingersoll Rand (p. 6) and EEI (p. 4) commented that the heating
load line equation for heat pumps should not be different than the
equation used for furnaces in order to maintain neutrality between
different heating products in performance information provided to
consumers. In response, DOE first notes that neither the capacity nor
the steady-state efficiency for furnaces varies significantly for
different outdoor air temperatures (see, e.g., Investigation of High
Efficiency Furnace SSE Measurements versus AFUE, No. 42 at p. 1), which
is not true for capacity and COP of heat pumps. Consequently, the load
line does not affect the furnace efficiency metric, AFUE; in other
words, the AFUE would not be significantly different if calculated for
any of the alternative load lines proposed in the CAC/HP rulemaking
notices and discussed in stakeholder comments. In contrast, the
capacity of a heat pump varies greatly with ambient temperature. For
example, the heating capacity at 7 [deg]F for a single speed heat pump
is about 50% of its capacity at 47 [deg]F. (Docket No. EERE-2009-BT-TP-
0004, An Analysis of Representative Heating Load Lines for Residential
HSPF Ratings, No. 46 at p. 21) The much greater sensitivity to outdoor
temperature of a heat pump suggests strongly that use of representative
load profiles for calculating seasonal efficiency is much more
important for them than for furnaces. DOE has based its proposal and
final rule on a recent comprehensive assessment of heating loads, i.e.
the ORNL analysis. (Id) The furnace test procedure has not recently
been reviewed from the perspective of a similar assessment of heating
loads. DOE acknowledges that the proposed change to the heating load
line for heat pumps does change the seasonal heating load that is the
basis of the annual operating cost calculation. However, due to the
greater importance of using a representative load line for heat pumps,
DOE believes that modification of the furnace test procedure to align
with the heat pump test procedure is the appropriate resolution. DOE
may consider in a future rulemaking whether the seasonal heating load
for the furnace test procedure should be adjusted to match that of the
heat pump test procedure.
Variable-Speed Slope Factor
Numerous comments addressed the different slope factor proposed for
variable-speed products. JCI disagreed with DOE's proposal to modify
the heating load line slope such that it varies with technology type.
JCI stated they would be willing to adopt a 1.02 slope for all product
types as proposed by industry in the CAC/HP ECS negotiations. (JCI, No.
24 at p. 16)
AHRI asserted that a single heating load line equation slope factor
is appropriate for all products, because the building load is
independent of the installed system. (AHRI, No. 27 at pp. 17-18)
Several other commenters made identical arguments. (Goodman, No. 39 at
p. 9; Carrier/UTC, No. 36 at p. 10; Lennox, No. 25 at p. 9; Ingersoll-
Rand, No. 38 at p. 6; Nortek, No. 22 at p. 12) Rheem commented that
different slope factors should not be used for single and two-stage
products, further commenting that building load is not determined by
the installed HVAC equipment. (Rheem, No. 37 at p. 5) Although DOE has
not proposed different slope factors for single and two-stage
equipment, DOE understands that the same argument might apply to
variable-speed products, for which DOE did propose a different slope
factor.
Emerson commented that DOE did not support the different oversizing
factor for variable-speed products with any field installation data and
noted that the May 2016 workshop on residential CAC/HP installation
highlighted field installation inconsistencies including improper
sizing and lack of data. Emerson stated that a misrepresentation of
HSPF in ``variable capacity'' systems should be corrected by modifying
the HSPF calculation, for example, by changing the run time. (Emerson,
No. 31 at p. 2) However, Emerson also stated that variable speed allows
oversizing in
[[Page 1456]]
installation and suggested that the variable-speed slope factor also be
allowed for use with other technologies that modulate capacity,
including two-stage, tandem, vapor injection, and digital. (Emerson,
No. 31 at p. 2)
BHEC supported a lower slope factor for variable-speed products
than for single-speed, indicating further that the proposal to use the
ratio of allowed cooling oversize factors in ACCA Manual S for these
types of equipment (leading to a proposed slope factor of 1.07 for
Region IV) is reasonable, and in the current test procedure is likely
to be a conservative adjustment.
The CA IOUs, NEEA, and ACEEE, NRDC, and ASAP supported the lower
slope factor for variable-speed products. (CA IOU, No. 32 at p. 4;
NEEA, No. 35 at p. 3; ACEEE, NRDC, and ASAP, No. 33 at pp. 7-8)
In response to comments that the building load does not change with
selection of heat pump technology, DOE notes that the proposal does not
suggest any difference in building load when using different
technology. The slope factor represents the ratio of building load to
heat pump capacity. DOE acknowledges that variable-speed products are a
bit more oversized in comparison to the building heating load than are
single-speed and two-stage products. Keeping the building load constant
and increasing the variable-speed heat pump capacity reduces the
building load/capacity ratio; hence DOE selected a lower slope factor.
Given that publicly available data regarding sizing trends is not
available, and in response to comments pointing out the lack of data to
support the lower slope factor for variable-speed products, DOE
understands that ACCA Manual S is the best available indication of what
sizing guidelines contractors and others may be using to select heat
pumps, due to widespread citation of the ACCA manuals for use in
calculating loads and sizing HVAC systems, including required use of
Manual S for sizing of systems in ENERGY STAR certified homes. (``Why
ACCA Manual S Means Superior Equipment Sizing'', No. 40; ``HVAC Design
Report, ENERGY STAR Certified Homes'', No 43; ``What Exactly is Manual
S in HVAC Design and Why Is It Important?'', No. 44; ``Residential
Mechanical Equipment Loads and Sizing'', No. 45)
In response to Emerson's comment that potential HSPF
misrepresentation for variable-speed products should be addressed by
adjusting run time, it is not clear what Emerson's suggested approach
is. DOE notes that the lower slope factor for variable-speed products
leads directly to calculation of lower percentage run time for
variable-speed products in the HSPF calculation when meeting loads
lower than the minimum-speed capacity. If Emerson's comment was
intended to address the cycle times used for variable-speed products
during the cyclic test, DOE notes that the cycle times for variable-
speed products are longer for variable-speed than for single-speed or
two-stage products (see, e.g., appendix M, section 3.5.b).
In response to Emerson's comment that the test procedure should
allow variable-capacity technologies other than variable speed to use
the lower slope factor, DOE declines to adopt that approach in this
final rule because there were no data either provided by Emerson, or
found by DOE that show how such systems would be sized and/or
differences in how such systems would operate. For example, two-stage
products currently on the market do not allow as wide a range of
capacity modulation as do variable-speed products, so it is not clear
that similar oversizing is justified for them. In fact, ACCA manual S
recommends only slightly more oversizing for two-stage products than
for single-stage. The modulation range of vapor-injection compressors
is also not as wide as for variable-speed. Finally, DOE is not aware of
any CAC/HP products on the market that use digital technology, so it is
not clear how the modulation range of future products using this
technology will compare, and it is also not clear whether alternative
sizing guidelines will be extended to them. DOE is not against
consideration of use of the lower slope factor for other variable-
capacity technologies, but prefers to consider such a step when more is
known about the products using these technologies.
Therefore, DOE is adopting the appendix M1 test procedure with the
heating load line equation slope factors (1.15 for single- and two-
stage heat pumps and 1.07 for variable-speed heat pumps) and zero-load
temperature (55 [deg]F) proposed in the August 2016 SNOPR.
Corrections
In the August 2016 SNOPR, DOE inadvertently included the incorrect
values for the representative heating load hours for each generalized
climatic region in Table 20 of appendix M1. 81 FR at 58268 (Aug. 24,
2016) The preamble also provided incorrect values for heating load
hours, the slope factor, and the variable-speed slope factor for Region
III. 81 FR at 58189-90. The corrected values were determined as
described and reported in the ORNL report addendum. (CAC TP: ORNL
Report Addendum, No. 2 at p. 8) Therefore in this final rule, DOE is
adopting the corrected values in the test procedure, including the
correct heating load hours for all of the climatic regions in Table 20,
which in this notice has become Table 21.
DOE also notes that, in the August 2016 SNOPR, the heating load
hours depicted in Figure 1 are not consistent with the new heating load
line analysis. 81 FR at 58267 (Aug. 24, 2016) However, the figure is
still helpful for depicting the climate zones. Therefore, in this final
rule, DOE is renaming Figure 1 to indicate that the figure depicts
climate zones rather than heating load hours. In addition, Figure 2,
which depicts cooling load hours, is not referenced by any part of the
test procedure as modified by the June 2016 final rule and the August
2016 SNOPR proposals. 81 FR at 37119 (June 8, 2016) and 81 FR at 58267
Hence, DOE is removing this figure to reduce potential confusion
regarding its applicability to the test procedure and calculations.
Clarification Regarding Negative Heating Loads
DOE's proposed changes to the test procedure did not include
removing fractional bin hour data for the temperature bins with
temperature higher or equal to the new zero-load temperatures--this
included data in Table 19 (number as proposed in the August 2016 SNOPR)
for the 62 [deg]F bin for Region I and both the 57 [deg]F and 62 [deg]F
bins for all other regions. 81 FR at 58254-55 (Aug. 24, 2016)
DOE notes that for these bins with temperatures higher than the
zero-load temperatures, a negative heating load would be calculated
according to equation 4.2-1 as proposed. Unico raised this issue in
comments submitted in response to the notice of data availability
(NODA) associated with the CAC/TP energy conservation standard
rulemaking which was published October 27, 2016 (see 81 FR 74727).
(Docket Number EERE-2014-BT-STD-0048, Unico, No. 95 at p. 1) However,
these negative-load contributions were not intended to be included in
HSPF calculation, because they would incorrectly reduce the calculated
total seasonal heating load and heating season energy use. In order to
exclude the negative-load contributions in the HSPF calculation, DOE
has set the fractional bin hours to zero for the 62[emsp14][deg]F bin
for Region I and both the 57 [deg]F and 62 [deg]F bins for all other
regions.
b. Impact of DOE Proposal on Current HSPF Ratings and Model
Differentiation
DOE provided in the August 2016 SNOPR a summary of the impacts of
the
[[Page 1457]]
revised heating load line equation proposal on HSPF ratings based on
test results provided by AHRI for 2, 3, and 5-ton two-stage and
variable-speed heat pumps. 81 FR at 58190 (Aug. 24, 2016) These impacts
are reproduced in Table III-5.
Table III-5--Effect of Region IV Slope Factors on HSPF of Two-Stage (TS) and Variable-Speed (VS) Models
----------------------------------------------------------------------------------------------------------------
Region IV slope factors
-------------------------------------------------------------------------------
August 2016
Current: 0.77 1.02 1.15 1.30 SNOPR *
----------------------------------------------------------------------------------------------------------------
Avg. TS HSPF.................... 9.49 8.47 8.17 7.80 8.17
Avg. VS HSPF.................... 10.93 9.44 8.95 8.44 9.26
Avg. HSPF Differential.......... 1.44 0.97 0.79 0.64 1.09
----------------------------------------------------------------------------------------------------------------
* Slope factor for two-stage equipment: 1.15. Slope factor for variable-speed equipment: 1.07.
EEI commented in the public meeting that the change in HSPF
associated with the test procedure proposal was so great that there
should be consideration of changing the name of the heating mode
efficiency metric. (EEI, Public Meeting Transcript, No. 20 at p. 86)
PG&E seconded this point. (PG&E, Public Meeting Transcript, No. 20 at
p. 87, 88) Other stakeholders mentioned that the working group in the
CAC/HP negotiations had settled on calling the new efficiency metric
HSPF2 and voiced support for this term--Goodman also indicated that it
would be beneficial to use both ``HSPF'' and ``HSPF2'' for a period of
time before the new test procedure becomes mandatory, to help consumers
understand the differences between the old and new ratings. (Goodman,
Rheem, Public Meeting Transcript, No. 20 at p. 87-88)
Consistent with the comments, and as discussed in section III.A.1,
DOE is renaming the heating mode efficiency metric ``HSPF2.''
EEI also commented that the new slope has a significant impact on
estimated energy usage. EEI commented many two-speed units would not
qualify for Energy Star or even meet the minimum DOE HSPF with the new
slope. EEI contended that the revision could take many high efficiency
units off of the market. (EEI, No. 34 at p. 4) DOE notes that these
comments do not take into consideration the changes in the standard
levels that would be made to account for the measurement changes. In
response, DOE expects that the Energy Star program will set new levels
for ``HSPF2'' consistent with the measurement change associated with
the test procedure change, as DOE has proposed to do with the new HSPF
standard levels selected based on the current test procedure by the
CAC/HP ECS Working Group.
No stakeholders stated that the heating load line slope factors
proposed in the August 2016 SNOPR result in overly diminished
differentiation of variable-speed heat pumps as compared with two-stage
heat pumps. Therefore, concerns regarding insufficient product
differentiation that had been raised regarding the slope factors
proposed in the November 2015 SNOPR appear to be removed, thus
strengthening the arguments for heating load line slope factors
proposed in the August 2016 SNOPR, which are adopted in this final
rule. Thus, DOE is adopting the new heating load line slope factors for
variable speed heat pumps in this final rule.
c. Translation of CAC/HP ECS Working Group Recommended HSPF Levels
Using Proposed Heating Load Line Equation Changes
Recommendation #9 of the CAC/HP ECS Working Group Term Sheet
included two sets of recommended national HSPF standard levels. The
Working Group based these levels on heating load line equation slope
factors of 1.02 and 1.30 to reflect the two factors primarily discussed
during the negotiations. The Working Group designated these levels as
``HSPF2'' to indicate that they are not equivalent to current HSPF
ratings. Table III-6 includes the Working Group's recommended HSPF
levels:
Table III-6--CAC/HP ECS Working Group Recommended HSPF Levels Based on
Previously Proposed Heating Load Line Equations
------------------------------------------------------------------------
Product class HSPF2-1.02 HSPF2-1.30
------------------------------------------------------------------------
Split-System Heat Pumps................. 7.8 7.1
Single-Package Heat Pumps............... 7.1 6.5
------------------------------------------------------------------------
Because the August 2016 SNOPR proposed a heating load line equation
with a slope factor of 1.15 for baseline systems, DOE calculated the
expected HSPF2 standard levels for this intermediate slope factor--
these values are presented in Table III-7.
Table III-7--CAC/HP ECS Working Group Recommended HSPF Levels Based on
Heating Load Line Equation Proposed in the August 2016 SNOPR
------------------------------------------------------------------------
Product class HSPF2-1.15
------------------------------------------------------------------------
Split-System Heat Pumps................................. 7.5
Single-Package Heat Pumps............................... 6.8
------------------------------------------------------------------------
DOE requested comment on the adjusted values of minimum HSPF2.
During the public meeting, Goodman expressed provisional support of the
values but indicated that some analysis would be conducted to confirm.
(Goodman, Public Meeting Transcript, No. 20 at pp. 89-90) However,
several commenters indicated in written comments that the 6.8 HSPF2
value for single-package heat pumps was too high.
AHRI expressed concern with the HSPF2 value determined for single-
package heat pumps, indicating that of
[[Page 1458]]
six such products with current-test HSPF of 8.0 and slightly higher
that were evaluated, the results for five indicate that the crosswalk
from HSPF of 8.0 to HSPF2 of 6.8 is not accurate using the 1.15 slope
factor. AHRI indicated that it was in the process of collecting
additional data and will provide a suggestion for an appropriate
crosswalk for this class within 30-days of the comment submittal
deadline. (AHRI, No. 27 at p. 18) Nortek submitted a nearly identical
comment, but claimed that three of the six evaluated units would not be
compliant with the 6.8 HSPF2 level, and indicated that more data would
be collected and provided within 30 days. (Nortek, No. 22 at p. 15)
Goodman performed simulation analysis, from which it concluded that
the proposed HSPF2 values for split system heat pumps is realistic, but
that the crosswalk value for single package heat pumps is higher than
it should be. Goodman requested a crosswalk HSPF2 value of 6.6 or 6.7
but indicated they would be providing more information. (Goodman, No.
39 at p. 10)
Rheem commented that, based on initial analysis of the HSPF to
HSPF2 crosswalk, some of their products would become obsolete if the
cross-walk is adopted--however, they did not clarify which type of
product. Rheem commented that it was working with AHRI to determine
appropriate cross-walk metrics, which would be reported to DOE. (Rheem
No. 37 at p.7)
Ingersoll Rand also expressed concerns about the HSPF to HSPF2
crosswalk, and indicated they would be providing data to AHRI.
(Ingersoll RandNo. 38 at p. 7)
JCI commented that residential single-package units will be more
severely affected than the crosswalk currently reflected and requested
more time for the industry to evaluate and confirm the HSPF to HSPF2
crosswalk. (JCI, No. 24 at p. 17)
ACEEE, NRDC, and ASAP supported the values assigned, commenting
that without better information, the linear interpolation is an
appropriate way to determine the adjusted minimum HSPF2 values for the
heating load line equation slope factor proposed in the August 2015
SNOPR. (ACEEE, NRDC, and ASAP, No. 33 at p.2) Carrier/UTC supported the
adjusted values of minimum HSPF2 as they are consistent with the CAC/HP
ECS Working Group term sheet recommendation. (Carrier/UTC, No. 36 at p.
11)
Lennox supported the 7.5 HSPF2 value determined by DOE for split
systems but did not support the 6.8 HSPF2 value for single package
products. Lennox commented that an HSPF2 level of 6.5 would be
appropriate for single package heat pumps under the M1 Appendix test
procedure proposed in the August 2015 SNOPR. Lennox indicated that it
was working to expand the sample of the data used in this determination
to provide DOE evidence that supports this recommendation. Lennox
expected this data collection to be complete within 30 days of the end
of the comment period. (Lennox, No. 25 at p. 10)
Unico requested that the DOE defer action until AHRI presents
additional data, since the crosswalk is a complex issue and requires
additional time to determine the effect that the proposed adjustments
will have on HSPF. (Unico, No. 30 at p.6)
DOE will consider these recommendations and any additional data
provided in a timely fashion when it considers the final HSPF2 values
to be set for single-package heat pumps in the energy conservation
standard rulemaking.
d. Consideration of Inaccuracies Associated With Minimum-Speed
Extrapolation for Variable-Speed Heat Pumps
DOE discussed in the November 2015 SNOPR potential inaccuracies
associated with the use of test data conducted at minimum speed in
47[emsp14][deg]F and 62[emsp14][deg]F ambient temperature to estimate
heat pump performance below 47[emsp14][deg]F. 80 FR at 69322-23 (Nov.
9, 2015). Specifically, for heat pumps that increase compressor speed
as ambient temperature drops below 47[emsp14][deg]F, the extrapolation
of performance based on the 47[emsp14][deg]F and 62[emsp14][deg]F
minimum-speed tests over-estimates efficiency. However, for the 1.3
slope factor proposed in the November 2015 SNOPR, DOE found that the
impact on HSPF for the available heat pump data was too small to
justify modifying the test procedure. The higher slope factor reduced
the impact of the issue because the higher heating load reduced the
weighting of the HSPF on minimum-speed performance. DOE did not propose
a resolution but indicated that it might reconsider this possibility if
a lower heating load line equation slope factor were adopted. Id. In
the August 2016 SNOPR, DOE proposed to reduce the heating load line
equation slope factor to 1.07 for variable-speed heat pumps. DOE's
analysis suggested that, with the lower slope factor, the HSPF may be
overestimated by as much as 16 percent as a result of the inaccuracy
associated with the minimum-speed extrapolation. Hence, DOE also
proposed revision to the estimation of minimum-speed performance to
reduce the impact of the error. Specifically, for heat pumps that vary
the minimum speed when operating in outdoor temperatures that are in a
range for which the minimum-speed performance factors into the HSPF
calculation, DOE proposed the following.
Adoption of a definition, ``minimum-speed-limiting
variable-speed heat pump,'' to refer to such heat pumps.
Minimum-speed performance between 35[emsp14][deg]F and
47[emsp14][deg]F would be estimated using the intermediate-speed
frosting-operation test at 35[emsp14][deg]F and the minimum-speed test
at 47[emsp14][deg]F, and minimum-speed performance below
35[emsp14][deg]F would be equal to intermediate-speed performance.
Including in certification reports for such variable-speed
heat pumps whether this alternative approach was used to determine the
rating.
81 FR at 58191 (Aug. 24, 2016)
Rheem, Unico, Nortek, Mitsubishi, AHRI, Ingersoll Rand, ACEEE,
NRDC, and ASAP, and Lennox supported DOE's proposal to use alternative
HSFP rating approach as part of M1. (Rheem, No. 37 at p. 6; Unico, No.
30 at p. 7; Nortek, No. 22 at p. 16; Mitsubishi, No. 29 at p.4; AHRI,
No. 27 at p.19; Ingersoll Rand, No. 38 at p. 7; ACEEE, NRDC, and ASAP,
No. 33 at p. 8; Lennox, No. 25 at p. 15) Carrier/UTC supported the
methodology to account for variable-speed heat pumps that limit the low
stage speed at lower ambient conditions by not requiring additional
testing. (Carrier/UTC, No. 36 at p. 12) JCI essentially agreed with the
proposal, commenting that additional tests would offer minimal
improvement in HSPF accuracy, and are not worth the additional test
burden. JCI also commented that if DOE adopts this change, it should be
in appendix M1 and not in appendix M. (JCI, No. 24 at p. 17)
Carrier also commented that DOE should invest in creating an
alternative load based (or some other) test method that simplifies the
test procedure and accounts for all of the benefits of variable-speed
technology, allowing a true comparison to other technologies. (Carrier/
UTC, No. 36 at p. 12)
Goodman did not specifically comment on the proposed test procedure
change for variable-speed products, but instead suggested a
significantly revised test procedure for these products that would
include two tests each at two different outdoor temperatures for each
of the relevant compressor speeds (low, intermediate, high, and boost),
where boost speed would be optional for testing and would
[[Page 1459]]
be used for very low temperatures, e.g. 17 [deg]F and below. In
Goodman's scheme, the manufacturer would determine at which speed the
heat pump would be operating for each temperature bin, and would
certify (a) the temperature bin at which the variable-speed heat pump
begins to increase above minimum speed, (b) the temperature bin at
which full speed is achieved, and (c) in which temperature bin the
boost speed is achieved. (Goodman, No. 39 at p. 11)
In response to Carrier and Goodman, DOE would support development
by the industry and interested stakeholders of a blank-slate revision
of the test procedure for variable-speed products with consideration of
load-based methods as suggested by Carrier, but since these alternative
methods are not fully defined, and certainly have not be made available
for public comment, DOE cannot finalize any such test procedure with
this final rule.
In this final rule, DOE adopts the proposal for the alternative
method for variable-speed heat pumps that raise the compressor speed
above the minimum speed at ambient temperatures below 47 [deg]F. In
response to JCI, this alternative method was proposed only for appendix
M1 and is adopted in this final rule only for appendix M1.
4. Revised Heating Mode Test Procedure for Units Equipped With
Variable-Speed Compressors
In the November 2015 SNOPR, DOE revisited the heating season
ratings procedure for variable-speed heat pumps found in section 4.2.4
of appendix M of 10 CFR part 430 subpart B. DOE proposed as part of
appendix M1 an optional approach for testing variable-speed heat pumps
that included a test conducted at 2 [deg]F outdoor temperature (or at
the low cutoff temperature, whichever is higher). The proposal would
have allowed manufacturers to choose to conduct one additional steady-
state test, at maximum compressor speed and at a low temperature of 2
[deg]F or at a low cutoff temperature, whichever is higher. 80 FR at
69322-23 (Nov. 9, 2015).
DOE received comments on this proposal, both in written form in
response to the November 2015 SNOPR, and in the CAC/HP ECS
negotiations. Working group members ultimately agreed that the optional
test should be conducted at 5 [deg]F rather than 2 [deg]F--this is
Recommendation #5 in the Term Sheet. (CAC ECS: ASRAC Term Sheet, No. 76
at p. 3)
The revised variable-speed heat pump test procedure proposed in the
August 2016 SNOPR included the following changes in appendix M1.
If the optional 5 [deg]F full-speed test (to be designated
H42) is conducted, full-speed performance for ambient
temperatures between 5 [deg]F and 17 [deg]F would be calculated using
interpolation between full-speed test measurements conducted at these
two temperatures, rather than the current approach, which uses
extrapolation of performance measured at 17 [deg]F and 47 [deg]F
ambient temperatures. For all heat pumps for which the 5 [deg]F full-
speed test is not conducted, the extrapolation approach would still be
used to represent performance for all ambient temperatures below 17
[deg]F.
A target wet bulb temperature of 3.5 [deg]F for the
optional 5 [deg]F test.
If the optional 5 [deg]F full-speed test is conducted,
performance for ambient temperatures below 5 [deg]F would be calculated
using the same slopes (capacity vs. temperature and power input vs.
temperature) as determined for the heat pump between 17 [deg]F and 47
[deg]F. Specifically, the extrapolation would be based on the 17
[deg]F-to-47 [deg]F slope rather than the 5 [deg]F-to-17 [deg]F slope.
If the 47 [deg]F full-speed test is conducted at a different speed than
the 17 [deg]F full-speed test, the extrapolation would be based on the
standardized slope discussed in section III.B.7.
Manufacturers would have to indicate in certification
reports whether the 5 [deg]F full-speed test was conducted.
As proposed for appendix M and discussed in section
III.B.7, a 47 [deg]F full-speed test, designated the H1N
test, would be used to represent the heating capacity. However, for
appendix M1, this test would be conducted at the maximum speed at which
the system controls would operate the compressor in normal operation in
a 47 [deg]F ambient temperature.
If the heat pump limits the use of the minimum speed
(measured in terms of RPM or power input frequency) of the heat pump
when operating at ambient temperatures below 47 [deg]F (i.e. does not
allow use of speeds as low as the minimum speed used at 47 [deg]F for
any temperature below 47 [deg]F), a modified calculation would be used
to determine minimum-speed performance below 47 [deg]F (this proposal
is discussed in section III.C.3.d).
81 FR at 58192-93 (Aug. 24, 2016).
DOE also requested comment regarding whether the 2 [deg]F test for
triple-capacity northern heat pumps should be changed to a 5 [deg]F
test. 81 FR at 58193. (Aug. 24, 2016).
Carrier/UTC, Lennox, the Joint Advocates, JCI, Ingersoll Rand,
Goodman, Nortek, Unico, NEEA, Rheem, CA IOU, AHRI, and Mitsubishi
agreed with DOE's proposal to adopt a very low temperature test for
heat pumps, at the 5 [deg]F temperature agreed to by the CAC/HP ECS
Working Group, rather than the 2 [deg]F initially proposed. (Carrier/
UTC, No. 36 at p. 12; Lennox, No. 25 at p. 15; ACEEE, NRDC, and ASAP,
No. 33 at p. 8, JCI, No. 24 at p. 17; Ingersoll Rand, No. 38 at p. 7,
Goodman, No. 39 at p. 11; Nortek, No. 22 at p. 16; Unico, No. 30 at p.
7; NEEA, No. 35 at p. 3; Rheem, No. 37 at p. 6; CA IOU, No. 32 at p.4;
AHRI, No. 27 at p.19; Mitsubishi, No. 29 at p.4) Rheem and the Joint
Advocates commented that if the 5 [deg]F full-speed test is conducted,
the full-speed performance should be calculated using interpolation,
rather than extrapolation. (Rheem, No. 37 at p. 6; ACEEE, NRDC, and
ASAP, No. 33 at p. 8)
Goodman further suggested that an optional 5 [deg]F test also be
allowed for two[hyphen]stage and single[hyphen]speed heat pumps. In
addition, Goodman recommended that for all of these products for which
the optional 5 [deg]F test is conducted, performance for all ambient
conditions below 17 [deg]F be based on the 5 [deg]F and 17 [deg]F
tests, using linear interpolation between these temperatures and linear
extrapolation below 5 [deg]F, explaining that the potential inaccuracy
of the extrapolation below 5 [deg]F is not so important because less
than 1% of heating performance for the HSPF in Region IV occurs at
temperatures less than 5 [deg]F. Goodman clarified that its support for
this approach, including extension to single-speed and two-stage
products, is contingent on the 5 [deg]F test being optional. (Goodman,
No. 39 at pp. 5-6)
Unico suggested that DOE consider establishing a cold climate heat
pump product class with different test methods both for heating and
cooling performance and different energy conservation standards for
both operating modes in order to incentivize development of such
products, claiming that they do not rate well using the current HSPF
and SEER metrics because they are optimized for heating in lower
ambient temperatures. (Unico, No. 30 at p. 7)
In response to stakeholders' comments, DOE has adopted the optional
5 [deg]F test for variable-speed heat pumps. DOE notes that the Joint
Advocate's suggestion to require use of interpolation, rather than
extrapolation based on tests conducted in 47 [deg]F and 17 [deg]F
temperatures, when the 5 [deg]F test is conducted, is fully consistent
with the proposal and is how the test procedure is adopted in this
rule.
In response to Goodman's comments, DOE has extended 5 [deg]F
testing as an
[[Page 1460]]
optional test to HSPF rating for single-speed and two-stage heat pumps.
For single-speed, two-stage, and variable-speed heat pumps that are
tested using the optional 5 [deg]F full-speed test (to be designated
H42), full-speed performance for ambient temperatures
between 5 [deg]F and 17 [deg]F will be calculated using interpolation
based on full-speed test measurements conducted at these two
temperatures, rather than the current approach, which uses
extrapolation of performance measured at 17 [deg]F and 47 [deg]F
ambient temperatures. Full speed-performance for temperatures lower
than 5 [deg]F will be calculated for single-speed and two-stage heat
pumps using extrapolation based on the tests conducted at 5 [deg]F and
17 [deg]F, rather than using the 17 [deg]F-to-47 [deg]F slope that was
proposed and is adopted for variable-speed heat pumps. DOE considers
extrapolation below 5 [deg]F for these products to be acceptable
because the 5 [deg]F and 17 [deg]F tests will be conducted at the same
compressor speed. For all heat pumps for which the 5 [deg]F full-speed
test is not conducted, the extrapolation approach using test results
for 17 [deg]F and 47 [deg]F temperatures (or the standardized slope
factors for variable-speed heat pumps which do not use the same speed
for these tests) would be used to represent performance for all ambient
temperatures below 17 [deg]F.
DOE considered Unico's suggestion to create a separate product
class with a different test standard and test procedure for products
designed for cold climate. However, because other stakeholders have not
had the opportunity to comment, DOE cannot adopt that suggestion in
this final rule.
In response to DOE's proposal of a target wet bulb temperature of
3.5 [deg]F for the optional 5 [deg]F test, ACEEE, NRDC, and ASAP agreed
with the proposed 3.5 [deg]F target wet bulb temperature. (ACEEE, NRDC,
and ASAP, No. 33 at p. 8) Carrier/UTC, Lennox, JCI, Ingersoll Rand,
Goodman, Nortek, NEEA, Rheem, the CA IOUs, AHRI, and Mitsubishi all
recommended that the target wet bulb temperature for the 5 [deg]F test
should be 3 [deg]F or less, rather than the proposed 3.5 [deg]F target.
The commenters indicated that holding tight tolerances on the wet bulb
temperature at such low temperatures is very challenging, but that the
frost loading for this temperature is so low that the variation in
moisture up to the 3 [deg]F wet bulb temperature level would not affect
the test significantly. Unico made a similar recommendation, but
suggested a maximum of 4 [deg]F wet bulb temperature. (Carrier/UTC, No.
36 at p. 12; Lennox, No. 25 at p. 15; JCI, No. 24 at p. 17; Ingersoll
Rand, No. 38 at p. 7, Goodman, No. 39 at p. 11; Nortek, No. 22 at p.
16; Unico, No. 30 at p. 7; NEEA, No. 35 at p. 3; Rheem, No. 37 at p. 6;
CA IOU, No. 32 at p.4; AHRI, No. 27 at p.19; Mitsubishi, No. 29 at
p.4). DOE agrees that the amount of moisture in 5 [deg]F air would be
sufficiently low that imposing a maximum wet bulb temperature of 3
[deg]F would be adequate to ensure test repeatability; hence, DOE
adopts the suggestion to set a maximum level of 3 [deg]F in this final
rule.
JCI, Goodman, Unico, UTC, AHRI, ACEEE, NRDC, and ASAP supported
testing triple-capacity northern heat pumps at 5 [deg]F to be
consistent with other heat pumps. In addition, AHRI suggests that DOE
modify the test procedure for triple-capacity northern heat pumps, and
allow variable speed heat pumps to be tested like the triple-capacity
northern heat pumps in heating mode. Unico also suggested that triple-
capacity systems should also be tested at 17 [deg]F at the third
(boost) capacity to allow for extrapolation (H33), thus adding a
capacity curve at the third capacity. (JCI, No.24, at p 17; Goodman,
No. 39, at p 14; Unico, No. 30 at p 7; Carrier/UTC No. 36 at p. 12;
AHRI, No. 27 at p. 19; ACEEE, NRDC, and ASAP, No. 33 at p. 8)
In response to those comments, DOE adopts testing of triple-
capacity northern heat pumps at 5 [deg]F in both appendix M and
appendix M1. DOE considered AHRI's suggestion of modifying the testing
of triple-capacity northern heat pumps and allowing testing variable-
speed heat pumps using the procedure, and decided not to make the
changes in this final rule. More discussion regarding this issue is in
section III.B.7. In response to Unico's suggestion on adding a 17
[deg]F test at the 3rd capacity to allow for extrapolation (H33), DOE
notes that the current triple-capacity test procedure already requires
the requested test.
As discussed in section III.B.7, many stakeholders responded to
DOE's proposal of modification to the test procedure for variable-speed
heat pumps in appendix M, recommending that the proposed changes, if
adopted, should be part of appendix M1 rather than appendix M. In
response to these comments, DOE has removed from appendix M the
requirement that the H32 test be conducted at the highest
speed that would normally be used in 17 [deg]F ambient conditions--this
change is adopted, however, in appendix M1.
D. Effective Dates and Representations
1. Effective Dates
DOE finalized some appendix M requirements in the June 2016 Final
Rule, and representations must be made in accordance with appendix M,
as adopted in that Final Rule, starting 180 days after it was published
(December 6, 2016). DOE proposed additional changes to appendix M in
the August 2016 SNOPR, some of which are adopted in this final rule,
and representations must be made in accordance with this revised
version of appendix M 180 days after this final rule is published.
Representations must be made in accordance with the adopted appendix M1
when compliance with amended energy conservation standards is required.
Carrier and Mortex requested that the effective date of appendix M,
including the changes published in the June 2016 final rule, be made
180 days from when this rule is finalized. (Carrier/UTC, No. 36 at p.
2; Mortex Products, Inc, No. 26 at p. 2) Ingersoll Rand recommended
that all changes to M be made effective at the same time. (Ingersoll
Rand, No. 38 at p. 3)
Mortex commented that if that is not possible, then the appendix M
changes in the August 2016 SNOPR should be moved to appendix M1.
(Mortex Products, Inc, No. 26 at p. 2) AHRI commented similarly. (AHRI,
No. 27 at p. 8) JCI also recommended that all of the proposed test
procedure changes in the August 2016 SNOPR in appendix M and all
updated sections of 10 CFR 429 become effective at the same time that
appendix M1 and the corresponding standard revision become effective.
(JCI, No. 24 at p. 18) Goodman requested for multiple changes to
variable-speed heat pumps be moved from appendix M to appendix M1 and
requested that for those changes not moved to appendix M1, DOE exercise
its authority under 42 U.S.C. 6293(c)(3) to extend the effective date
another 180 days, for a total of 360 days in order to permit
manufacturers a more appropriate time period to address the required
changes. (Goodman, No. 39 at p. 12)
DOE notes that appendix M, as adopted in the June 2016 Final Rule,
is already effective, and that the date by which representations must
be in accordance with appendix M, as so adopted, is mandated by
statute. (42 U.S.C. 6293(c)(2)) DOE maintains that appendix M revisions
adopted in the final rule do not require re-testing as compared with
appendix M as adopted in the June 2016 Final Rule (i.e., DOE does not
expect the revisions to change the ratings). In certain cases where
commenters expressed specific concern, such as for the time delay
requirement for off mode power consumption, DOE has moved items to
appendix M1. As noted by Goodman, 42 U.S.C. 6293(c)(3)
[[Page 1461]]
does allow individual manufacturers to request an additional 180 days
for representations. This request cannot be made through a rulemaking
public comment submission and must be done through petition separately.
(42 U.S.C. 6293(c)(3))
2. Comment Period Length
JCI commented that Under Section 323(b)(2) of EPCA, the public's
opportunity to comment ``shall be not less than 60 days and may be
extended for good cause shown to not more than 270 days.'' 42 U.S.C.
6293(b)(2) JCI commented that given the nature of the proposals in the
August 2016 SNOPR, DOE is required to provide a minimum 60-day comment
period. JCI commented that test procedure revisions are frequently
complex and technical, and Section 323(b)(2) can only reasonably be
read to provide a new comment period to ensure that the public has an
adequate opportunity for public comment on each discrete test procedure
proposal.
In response, DOE notes that this was the fifth round of comments on
this particular test procedure rulemaking. Further, DOE made available
the pre-publication notice to stakeholders 3 weeks in advance of the
actual Federal Register publication, effectively allowing for almost a
two-month review period. Third, DOE received comments on both sides of
the issue both requesting an extension and urging the Secretary to
finalize the test procedure as expeditiously as possible. Lastly, there
is a statutory maximum comment period for which DOE must be mindful,
which DOE was close to reaching. Consequently, DOE did not extend the
comment period for the CAC/HP TP SNOPR.
3. Representations From Appendix M1 Before Compliance Date
Lennox recommended that representations in accordance with appendix
M1 be permitted 12 months prior to the compliance date of the 2023
amended energy conservation standards. They stated that while there
must be a clear differentiation between the current appendix M and new
appendix M1 efficiency descriptors associated with the amended
standards, permitting representations 12 months prior to adoption helps
avoid market disruption on the compliance date. They added that one
year allows contractors, distributors and manufacturers adequate time
to plan and educate the supply chain in advance of the standard change.
(Lennox, No. 25 at p. 2-3) ADP made a similar suggestion, except
without setting a time limit on when the representations in accordance
with appendix M1 could begin. (ADP, No. 23 at p. 3) Carrier strongly
suggested that manufacturers not have any repercussion or penalties
from DOE for choosing to comply early with appendix M1. (Carrier/UTC,
No. 36 at p. 4)
DOE has guidance in place that allow manufacturers to use the
appendix M1 test procedure early as long as they are following the
guidelines outlined therein. More information regarding early
compliance can be found at: https://www1.eere.energy.gov/buildings/appliance_standards/pdfs/tp_earlyuse_faq_2014-8-25.pdf.
E. Comments Regarding the June 2016 Final Rule
1. Determination of Represented Values for Single-Split Systems
In the June 2016 final rule DOE adopted provisions for determining
the represented values of single-split system air conditioners based on
recommendations from the CAC/HP ECS Working Group. The recommendations
from the CAC/HP ECS Working Group (Recommendation #7 of the Term Sheet,
see CAC ECS, No. 76 at p. 4) read as follows:
Every combination distributed in commerce must be rated.
[cir] Every single-stage and two-stage condensing unit distributed
in commerce (other than a condensing unit for a 1-to-1 mini split) must
have at least 1 coil-only rating that is representative of the least
efficient coil distributed in commerce with a particular condensing
unit.
Every condensing unit distributed in commerce must have at
least 1 tested combination.
[cir] For single-stage and two-stage condensing units (other than
condensing units for a 1-to-1 mini split), this must be a coil-only
combination.
All other combinations distributed in commerce for a given
condensing unit may be rated based on the application of an AEDM or
testing in accordance with the applicable sampling plan.
81 FR at 37002-03 (June 8, 2016)
In the June 2016 final rule, DOE adopted the first and third
recommendations. DOE did not relax the HSVC requirement for tested
combinations as intended as part of the second recommendation, but did
explicitly codify the requirement to test a coil-only combinations for
single-stage and two-stage condensing units (including SDHV and space-
constrained systems).
AHRI commented that the CAC/HP ECS ASRAC Working Group's
recommendations were made in the context of appendix M1, including the
proposed requirement for two-stage condensing units (other than
condensing units for a 1-to-1 mini split) to be a coil-only combination
and have at least one tested combination. AHRI commented that
implementing this requirement before the effective date of the 2023
standard would be contradictory to the Working Group's recommendation
and that would be an excessive burden on manufacturers to retest
products, specifically two-stage air conditioners, in a short period of
time. AHRI requested that DOE modify the test procedure so this
requirement would be implemented January 1, 2023. Nortek, Carrier/UTC,
Lennox, and Ingersoll Rand commented similarly. (AHRI, No. 27, p. 2;
Nortek, No. 22 at p. 2-3; Carrier/UTC, No. 36 at p. 2-3; Lennox, No. 25
at p. 3; Ingersoll Rand, No. 38 at p. 1-2)
Additionally, Nortek commented that the requirement that two-speed
products be tested with a coil-only combination has the potential to
change ratings derived previously using a blower coil or the ARM.
Nortek commented that this was part of the consensus agreement of the
negotiated rulemaking for the appendix M1 test procedure, and that
implementing this in the appendix M test procedure may provide
unintended consequences, namely that some high efficiency products may
be removed from the market as a result of regional standards. Nortek
suggested it would be best to implement this change in tested
combination requirements with the appendix M1 test procedure. (Nortek,
No. 22 at p. 19-20)
Nortek commented that it did not agree with DOE requiring a coil-
only match for two-stage equipment, which they believed should be
optional. Nortek commented that to provide the rated efficiency,
multiple capacity systems require a matched indoor blower system to
provide the correct air-flows at the different stages, and that a
blower-coil match is appropriate for these systems. Nortek commented
that they do not wish to market a match they believe is inconsistent
with providing the rated efficiency. Nortek strongly encouraged DOE to
reconsider requiring manufacturers to rate a hypothetical two-stage
match that the manufacturer does not intend to market, and that it
believes that unintended consequences will occur if they are forced to
do so. (Nortek, No. 22 at p. 19-20)
First Co. commented that space-constrained thru-the-wall units are
sold
[[Page 1462]]
and designed for installation with indoor air handlers fitted with ECM
motors, meeting the applicable 12 SEER standard when matched with
blower coil units. If the ``coil only'' testing requirement is
enforced, most of these units will be unable to meet the 12 SEER
standard because the default value for wattage in ``coil only'' testing
exceeds the actual wattage of the high efficiency motors used in the
blower coils with First Co. products. First Co. commented that their
understanding is that the Working Group did not include a member that
manufactures space-constrained units, but includes members that may
benefit from the elimination of these products. (First Co, No. 21 at p.
2-3)
Lennox recommended that DOE further define the requirements for
single and two-stage AC systems to test the ``least efficient''
combination and recommended that the ``least efficient'' combination be
defined as the up-flow coil match with the lowest NGIFS. Lennox
commented that it is common practice for manufacturers to rate several
coils of various geometries at the base (i.e., the least efficient
level) for that product with the up-flow configuration being the most
common, and that requiring a test of the lowest NGIFS up-flow coil
clarifies which coil is required as the basis for testing. (Lennox, No.
25 at p. 3)
All of these comments address language adopted in the June 2016
Final Rule and for which no proposals were made in the August 2016
SNOPR. DOE notes that numerous coil-only two-stage combinations have
been listed in DOE's CCMS and AHRI's database for years. For example,
DOE identified 2,400 such combinations of two-stage split system air
conditioners in a version of the database dating to late 2014. DOE also
notes that the test procedure has specific provisions for setting air
volume rate when testing such units (i.e. section 3.1.4.2.c of Appendix
M), which correspond to how these units are typically installed in the
field. These observations counter claims that multiple capacity systems
require a matched indoor blower system and render this assertion false.
In response to First Co.'s comment regarding the required coil-only
test for testing of space constrained products, DOE asserts that an
exclusion for coil-only testing of space-constrained products was never
established. DOE notes that prior to the effective date of the June
2016 final rule, paragraph (a)(2)(ii) of 10 CFR 429.16 still included
text that stated that an exclusion for the coil-only test requirement
applied for through-the-wall units that were sold and installed with
blower coil indoor units. On January 23, 2010, all of the products
meeting the definition for the product class of through-the-wall class
of split system air conditioners were reclassified as part of the space
constrained product class, for which a 12-SEER standard was set for
cooling mode and a 7.4 HSPF standard was set for heat pump heating mode
in a final rule published August 17, 2004. 69 FR 50997, 51001.
Subsequently, the American Energy Manufacturing Technical Corrections
Act (AEMTCA), which was signed into law on December 8, 2012,
reintroduced definitions of through-the-wall air conditioners and
through-the-wall heat pumps, which DOE subsequently codified into its
regulations in a final rule published April 11, 2014. As part of that
final rule, DOE made clear that products that meet the definition of
through-the-wall air conditioners and heat pumps would be considered
part of the space constrained air conditioner product class for
regulatory purposes, regardless of whether they also met the definition
of through-the-wall air conditioner. 79 FR 20091. Thus in DOE's view,
First Company's assertion that the coil-only testing requirement did
not apply to its through-the-wall products is invalid. Notwithstanding
the requirement of all space constrained split system air conditioners
that are single stage must be tested as coil-only, First Company
explains in their own comment that their space-constrained through-the-
wall condensing units are sold and designed for installation with
indoor air handlers fitted with ECM motors. However, DOE notes the
exclusion previously in 10 CFR 429.16(a)(2)(ii) for units that were
sold and installed with blower coil indoor units would not have
encompassed the circumstances that First Company describes. Thus, First
Company would have always been subject to the coil-only requirement.
While the language being adopted in this final rule removes the
exclusion for through-the-wall units that were sold and installed with
blower coil units from the coil-only testing requirement, this should
have no effect on First Company's ratings if rated in accordance with
current regulations. If a manufacturer believes that coil-only testing
of a product is not appropriate because the basic model is only sold
and installed exclusively with blower coil indoor units, the
manufacturer may petition DOE for a test procedure waiver showing that
installation is exclusively blower coil and requesting a blower coil
test. To date, DOE has not received any petitions of this kind.
2. Alternative Efficiency Determination Methods
In the June 2016 Final Rule, DOE adopted alternative efficiency
determination method (AEDM) requirements for central air conditioner
and heat pumps in place of the previously used alternative rating
methods (ARMs). 81 FR at 37054 (June 8, 2016). DOE did not allow the
use of AEDMs for multi-split systems. 81 FR at 37052.
First Co. commented that ICMs, including First Co., have used DOE
approved Alternative Rating Methods (ARMs) for many years, and
converting from using an ARM to an ADEM requires extensive engineering
time and laboratory testing. First Co. contends that DOE's claim that
it is not requiring ICMs to conduct additional testing for AEDM
validation fails to recognize that additional testing beyond
certification testing is necessary for ICMs to develop a new AEDM.
First Co. commented that compliance by the deadline will be nearly
impossible for ICMs that lack their own testing facility and that the
extensive time and engineering that ICMs must devote to the meet the
new regulations deprives them of the opportunity to innovate or improve
existing product lines. (First Co, No. 21 at p. 1)
AHRI commented that the ``tested combination'' requirements for
multi-split systems require manufacturers to test at least two samples
of a ``tested combination'' for non-ducted indoor units and at least
another two samples of a ``tested combination'' for ducted indoor
units. AHRI commented that as an AEDM cannot be used to rate a Basic
Model, this causes more burden on the multi-split manufacturer than the
non-multi-split manufacturer, and is not in line with the fact that
other products can have two samples of a single tested combination
tested with unlimited number of non-tested combinations rated by AEDM.
AHRI commented that performing all required tests in six months is not
achievable by some manufacturers. AHRI requested that DOE reconsider
the option to apply the AEDM for multi-splits <65,000 Btu/h in the same
manner as applied for VRFs >=65,000 Btu/h. (AHRI, No. 27 at p. 20)
All of these comments address language adopted in the June 2016
Final Rule and for which no proposals were made in the August 2016
SNOPR. As a result, DOE is declining to modify these requirements in
this final rule.
[[Page 1463]]
3. NGIFS Limit for Outdoor Unit With No Match
In the June 2016 Final Rule, DOE adopted the required NGIFS for an
indoor unit tested with an outdoor unit with no match to be 1.0. 81 FR
at 37009-10 (June 8, 2016)
Nortek and AHRI commented that the NGIFS limitation of 1.0 as
finalized in the June 2016 Final Rule is only applicable to coils with
\3/8\-inch diameter tubes and is not applicable to either microchannel,
\5/16\'', or 7mm diameter tubes, or any other diameter tubes. (Nortek,
No. 22 at p. 5-6; AHRI, No. 27 at p. 6)
DOE responds that the vast majority of indoor units that are field-
matched with no-match outdoor units have \3/8\-in OD tubing, which was
used almost exclusively for CAC/HP evaporators before 2010. Further, as
stated previously, this requirement was not part of the August 2016
SNOPR, and as such, DOE cannot modify this requirement in this final
rule. Section III.A.5.f addresses concerns about the applicability of
the requirements (such as for tube styles) of indoor units to be tested
with no-match outdoor units.
4. Definitions
In the June 2016 Final Rule, DOE adopted definitions for multi-
split system. 81 FR at 37059 (June 8, 2016).
Mitsubishi, AHRI and Nortek commented that DOE had previously
agreed to remove coil-only from the multi-split definition.
(Mitsubishi, No. 29 at p. 5; AHRI, No. 27 at p. 22; Nortek, No. 22 at
p. 19) Mortex commented that there will be applications for coil-only
indoor units and thus there is no reason to remove coil-only from the
proposed definition. (EERE-2016-BT-TP-0029, No. 26 at p. 3) As stated
previously, this requirement was not part of the August 2016 SNOPR, and
as such, DOE cannot modify this requirement in this final rule.
Additionally, DOE agrees with Mortex that it is a possible application
that coil-only indoor units are used in a multi-split system, so
keeping coil-only in the multi-split definition is reasonable and there
is no need to modify the definition.
5. Inlet Plenum Setup
In the June 2016 Final Rule, DOE clarified the indoor unit air
inlet geometry and specifically made revision to avoid inlet plenum
being installed upstream of the airflow prevention device. 81 FR at
37037 (June 8, 2016).
AHRI and Nortek commented that DOE's clarification of inlet plenum
brings concern that an overall height will exceed the current height
limit of many psychrometric rooms. AHRI and Nortek requested DOE to
consider allowing an alternative approach, included in ASHRAE's
research project 1581. Specifically, AHRI and Nortek requested that DOE
approve the use of the 6'' skirt coupled with the 90[deg] square vane
elbow and the appropriate leaving duct as being an alternative to the
configuration. ASHRAE Standards Policy Committee (SPC) is currently
working to add the details of RP 1581 to the standard and has a Work
Statement for a project investigating the damper box/inlet duct to
provide an improved recommendation for that as well. (AHRI, No. 27 at
p. 21; Nortek, No. 22 at p. 17-18)
As stated previously, this requirement was not part of the August
2016 SNOPR, and as such, DOE cannot modify this requirement in this
final rule. However, DOE is willing to consider this change in a future
rulemaking after ASHRAE Standards Policy Committee has published
standard revision to reflect this recommendation.
6. Off-Mode Power Consumption
In the June 2016 Final Rule, DOE adopted the off-mode test
procedure and the method of calculation. In addition, DOE required that
the calculated P1 and P2 should be rounded to the nearest watt. 81 FR
at 37095-97 (June 8, 2016).
AHRI and Nortek commented that the accuracy of 0.5% for all watt-
hour measurement in section 2.8 is not feasible for off-mode power
measurement because it can be very close to zero. So AHRI suggested
that the accuracy requirement in section 2.8 be 0.5% or 0.5 W,
whichever is greater. (AHRI, No. 27 at p. 22; Nortek, No. 22 at p. 18)
Ingersoll Rand recommended that the accuracy for the off mode power
consumption measurement be 0.5 watts. (Ingersoll Rand, No. 38 at p. 5)
As stated previously, this requirement was not part of the August
2016 SNOPR, and as such, DOE cannot modify this requirement in this
final rule. Mitsubishi expressed concern that multi-split systems were
not fully considered in the development of off-mode tests, and
requested that DOE review the off-mode power requirements to ensure
that multi-split systems are not inadvertently disadvantaged.
(Mitsubishi, No. 29 at p. 5)
Although DOE cannot modify this requirement in this final rule, DOE
has reviewed the off-mode requirements and believes that multi-split
systems should follow the same procedure--thus no change to the test
procedure to specifically address multi-split systems is needed. DOE
understands that the off-mode testing for multi-split system may be
more complicated, but manufacturers have the option to develop an AEDM
for most off-mode ratings if additional test requirements are
necessary.
IV. Procedural Issues and Regulatory Review
A. Review Under Executive Order 12866
The Office of Management and Budget (OMB) has determined that test
procedure rulemakings do not constitute ``significant regulatory
actions'' under section 3(f) of Executive Order 12866, Regulatory
Planning and Review, 58 FR 51735 (Oct. 4, 1993). Accordingly, this
action was not subject to review under the Executive Order by the
Office of Information and Regulatory Affairs (OIRA) in the Office of
Management and Budget.
B. Review Under the Regulatory Flexibility Act
The Regulatory Flexibility Act (5 U.S.C. 601 et seq.) requires
preparation of a final regulatory flexibility analysis (FRFA) for any
final rule, unless the agency certifies that the rule, if promulgated,
will not have a significant economic impact on a substantial number of
small entities. A required by Executive Order 13272, ``Proper
Consideration of Small Entities in Agency Rulemaking,'' 67 FR 53461
(August 16, 2002), DOE published procedures and policies on February
19, 2003, to ensure that the potential impacts of its rules on small
entities are properly considered during the DOE rulemaking process. 68
FR 7990. DOE has made its procedures and policies available on the
Office of the General Counsel's Web site: http://energy.gov/gc/office-general-counsel.
DOE reviewed this final rule under the provisions of the Regulatory
Flexibility Act and the procedures and policies published on February
19, 2003. This final rule establishes two sets of test procedure
changes: One set of changes to DOE's already-existing test procedure,
appendix M; and another set of changes to create a new appendix M1 that
would be used for testing to demonstrate compliance with any amended
energy conservation standards. DOE has estimated the impacts of both
sets of test procedure changes on small business manufacturers.
1. Description and Estimate of the Number of Small Entities Affected
For the purpose of the regulatory flexibility analysis for this
final rule, DOE adopts the Small Business Administration (SBA)
definition of a
[[Page 1464]]
small entity within this industry as a manufacturing enterprise with
1,250 employees or fewer. DOE used the SBA's size standards to
determine whether any small entities would be required to comply with
the rule. The size standards are codified at 13 CFR part 121. The
standards are listed by North American Industry Classification System
(NAICS) code and industry description are available at: https://www.sba.gov/sites/default/files/files/Size_Standards_Table.pdf. CAC/HP
manufacturers are classified under NAICS 333415, ``Air Conditioning and
Warm Air Heating Equipment and Commercial and Industrial Refrigeration
Equipment Manufacturing.'' 70 FR 12395 (March 11, 2005)
To estimate the number of small business manufacturers of equipment
affected by this rulemaking, DOE conducted a market survey using
available public information. DOE's research involved industry trade
association membership directories (including AHRI), individual company
Web sites, and market research tools (e.g., Hoovers reports) to create
a list of companies that manufacture products applicable to this
rulemaking. DOE presented its list to manufacturers in MIA interviews
and asked industry representatives if they were aware of any other
small manufacturers during manufacturer interviews and ASRAC Working
Group meetings. DOE reviewed publicly-available data and contacted
companies on its list, as necessary, to determine whether they met the
SBA's definition of a small business manufacturer. DOE screened out
companies that do not offer products applicable to this rulemaking, do
not meet the definition of a small business, or are foreign-owned and
operated.
DOE identified 22 manufacturers of residential central air
conditioners and heat pumps that would be considered domestic small
businesses with a total of less than 3 percent of the market sales.
2. Discussion of Testing Burden and Comments
a. Testing Burdens
Potential impacts of the amended test procedure on all
manufacturers, including small businesses, come from impacts associated
with the cost of additional testing. DOE expects that many of the
provisions in this notice will result in no increase to test burden.
DOE's mandate to use new heating load line equation provisions to
calculate HSPF for heat pumps, new default values for indoor fan power
consumption, and a new interpolation approach for COP of variable-speed
heat pumps are changes to calculations and do not require any
additional time or investment from manufacturers. Similarly, DOE's
mandate to require certification of the time delay used when testing
coil-only units does not affect testing. DOE's mandate to test at new
minimum external static pressure conditions would require manufacturers
to test at different, but not additional test points using the same
equipment and methodologies required by the current test procedure.
DOE's mandate for single-package units to make the official test the
test that does not include the secondary outdoor air enthalpy method
measurement also does not require any additional testing. Similarly,
DOE's mandate to include an optional test at 5 [deg]F for variable-
speed heat pumps does not require manufacturers to do any additional
testing. However, other provisions may increase test burden. DOE
anticipates that changes to provisions for mini-split refrigerant
pressure lines may cause labs and manufacturers to relocate pressure
transducers or in a worst case scenario, build a separate satellite
test instrumentation console for pressure measurements closer to the
test samples. DOE estimates that building such a satellite console
would constitute a one-time cost on the order of $1,000 per test room.
DOE's mandate to modify the off mode test for units with self-regulated
crankcase heaters could result in more significant increases to test
burden, but for a small number of models. DOE estimates that the new
provisions could add 8 hours per test for units with self-regulated
crankcase heaters and an additional 8 hours for those units with self-
regulated crankcase heaters that also have a compressor sound blanket.
Sound blankets are premium features. DOE estimates that less than 25
percent of all units have self-regulated crankcase heaters and less
than 5 percent have self-regulated crankcase heaters and sound
blankets. DOE estimates the additional cost of testing to be $250 for
units with self-regulating crankcase heaters and $500 for units with
self-regulating crankcase heaters and sound blankets. DOE also
estimates that testing of basic models may not have to be updated more
than once every five years, and therefore the average incremental
burden of testing one basic model may be one-fifth of these values when
the cost is spread over several years.
DOE mandates labeling requirements for the indoor and outdoor units
of mobile home blower coil and coil-only systems and is also requiring
that manufacturers include a specific designation in the installation
instructions for these units. DOE estimates the additional cost to
manufacturers associated with meeting the labeling requirement to be
marginal as compared to the total production cost and the overall
impact to be small.
As discussed in this preamble, DOE identified 22 domestic small
business manufacturers of residential central air conditioners and heat
pumps. Of these, only OUMs that operate their own manufacturing
facilities (i.e., are not private labelers selling only models
manufactured by other entities) and OUM importing private labelers
would be subject to the additional requirements for testing required by
this proposed rule. DOE identified 12 such small businesses but was
able to estimate the number of basic models associated only with nine
of these.
DOE requires that only one combination associated with any given
outdoor unit be laboratory tested. 10 CFR 429.16(b). The majority of
residential central air conditioners and heat pumps offered by a
manufacturer are split-system combinations that are not required to be
laboratory tested but can be certified using an AEDM that does not
require DOE testing of these units. DOE reviewed available data for the
nine small businesses to estimate the incremental testing cost burden
those firms might experience due to the revised test procedure. These
manufacturers had an average of 35 models requiring testing. DOE
determined the numbers of models using the AHRI Directory of Certified
Product Performance, www.ahridirectory.org/ahridirectory/pages/home.aspx. As discussed, DOE estimates that less than 25 percent of
models have self-regulating crankcase heaters and less than 5 percent
have self-regulating crankcase heaters with blankets. Applying these
estimates to the average 35 models for each small manufacturer results
in an estimated two models with $500 per model in additional test costs
and nine models with $250 per model in additional test costs as a
result of the proposed changes. The additional testing cost for final
certification of these models was therefore estimated at $3,250.
Meanwhile, these certifications would be expected to last the
residential central air conditioner and heat pump life, estimated to be
at least five years based on the time frame established in EPCA for DOE
review of central air conditioner efficiency standards. Hence, average
annual additional costs for these small business manufacturers to
perform the tests is $650.
[[Page 1465]]
DOE does not expect ICMs to incur any additional burden as a result
of the amended changes because the changes for which DOE estimates
there will be increased burden do not apply to ICMs. Only outdoor units
include self-regulating crankcase heaters with or without blankets, and
DOE assumes that ICM manufacturers do not produce indoor units that
have components with off mode power consumption. Consequently, ICMs
would be able to use the off mode power measurements acquired and
certified by OUMs to meet the test procedure requirements for off mode.
Regarding the changes for mini-split refrigerant lines, DOE is not
aware of any ICMs that maintain in-house test facilities. Consequently,
the one-time cost associated with the amended changes for mini-split
refrigerant lines would not be incurred by the ICM. DOE also
anticipates that the one-time cost is low enough that the per-test cost
charged by independent labs that provide testing services to ICMs would
not increase as a result of this change.
b. Comments on the SNOPR Regulatory Flexibility Analysis
Manufacturers commented that DOE's analysis does not accurately
address the negative impacts of M and M1 test procedure changes that
small manufacturers and ICMs may face. Particularly, Advanced
Distributor Products (ADP) noted that DOE's small business impacts
focused solely on the cost of these test procedure changes and do not
take cumulative regulatory burden into consideration. A few
manufacturers stated that residential central air conditioner and heat
pump regulations threaten their ability to compete in the market, which
in turn will reduce competition and consumer choices. According to ADP,
these negative impacts are primarily due to the requirement to report
data that ICMs do not possess. (ADP, No. 23 at p. 6) Mortex attributes
these negative impacts to cumulative regulatory burden. (Mortex, No. 26
at p. 4) First Co. cites excessive testing and unreasonable deadlines
as drivers of disproportionate impacts that may reduce competition.
First Co. attributes these negative impacts to the provisions finalized
in the June 2016 test procedure final rule. (First Co., No. 21 at p. 5)
DOE acknowledges the commenters' concerns that manufacturers may
face cumulative regulatory burdens and disproportionate impacts. As
discussed throughout this notice, DOE recognizes ADP's concern related
to data reporting for ICMs and will address these issues through a
separate process. Regarding Mortex's concerns with cumulative
regulatory burden, DOE conducts an analysis of cumulative regulatory
burden as part of the concurrent energy conservation standards
rulemaking. Regardless of the findings of that analysis, DOE concludes
with this FRFA that the burdens associated only with this rulemaking
are not significant. DOE also understands that not all manufacturers
have equal access to the resources needed to meet with the requirements
of this final rule. EPCA does allow individual manufacturers to request
an additional 180 days for representations--such a request cannot be
made through a rulemaking public comment period submission and must be
done through petition. (42 U.S.C 6293(c)(3)) The majority of the
factors cited by First Co. as contributing to threats to their ability
to compete are provisions adopted in the June 2016 Final Rule and for
which no proposals were made in the August 2016 SNOPR. As a result, DOE
cannot modify these requirements in this final rule.
First Co. noted that the ASRAC Working Group did not include a
manufacturer of space-constrained products, but rather included
manufacturers that may benefit from the elimination of these products
from the market. Prior to adopting the Working Group recommendations,
First Co. said that DOE should have sought public comments on this
matter. (First Co., No. 21 at p. 2) Additionally, Unico commented that
small entities typically offer niche products, such as space-
constrained and small duct high velocity products, that larger
companies do not manufacture. Unico believes small entities, like
itself, will be disproportionately impacted by this final rule because,
for SDHV, half the system is duct work which is not tested as part of
the equipment. Consequently, comparing the real-life performance of
small duct systems with other systems is difficult. (Unico, No. 30 at
p. 7)
In response, DOE acknowledges First Co.'s concerns regarding the
lack of representation of space-constrained manufacturers in the
Working Group. During the NOPR stage, DOE identified four manufacturers
of space-constrained units. Of the four, two are AHRI members. Although
these manufacturers were not present at Working Group meetings, AHRI
served as a Working Group member. DOE assumes that AHRI represented all
of their members' interests throughout the negotiations. During the
NODA phase of the rulemaking, DOE invited space-constrained
manufacturers to participate in interviews but none were conducted.
In regards to Unico's comment, many of the CAC/HP products subject
to this test procedure are installed and used with duct work. The test
procedure does not include duct work for these products either.
Instead, the test conditions for this procedure include provisions for
minimum external static pressure, which is intended to mimic the
operating conditions consistent with field duct work for each product.
These minimum external static pressure requirements differ by product
because not all CAC/HP are installed with the same duct work. These
differing external static pressure requirements ensure that test
results are representative of field conditions and can provide
reasonable comparisons of performance.
Based on its research and discussions presented in this section,
DOE concludes that the cost burdens accruing from the residential
central air conditioner and heat pump test procedure final rule will
not constitute ``significant economic impact on a substantial number of
small entities.''
C. Review Under the Paperwork Reduction Act of 1995
Manufacturers of central air conditioners and heat pumps must
certify to DOE that their products comply with any applicable energy
conservation standards. In certifying compliance, manufacturers must
test their products according to the DOE test procedures for central
air conditioners and heat pumps, including any amendments adopted for
those test procedures. DOE has established regulations for the
certification and recordkeeping requirements for all covered consumer
products and commercial equipment, including central air conditioners
and heat pumps. 76 FR 12422 (March 7, 2011); 80 FR 5099 (Jan. 30,
2015). The collection-of-information requirement for the certification
and recordkeeping is subject to review and approval by OMB under the
Paperwork Reduction Act (PRA). This requirement has been approved by
OMB under OMB control number 1910-1400. Public reporting burden for the
certification is estimated to average 30 hours per response, including
the time for reviewing instructions, searching existing data sources,
gathering and maintaining the data needed, and completing and reviewing
the collection of information.
Notwithstanding any other provision of the law, no person is
required to respond to, nor shall any person be subject to a penalty
for failure to comply with, a collection of information subject to the
requirements of the PRA, unless that collection of information displays
a currently valid OMB Control Number.
[[Page 1466]]
D. Review Under the National Environmental Policy Act of 1969
In this final rule, DOE amends its test procedure amendments that
it expects will be used to develop and implement future energy
conservation standards for central air conditioners and heat pumps. DOE
has determined that this rule falls into a class of actions that are
categorically excluded from review under the National Environmental
Policy Act of 1969 (42 U.S.C. 4321 et seq.) and DOE's implementing
regulations at 10 CFR part 1021. Specifically, this final rule amends
the existing test procedures without affecting the amount, quality or
distribution of energy usage, and, therefore, will not result in any
environmental impacts. Thus, this rulemaking is covered by Categorical
Exclusion A5 under 10 CFR part 1021, subpart D, which applies to any
rulemaking that interprets or amends an existing rule without changing
the environmental effect of that rule. Accordingly, neither an
environmental assessment nor an environmental impact statement is
required.
DOE's CX determination for this final rule is available at http://energy.gov/nepa/categorical-exclusion-cx-determinations-cx.
E. Review Under Executive Order 13132
Executive Order 13132, ``Federalism,'' 64 FR 43255 (August 4, 1999)
imposes certain requirements on agencies formulating and implementing
policies or regulations that preempt State law or that have Federalism
implications. The Executive Order requires agencies to examine the
constitutional and statutory authority supporting any action that would
limit the policymaking discretion of the States and to carefully assess
the necessity for such actions. The Executive Order also requires
agencies to have an accountable process to ensure meaningful and timely
input by State and local officials in the development of regulatory
policies that have Federalism implications. On March 14, 2000, DOE
published a statement of policy describing the intergovernmental
consultation process it will follow in the development of such
regulations. 65 FR 13735. DOE has examined this final rule and has
determined that it would not have a substantial direct effect on the
States, on the relationship between the national government and the
States, or on the distribution of power and responsibilities among the
various levels of government. EPCA governs and prescribes Federal
preemption of State regulations as to energy conservation for the
products that are the subject of this final rule. States can petition
DOE for exemption from such preemption to the extent, and based on
criteria, set forth in EPCA. (42 U.S.C. 6297(d)) No further action is
required by Executive Order 13132.
F. Review Under Executive Order 12988
Regarding the review of existing regulations and the promulgation
of new regulations, section 3(a) of Executive Order 12988, ``Civil
Justice Reform,'' 61 FR 4729 (Feb. 7, 1996), imposes on Federal
agencies the general duty to adhere to the following requirements: (1)
Eliminate drafting errors and ambiguity; (2) write regulations to
minimize litigation; (3) provide a clear legal standard for affected
conduct rather than a general standard; and (4) promote simplification
and burden reduction. Section 3(b) of Executive Order 12988
specifically requires that Executive agencies make every reasonable
effort to ensure that the regulation: (1) Clearly specifies the
preemptive effect, if any; (2) clearly specifies any effect on existing
Federal law or regulation; (3) provides a clear legal standard for
affected conduct while promoting simplification and burden reduction;
(4) specifies the retroactive effect, if any; (5) adequately defines
key terms; and (6) addresses other important issues affecting clarity
and general draftsmanship under any guidelines issued by the Attorney
General. Section 3(c) of Executive Order 12988 requires Executive
agencies to review regulations in light of applicable standards in
sections 3(a) and 3(b) to determine whether they are met or it is
unreasonable to meet one or more of them. DOE has completed the
required review and determined that, to the extent permitted by law,
this final rule meets the relevant standards of Executive Order 12988.
G. Review Under the Unfunded Mandates Reform Act of 1995
Title II of the Unfunded Mandates Reform Act of 1995 (UMRA)
requires each Federal agency to assess the effects of Federal
regulatory actions on State, local, and Tribal governments and the
private sector. Public Law 104-4, sec. 201 (codified at 2 U.S.C. 1531).
For a regulatory action likely to result in a rule that may cause the
expenditure by State, local, and Tribal governments, in the aggregate,
or by the private sector of $100 million or more in any one year
(adjusted annually for inflation), section 202 of UMRA requires a
Federal agency to publish a written statement that estimates the
resulting costs, benefits, and other effects on the national economy.
(2 U.S.C. 1532(a), (b)) The UMRA also requires a Federal agency to
develop an effective process to permit timely input by elected officers
of State, local, and Tribal governments on a proposed ``significant
intergovernmental mandate,'' and requires an agency plan for giving
notice and opportunity for timely input to potentially affected small
governments before establishing any requirements that might
significantly or uniquely affect small governments. On March 18, 1997,
DOE published a statement of policy on its process for
intergovernmental consultation under UMRA. 62 FR 12820; also available
at http://energy.gov/gc/office-general-counsel. DOE examined this final
rule according to UMRA and its statement of policy and determined that
the rule contains neither an intergovernmental mandate, nor a mandate
that may result in the expenditure of $100 million or more in any year,
so these requirements do not apply.
H. Review Under the Treasury and General Government Appropriations Act,
1999
Section 654 of the Treasury and General Government Appropriations
Act, 1999 (Public Law 105-277) requires Federal agencies to issue a
Family Policymaking Assessment for any rule that may affect family
well-being. This final rule will not have any impact on the autonomy or
integrity of the family as an institution. Accordingly, DOE has
concluded that it is not necessary to prepare a Family Policymaking
Assessment.
I. Review Under Executive Order 12630
DOE has determined, under Executive Order 12630, ``Governmental
Actions and Interference with Constitutionally Protected Property
Rights'' 53 FR 8859 (March 18, 1988), that this regulation will not
result in any takings that might require compensation under the Fifth
Amendment to the U.S. Constitution.
J. Review Under Treasury and General Government Appropriations Act,
2001
Section 515 of the Treasury and General Government Appropriations
Act, 2001 (44 U.S.C. 3516 note) provides for agencies to review most
disseminations of information to the public under guidelines
established by each agency pursuant to general guidelines issued by
OMB. OMB's guidelines were published at 67 FR 8452 (Feb. 22, 2002), and
DOE's guidelines were published at 67 FR 62446 (Oct. 7, 2002). DOE has
reviewed this final rule under the OMB and DOE guidelines and has
concluded that it is
[[Page 1467]]
consistent with applicable policies in those guidelines.
K. Review Under Executive Order 13211
Executive Order 13211, ``Actions Concerning Regulations That
Significantly Affect Energy Supply, Distribution, or Use,'' 66 FR 28355
(May 22, 2001), requires Federal agencies to prepare and submit to OMB,
a Statement of Energy Effects for any significant energy action. A
``significant energy action'' is defined as any action by an agency
that promulgated or is expected to lead to promulgation of a final
rule, and that: (1) Is a significant regulatory action under Executive
Order 12866, or any successor order; and (2) is likely to have a
significant adverse effect on the supply, distribution, or use of
energy; or (3) is designated by the Administrator of OIRA as a
significant energy action. For any significant energy action, the
agency must give a detailed statement of any adverse effects on energy
supply, distribution, or use should the proposal be implemented, and of
reasonable alternatives to the action and their expected benefits on
energy supply, distribution, and use.
The regulatory action to amend the test procedure for measuring the
energy efficiency of central air conditioners and heat pumps is not a
significant regulatory action under Executive Order 12866. Moreover, it
will not have a significant adverse effect on the supply, distribution,
or use of energy, nor has it been designated as a significant energy
action by the Administrator of OIRA. Therefore, it is not a significant
energy action, and, accordingly, DOE has not prepared a Statement of
Energy Effects.
L. Review Under Section 32 of the Federal Energy Administration Act of
1974
Under section 301 of the Department of Energy Organization Act
(Pub. L. 95-91; 42 U.S.C. 7101), DOE must comply with section 32 of the
Federal Energy Administration Act of 1974, as amended by the Federal
Energy Administration Authorization Act of 1977. (15 U.S.C. 788; FEAA)
Section 32 essentially provides in relevant part that, where a proposed
rule authorizes or requires use of commercial standards, the notice of
proposed rulemaking must inform the public of the use and background of
such standards. In addition, section 32(c) requires DOE to consult with
the Attorney General and the Chairman of the Federal Trade Commission
(FTC) concerning the impact of the commercial or industry standards on
competition.
The rule incorporates testing methods contained in the following
commercial standards: AHRI 210/240-2008 with Addendum 1 and 2,
Performance Rating of Unitary Air Conditioning & Air-Source Heat Pump
Equipment; and ANSI/AHRI 1230-2010 with Addendum 2, Performance Rating
of Variable Refrigerant Flow Multi-Split Air Conditioning and Heat Pump
Equipment. While the proposed test procedure is not exclusively based
on AHRI 210/240-2008 or ANSI/AHRI 1230-2010, one component of the test
procedure, namely test setup requirements, adopts language from AHRI
210/240-2008 without amendment; and another component of the test
procedure, namely test setup and test performance requirements for
multi-split systems, adopts language from ANSI/AHRI 1230-2010 without
amendment. DOE has evaluated these standards and consulted with the
Attorney General and the Chairman of the FTC and has concluded that
this final rule fully complies with the requirement of section 32(b) of
the FEAA.
M. Description of Materials Incorporated by Reference
In this final rule, DOE incorporates by reference (IBR) into
appendix M1 to subpart B of part 430 specific sections, figures, and
tables of several test standards published by AHRI, ASHRAE, and AMCA
that are already incorporated by reference into appendix M to subpart B
of part 430: ANSI/AHRI 210/240-2008 with Addenda 1 and 2, titled
``Performance Rating of Unitary Air-Conditioning & Air-Source Heat Pump
Equipment;'' ANSI/AHRI 1230-2010 with Addendum 2, titled ``Performance
Rating of Variable Refrigerant Flow (VRF) Multi-Split Air-Conditioning
and Heat Pump Equipment;'' ASHRAE 23.1-2010, titled ``Methods of
Testing for Rating the Performance of Positive Displacement Refrigerant
Compressors and Condensing Units that Operate at Subcritical
Temperatures of the Refrigerant;'' ASHRAE Standard 37-2009, titled
``Methods of Testing for Rating Electrically Driven Unitary Air-
Conditioning and Heat Pump Equipment;'' ASHRAE 41.1-2013, titled
``Standard Method for Temperature Measurement;'' ASHRAE 41.2-1987 (RA
1992), titled ``Standard Methods for Laboratory Airflow Measurement;''
ASHRAE 41.6-2014, titled ``Standard Method for Humidity Measurement;''
ASHRAE 41.9-2011, titled ``Standard Methods for Volatile-Refrigerant
Mass Flow Measurements Using Calorimeters;'' ASHRAE 116-2010, titled
``Methods of Testing for Rating Seasonal Efficiency of Unitary Air
Conditioners and Heat Pumps;'' and AMCA 210-2007, titled ``Laboratory
Methods of Testing Fans for Certified Aerodynamic Performance Rating.''
ANSI/AHRI 210/240-2008 is an industry accepted test procedure that
measures the cooling and heating performance of central air
conditioners and heat pumps and is applicable to products sold in North
America. The test procedure in this final rule references various
sections of ANSI/AHRI 210/240-2008 that address test setup, test
conditions, and rating requirements. ANSI/AHRI 210/240-2008 is readily
available on AHRI's Web site at http://www.ahrinet.org/site/686/Standards/HVACR-Industry-Standards/Search-Standards.
ANSI/AHRI 1230-2010 is an industry accepted test procedure that
measures the cooling and heating performance of variable refrigerant
flow (VRF) multi-split air conditioners and heat pumps and is
applicable to products sold in North America. The test procedure in
this final rule for VRF multi-split systems references various sections
of ANSI/AHRI 1230-2010 that address test setup, test conditions, and
rating requirements. ANSI/AHRI 1230-2010 is readily available on AHRI's
Web site at http://www.ahrinet.org/site/686/Standards/HVACR-Industry-Standards/Search-Standards.
ASHRAE 23.1-2010 is an industry accepted test procedure for rating
the thermodynamic performance of positive displacement refrigerant
compressors and condensing units that operate at subcritical
temperatures. The test procedure in this final rule references sections
of ASHRAE 23.1-2010 that address requirements, instruments, methods of
testing, and testing procedure specific to compressor calibration.
ASHRAE 23.1-2010 can be purchased from ASHRAE's Web site at https://www.ashrae.org/resources-publications.
ASHRAE Standard 37-2009 is an industry accepted standard that
provides test methods for determining the cooling capacity of unitary
air conditioning equipment and the cooling or heating capacities, or
both, of unitary heat pump equipment. The test procedure in this final
rule references various sections of ASHRAE Standard 37-2009 that
address test conditions and test procedures. ASHRAE Standard 37-2009
can be purchased from ASHRAE's Web site at https://www.ashrae.org/resources-publications.
ASHRAE 41.1-2013 is an industry accepted method for measuring
temperature in testing heating, refrigerating, and air conditioning
equipment. The test procedure in this
[[Page 1468]]
final rule references sections of ASHRAE 41.1-2013 that address
requirements, instruments, and methods for measuring temperature.
ASHRAE 41.1-2013 can be purchased from ASHRAE's Web site at https://www.ashrae.org/resources-publications.
ASHRAE 41.2-1987 (RA 1992) is an industry accepted test method for
measuring airflow. The test procedure in this final rule references
sections of ASHRAE 41.2-1987 (RA 1992) that address test setup and test
methods. ASHRAE 41.2-1987 (RA 1992) can be purchased from ASHRAE's Web
site at https://www.ashrae.org/resources-publications.
ASHRAE 41.6-2014 is an industry accepted test method for measuring
humidity of moist air. The test procedure in this final rule references
sections of ASHRAE 41.6-2014 that address requirements, instruments,
and methods for measuring humidity. ASHRAE 41.6-2014 can be purchased
from ASHRAE's Web site at https://www.ashrae.org/resources-publications.
ASHRAE 41.9-2011 is an industry accepted standard that provides
recommended practices for measuring the mass flow rate of volatile
refrigerants using calorimeters. The test procedure in this final rule
references sections of ASHRAE 41.9-2011 that address requirements,
instruments, and methods for measuring refrigerant flow during
compressor calibration. ASHRAE 41.9-2011 can be purchased from ASHRAE's
Web site at https://www.ashrae.org/resources-publications.
ANSI/ASHRAE Standard 116-2010 is an industry accepted standard that
provides test methods and calculation procedures for determining the
capacities and cooling seasonal efficiency ratios for unitary air-
conditioning, and heat pump equipment and heating seasonal performance
factors for heat pump equipment. The test procedure in this final rule
references various sections of ANSI/ASHRAE 116-2010 that addresses test
methods and calculations. ANSI/ASHRAE Standard 116-2010 can be
purchased from ASHRAE's Web site at https://www.ashrae.org/resources-publications.
AMCA 210-2007 is an industry accepted standard that establishes
uniform test methods for a laboratory test of a fan or other air moving
device to determine its aerodynamic performance in terms of airflow
rate, pressure developed, power consumption, air density, speed of
rotation, and efficiency for rating or guarantee purposes. The test
procedure in this final rule references various sections of AMCA 210-
2007 that address test conditions. AMCA 210-2007 can be purchased from
AMCA's Web site at http://www.amca.org/store/index.php.
N. Congressional Notification
As required by 5 U.S.C. 801, DOE will report to Congress on the
promulgation of this rule before its effective date. The report will
state that it has been determined that the rule is not a ``major rule''
as defined by 5 U.S.C. 804(2).
V. Approval of the Office of the Secretary
The Secretary of Energy has approved publication of this final
rule.
List of Subjects
10 CFR Part 429
Administrative practice and procedure, Confidential business
information, Energy conservation, Reporting and recordkeeping
requirements.
10 CFR Part 430
Administrative practice and procedure, Confidential business
information, Energy conservation, Energy conservation test procedures,
Household appliances, Imports, Incorporation by reference,
Intergovernmental relations, Small businesses.
Issued in Washington, DC, on November 30, 2016.
Kathleen B. Hogan,
Deputy Assistant Secretary for Energy Efficiency, Energy Efficiency and
Renewable Energy.
For the reasons stated in the preamble, DOE amends parts 429 and
430 of chapter II of title 10, subpart B, Code of Federal Regulations,
as set forth below:
PART 429--CERTIFICATION, COMPLIANCE, AND ENFORCEMENT FOR CONSUMER
PRODUCTS AND COMMERCIAL AND INDUSTRIAL EQUIPMENT
0
1. The authority citation for part 429 continues to read as follows:
Authority: 42 U.S.C. 6291-6317; 28 U.S.C. 2461 note.
0
2. Section 429.11 is amended by revising paragraph (a) to read as
follows:
Sec. 429.11 General sampling requirements for selecting units to be
tested.
(a) When testing of covered products or covered equipment is
required to comply with section 323(c) of the Act, or to comply with
rules prescribed under section 324, 325, or 342, 344, 345 or 346 of the
Act, a sample comprised of production units (or units representative of
production units) of the basic model being tested must be selected at
random and tested, and must meet the criteria found in Sec. Sec.
429.14 through 429.62 of this subpart. Components of similar design may
be substituted without additional testing if the substitution does not
affect energy or water consumption. Any represented values of measures
of energy efficiency, water efficiency, energy consumption, or water
consumption for all individual models represented by a given basic
model must be the same, except for central air conditioners and central
air conditioning heat pumps, as specified in Sec. 429.16 of this
subpart.
* * * * *
0
3. Section 429.16 is amended by:
0
a. Revising paragraph (a)(1);
0
b. Redesignating paragraphs (a)(3) and (4) as paragraphs (a)(4) and
(5);
0
c. Adding new paragraph (a)(3);
0
d. Revising newly designated paragraph (a)(4)(i) and paragraph
(b)(2)(i);
0
e. Revising paragraphs (b)(3) introductory text and (b)(3)(ii) and
(iii);
0
f. Removing paragraph (b)(3)(iv); and
0
g. Revising paragraphs (c)(1)(i)(B), (c)(2) and (3), (d)(2) through
(4), (e)(2) through (4), (f) introductory text, (f)(1) and (2), and
(f)(4) and (5).
The revisions and addition read as follows:
Sec. 429.16 Central air conditioners and central air conditioning
heat pumps.
(a) Determination of Represented Value--(1) Required represented
values. Determine the represented values (including SEER, EER, HSPF,
SEER2, EER2, HSPF2, PW,OFF, cooling capacity, and heating
capacity, as applicable) for the individual models/combinations (or
``tested combinations'') specified in the following table.
[[Page 1469]]
------------------------------------------------------------------------
Equipment Required represented
Category subcategory values
------------------------------------------------------------------------
Single-Package unit........... Single-Package AC Every individual
(including Space- model distributed in
Constrained). commerce.
Single-Package HP .....................
(including Space-
Constrained).
Outdoor Unit and Indoor Unit Single-Split- Every individual
(Distributed in Commerce by System AC with combination
OUM). Single-Stage or distributed in
Two-Stage commerce must be
Compressor rated as a coil-only
(including Space- combination. For
Constrained and each model of
Small-Duct, High outdoor unit, this
Velocity Systems must include at
(SDHV)). least one coil-only
value that is
representative of
the least efficient
combination
distributed in
commerce with that
particular model of
outdoor unit.
Additional blower-
coil representations
are allowed for any
applicable
individual
combinations, if
distributed in
commerce.
Single-Split- Every individual
System AC with combination
Other Than distributed in
Single-Stage or commerce, including
Two-Stage all coil-only and
Compressor blower coil
(including Space- combinations.
Constrained and
SDHV).
Single-Split- Every individual
System HP combination
(including Space- distributed in
Constrained and commerce.
SDHV).
Multi-Split, For each model of
Multi-Circuit, outdoor unit, at a
or Multi-Head minimum, a non-
Mini-Split Split ducted ``tested
System--non-SDHV combination.'' For
(including Space- any model of outdoor
Constrained). unit also sold with
models of ducted
indoor units, a
ducted ``tested
combination.'' When
determining
represented values
on or after January
1, 2023, the ducted
``tested
combination'' must
comprise the highest
static variety of
ducted indoor unit
distributed in
commerce (i.e.,
conventional, mid-
static, or low-
static). Additional
representations are
allowed, as
described in
paragraph (c)(3)(i)
of this section.
Multi-Split, For each model of
Multi-Circuit, outdoor unit, an
or Multi-Head SDHV ``tested
Mini-Split Split combination.''
System--SDHV. Additional
representations are
allowed, as
described in
paragraph (c)(3)(ii)
of this section.
Indoor Unit Only Distributed Single-Split- Every individual
in Commerce by ICM). System Air combination
Conditioner distributed in
(including Space- commerce.
Constrained and
SDHV).
Single-Split- .....................
System Heat Pump
(including Space-
Constrained and
SDHV).
Multi-Split, For a model of indoor
Multi-Circuit, unit within each
or Multi-Head basic model, an SDHV
Mini-Split Split ``tested
System--SDHV. combination.''
Additional
representations are
allowed, as
described in section
(c)(3)(ii) of this
section.
------------------------------------------------------------------------
Outdoor Unit with no Match....................... Every model of
outdoor unit
distributed in
commerce (tested
with a model of coil-
only indoor unit as
specified in
paragraph (b)(2)(i)
of this section).
------------------------------------------------------------------------
* * * * *
(3) Refrigerants. (i) If a model of outdoor unit (used in a single-
split, multi-split, multi-circuit, multi-head mini-split, and/or
outdoor unit with no match system) is distributed in commerce and
approved for use with multiple refrigerants, a manufacturer must
determine all represented values for that model using each refrigerant
that can be used in an individual combination of the basic model
(including outdoor units with no match or ``tested combinations'').
This requirement may apply across the listed categories in the table in
paragraph (a)(1) of this section. A refrigerant is considered approved
for use if it is listed on the nameplate of the outdoor unit. If any of
the refrigerants approved for use is HCFC-22 or has a 95[emsp14][deg]F
midpoint saturation absolute pressure that is +/- 18 percent of the
95[emsp14][deg]F saturation absolute pressure for HCFC-22, or if there
are no refrigerants designated as approved for use, a manufacturer must
determine represented values (including SEER, EER, HSPF, SEER2, EER2,
HSPF2, PW,OFF, cooling capacity, and heating capacity, as
applicable) for, at a minimum, an outdoor unit with no match. If a
model of outdoor unit is not charged with a specified refrigerant from
the point of manufacture or if the unit is shipped requiring the
addition of more than two pounds of refrigerant to meet the charge
required for testing per section 2.2.5 of appendix M or appendix M1
(unless either (a) the factory charge is equal to or greater than 70%
of the outdoor unit internal volume times the liquid density of
refrigerant at 95[emsp14][deg]F or (b) an A2L refrigerant is approved
for use and listed in the certification report), a manufacturer must
determine represented values (including SEER, EER, HSPF, SEER2, EER2,
HSPF2, PW,OFF, cooling capacity, and heating capacity, as
applicable) for, at a minimum, an outdoor unit with no match.
(ii) If a model is approved for use with multiple refrigerants, a
manufacturer may make multiple separate representations for the
performance of that model (all within the same individual combination
or outdoor unit with no match) using the multiple approved
refrigerants. In the alternative, manufacturers may certify the model
(all within the same individual combination or outdoor unit with no
match) with a single representation, provided that the represented
value is no more efficient than its performance using the least-
efficient refrigerant. If a manufacturer certifies a single model with
multiple representations for the different approved refrigerants, it
may use an AEDM to determine the represented values for all other
refrigerants besides the refrigerant used for testing. A single
representation made for multiple refrigerants may not include equipment
in multiple categories or equipment subcategories listed in the table
in paragraph (a)(1) of this section.
(4) * * *
(i) Regional. A basic model may only be certified as compliant with
a regional standard if all individual combinations within that basic
model meet the regional standard for which it is certified. A model of
outdoor unit that is certified below a regional standard can only be
rated and certified as compliant with a regional standard if the model
of outdoor unit has a unique model number and has been certified as a
different basic model for distribution in each region. An ICM cannot
certify an
[[Page 1470]]
individual combination with a rating that is compliant with a regional
standard if the individual combination includes a model of outdoor unit
that the OUM has certified with a rating that is not compliant with a
regional standard. Conversely, an ICM cannot certify an individual
combination with a rating that is not compliant with a regional
standard if the individual combination includes a model of outdoor unit
that an OUM has certified with a rating that is compliant with a
regional standard.
* * * * *
(b) * * *
(2) Individual model/combination selection for testing. (i) The
table identifies the minimum testing requirements for each basic model
that includes multiple individual models/combinations; if a basic model
spans multiple categories or subcategories listed in the table,
multiple testing requirements apply. For each basic model that includes
only one individual model/combination, test that individual model/
combination. For single-split-system non-space-constrained air
conditioners and heat pumps, when testing is required in accordance
with 10 CFR part 430, subpart B, appendix M1, these requirements do not
apply until July 1, 2024, provided that the manufacturer is certifying
compliance of all basic models using an AEDM in accordance with
paragraph (c)(1)(i)(B) of this section and paragraph (e)(2)(i)(A) of
Sec. 429.70.
----------------------------------------------------------------------------------------------------------------
Category Equipment subcategory Must test: With:
----------------------------------------------------------------------------------------------------------------
Single-Package Unit................ Single-Package AC The individual model N/A.
(including Space- with the lowest SEER
Constrained). (when testing in
accordance with
appendix M to subpart
B of part 430) or
SEER2 (when testing
in accordance with
appendix M1 to
subpart B of part
430).
Single-Package HP
(including Space-
Constrained).
Outdoor Unit and Indoor Unit Single-Split-System AC The model of outdoor A model of coil-only indoor
(Distributed in Commerce by OUM). with Single-Stage or unit. unit.
Two-Stage Compressor
(including Space-
Constrained and Small-
Duct, High Velocity
Systems (SDHV)).
Single-Split-System AC The model of outdoor A model of indoor unit.
with Other Than unit.
Single-Stage or Two-
Stage Compressor
(including Space-
Constrained and SDHV).
Single-Split-System HP
(including Space-
Constrained and SDHV).
Multi-Split, Multi- The model of outdoor At a minimum, a ``tested
Circuit, or Multi- unit. combination'' composed
Head Mini-Split Split entirely of non-ducted
System--non-SDHV indoor units. For any
(including Space- models of outdoor units
Constrained). also sold with models of
ducted indoor units, test
a second ``tested
combination'' composed
entirely of ducted indoor
units (in addition to the
non-ducted combination).
If testing under appendix
M1 to subpart B of part
430, the ducted ``tested
combination'' must
comprise the highest
static variety of ducted
indoor unit distributed in
commerce (i.e.,
conventional, mid-static,
or low-static).
Multi-Split, Multi- The model of outdoor A ``tested combination''
Circuit, or Multi- unit. composed entirely of SDHV
Head Mini-Split Split indoor units.
System--SDHV.
Indoor Unit Only (Distributed in Single-Split-System A model of indoor unit The least efficient model
Commerce by ICM). Air Conditioner of outdoor unit with which
(including Space- it will be paired where
Constrained and SDHV). the least efficient model
of outdoor unit is the
model of outdoor unit in
the lowest SEER
combination (when testing
under appendix M to
subpart B of part 430) or
SEER2 combination (when
testing under appendix M1
to subpart B of part 430)
as certified by the OUM.
If there are multiple
models of outdoor unit
with the same lowest SEER
(when testing under
appendix M to subpart B of
part 430) or SEER2 (when
testing under appendix M1
to subpart B of part 430)
represented value, the ICM
may select one for testing
purposes.
[[Page 1471]]
Single-Split-System Nothing, as long as an ...........................
Heat Pump (including equivalent air
Space-Constrained and conditioner basic
SDHV). model has been tested.
If an equivalent air
conditioner basic
model has not been
tested, must test a
model of indoor unit.
Multi-Split, Multi- A model of indoor unit A ``tested combination''
Circuit, or Multi- composed entirely of SDHV
Head Mini-Split Split indoor units, where the
System--SDHV. outdoor unit is the least
efficient model of outdoor
unit with which the SDHV
indoor unit will be
paired. The least
efficient model of outdoor
unit is the model of
outdoor unit in the lowest
SEER combination (when
testing under appendix M
to subpart B of part 430)
or SEER2 combination (when
testing under appendix M1
to subpart B of part 430)
as certified by the OUM.
If there are multiple
models of outdoor unit
with the same lowest SEER
represented value (when
testing under appendix M
to subpart B of part 430)
or SEER2 represented value
(when testing under
appendix M1 to subpart B
of part 430), the ICM may
select one for testing
purposes.
Outdoor Unit with No Match......... ...................... The model of outdoor A model of coil-only indoor
unit. unit meeting the
requirements of section
2.2e of appendix M or M1
to subpart B of part 430.
----------------------------------------------------------------------------------------------------------------
* * * * *
(3) Sampling plans and represented values. For individual models
(for single-package systems) or individual combinations (for split-
systems, including ``tested combinations'' for multi-split, multi-
circuit, and multi-head mini-split systems) with represented values
determined through testing, each individual model/combination (or
``tested combination'') must have a sample of sufficient size tested in
accordance with the applicable provisions of this subpart. For heat
pumps (other than heating-only heat pumps), all units of the sample
population must be tested in both the cooling and heating modes and the
results used for determining all representations. The represented
values for any individual model/combination must be assigned such that:
* * * * *
(ii) SEER, EER, HSPF, SEER2, EER2, and HSPF2. Any represented value
of the energy efficiency or other measure of energy consumption for
which consumers would favor higher values shall be less than or equal
to the lower of:
(A) The mean of the sample, where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.000
and, x is the sample mean; n is the number of samples; and xi is the
ith sample; or,
(B) The lower 90 percent confidence limit (LCL) of the true mean
divided by 0.95, where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.001
And x is the sample mean; s is the sample standard deviation; n is the
number of samples; and t0.90 is the t statistic for a 90
percent one-tailed confidence interval with n-1 degrees of freedom
(from appendix D). Round represented values of EER, SEER, HSPF, EER2,
SEER2, and HSPF2 to the nearest 0.05.
(iii) Cooling Capacity and Heating Capacity. The represented values
of cooling capacity and heating capacity must each be a self-declared
value that is:
(A) Less than or equal to the lower of:
(1) The mean of the sample, where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.002
and, x is the sample mean; n is the number of samples; and xi is the
ith sample; or,
(2) The lower 90 percent confidence limit (LCL) of the true mean
divided by 0.95, where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.003
And x is the sample mean; s is the sample standard deviation; n is the
number of samples; and t0.90 is the t statistic for a 90
percent one-tailed confidence interval with n-1 degrees of freedom
(from appendix D).
(B) Rounded according to:
(1) To the nearest 100 Btu/h if cooling capacity or heating
capacity is less than 20,000 Btu/h,
(2) To the nearest 200 Btu/h if cooling capacity or heating
capacity is greater than or equal to 20,000 Btu/h but less than 38,000
Btu/h, and
(3) To the nearest 500 Btu/h if cooling capacity or heating
capacity is greater than or equal to 38,000 Btu/h and less than 65,000
Btu/h.
(c) * * *
(1) * * *
(i) * * *
(B) The represented values of the measures of energy efficiency or
energy consumption through the application of an AEDM in accordance
with paragraph (d) of this section and Sec. 429.70. An AEDM may only
be used to determine represented values for individual models or
combinations in a basic model (or separate approved refrigerants within
an individual combination) other than the individual model or
combination(s) required for mandatory testing under paragraph (b)(2) of
this section, except that, for single-split, non-space-constrained
systems, when testing is required in accordance with 10 CFR part 430,
subpart B, appendix M1, an AEDM may be used to rate the individual
model or combination(s) required for mandatory testing under paragraph
(b)(2) of this section until July
[[Page 1472]]
1, 2024, in accordance with paragraph (e)(2)(i)(A) of Sec. 429.70.
* * * * *
(2) Outdoor units with no match. All models of outdoor units with
no match within a basic model must be tested. No model of outdoor unit
with no match may be rated with an AEDM, other than to determine the
represented values for models using approved refrigerants other than
the one used in testing.
(3) For multi-split systems, multi-circuit systems, and multi-head
mini-split systems. The following applies:
(i) When testing in accordance with 10 CFR part 430, subpart B,
appendix M1, for basic models that include additional varieties of
ducted indoor units (i.e., conventional, low-static, or mid-static)
other than the one for which representation is required in paragraph
(a)(1) of this section, if a manufacturer chooses to make a
representation, the manufacturer must conduct testing of a tested
combination according to the requirements in paragraph (b)(3) of this
section.
(ii) When testing in accordance with 10 CFR part 430, subpart B,
appendix M, for basic models composed of both non-ducted and ducted
combinations, the represented value for the mixed non-ducted/ducted
combination is the mean of the represented values for the non-ducted
and ducted combinations as determined in accordance with paragraph
(b)(3) of this section. When testing in accordance with 10 CFR part
430, subpart B, appendix M1, for basic models that include mixed
combinations of indoor units (any two kinds of non-ducted, low-static,
mid-static, and conventional ducted indoor units), the represented
value for the mixed combination is the mean of the represented values
for the individual component combinations as determined in accordance
with paragraph (b)(3) of this section.
(iii) When testing in accordance with 10 CFR part 430, subpart B,
appendix M, for basic models composed of both SDHV and non-ducted or
ducted combinations, the represented value for the mixed SDHV/non-
ducted or SDHV/ducted combination is the mean of the represented values
for the SDHV, non-ducted, or ducted combinations, as applicable, as
determined in accordance with paragraph (b)(3) of this section. When
testing in accordance with 10 CFR part 430, subpart B, appendix M1, for
basic models including mixed combinations of SDHV and another kind of
indoor unit (any of non-ducted, low-static, mid-static, and
conventional ducted), the represented value for the mixed SDHV/other
combination is the mean of the represented values for the SDHV and
other tested combination as determined in accordance with paragraph
(b)(3) of this section.
(iv) All other individual combinations of models of indoor units
for the same model of outdoor unit for which the manufacturer chooses
to make representations must be rated as separate basic models, and the
provisions of paragraphs (b)(1) through (3) and (c)(3)(i) through (iii)
of this section apply.
(v) With respect to PW,OFF only, for every individual
combination (or ``tested combination'') within a basic model tested
pursuant to paragraph (b)(2) of this section, but for which
PW,OFF testing was not conducted, the representative values
of PW,OFF may be assigned through either:
(A) The testing result from an individual model or combination of
similar off-mode construction, or
(B) Application of an AEDM in accordance with paragraph (d) of this
section and Sec. 429.70.
(d) * * *
(2) Energy efficiency. Any represented value of the SEER, EER,
HSPF, SEER2, EER2, HSPF2 or other measure of energy efficiency of an
individual model/combination for which consumers would favor higher
values must be less than or equal to the output of the AEDM but no less
than the standard.
(3) Cooling capacity. The represented value of cooling capacity of
an individual model/combination must be no greater than the cooling
capacity output simulated by the AEDM.
(4) Heating capacity. The represented value of heating capacity of
an individual model/combination must be no greater than the heating
capacity output simulated by the AEDM.
(e) * * *
(2) Public product-specific information. Pursuant to Sec.
429.12(b)(13), for each individual model (for single-package systems)
or individual combination (for split-systems, including outdoor units
with no match and ``tested combinations'' for multi-split, multi-
circuit, and multi-head mini-split systems), a certification report
must include the following public product-specific information: When
certifying compliance with January 1, 2015, energy conservation
standards, the seasonal energy efficiency ratio (SEER in British
thermal units per Watt-hour (Btu/W-h)) or when certifying compliance
with January 1, 2023, energy conservation standards, seasonal energy
efficiency ratio 2 (SEER2 in British thermal units per Watt-hour (Btu/
W-h)); the average off mode power consumption (PW,OFF in
Watts); the cooling capacity in British thermal units per hour (Btu/h);
the region(s) in which the basic model can be sold; when certifying
compliance with January 1, 2023, energy conservation standards, the
kind(s) of air conditioner or heat pump associated with the minimum
external static pressure used in testing or rating (ceiling-mount,
wall-mount, mobile home, low-static, mid-static, small duct high
velocity, space-constrained, or conventional/not otherwise listed); and
(i) For heat pumps, when certifying compliance with January 1,
2015, energy conservation standards, the heating seasonal performance
factor (HSPF in British thermal units per Watt-hour (Btu/W-h)) or, when
certifying compliance with January 1, 2023, energy conservation
standards, heating seasonal performance factor 2 (HSPF2 in British
thermal units per Watt-hour (Btu/W-h));
(ii) For central air conditioners (excluding space-constrained
products), when certifying compliance with January 1, 2015, energy
conservation standards, the energy efficiency ratio (EER in British
thermal units per Watt-hour (Btu/W-h)) from the A or A2
test, whichever applies, or when certifying compliance with January 1,
2023, energy conservation standards, the energy efficiency ratio 2
(EER2 in Btu/W-h);
(iii) For single-split-systems, whether the represented value is
for a coil-only or blower coil system;
(iv) For multi-split, multiple-circuit, and multi-head mini-split
systems (including VRF and SDHV), when certifying compliance with
January 1, 2015, energy conservation standards, whether the represented
value is for a non-ducted, ducted, mixed non-ducted/ducted system,
SDHV, mixed non-ducted/SDHV system, or mixed ducted/SDHV system;
(v) For all split systems including outdoor units with no match,
the refrigerant.
(3) Basic and individual model numbers. The basic model number and
individual model number(s) required to be reported under Sec.
429.12(b)(6) must consist of the following:
[[Page 1473]]
----------------------------------------------------------------------------------------------------------------
Individual model number(s)
Equipment type Basic model number -----------------------------------------------------------
1 2 3
----------------------------------------------------------------------------------------------------------------
Single-Package (including Space- Number unique to Package........... N/A............... N/A.
Constrained). the basic model.
Single-Split System (including Number unique to Outdoor Unit...... Indoor Unit....... If applicable--Air
Space-Constrained and SDHV). the basic model. Mover (could be
same as indoor
unit if fan is
part of indoor
unit model
number).
Multi-Split, Multi-Circuit, and Number unique to Outdoor Unit...... When certifying a If applicable--
Multi-Head Mini-Split System the basic model. basic model based When certifying a
(including Space-Constrained on tested basic model based
and SDHV). combination(s): * on tested
* *. combination(s): *
When certifying an * *.
individual When certifying an
combination: individual
Indoor Unit(s). combination: Air
Mover(s).
Outdoor Unit with No Match...... Number unique to Outdoor Unit...... N/A............... N/A.
the basic model.
----------------------------------------------------------------------------------------------------------------
(4) Additional product-specific information. Pursuant to Sec.
429.12(b)(13), for each individual model/combination (including outdoor
units with no match and ``tested combinations''), a certification
report must include the following additional product-specific
information: The cooling full load air volume rate for the system or
for each indoor unit as applicable (in cubic feet per minute of
standard air (scfm)); the air volume rates that represent normal
operation for other test conditions including minimum cooling air
volume rate, intermediate cooling air volume rate, full load heating
air volume rate, minimum heating air volume rate, intermediate heating
air volume rate, and nominal heating air volume rate (scfm) for the
system or for each indoor unit as applicable, if different from the
cooling full load air volume rate; whether the individual model uses a
fixed orifice, thermostatic expansion valve, electronic expansion
valve, or other type of metering device; the duration of the compressor
break-in period, if used; whether the optional tests were conducted to
determine the CDc value used to represent cooling mode cycling losses
or whether the default value was used; the temperature at which the
crankcase heater with controls is designed to turn on, if applicable;
whether an inlet plenum was installed during testing; the duration of
the indoor fan time delay, if used; and
(i) For heat pumps, whether the optional tests were conducted to
determine the CDh value or whether the default value was used; and the
maximum time between defrosts as allowed by the controls (in hours);
(ii) For multi-split, multiple-circuit, and multi-head mini-split
systems, the number of indoor units tested with the outdoor unit; the
nominal cooling capacity of each indoor unit and outdoor unit in the
combination; and the indoor units that are not providing heating or
cooling for part-load tests;
(iii) For ducted systems having multiple indoor fans within a
single indoor unit, the number of indoor fans; the nominal cooling
capacity of the indoor unit and outdoor unit; which fan(s) operate to
attain the full-load air volume rate when controls limit the
simultaneous operation of all fans within the single indoor unit; and
the allocation of the full-load air volume rate to each operational fan
when different capacity blowers are connected to the common duct;
(iv) For blower coil systems, the airflow-control settings
associated with full load cooling operation; and the airflow-control
settings or alternative instructions for setting fan speed to the speed
upon which the rating is based;
(v) For models with time-adaptive defrost control, the frosting
interval to be used during Frost Accumulation tests and the procedure
for manually initiating the defrost at the specified time;
(vi) For models of indoor units designed for both horizontal and
vertical installation or for both up-flow and down-flow vertical
installations, the orientation used for testing;
(vii) For variable-speed models, the compressor frequency set
points, and the required dip switch/control settings for step or
variable components;
(viii) For variable-speed heat pumps, whether the H1N or
H12 test speed is the same as the H32 test speed;
the compressor frequency that corresponds to maximum speed at which the
system controls would operate the compressor in normal operation in a
17 [deg]F ambient temperature; and when certifying compliance with
January 1, 2023, energy conservation standards, whether the optional 5
[deg]F very low temperature heating mode test was used to characterize
performance at temperatures below 17 [deg]F (except for triple-capacity
northern heat pumps, for which the very low temperature test is
required,) and whether the alternative test required for minimum-speed-
limiting variable-speed heat pumps was used;
(ix) For models of outdoor units with no match, the following
characteristics of the indoor coil: The face area, the coil depth in
the direction of airflow, the fin density (fins per inch), the fin
material, the fin style, the tube diameter, the tube material, and the
numbers of tubes high and deep; and
(x) For central air conditioners and heat pumps that have two-
capacity compressors that lock out low capacity operation for cooling
at higher outdoor temperatures and/or heating at lower outdoor
temperatures, the outdoor temperature(s) at which the unit locks out
low capacity operation.
(f) Represented values for the Federal Trade Commission. Use the
following represented value determinations to meet the requirements of
the Federal Trade Commission.
(1) Annual Operating Cost--Cooling. Determine the represented value
of estimated annual operating cost for cooling-only units or the
cooling portion of the estimated annual operating cost for air-source
heat pumps that provide both heating and cooling by calculating the
product of:
(i) The value determined in paragraph (f)(1)(i)(A) of this section
if using appendix M to subpart B of part 430 or the value determined in
paragraph (f)(1)(i)(B) of this section if using appendix M1 to subpart
B of part 430;
(A) the quotient of the represented value of cooling capacity, in
Btu's per hour as determined in paragraph
[[Page 1474]]
(b)(3)(iii) of this section, divided by the represented value of SEER,
in Btu's per watt-hour, as determined in paragraph (b)(3)(ii) of this
section;
(B) the quotient of the represented value of cooling capacity, in
Btu's per hour as determined in paragraph (b)(3)(i)(C) of this section,
and multiplied by 0.93 for variable-speed heat pumps only, divided by
the represented value of SEER2, in Btu's per watt-hour, as determined
in paragraph (b)(3)(i)(B) of this section.
(ii) The representative average use cycle for cooling of 1,000
hours per year;
(iii) A conversion factor of 0.001 kilowatt per watt; and
(iv) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act.
(2) Annual Operating Cost--Heating. Determine the represented value
of estimated annual operating cost for air-source heat pumps that
provide only heating or for the heating portion of the estimated annual
operating cost for air-source heat pumps that provide both heating and
cooling, as follows:
(i) When using appendix M to subpart B of part 430, the product of:
(A) The quotient of the mean of the standardized design heating
requirement for the sample, in Btu's per hour, nearest to the Region IV
minimum design heating requirement, determined for each unit in the
sample in section 4.2 of appendix M to subpart B of part 430, divided
by the represented value of heating seasonal performance factor (HSPF),
in Btu's per watt-hour, calculated for Region IV corresponding to the
above-mentioned standardized design heating requirement, as determined
in paragraph (b)(3)(ii) of this section;
(B) The representative average use cycle for heating of 2,080 hours
per year;
(C) The adjustment factor of 0.77, which serves to adjust the
calculated design heating requirement and heating load hours to the
actual load experienced by a heating system;
(D) A conversion factor of 0.001 kilowatt per watt; and
(E) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act;
(ii) When using appendix M1 to subpart B of part 430, the product
of:
(A) The quotient of the represented value of cooling capacity (for
air-source heat pumps that provide both cooling and heating) in Btu's
per hour, as determined in paragraph (b)(3)(i)(C) of this section, or
the represented value of heating capacity (for air-source heat pumps
that provide only heating), as determined in paragraph (b)(3)(i)(D) of
this section, divided by the represented value of heating seasonal
performance factor 2 (HSPF2), in Btu's per watt-hour, calculated for
Region IV, as determined in paragraph (b)(3)(i)(B) of this section;
(B) The representative average use cycle for heating of 1,572 hours
per year;
(C) The adjustment factor of 1.15 (for heat pumps that are not
variable-speed) or 1.07 (for heat pumps that are variable-speed), which
serves to adjust the calculated design heating requirement and heating
load hours to the actual load experienced by a heating system;
(D) A conversion factor of 0.001 kilowatt per watt; and
(E) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act;
* * * * *
(4) Regional Annual Operating Cost--Cooling. Determine the
represented value of estimated regional annual operating cost for
cooling-only units or the cooling portion of the estimated regional
annual operating cost for air-source heat pumps that provide both
heating and cooling by calculating the product of:
(i) The value determined in paragraph (f)(4)(i)(A) of this section
if using appendix M to subpart B of part 430 or the value determined in
paragraph (f)(4)(i)(B) of this section if using appendix M1 to subpart
B of part 430;
(A) the quotient of the represented value of cooling capacity, in
Btu's per hour as determined in paragraph (b)(3)(iii) of this section,
divided by the represented value of SEER, in Btu's per watt-hour, as
determined in paragraph (b)(3)(ii) of this section;
(B) the quotient of the represented value of cooling capacity, in
Btu's per hour as determined in paragraph (b)(3)(i)(C) of this section,
and multiplied by 0.93 for variable-speed heat pumps only, divided by
the represented value of SEER2, in Btu's per watt-hour, as determined
in paragraph (b)(3)(i)(B) of this section;
(ii) The value determined in paragraph (f)(4)(ii)(A) of this
section if using appendix M to subpart B of part 430 or the value
determined in paragraph (f)(4)(ii)(B) of this section if using appendix
M1 to subpart B of part 430;
(A) the estimated number of regional cooling load hours per year
determined from Table 22 in section 4.4 of appendix M to subpart B of
part 430;
(B) the estimated number of regional cooling load hours per year
determined from Table 21 in section 4.4 of appendix M1 to subpart B of
part 430;
(iii) A conversion factor of 0.001 kilowatts per watt; and
(iv) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act.
(5) Regional Annual Operating Cost--Heating. Determine the
represented value of estimated regional annual operating cost for air-
source heat pumps that provide only heating or for the heating portion
of the estimated regional annual operating cost for air-source heat
pumps that provide both heating and cooling as follows:
(i) When using appendix M to subpart B of part 430, the product of:
(A) The estimated number of regional heating load hours per year
determined from Table 22 in section 4.4 of appendix M to subpart B of
part 430;
(B) The quotient of the mean of the standardized design heating
requirement for the sample, in Btu's per hour, for the appropriate
generalized climatic region of interest (i.e., corresponding to the
regional heating load hours from ``A'') and determined for each unit in
the sample in section 4.2 of appendix M to subpart B of part 430,
divided by the represented value of HSPF, in Btu's per watt-hour,
calculated for the appropriate generalized climatic region of interest
and corresponding to the above-mentioned standardized design heating
requirement, and determined in paragraph (b)(3)(ii);
(C) The adjustment factor of 0.77; which serves to adjust the
calculated design heating requirement and heating load hours to the
actual load experienced by a heating system;
(D) A conversion factor of 0.001 kilowatts per watt; and
(E) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act.
(ii) When using appendix M1 to subpart B of part 430, the product
of:
(A) The estimated number of regional heating load hours per year
determined from Table 21 in section 4.4 of appendix M1 to subpart B of
part 430;
(B) The quotient of the represented value of cooling capacity (for
air-source heat pumps that provide both cooling and heating) in Btu's
per hour, as determined in paragraph (b)(3)(i)(C) of this section, or
the represented value of heating capacity (for air-source heat pumps
that provide only heating), as determined in paragraph (b)(3)(i)(D) of
this section, divided by the represented value of HSPF2, in Btu's per
watt-hour,
[[Page 1475]]
calculated for the appropriate generalized climatic region of interest,
and determined in paragraph (b)(3)(i)(B) of this section;
(C) The adjustment factor of 1.15 (for heat pumps that are not
variable-speed) or 1.07 (for heat pumps that are variable-speed), which
serves to adjust the calculated design heating requirement and heating
load hours to the actual load experienced by a heating system;
(D) A conversion factor of 0.001 kilowatts per watt; and
(E) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act.
* * * * *
0
4. Section 429.70 is amended by revising paragraphs (e)(1), (e)(2)(i),
and (e)(5)(iv) to read as follows:
Sec. 429.70 Alternative methods for determining energy efficiency or
energy use.
* * * * *
(e) * * *
(1) Criteria an AEDM must satisfy. A manufacturer may not apply an
AEDM to an individual model/combination to determine its represented
values (SEER, EER, HSPF, SEER2, EER2, HSPF2, and/or PW,OFF)
pursuant to this section unless authorized pursuant to Sec. 429.16(d)
and:
(i) The AEDM is derived from a mathematical model that estimates
the energy efficiency or energy consumption characteristics of the
individual model or combination (SEER, EER, HSPF, SEER2, EER2, HSPF2,
and/or PW,OFF) as measured by the applicable DOE test
procedure; and
(ii) The manufacturer has validated the AEDM in accordance with
paragraph (e)(2) of this section.
(2) * * *
(i) Follow paragraph (e)(2)(i)(A) of this section for requirements
on minimum testing. Follow paragraph (e)(2)(i)(B) of this section for
requirements on ensuring the accuracy and reliability of the AEDM.
(A) Minimum testing. (1) For non-space-constrained single-split
system air conditioners and heat pumps rated based on testing in
accordance with appendix M to subpart B of part 430, the manufacturer
must test each basic model as required under Sec. 429.16(b)(2). Until
July 1, 2024, for non-space-constrained single-split-system air
conditioners and heat pumps rated based on testing in accordance with
appendix M1 to subpart B of part 430, the manufacturer must test a
single-unit sample from 20 percent of the basic models distributed in
commerce to validate the AEDM. On or after July 1, 2024, for non-space-
constrained single-split-system air conditioners and heat pumps rated
based on testing in accordance with appendix M1 to subpart B of part
430, the manufacturer must complete testing of each basic model as
required under Sec. 429.16(b)(2).
(2) For other than non-space-constrained single-split-system air
conditioners and heat pumps, the manufacturer must test each basic
model as required under Sec. 429.16(b)(2).
(B) Using the AEDM, calculate the energy use or efficiency for each
of the tested individual models/combinations within each basic model.
Compare the represented value based on testing and the AEDM energy use
or efficiency output according to paragraph (e)(2)(ii) of this section.
The manufacturer is responsible for ensuring the accuracy and
reliability of the AEDM and that their representations are appropriate
and the models being distributed in commerce meet the applicable
standards, regardless of the amount of testing required in paragraphs
(e)(2)(i)(A) and (e)(2)(i)(B) of this section.
* * * * *
(5) * * *
(iv) Failure to meet certified value. If an individual model/
combination tests worse than its certified value (i.e., lower than the
certified efficiency value or higher than the certified consumption
value) by more than 5 percent, or the test results in cooling capacity
that is lower than its certified cooling capacity, DOE will notify the
manufacturer. DOE will provide the manufacturer with all documentation
related to the test set up, test conditions, and test results for the
unit. Within the timeframe allotted by DOE, the manufacturer may
present any and all claims regarding testing validity.
* * * * *
PART 430--ENERGY CONSERVATION PROGRAM FOR CONSUMER PRODUCTS
0
5. The authority citation for part 430 continues to read as follows:
Authority: 42 U.S.C. 6291-6309; 28 U.S.C. 2461 note.
0
6. Section 430.2 is amended by revising the definition of ``central air
conditioner or central air conditioning heat pump'' to read as follows:
Sec. 430.2 Definitions.
* * * * *
Central air conditioner or central air conditioning heat pump means
a product, other than a packaged terminal air conditioner or packaged
terminal heat pump, which is powered by single phase electric current,
air cooled, rated below 65,000 Btu per hour, not contained within the
same cabinet as a furnace, the rated capacity of which is above 225,000
Btu per hour, and is a heat pump or a cooling unit only. A central air
conditioner or central air conditioning heat pump may consist of: A
single-package unit; an outdoor unit and one or more indoor units; an
indoor unit only; or an outdoor unit with no match. In the case of an
indoor unit only or an outdoor unit with no match, the unit must be
tested and rated as a system (combination of both an indoor and an
outdoor unit). For all central air conditioner and central air
conditioning heat pump-related definitions, see appendix M or M1 of
subpart B of this part.
* * * * *
Sec. 430.3 [Amended]
0
7. Section 430.3 is amended by removing in paragraphs (b)(2)
introductory text, (c)(1) introductory text, (c)(3) introductory text,
(g)(2) introductory text, (g)(4) introductory text, (g)(7) introductory
text, (g)(8) introductory text, (g)(9) introductory text, (g)(10)
introductory text, and (g)(13) ``appendix M'' and adding in its place
``appendices M and M1''.
0
8. Section 430.23 is amended by revising paragraph (m) to read as
follows:
Sec. 430.23 Test procedures for the measurement of energy and water
consumption.
* * * * *
(m) Central air conditioners and heat pumps. See the note at the
beginning of appendix M and M1 to determine the appropriate test
method. Determine all values discussed in this section using a single
appendix.
(1) Determine cooling capacity from the steady-state wet-coil test
(A or A2 Test), as described in section 3.2 of appendix M or
M1 to this subpart, and rounded off to the nearest
(i) To the nearest 50 Btu/h if cooling capacity is less than 20,000
Btu/h;
(ii) To the nearest 100 Btu/h if cooling capacity is greater than
or equal to 20,000 Btu/h but less than 38,000 Btu/h; and
(iii) To the nearest 250 Btu/h if cooling capacity is greater than
or equal to 38,000 Btu/h and less than 65,000 Btu/h.
(2) Determine seasonal energy efficiency ratio (SEER) as described
in section 4.1 of appendix M to this subpart or seasonal energy
efficiency ratio 2 (SEER2) as described in section
[[Page 1476]]
4.1 of appendix M1 to this subpart, and round off to the nearest 0.025
Btu/W-h.
(3) Determine energy efficiency ratio (EER) as described in section
4.6 of appendix M or M1 to this subpart, and round off to the nearest
0.025 Btu/W-h. The EER from the A or A2 test, whichever
applies, when tested in accordance with appendix M1 to this subpart, is
referred to as EER2.
(4) Determine heating seasonal performance factors (HSPF) as
described in section 4.2 of appendix M to this subpart or heating
seasonal performance factors 2 (HSPF2) as described in section 4.2 of
appendix M1 to this subpart, and round off to the nearest 0.025 Btu/W-
h.
(5) Determine average off mode power consumption as described in
section 4.3 of appendix M or M1 to this subpart, and round off to the
nearest 0.5 W.
(6) Determine all other measures of energy efficiency or
consumption or other useful measures of performance using appendix M or
M1 of this subpart.
* * * * *
0
9. Appendix M to subpart B of part 430 is revised to read as follows:
Appendix M to Subpart B of Part 430--Uniform Test Method for Measuring
the Energy Consumption of Central Air Conditioners and Heat Pumps
Note: Prior to July 5, 2017, any representations, including
compliance certifications, made with respect to the energy use,
power, or efficiency of central air conditioners and central air
conditioning heat pumps must be based on the results of testing
pursuant to either this appendix or the procedures in Appendix M as
it appeared at 10 CFR part 430, subpart B, Appendix M, in the 10 CFR
parts 200 to 499 edition revised as of January 1, 2017. Any
representations made with respect to the energy use or efficiency of
such central air conditioners and central air conditioning heat
pumps must be in accordance with whichever version is selected.
On or after July 5, 2017 and prior to January 1, 2023, any
representations, including compliance certifications, made with
respect to the energy use, power, or efficiency of central air
conditioners and central air conditioning heat pumps must be based
on the results of testing pursuant to this appendix.
On or after January 1, 2023, any representations, including
compliance certifications, made with respect to the energy use,
power, or efficiency of central air conditioners and central air
conditioning heat pumps must be based on the results of testing
pursuant to appendix M1 of this subpart.
1. Scope and Definitions
1.1 Scope
This test procedure provides a method of determining SEER, EER,
HSPF and PW,OFF for central air conditioners and central
air conditioning heat pumps including the following categories:
(a) Split-system air conditioners, including single-split, multi-
head mini-split, multi-split (including VRF), and multi-circuit
systems
(b) Split-system heat pumps, including single-split, multi-head
mini-split, multi-split (including VRF), and multi-circuit systems
(c) Single-package air conditioners
(d) Single-package heat pumps
(e) Small-duct, high-velocity systems (including VRF)
(f) Space-constrained products--air conditioners
(g) Space-constrained products--heat pumps
For purposes of this appendix, the Department of Energy
incorporates by reference specific sections of several industry
standards, as listed in Sec. 430.3. In cases where there is a
conflict, the language of the test procedure in this appendix takes
precedence over the incorporated standards.
All section references refer to sections within this appendix
unless otherwise stated.
1.2 Definitions
Airflow-control settings are programmed or wired control system
configurations that control a fan to achieve discrete, differing
ranges of airflow--often designated for performing a specific
function (e.g., cooling, heating, or constant circulation)--without
manual adjustment other than interaction with a user-operable
control (i.e., a thermostat) that meets the manufacturer
specifications for installed-use. For the purposes of this appendix,
manufacturer specifications for installed-use are those found in the
product literature shipped with the unit.
Air sampling device is an assembly consisting of a manifold with
several branch tubes with multiple sampling holes that draws an air
sample from a critical location from the unit under test (e.g.
indoor air inlet, indoor air outlet, outdoor air inlet, etc.).
Airflow prevention device denotes a device that prevents airflow
via natural convection by mechanical means, such as an air damper
box, or by means of changes in duct height, such as an upturned
duct.
Aspirating psychrometer is a piece of equipment with a monitored
airflow section that draws uniform airflow through the measurement
section and has probes for measurement of air temperature and
humidity.
Blower coil indoor unit means an indoor unit either with an
indoor blower housed with the coil or with a separate designated air
mover such as a furnace or a modular blower (as defined in appendix
AA to the subpart).
Blower coil system refers to a split system that includes one or
more blower coil indoor units.
Cased coil means a coil-only indoor unit with external
cabinetry.
Coefficient of Performance (COP) means the ratio of the average
rate of space heating delivered to the average rate of electrical
energy consumed by the heat pump. These rate quantities must be
determined from a single test or, if derived via interpolation, must
be determined at a single set of operating conditions. COP is a
dimensionless quantity. When determined for a ducted coil-only
system, COP must include the sections 3.7 and 3.9.1 of this
appendix: Default values for the heat output and power input of a
fan motor.
Coil-only indoor unit means an indoor unit that is distributed
in commerce without an indoor blower or separate designated air
mover. A coil-only indoor unit installed in the field relies on a
separately-installed furnace or a modular blower for indoor air
movement. Coil-only system refers to a system that includes only
(one or more) coil-only indoor units.
Condensing unit removes the heat absorbed by the refrigerant to
transfer it to the outside environment and consists of an outdoor
coil, compressor(s), and air moving device.
Constant-air-volume-rate indoor blower means a fan that varies
its operating speed to provide a fixed air-volume-rate from a ducted
system.
Continuously recorded, when referring to a dry bulb measurement,
dry bulb temperature used for test room control, wet bulb
temperature, dew point temperature, or relative humidity
measurements, means that the specified value must be sampled at
regular intervals that are equal to or less than 15 seconds.
Cooling load factor (CLF) means the ratio having as its
numerator the total cooling delivered during a cyclic operating
interval consisting of one ON period and one OFF period, and as its
denominator the total cooling that would be delivered, given the
same ambient conditions, had the unit operated continuously at its
steady-state, space-cooling capacity for the same total time (ON +
OFF) interval.
Crankcase heater means any electrically powered device or
mechanism for intentionally generating heat within and/or around the
compressor sump volume. Crankcase heater control may be achieved
using a timer or may be based on a change in temperature or some
other measurable parameter, such that the crankcase heater is not
required to operate continuously. A crankcase heater without
controls operates continuously when the compressor is not operating.
Cyclic Test means a test where the unit's compressor is cycled
on and off for specific time intervals. A cyclic test provides half
the information needed to calculate a degradation coefficient.
Damper box means a short section of duct having an air damper
that meets the performance requirements of section 2.5.7 of this
appendix.
Degradation coefficient (CD) means a parameter used
in calculating the part load factor. The degradation coefficient for
cooling is denoted by CD\c\. The degradation coefficient
for heating is denoted by CD\h\.
Demand-defrost control system means a system that defrosts the
heat pump outdoor coil-only when measuring a predetermined
degradation of performance. The heat pump's controls either:
(1) Monitor one or more parameters that always vary with the
amount of frost
[[Page 1477]]
accumulated on the outdoor coil (e.g., coil to air differential
temperature, coil differential air pressure, outdoor fan power or
current, optical sensors) at least once for every ten minutes of
compressor ON-time when space heating or
(2) operate as a feedback system that measures the length of the
defrost period and adjusts defrost frequency accordingly. In all
cases, when the frost parameter(s) reaches a predetermined value,
the system initiates a defrost. In a demand-defrost control system,
defrosts are terminated based on monitoring a parameter(s) that
indicates that frost has been eliminated from the coil. (Note:
Systems that vary defrost intervals according to outdoor dry-bulb
temperature are not demand-defrost systems.) A demand-defrost
control system, which otherwise meets the above requirements, may
allow time-initiated defrosts if, and only if, such defrosts occur
after 6 hours of compressor operating time.
Design heating requirement (DHR) predicts the space heating load
of a residence when subjected to outdoor design conditions.
Estimates for the minimum and maximum DHR are provided for six
generalized U.S. climatic regions in section 4.2 of this appendix.
Dry-coil tests are cooling mode tests where the wet-bulb
temperature of the air supplied to the indoor unit is maintained low
enough that no condensate forms on the evaporator coil.
Ducted system means an air conditioner or heat pump that is
designed to be permanently installed equipment and delivers
conditioned air to the indoor space through a duct(s). The air
conditioner or heat pump may be either a split-system or a single-
package unit.
Energy efficiency ratio (EER) means the ratio of the average
rate of space cooling delivered to the average rate of electrical
energy consumed by the air conditioner or heat pump. Determine these
rate quantities from a single test or, if derived via interpolation,
determine at a single set of operating conditions. EER is expressed
in units of
[GRAPHIC] [TIFF OMITTED] TR05JA17.305
When determined for a ducted coil-only system, EER must include,
from this appendix, the section 3.3 and 3.5.1 default values for the
heat output and power input of a fan motor.
Evaporator coil means an assembly that absorbs heat from an
enclosed space and transfers the heat to a refrigerant.
Heat pump means a kind of central air conditioner that utilizes
an indoor conditioning coil, compressor, and refrigerant-to-outdoor
air heat exchanger to provide air heating, and may also provide air
cooling, air dehumidifying, air humidifying, air circulating, and
air cleaning.
Heat pump having a heat comfort controller means a heat pump
with controls that can regulate the operation of the electric
resistance elements to assure that the air temperature leaving the
indoor section does not fall below a specified temperature. Heat
pumps that actively regulate the rate of electric resistance heating
when operating below the balance point (as the result of a second
stage call from the thermostat) but do not operate to maintain a
minimum delivery temperature are not considered as having a heat
comfort controller.
Heating load factor (HLF) means the ratio having as its
numerator the total heating delivered during a cyclic operating
interval consisting of one ON period and one OFF period, and its
denominator the heating capacity measured at the same test
conditions used for the cyclic test, multiplied by the total time
interval (ON plus OFF) of the cyclic-test.
Heating season means the months of the year that require
heating, e.g., typically, and roughly, October through April.
Heating seasonal performance factor (HSPF) means the total space
heating required during the heating season, expressed in Btu,
divided by the total electrical energy consumed by the heat pump
system during the same season, expressed in watt-hours. The HSPF
used to evaluate compliance with 10 CFR 430.32(c) is based on Region
IV and the sampling plan stated in 10 CFR 429.16(a). HSPF is
determined in accordance with appendix M.
Independent coil manufacturer (ICM) means a manufacturer that
manufactures indoor units but does not manufacture single-package
units or outdoor units.
Indoor unit means a separate assembly of a split system that
includes--
(1) An arrangement of refrigerant-to-air heat transfer coil(s)
for transfer of heat between the refrigerant and the indoor air,
(2) A condensate drain pan, and may or may not include
(3) Sheet metal or plastic parts not part of external cabinetry
to direct/route airflow over the coil(s),
(4) A cooling mode expansion device,
(5) External cabinetry, and
(6) An integrated indoor blower (i.e. a device to move air
including its associated motor). A separate designated air mover
that may be a furnace or a modular blower (as defined in appendix AA
to the subpart) may be considered to be part of the indoor unit. A
service coil is not an indoor unit.
Multi-head mini-split system means a split system that has one
outdoor unit and that has two or more indoor units connected with a
single refrigeration circuit. The indoor units operate in unison in
response to a single indoor thermostat.
Multiple-circuit (or multi-circuit) system means a split system
that has one outdoor unit and that has two or more indoor units
installed on two or more refrigeration circuits such that each
refrigeration circuit serves a compressor and one and only one
indoor unit, and refrigerant is not shared from circuit to circuit.
Multiple-split (or multi-split) system means a split system that
has one outdoor unit and two or more coil-only indoor units and/or
blower coil indoor units connected with a single refrigerant
circuit. The indoor units operate independently and can condition
multiple zones in response to at least two indoor thermostats or
temperature sensors. The outdoor unit operates in response to
independent operation of the indoor units based on control input of
multiple indoor thermostats or temperature sensors, and/or based on
refrigeration circuit sensor input (e.g., suction pressure).
Nominal capacity means the capacity that is claimed by the
manufacturer on the product name plate. Nominal cooling capacity is
approximate to the air conditioner cooling capacity tested at A or
A2 condition. Nominal heating capacity is approximate to the heat
pump heating capacity tested in H12 test (or the optional H1N test).
Non-ducted indoor unit means an indoor unit that is designed to
be permanently installed, mounted on room walls and/or ceilings, and
that directly heats or cools air within the conditioned space.
Normalized Gross Indoor Fin Surface (NGIFS) means the gross fin
surface area of the indoor unit coil divided by the cooling capacity
measured for the A or A2 Test, whichever applies.
Off-mode power consumption means the power consumption when the
unit is connected to its main power source but is neither providing
cooling nor heating to the building it serves.
Off-mode season means, for central air conditioners other than
heat pumps, the shoulder season and the entire heating season; and
for heat pumps, the shoulder season only.
Outdoor unit means a separate assembly of a split system that
transfers heat between the refrigerant and the outdoor air, and
consists of an outdoor coil, compressor(s), an air moving device,
and in addition for heat pumps, may include a heating mode expansion
device, reversing valve, and/or defrost controls.
Outdoor unit manufacturer (OUM) means a manufacturer of single-
package units, outdoor units, and/or both indoor units and outdoor
units.
Part-load factor (PLF) means the ratio of the cyclic EER (or COP
for heating) to the steady-state EER (or COP), where both EERs (or
COPs) are determined based on operation at the same ambient
conditions.
Seasonal energy efficiency ratio (SEER) means the total heat
removed from the conditioned space during the annual cooling season,
expressed in Btu's, divided by the total electrical energy consumed
by the central air conditioner or heat pump during the same season,
expressed in watt-hours. SEER is determined in accordance with
appendix M.
Service coil means an arrangement of refrigerant-to-air heat
transfer coil(s), condensate drain pan, sheet metal or plastic parts
to direct/route airflow over the coil(s), which may or may not
include external cabinetry and/or a cooling mode expansion device,
distributed in commerce solely for replacing an uncased coil or
cased coil that has already been placed into service, and that has
been labeled ``for indoor coil replacement only'' on the nameplate
and in manufacturer technical and product literature. The model
number for any service coil must include some mechanism (e.g., an
additional letter or number) for differentiating a service coil from
a coil intended for an indoor unit.
Shoulder season means the months of the year in between those
months that require cooling and those months that require
[[Page 1478]]
heating, e.g., typically, and roughly, April through May, and
September through October.
Single-package unit means any central air conditioner or heat
pump that has all major assemblies enclosed in one cabinet.
Single-split system means a split system that has one outdoor
unit and one indoor unit connected with a single refrigeration
circuit. Small-duct, high-velocity system means a split system for
which all indoor units are blower coil indoor units that produce at
least 1.2 inches (of water column) of external static pressure when
operated at the full-load air volume rate certified by the
manufacturer of at least 220 scfm per rated ton of cooling.
Split system means any air conditioner or heat pump that has at
least two separate assemblies that are connected with refrigerant
piping when installed. One of these assemblies includes an indoor
coil that exchanges heat with the indoor air to provide heating or
cooling, while one of the others includes an outdoor coil that
exchanges heat with the outdoor air. Split systems may be either
blower coil systems or coil-only systems.
Standard Air means dry air having a mass density of 0.075 lb/
ft\3\.
Steady-state test means a test where the test conditions are
regulated to remain as constant as possible while the unit operates
continuously in the same mode.
Temperature bin means the 5[emsp14][deg]F increments that are
used to partition the outdoor dry-bulb temperature ranges of the
cooling (>=65[emsp14][deg]F) and heating (<65[emsp14][deg]F)
seasons.
Test condition tolerance means the maximum permissible
difference between the average value of the measured test parameter
and the specified test condition.
Test operating tolerance means the maximum permissible range
that a measurement may vary over the specified test interval. The
difference between the maximum and minimum sampled values must be
less than or equal to the specified test operating tolerance.
Tested combination means a multi-head mini-split, multi-split,
or multi-circuit system having the following features:
(1) The system consists of one outdoor unit with one or more
compressors matched with between two and five indoor units;
(2) The indoor units must:
(i) Collectively, have a nominal cooling capacity greater than
or equal to 95 percent and less than or equal to 105 percent of the
nominal cooling capacity of the outdoor unit;
(ii) Each represent the highest sales volume model family, if
this is possible while meeting all the requirements of this section.
If this is not possible, one or more of the indoor units may
represent another indoor model family in order that all the other
requirements of this section are met.
(iii) Individually not have a nominal cooling capacity greater
than 50 percent of the nominal cooling capacity of the outdoor unit,
unless the nominal cooling capacity of the outdoor unit is 24,000
Btu/h or less;
(iv) Operate at fan speeds consistent with manufacturer's
specifications; and
(v) All be subject to the same minimum external static pressure
requirement while able to produce the same external static pressure
at the exit of each outlet plenum when connected in a manifold
configuration as required by the test procedure.
(3) Where referenced, ``nominal cooling capacity'' means, for
indoor units, the highest cooling capacity listed in published
product literature for 95[emsp14][deg]F outdoor dry bulb temperature
and 80[emsp14][deg]F dry bulb, 67[emsp14][deg]F wet bulb indoor
conditions, and for outdoor units, the lowest cooling capacity
listed in published product literature for these conditions. If
incomplete or no operating conditions are published, the highest
(for indoor units) or lowest (for outdoor units) such cooling
capacity available for sale must be used.
Time-adaptive defrost control system is a demand-defrost control
system that measures the length of the prior defrost period(s) and
uses that information to automatically determine when to initiate
the next defrost cycle.
Time-temperature defrost control systems initiate or evaluate
initiating a defrost cycle only when a predetermined cumulative
compressor ON-time is obtained. This predetermined ON-time is
generally a fixed value (e.g., 30, 45, 90 minutes) although it may
vary based on the measured outdoor dry-bulb temperature. The ON-time
counter accumulates if controller measurements (e.g., outdoor
temperature, evaporator temperature) indicate that frost formation
conditions are present, and it is reset/remains at zero at all other
times. In one application of the control scheme, a defrost is
initiated whenever the counter time equals the predetermined ON-
time. The counter is reset when the defrost cycle is completed.
In a second application of the control scheme, one or more
parameters are measured (e.g., air and/or refrigerant temperatures)
at the predetermined, cumulative, compressor ON-time. A defrost is
initiated only if the measured parameter(s) falls within a
predetermined range. The ON-time counter is reset regardless of
whether or not a defrost is initiated. If systems of this second
type use cumulative ON-time intervals of 10 minutes or less, then
the heat pump may qualify as having a demand defrost control system
(see definition).
Triple-capacity, northern heat pump means a heat pump that
provides two stages of cooling and three stages of heating. The two
common stages for both the cooling and heating modes are the low
capacity stage and the high capacity stage. The additional heating
mode stage is the booster capacity stage, which offers the highest
heating capacity output for a given set of ambient operating
conditions.
Triple-split system means a split system that is composed of
three separate assemblies: An outdoor fan coil section, a blower
coil indoor unit, and an indoor compressor section.
Two-capacity (or two-stage) compressor system means a central
air conditioner or heat pump that has a compressor or a group of
compressors operating with only two stages of capacity. For such
systems, low capacity means the compressor(s) operating at low
stage, or at low load test conditions. The low compressor stage that
operates for heating mode tests may be the same or different from
the low compressor stage that operates for cooling mode tests. For
such systems, high capacity means the compressor(s) operating at
high stage, or at full load test conditions.
Two-capacity, northern heat pump means a heat pump that has a
factory or field-selectable lock-out feature to prevent space
cooling at high-capacity. Two-capacity heat pumps having this
feature will typically have two sets of ratings, one with the
feature disabled and one with the feature enabled. The heat pump is
a two-capacity northern heat pump only when this feature is enabled
at all times. The certified indoor coil model number must reflect
whether the ratings pertain to the lockout enabled option via the
inclusion of an extra identifier, such as ``+LO''. When testing as a
two-capacity, northern heat pump, the lockout feature must remain
enabled for all tests.
Uncased coil means a coil-only indoor unit without external
cabinetry.
Variable refrigerant flow (VRF) system means a multi-split
system with at least three compressor capacity stages, distributing
refrigerant through a piping network to multiple indoor blower coil
units each capable of individual zone temperature control, through
proprietary zone temperature control devices and a common
communications network. Note: Single-phase VRF systems less than
65,000 Btu/h are central air conditioners and central air
conditioning heat pumps.
Variable-speed compressor system means a central air conditioner
or heat pump that has a compressor that uses a variable-speed drive
to vary the compressor speed to achieve variable capacities.
Wet-coil test means a test conducted at test conditions that
typically cause water vapor to condense on the test unit evaporator
coil.
2. Testing Overview and Conditions
(A) Test VRF systems using AHRI 1230-2010 (incorporated by
reference, see Sec. 430.3) and appendix M. Where AHRI 1230-2010
refers to the appendix C therein substitute the provisions of this
appendix. In cases where there is a conflict, the language of the
test procedure in this appendix takes precedence over AHRI 1230-
2010.
For definitions use section 1 of appendix M and section 3 of
AHRI 1230-2010 (incorporated by reference, see Sec. 430.3). For
rounding requirements, refer to Sec. 430.23(m). For determination
of certified ratings, refer to Sec. 429.16 of this chapter.
For test room requirements, refer to section 2.1 of this
appendix. For test unit installation requirements refer to sections
2.2.a, 2.2.b, 2.2.c, 2.2.1, 2.2.2, 2.2.3(a), 2.2.3(c), 2.2.4, 2.2.5,
and 2.4 to 2.12 of this appendix, and sections 5.1.3 and 5.1.4 of
AHRI 1230-2010. The ``manufacturer's published instructions,'' as
stated in section 8.2 of ANSI/ASHRAE 37-2009 (incorporated by
reference, see Sec. 430.3) and ``manufacturer's installation
instructions'' discussed in this appendix mean the manufacturer's
installation instructions that come packaged with or appear in the
labels applied to the unit. This does not include online manuals.
Installation instructions that appear in the labels applied
[[Page 1479]]
to the unit take precedence over installation instructions that are
shipped with the unit.
For general requirements for the test procedure, refer to
section 3.1 of this appendix, except for sections 3.1.3 and 3.1.4,
which are requirements for indoor air volume and outdoor air volume.
For indoor air volume and outdoor air volume requirements, refer
instead to section 6.1.5 (except where section 6.1.5 refers to Table
8, refer instead to Table 4 of this appendix) and 6.1.6 of AHRI
1230-2010.
For the test method, refer to sections 3.3 to 3.5 and 3.7 to
3.13 of this appendix. For cooling mode and heating mode test
conditions, refer to section 6.2 of AHRI 1230-2010. For calculations
of seasonal performance descriptors, refer to section 4 of this
appendix.
(B) For systems other than VRF, only a subset of the sections
listed in this test procedure apply when testing and determining
represented values for a particular unit. Table 1 shows the sections
of the test procedure that apply to each system. This table is meant
to assist manufacturers in finding the appropriate sections of the
test procedure; the appendix sections rather than the table provide
the specific requirements for testing, and given the varied nature
of available units, manufacturers are responsible for determining
which sections apply to each unit tested based on the unit's
characteristics. To use this table, first refer to the sections
listed under ``all units''. Then refer to additional requirements
based on:
(1) System configuration(s),
(2) The compressor staging or modulation capability, and
(3) Any special features.
Testing requirements for space-constrained products do not
differ from similar equipment that is not space-constrained and thus
are not listed separately in this table. Air conditioners and heat
pumps are not listed separately in this table, but heating
procedures and calculations apply only to heat pumps.
[GRAPHIC] [TIFF OMITTED] TR05JA17.004
[[Page 1480]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.005
[[Page 1481]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.006
2.1 Test Room Requirements
a. Test using two side-by-side rooms: An indoor test room and an
outdoor test room. For multiple-split, single-zone-multi-coil or
multi-circuit air conditioners and heat pumps, however, use as many
indoor test rooms as needed to accommodate the total number of
indoor units. These rooms must comply with the requirements
specified in sections 8.1.2 and 8.1.3 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3).
b. Inside these test rooms, use artificial loads during cyclic
tests and frost accumulation tests, if needed, to produce stabilized
room air temperatures. For one room, select an electric resistance
heater(s) having a heating capacity that is approximately equal to
the heating capacity of the test unit's condenser. For the second
room, select a heater(s) having a capacity that is close to the
sensible cooling capacity of the test unit's evaporator. Cycle the
heater located in the same room as the test unit evaporator coil ON
and OFF when the test unit cycles ON and OFF. Cycle the heater
located in the same room as the test unit condensing coil ON and OFF
when the test unit cycles OFF and ON.
2.2 Test Unit Installation Requirements
a. Install the unit according to section 8.2 of ANSI/ASHRAE 37-
2009 (incorporated by reference, see Sec. 430.3), subject to the
following additional requirements:
(1) When testing split systems, follow the requirements given in
section 6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see
Sec. 430.3). For the vapor refrigerant line(s), use the insulation
included with the unit; if no insulation is provided, use insulation
meeting the specifications for the insulation in the installation
instructions included with the unit by the manufacturer; if no
insulation is included with the unit and the installation
instructions do not contain provisions for insulating the line(s),
fully insulate the vapor refrigerant line(s) with vapor proof
insulation having an inside diameter that matches the refrigerant
tubing and a nominal thickness of at least 0.5 inches. For the
liquid refrigerant line(s), use the insulation included with the
unit; if no insulation is provided, use insulation meeting the
specifications for the insulation in the installation instructions
included with the unit by the manufacturer; if no insulation is
included with the unit and the installation instructions do not
contain provisions for insulating the line(s), leave the liquid
refrigerant line(s) exposed to the air for air conditioners and heat
pumps that heat and cool; or, for heating-only heat pumps, insulate
the liquid refrigerant line(s) with insulation having an inside
diameter that
[[Page 1482]]
matches the refrigerant tubing and a nominal thickness of at least
0.5 inches. However, these requirements do not take priority over
instructions for application of insulation for the purpose of
improving refrigerant temperature measurement accuracy as required
by sections 2.10.2 and 2.10.3 of this appendix. Insulation must be
the same for the cooling and heating tests.
(2) When testing split systems, if the indoor unit does not ship
with a cooling mode expansion device, test the system using the
device as specified in the installation instructions provided with
the indoor unit. If none is specified, test the system using a fixed
orifice or piston type expansion device that is sized appropriately
for the system.
(3) When testing triple-split systems (see section 1.2 of this
appendix, Definitions), use the tubing length specified in section
6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see Sec.
430.3) to connect the outdoor coil, indoor compressor section, and
indoor coil while still meeting the requirement of exposing 10 feet
of the tubing to outside conditions;
(4) When testing split systems having multiple indoor coils,
connect each indoor blower coil unit to the outdoor unit using:
(a) 25 feet of tubing, or
(b) tubing furnished by the manufacturer, whichever is longer.
At least 10 feet of the system interconnection tubing shall be
exposed to the outside conditions. If they are needed to make a
secondary measurement of capacity or for verification of refrigerant
charge, install refrigerant pressure measuring instruments as
described in section 8.2.5 of ANSI/ASHRAE 37-2009 (incorporated by
reference, see Sec. 430.3). Section 2.10 of this appendix specifies
which secondary methods require refrigerant pressure measurements
and section 2.2.5.5 of this appendix discusses use of pressure
measurements to verify charge. At a minimum, insulate the low-
pressure line(s) of a split system with insulation having an inside
diameter that matches the refrigerant tubing and a nominal thickness
of 0.5 inch.
b. For units designed for both horizontal and vertical
installation or for both up-flow and down-flow vertical
installations, use the orientation for testing specified by the
manufacturer in the certification report. Conduct testing with the
following installed:
(1) The most restrictive filter(s);
(2) Supplementary heating coils; and
(3) Other equipment specified as part of the unit, including all
hardware used by a heat comfort controller if so equipped (see
section 1 of this appendix, Definitions). For small-duct, high-
velocity systems, configure all balance dampers or restrictor
devices on or inside the unit to fully open or lowest restriction.
c. Testing a ducted unit without having an indoor air filter
installed is permissible as long as the minimum external static
pressure requirement is adjusted as stated in Table 4, note 3 (see
section 3.1.4 of this appendix). Except as noted in section 3.1.10
of this appendix, prevent the indoor air supplementary heating coils
from operating during all tests. For uncased coils, create an
enclosure using 1 inch fiberglass foil-faced ductboard having a
nominal density of 6 pounds per cubic foot. Or alternatively,
construct an enclosure using sheet metal or a similar material and
insulating material having a thermal resistance (``R'' value)
between 4 and 6 hr[middot]ft\2\[middot] [deg]F/Btu. Size the
enclosure and seal between the coil and/or drainage pan and the
interior of the enclosure as specified in installation instructions
shipped with the unit. Also seal between the plenum and inlet and
outlet ducts.
d. When testing a coil-only system, install a toroidal-type
transformer to power the system's low-voltage components, complying
with any additional requirements for the transformer mentioned in
the installation manuals included with the unit by the system
manufacturer. If the installation manuals do not provide
specifications for the transformer, use a transformer having the
following features:
(1) A nominal volt-amp rating such that the transformer is
loaded between 25 and 90 percent of this rating for the highest
level of power measured during the off mode test (section 3.13 of
this appendix);
(2) Designed to operate with a primary input of 230 V, single
phase, 60 Hz; and
(3) That provides an output voltage that is within the specified
range for each low-voltage component. Include the power consumption
of the components connected to the transformer as part of the total
system power consumption during the off mode tests; do not include
the power consumed by the transformer when no load is connected to
it.
e. Test an outdoor unit with no match (i.e., that is not
distributed in commerce with any indoor units) using a coil-only
indoor unit with a single cooling air volume rate whose coil has:
(1) Round tubes of outer diameter no less than 0.375 inches, and
(2) a normalized gross indoor fin surface (NGIFS) no greater
than 1.0 square inches per British thermal unit per hour (sq. in./
Btu/hr). NGIFS is calculated as follows:
NGIFS = 2 x Lf x Wf x Nf / Qc(95)
where:
Lf = Indoor coil fin length in inches, also height of the
coil transverse to the tubes.
Wf = Indoor coil fin width in inches, also depth of the
coil.
Nf = Number of fins.
Qc(95) = the measured space cooling capacity of the
tested outdoor unit/indoor unit combination as determined from the
A2 or A Test whichever applies, Btu/h.
[fnof]. If the outdoor unit or the outdoor portion of a single-
package unit has a drain pan heater to prevent freezing of defrost
water, the heater shall be energized, subject to control to de-
energize it when not needed by the heater's thermostat or the unit's
control system, for all tests.
g. If pressure measurement devices are connected to a cooling/
heating heat pump refrigerant circuit, the refrigerant charge
Mt that could potentially transfer out of the connected
pressure measurement systems (transducers, gauges, connections, and
lines) between operating modes must be less than 2 percent of the
factory refrigerant charge listed on the nameplate of the outdoor
unit. If the outdoor unit nameplate has no listed refrigerant
charge, or the heat pump is shipped without a refrigerant charge,
use a factory refrigerant charge equal to 30 ounces per ton of
certified cooling capacity. Use Equation 2.2-1 to calculate
Mt for heat pumps that have a single expansion device
located in the outdoor unit to serve each indoor unit, and use
Equation 2.2-2 to calculate Mt for heat pumps that have
two expansion devices per indoor unit.
[GRAPHIC] [TIFF OMITTED] TR05JA17.007
[GRAPHIC] [TIFF OMITTED] TR05JA17.027
where:
Vi (i=2,3,4. . .) = the internal volume of the pressure
measurement system (pressure lines, fittings, and gauge and/or
transducer) at the location i (as indicated in Table 2), (cubic
inches)
fi (i=5,6) = 0 if the pressure measurement system is
pitched upwards from the pressure tap location to the gauge or
transducer, 1 if it is not.
r = the density associated with liquid refrigerant at
100[emsp14][deg]F bubble point conditions (ounces per cubic inch)
Table 2--Pressure Measurement Locations
------------------------------------------------------------------------
Location
------------------------------------------------------------------------
Compressor Discharge.................................... 1
Between Outdoor Coil and Outdoor Expansion Valve(s)..... 2
Liquid Service Valve.................................... 3
Indoor Coil Inlet....................................... 4
Indoor Coil Outlet...................................... 5
[[Page 1483]]
Common Suction Port (i.e. vapor service valve).......... 6
Compressor Suction...................................... 7
------------------------------------------------------------------------
Calculate the internal volume of each pressure measurement
system using internal volume reported for pressure transducers and
gauges in product literature, if available. If such information is
not available, use the value of 0.1 cubic inches internal volume for
each pressure transducer, and 0.2 cubic inches for each pressure
gauge.
In addition, for heat pumps that have a single expansion device
located in the outdoor unit to serve each indoor unit, the internal
volume of the pressure system at location 2 (as indicated in Table
2) must be no more than 1 cubic inch. Once the pressure measurement
lines are set up, no change should be made until all tests are
finished.
2.2.1 Defrost Control Settings
Set heat pump defrost controls at the normal settings which most
typify those encountered in generalized climatic region IV. (Refer
to Figure 1 and Table 20 of section 4.2 of this appendix for
information on region IV.) For heat pumps that use a time-adaptive
defrost control system (see section 1.2 of this appendix,
Definitions), the manufacturer must specify in the certification
report the frosting interval to be used during frost accumulation
tests and provide the procedure for manually initiating the defrost
at the specified time.
2.2.2 Special Requirements for Units Having a Multiple-Speed Outdoor
Fan
Configure the multiple-speed outdoor fan according to the
installation manual included with the unit by the manufacturer, and
thereafter, leave it unchanged for all tests. The controls of the
unit must regulate the operation of the outdoor fan during all lab
tests except dry coil cooling mode tests. For dry coil cooling mode
tests, the outdoor fan must operate at the same speed used during
the required wet coil test conducted at the same outdoor test
conditions.
2.2.3 Special Requirements for Multi-Split Air Conditioners and Heat
Pumps and Ducted Systems Using a Single Indoor Section Containing
Multiple Indoor Blowers That Would Normally Operate Using Two or More
Indoor Thermostats
Because these systems will have more than one indoor blower and
possibly multiple outdoor fans and compressor systems, references in
this test procedure to a singular indoor blower, outdoor fan, and/or
compressor means all indoor blowers, all outdoor fans, and all
compressor systems that are energized during the test.
a. Additional requirements for multi-split air conditioners and
heat pumps. For any test where the system is operated at part load
(i.e., one or more compressors ``off'', operating at the
intermediate or minimum compressor speed, or at low compressor
capacity), record the indoor coil(s) that are not providing heating
or cooling during the test. For variable-speed systems, the
manufacturer must designate in the certification report at least one
indoor unit that is not providing heating or cooling for all tests
conducted at minimum compressor speed.
b. Additional requirements for ducted split systems with a
single indoor unit containing multiple indoor blowers (or for
single-package units with an indoor section containing multiple
indoor blowers) where the indoor blowers are designed to cycle on
and off independently of one another and are not controlled such
that all indoor blowers are modulated to always operate at the same
air volume rate or speed. For any test where the system is operated
at its lowest capacity--i.e., the lowest total air volume rate
allowed when operating the single-speed compressor or when operating
at low compressor capacity--indoor blowers accounting for at least
one-third of the full-load air volume rate must be turned off unless
prevented by the controls of the unit. In such cases, turn off as
many indoor blowers as permitted by the unit's controls. Where more
than one option exists for meeting this ``off'' requirement, the
manufacturer shall indicate in its certification report which indoor
blower(s) are turned off. The chosen configuration shall remain
unchanged for all tests conducted at the same lowest capacity
configuration. For any indoor coil turned off during a test, cease
forced airflow through any outlet duct connected to a switched-off
indoor blower.
c. For test setups where the laboratory's physical limitations
requires use of more than the required line length of 25 feet as
listed in section 2.2.a(4) of this appendix, then the actual
refrigerant line length used by the laboratory may exceed the
required length and the refrigerant line length correction factors
in Table 4 of AHRI 1230-2010 are applied to the cooling capacity
measured for each cooling mode test.
2.2.4 Wet-Bulb Temperature Requirements for the Air Entering the Indoor
and Outdoor Coils
2.2.4.1 Cooling Mode Tests
For wet-coil cooling mode tests, regulate the water vapor
content of the air entering the indoor unit so that the wet-bulb
temperature is as listed in Tables 5 to 8. As noted in these same
tables, achieve a wet-bulb temperature during dry-coil cooling mode
tests that results in no condensate forming on the indoor coil.
Controlling the water vapor content of the air entering the outdoor
side of the unit is not required for cooling mode tests except when
testing:
(1) Units that reject condensate to the outdoor coil during wet
coil tests. Tables 5-8 list the applicable wet-bulb temperatures.
(2) Single-package units where all or part of the indoor section
is located in the outdoor test room. The average dew point
temperature of the air entering the outdoor coil during wet coil
tests must be within 3.0[emsp14][deg]F of the average
dew point temperature of the air entering the indoor coil over the
30-minute data collection interval described in section 3.3 of this
appendix. For dry coil tests on such units, it may be necessary to
limit the moisture content of the air entering the outdoor coil of
the unit to meet the requirements of section 3.4 of this appendix.
2.2.4.2 Heating Mode Tests
For heating mode tests, regulate the water vapor content of the
air entering the outdoor unit to the applicable wet-bulb temperature
listed in Tables 12 to 15. The wet-bulb temperature entering the
indoor side of the heat pump must not exceed 60[emsp14][deg]F.
Additionally, if the Outdoor Air Enthalpy test method (section
2.10.1 of this appendix) is used while testing a single-package heat
pump where all or part of the outdoor section is located in the
indoor test room, adjust the wet-bulb temperature for the air
entering the indoor side to yield an indoor-side dew point
temperature that is as close as reasonably possible to the dew point
temperature of the outdoor-side entering air.
2.2.5 Additional Refrigerant Charging Requirements
2.2.5.1 Instructions To Use for Charging
a. Where the manufacturer's installation instructions contain
two sets of refrigerant charging criteria, one for field
installations and one for lab testing, use the field installation
criteria.
b. For systems consisting of an outdoor unit manufacturer's
outdoor section and indoor section with differing charging
procedures, adjust the refrigerant charge per the outdoor
installation instructions.
c. For systems consisting of an outdoor unit manufacturer's
outdoor unit and an independent coil manufacturer's indoor unit with
differing charging procedures, adjust the refrigerant charge per the
indoor unit's installation instructions. If instructions are
provided only with the outdoor unit or are provided only with an
independent coil manufacturer's indoor unit, then use the provided
instructions.
2.2.5.2 Test(s) To Use for Charging
a. Use the tests or operating conditions specified in the
manufacturer's installation instructions for charging. The
manufacturer's installation instructions may specify use of tests
other than the A or A2 test for charging, but, unless the
unit is a heating-only heat pump, the air volume rate must be
determined by the A or A2 test as specified in section
3.1 of this appendix.
b. If the manufacturer's installation instructions do not
specify a test or operating conditions for charging or there are no
manufacturer's instructions, use the following test(s):
(1) For air conditioners or cooling and heating heat pumps, use
the A or A2 test.
(2) For cooling and heating heat pumps that do not operate in
the H1 or H12 test (e.g. due to shut down by the unit
limiting devices) when tested using the charge determined at the A
or A2 test, and for heating-only heat pumps, use the H1
or H12 test.
2.2.5.3 Parameters To Set and Their Target Values
a. Consult the manufacturer's installation instructions
regarding which parameters (e.g., superheat) to set and their target
values. If the instructions provide ranges of values, select target
values equal to the midpoints of the provided ranges.
[[Page 1484]]
b. In the event of conflicting information between charging
instructions (i.e., multiple conditions given for charge adjustment
where all conditions specified cannot be met), follow the following
hierarchy.
(1) For fixed orifice systems:
(i) Superheat
(ii) High side pressure or corresponding saturation or dew-point
temperature
(iii) Low side pressure or corresponding saturation or dew-point
temperature
(iv) Low side temperature
(v) High side temperature
(vi) Charge weight
(2) For expansion valve systems:
(i) Subcooling
(ii) High side pressure or corresponding saturation or dew-point
temperature
(iii) Low side pressure or corresponding saturation or dew-point
temperature
(iv) Approach temperature (difference between temperature of
liquid leaving condenser and condenser average inlet air
temperature)
(v) Charge weight
c. If there are no installation instructions and/or they do not
provide parameters and target values, set superheat to a target
value of 12 [deg]F for fixed orifice systems or set subcooling to a
target value of 10 [deg]F for expansion valve systems.
2.2.5.4 Charging Tolerances
a. If the manufacturer's installation instructions specify
tolerances on target values for the charging parameters, set the
values within these tolerances.
b. Otherwise, set parameter values within the following test
condition tolerances for the different charging parameters:
1. Superheat: +/- 2.0 [deg]F
2. Subcooling: +/- 2.0 [deg]F
3. High side pressure or corresponding saturation or dew point
temperature: +/- 4.0 psi or +/- 1.0 [deg]F
4. Low side pressure or corresponding saturation or dew point
temperature: +/- 2.0 psi or +/- 0.8 [deg]F
5. High side temperature: +/-2.0 [deg]F
6. Low side temperature: +/-2.0 [deg]F
7. Approach temperature: +/- 1.0 [deg]F
8. Charge weight: +/- 2.0 ounce
2.2.5.5 Special Charging Instructions
a. Cooling and Heating Heat Pumps
If, using the initial charge set in the A or A2 test,
the conditions are not within the range specified in manufacturer's
installation instructions for the H1 or H12 test, make as
small as possible an adjustment to obtain conditions for this test
in the specified range. After this adjustment, recheck conditions in
the A or A2 test to confirm that they are still within
the specified range for the A or A2 test.
b. Single-Package Systems
Unless otherwise directed by the manufacturer's installation
instructions, install one or more refrigerant line pressure gauges
during the setup of the unit, located depending on the parameters
used to verify or set charge, as described:
(1) Install a pressure gauge at the location of the service
valve on the liquid line if charging is on the basis of subcooling,
or high side pressure or corresponding saturation or dew point
temperature;
(2) Install a pressure gauge at the location of the service
valve on the suction line if charging is on the basis of superheat,
or low side pressure or corresponding saturation or dew point
temperature.
Use methods for installing pressure gauge(s) at the required
location(s) as indicated in manufacturer's instructions if
specified.
2.2.5.6 Near-Azeotropic and Zeotropic Refrigerants.
Perform charging of near-azeotropic and zeotropic refrigerants
only with refrigerant in the liquid state.
2.2.5.7 Adjustment of Charge Between Tests.
After charging the system as described in this test procedure,
use the set refrigerant charge for all tests used to determine
performance. Do not adjust the refrigerant charge at any point
during testing. If measurements indicate that refrigerant charge has
leaked during the test, repair the refrigerant leak, repeat any
necessary set-up steps, and repeat all tests.
2.3 Indoor Air Volume Rates.
If a unit's controls allow for overspeeding the indoor blower
(usually on a temporary basis), take the necessary steps to prevent
overspeeding during all tests.
2.3.1 Cooling Tests
a. Set indoor blower airflow-control settings (e.g., fan motor
pin settings, fan motor speed) according to the requirements that
are specified in section 3.1.4 of this appendix.
b. Express the Cooling full-load air volume rate, the Cooling
Minimum Air Volume Rate, and the Cooling Intermediate Air Volume
Rate in terms of standard air.
2.3.2 Heating Tests
a. Set indoor blower airflow-control settings (e.g., fan motor
pin settings, fan motor speed) according to the requirements that
are specified in section 3.1.4 of this appendix.
b. Express the heating full-load air volume rate, the heating
minimum air volume rate, the heating intermediate air volume rate,
and the heating nominal air volume rate in terms of standard air.
2.4 Indoor Coil Inlet and Outlet Duct Connections
Insulate and/or construct the outlet plenum as described in
section 2.4.1 of this appendix and, if installed, the inlet plenum
described in section 2.4.2 of this appendix with thermal insulation
having a nominal overall resistance (R-value) of at least 19
hr[middot]ft\2\[middot] [deg]F/Btu.
2.4.1 Outlet Plenum for the Indoor Unit
a. Attach a plenum to the outlet of the indoor coil. (Note: For
some packaged systems, the indoor coil may be located in the outdoor
test room.)
b. For systems having multiple indoor coils, or multiple indoor
blowers within a single indoor section, attach a plenum to each
indoor coil or indoor blower outlet. In order to reduce the number
of required airflow measurement apparati (section 2.6 of this
appendix), each such apparatus may serve multiple outlet plenums
connected to a single common duct leading to the apparatus. More
than one indoor test room may be used, which may use one or more
common ducts leading to one or more airflow measurement apparati
within each test room that contains multiple indoor coils. At the
plane where each plenum enters a common duct, install an adjustable
airflow damper and use it to equalize the static pressure in each
plenum. Each outlet air temperature grid (section 2.5.4 of this
appendix) and airflow measuring apparatus are located downstream of
the inlet(s) to the common duct. For multiple-circuit (or multi-
circuit) systems for which each indoor coil outlet is measured
separately and its outlet plenum is not connected to a common duct
connecting multiple outlet plenums, the outlet air temperature grid
and airflow measuring apparatus must be installed at each outlet
plenum.
c. For small-duct, high-velocity systems, install an outlet
plenum that has a diameter that is equal to or less than the value
listed in Table 3. The limit depends only on the Cooling full-load
air volume rate (see section 3.1.4.1.1 of this appendix) and is
effective regardless of the flange dimensions on the outlet of the
unit (or an air supply plenum adapter accessory, if installed in
accordance with the manufacturer's installation instructions).
d. Add a static pressure tap to each face of the (each) outlet
plenum, if rectangular, or at four evenly distributed locations
along the circumference of an oval or round plenum. Create a
manifold that connects the four static pressure taps. Figure 9 of
ANSI/ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3)
shows allowed options for the manifold configuration. The cross-
sectional dimensions of plenum shall be equal to the dimensions of
the indoor unit outlet. See Figures 7a, 7b, and 7c of ANSI/ASHRAE
37-2009 for the minimum length of the (each) outlet plenum and the
locations for adding the static pressure taps for ducted blower coil
indoor units and single-package systems. See Figure 8 of ANSI/ASHRAE
37-2009 for coil-only indoor units.
Table 3--Size of Outlet Plenum for Small-Duct High-Velocity Indoor Units
------------------------------------------------------------------------
Maximum
diameter * of
Cooling full-load air volume rate (scfm) outlet plenum
(inches)
------------------------------------------------------------------------
<=500................................................... 6
501 to 700.............................................. 7
701 to 900.............................................. 8
901 to 1100............................................. 9
1101 to 1400............................................ 10
1401 to 1750............................................ 11
------------------------------------------------------------------------
* If the outlet plenum is rectangular, calculate its equivalent diameter
using (4A/P,) where A is the cross-sectional area and P is the
perimeter of the rectangular plenum, and compare it to the listed
maximum diameter.
[[Page 1485]]
2.4.2 Inlet Plenum for the Indoor Unit
Install an inlet plenum when testing a coil-only indoor unit, a
ducted blower coil indoor unit, or a single-package system. See
Figures 7b and 7c of ANSI/ASHRAE 37-2009 for cross-sectional
dimensions, the minimum length of the inlet plenum, and the
locations of the static-pressure taps for ducted blower coil indoor
units and single-package systems. See Figure 8 of ANSI/ASHRAE 37-
2009 for coil-only indoor units. The inlet plenum duct size shall
equal the size of the inlet opening of the air-handling (blower
coil) unit or furnace. For a ducted blower coil indoor unit the set
up may omit the inlet plenum if an inlet airflow prevention device
is installed with a straight internally unobstructed duct on its
outlet end with a minimum length equal to 1.5 times the square root
of the cross-sectional area of the indoor unit inlet. See section
2.5.1.2 of this appendix for requirements for the locations of
static pressure taps built into the inlet airflow prevention device.
For all of these arrangements, make a manifold that connects the
four static-pressure taps using one of the three configurations
specified in section 2.4.1.d of this appendix. Never use an inlet
plenum when testing non-ducted indoor units.
2.5 Indoor Coil Air Property Measurements and Airflow Prevention
Devices
Follow instructions for indoor coil air property measurements as
described in section 2.14 of this appendix, unless otherwise
instructed in this section.
a. Measure the dry-bulb temperature and water vapor content of
the air entering and leaving the indoor coil. If needed, use an air
sampling device to divert air to a sensor(s) that measures the water
vapor content of the air. See section 5.3 of ANSI/ASHRAE 41.1-2013
(incorporated by reference, see Sec. 430.3) for guidance on
constructing an air sampling device. No part of the air sampling
device or the tubing transferring the sampled air to the sensor
shall be within two inches of the test chamber floor, and the
transfer tubing shall be insulated. The sampling device may also be
used for measurement of dry bulb temperature by transferring the
sampled air to a remotely located sensor(s). The air sampling device
and the remotely located temperature sensor(s) may be used to
determine the entering air dry bulb temperature during any test. The
air sampling device and the remotely located sensor(s) may be used
to determine the leaving air dry bulb temperature for all tests
except:
(1) Cyclic tests; and
(2) Frost accumulation tests.
b. Install grids of temperature sensors to measure dry bulb
temperatures of both the entering and leaving airstreams of the
indoor unit. These grids of dry bulb temperature sensors may be used
to measure average dry bulb temperature entering and leaving the
indoor unit in all cases (as an alternative to the dry bulb sensor
measuring the sampled air). The leaving airstream grid is required
for measurement of average dry bulb temperature leaving the indoor
unit for the two special cases noted above. The grids are also
required to measure the air temperature distribution of the entering
and leaving airstreams as described in sections 3.1.8 and 3.1.9 of
this appendix. Two such grids may applied as a thermopile, to
directly obtain the average temperature difference rather than
directly measuring both entering and leaving average temperatures.
c. Use of airflow prevention devices. Use an inlet and outlet
air damper box, or use an inlet upturned duct and an outlet air
damper box when conducting one or both of the cyclic tests listed in
sections 3.2 and 3.6 of this appendix on ducted systems. If not
conducting any cyclic tests, an outlet air damper box is required
when testing ducted and non-ducted heat pumps that cycle off the
indoor blower during defrost cycles and there is no other means for
preventing natural or forced convection through the indoor unit when
the indoor blower is off. Never use an inlet damper box or an inlet
upturned duct when testing non-ducted indoor units. An inlet
upturned duct is a length of ductwork installed upstream from the
inlet such that the indoor duct inlet opening, facing upwards, is
sufficiently high to prevent natural convection transfer out of the
duct. If an inlet upturned duct is used, install a dry bulb
temperature sensor near the inlet opening of the indoor duct at a
centerline location not higher than the lowest elevation of the duct
edges at the inlet, and ensure that any pair of 5-minute averages of
the dry bulb temperature at this location, measured at least every
minute during the compressor OFF period of the cyclic test, do not
differ by more than 1.0[emsp14][deg]F.
2.5.1 Test Set-Up on the Inlet Side of the Indoor Coil: For Cases Where
the Inlet Airflow Prevention Device Is Installed
a. Install an airflow prevention device as specified in section
2.5.1.1 or 2.5.1.2 of this appendix, whichever applies.
b. For an inlet damper box, locate the grid of entering air dry-
bulb temperature sensors, if used, and the air sampling device, or
the sensor used to measure the water vapor content of the inlet air,
at a location immediately upstream of the damper box inlet. For an
inlet upturned duct, locate the grid of entering air dry-bulb
temperature sensors, if used, and the air sampling device, or the
sensor used to measure the water vapor content of the inlet air, at
a location at least one foot downstream from the beginning of the
insulated portion of the duct but before the static pressure
measurement.
2.5.1.1 If the Section 2.4.2 Inlet Plenum Is Installed
Construct the airflow prevention device having a cross-sectional
flow area equal to or greater than the flow area of the inlet
plenum. Install the airflow prevention device upstream of the inlet
plenum and construct ductwork connecting it to the inlet plenum. If
needed, use an adaptor plate or a transition duct section to connect
the airflow prevention device with the inlet plenum. Insulate the
ductwork and inlet plenum with thermal insulation that has a nominal
overall resistance (R-value) of at least 19 hr [middot] ft\2\
[middot] [deg]F/Btu.
2.5.1.2 If the Section 2.4.2 Inlet Plenum Is Not Installed
Construct the airflow prevention device having a cross-sectional
flow area equal to or greater than the flow area of the air inlet of
the indoor unit. Install the airflow prevention device immediately
upstream of the inlet of the indoor unit. If needed, use an adaptor
plate or a short transition duct section to connect the airflow
prevention device with the unit's air inlet. Add static pressure
taps at the center of each face of a rectangular airflow prevention
device, or at four evenly distributed locations along the
circumference of an oval or round airflow prevention device. Locate
the pressure taps at a distance from the indoor unit inlet equal to
0.5 times the square root of the cross sectional area of the indoor
unit inlet. This location must be between the damper and the inlet
of the indoor unit, if a damper is used. Make a manifold that
connects the four static pressure taps using one of the
configurations shown in Figure 9 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3). Insulate the ductwork
with thermal insulation that has a nominal overall resistance (R-
value) of at least 19 hr [middot] ft\2\ [middot] [deg]F/Btu.
2.5.2 Test Set-Up on the Inlet Side of the Indoor Unit: for Cases Where
No Airflow Prevention Device is Installed
If using the section 2.4.2 inlet plenum and a grid of dry bulb
temperature sensors, mount the grid at a location upstream of the
static pressure taps described in section 2.4.2 of this appendix,
preferably at the entrance plane of the inlet plenum. If the section
2.4.2 inlet plenum is not used (i.e. for non-ducted units) locate a
grid approximately 6 inches upstream of the indoor unit inlet. In
the case of a system having multiple non-ducted indoor units, do
this for each indoor unit. Position an air sampling device, or the
sensor used to measure the water vapor content of the inlet air,
immediately upstream of the (each) entering air dry-bulb temperature
sensor grid. If a grid of sensors is not used, position the entering
air sampling device (or the sensor used to measure the water vapor
content of the inlet air) as if the grid were present.
2.5.3 Indoor Coil Static Pressure Difference Measurement
Fabricate pressure taps meeting all requirements described in
section 6.5.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see
Sec. 430.3) and illustrated in Figure 2A of AMCA 210-2007
(incorporated by reference, see Sec. 430.3), however, if adhering
strictly to the description in section 6.5.2 of ANSI/ASHRAE 37-2009,
the minimum pressure tap length of 2.5 times the inner diameter of
Figure 2A of AMCA 210-2007 is waived. Use a differential pressure
measuring instrument that is accurate to within 0.01
inches of water and has a resolution of at least 0.01 inches of
water to measure the static pressure difference between the indoor
coil air inlet and outlet. Connect one side of the differential
pressure instrument to the manifolded pressure taps installed in the
outlet plenum. Connect the other side of the instrument to the
manifolded pressure taps located in either
[[Page 1486]]
the inlet plenum or incorporated within the airflow prevention
device. For non-ducted indoor units that are tested with multiple
outlet plenums, measure the static pressure within each outlet
plenum relative to the surrounding atmosphere.
2.5.4 Test Set-Up on the Outlet Side of the Indoor Coil
a. Install an interconnecting duct between the outlet plenum
described in section 2.4.1 of this appendix and the airflow
measuring apparatus described below in section 2.6 of this appendix.
The cross-sectional flow area of the interconnecting duct must be
equal to or greater than the flow area of the outlet plenum or the
common duct used when testing non-ducted units having multiple
indoor coils. If needed, use adaptor plates or transition duct
sections to allow the connections. To minimize leakage, tape joints
within the interconnecting duct (and the outlet plenum). Construct
or insulate the entire flow section with thermal insulation having a
nominal overall resistance (R-value) of at least 19
hr[middot]ft\2\[middot] [deg]F/Btu.
b. Install a grid(s) of dry-bulb temperature sensors inside the
interconnecting duct. Also, install an air sampling device, or the
sensor(s) used to measure the water vapor content of the outlet air,
inside the interconnecting duct. Locate the dry-bulb temperature
grid(s) upstream of the air sampling device (or the in-duct
sensor(s) used to measure the water vapor content of the outlet
air). Turn off the sampler fan motor during the cyclic tests. Air
leaving an indoor unit that is sampled by an air sampling device for
remote water-vapor-content measurement must be returned to the
interconnecting duct at a location:
(1) Downstream of the air sampling device;
(2) On the same side of the outlet air damper as the air
sampling device; and
(3) Upstream of the section 2.6 airflow measuring apparatus.
2.5.4.1 Outlet Air Damper Box Placement and Requirements
If using an outlet air damper box (see section 2.5 of this
appendix), the leakage rate from the combination of the outlet
plenum, the closed damper, and the duct section that connects these
two components must not exceed 20 cubic feet per minute when a
negative pressure of 1 inch of water column is maintained at the
plenum's inlet.
2.5.4.2 Procedures To Minimize Temperature Maldistribution
Use these procedures if necessary to correct temperature
maldistributions. Install a mixing device(s) upstream of the outlet
air, dry-bulb temperature grid (but downstream of the outlet plenum
static pressure taps). Use a perforated screen located between the
mixing device and the dry-bulb temperature grid, with a maximum open
area of 40 percent. One or both items should help to meet the
maximum outlet air temperature distribution specified in section
3.1.8 of this appendix. Mixing devices are described in sections
5.3.2 and 5.3.3 of ANSI/ASHRAE 41.1-2013 and section 5.2.2 of ASHRAE
41.2-1987 (RA 1992) (incorporated by reference, see Sec. 430.3).
2.5.4.3 Minimizing Air Leakage
For small-duct, high-velocity systems, install an air damper
near the end of the interconnecting duct, just prior to the
transition to the airflow measuring apparatus of section 2.6 of this
appendix. To minimize air leakage, adjust this damper such that the
pressure in the receiving chamber of the airflow measuring apparatus
is no more than 0.5 inch of water higher than the surrounding test
room ambient. If applicable, in lieu of installing a separate
damper, use the outlet air damper box of sections 2.5 and 2.5.4.1 of
this appendix if it allows variable positioning. Also apply these
steps to any conventional indoor blower unit that creates a static
pressure within the receiving chamber of the airflow measuring
apparatus that exceeds the test room ambient pressure by more than
0.5 inches of water column.
2.5.5 Dry Bulb Temperature Measurement
a. Measure dry bulb temperatures as specified in sections 4,
5.3, 6, and 7 of ANSI/ASHRAE 41.1-2013 (incorporated by reference,
see Sec. 430.3).
b. Distribute the sensors of a dry-bulb temperature grid over
the entire flow area. The required minimum is 9 sensors per grid.
2.5.6 Water Vapor Content Measurement
Determine water vapor content by measuring dry-bulb temperature
combined with the air wet-bulb temperature, dew point temperature,
or relative humidity. If used, construct and apply wet-bulb
temperature sensors as specified in sections 4, 5, 6, 7.2, 7.3, and
7.4 of ASHRAE 41.6-2014 (incorporated by reference, see Sec.
430.3). The temperature sensor (wick removed) must be accurate to
within 0.2[emsp14][deg]F. If used, apply dew point
hygrometers as specified in sections 4, 5, 6, 7.1, and 7.4 of ASHRAE
41.6-2014 (incorporated by reference, see Sec. 430.3). The dew
point hygrometers must be accurate to within 0.4[emsp14][deg]F when operated at conditions that result in
the evaluation of dew points above 35[emsp14][deg]F. If used, a
relative humidity (RH) meter must be accurate to within 0.7% RH. Other means to determine the psychrometric state of
air may be used as long as the measurement accuracy is equivalent to
or better than the accuracy achieved from using a wet-bulb
temperature sensor that meets the above specifications.
2.5.7 Air Damper Box Performance Requirements
If used (see section 2.5 of this appendix), the air damper
box(es) must be capable of being completely opened or completely
closed within 10 seconds for each action.
2.6 Airflow Measuring Apparatus
a. Fabricate and operate an airflow measuring apparatus as
specified in section 6.2 and 6.3 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3). Place the static
pressure taps and position the diffusion baffle (settling means)
relative to the chamber inlet as indicated in Figure 12 of AMCA 210-
2007 and/or Figure 14 of ASHRAE 41.2-1987 (RA 1992) (incorporated by
reference, see Sec. 430.3). When measuring the static pressure
difference across nozzles and/or velocity pressure at nozzle throats
using electronic pressure transducers and a data acquisition system,
if high frequency fluctuations cause measurement variations to
exceed the test tolerance limits specified in section 9.2 and Table
2 of ANSI/ASHRAE 37-2009, dampen the measurement system such that
the time constant associated with response to a step change in
measurement (time for the response to change 63% of the way from the
initial output to the final output) is no longer than five seconds.
b. Connect the airflow measuring apparatus to the
interconnecting duct section described in section 2.5.4 of this
appendix. See sections 6.1.1, 6.1.2, and 6.1.4, and Figures 1, 2,
and 4 of ANSI/ASHRAE 37-2009; and Figures D1, D2, and D4 of AHRI
210/240-2008 (incorporated by reference, see Sec. 430.3) for
illustrative examples of how the test apparatus may be applied
within a complete laboratory set-up. Instead of following one of
these examples, an alternative set-up may be used to handle the air
leaving the airflow measuring apparatus and to supply properly
conditioned air to the test unit's inlet. The alternative set-up,
however, must not interfere with the prescribed means for measuring
airflow rate, inlet and outlet air temperatures, inlet and outlet
water vapor contents, and external static pressures, nor create
abnormal conditions surrounding the test unit. (Note: Do not use an
enclosure as described in section 6.1.3 of ANSI/ASHRAE 37-2009 when
testing triple-split units.)
2.7 Electrical Voltage Supply
Perform all tests at the voltage specified in section 6.1.3.2 of
AHRI 210/240-2008 (incorporated by reference, see Sec. 430.3) for
``Standard Rating Tests.'' If either the indoor or the outdoor unit
has a 208V or 200V nameplate voltage and the other unit has a 230V
nameplate rating, select the voltage supply on the outdoor unit for
testing. Otherwise, supply each unit with its own nameplate voltage.
Measure the supply voltage at the terminals on the test unit using a
volt meter that provides a reading that is accurate to within 1.0 percent of the measured quantity.
2.8 Electrical Power and Energy Measurements
a. Use an integrating power (watt-hour) measuring system to
determine the electrical energy or average electrical power supplied
to all components of the air conditioner or heat pump (including
auxiliary components such as controls, transformers, crankcase
heater, integral condensate pump on non-ducted indoor units, etc.).
The watt-hour measuring system must give readings that are accurate
to within 0.5 percent. For cyclic tests, this accuracy
is required during both the ON and OFF cycles. Use either two
different scales on the same watt-hour meter or two separate watt-
hour meters. Activate the scale or meter having the lower power
rating within 15 seconds after beginning an OFF cycle. Activate the
scale or meter having the higher power rating within 15 seconds
prior to beginning an ON cycle. For ducted blower coil systems, the
ON cycle lasts from compressor ON to indoor blower OFF. For ducted
coil-only systems, the ON cycle lasts from compressor ON to
compressor OFF. For non-ducted units, the ON cycle lasts from
[[Page 1487]]
indoor blower ON to indoor blower OFF. When testing air conditioners
and heat pumps having a variable-speed compressor, avoid using an
induction watt/watt-hour meter.
b. When performing section 3.5 and/or 3.8 cyclic tests on non-
ducted units, provide instrumentation to determine the average
electrical power consumption of the indoor blower motor to within
1.0 percent. If required according to sections 3.3, 3.4,
3.7, 3.9.1 of this appendix, and/or 3.10 of this appendix, this same
instrumentation requirement (to determine the average electrical
power consumption of the indoor blower motor to within 1.0 percent) applies when testing air conditioners and heat
pumps having a variable-speed constant-air-volume-rate indoor blower
or a variable-speed, variable-air-volume-rate indoor blower.
2.9 Time Measurements
Make elapsed time measurements using an instrument that yields
readings accurate to within 0.2 percent.
2.10 Test Apparatus for the Secondary Space Conditioning Capacity
Measurement
For all tests, use the indoor air enthalpy method to measure the
unit's capacity. This method uses the test set-up specified in
sections 2.4 to 2.6 of this appendix. In addition, for all steady-
state tests, conduct a second, independent measurement of capacity
as described in section 3.1.1 of this appendix. For split systems,
use one of the following secondary measurement methods: Outdoor air
enthalpy method, compressor calibration method, or refrigerant
enthalpy method. For single-package units, use either the outdoor
air enthalpy method or the compressor calibration method as the
secondary measurement.
2.10.1 Outdoor Air Enthalpy Method
a. To make a secondary measurement of indoor space conditioning
capacity using the outdoor air enthalpy method, do the following:
(1) Measure the electrical power consumption of the test unit;
(2) Measure the air-side capacity at the outdoor coil; and
(3) Apply a heat balance on the refrigerant cycle.
b. The test apparatus required for the outdoor air enthalpy
method is a subset of the apparatus used for the indoor air enthalpy
method. Required apparatus includes the following:
(1) On the outlet side, an outlet plenum containing static
pressure taps (sections 2.4, 2.4.1, and 2.5.3 of this appendix),
(2) An airflow measuring apparatus (section 2.6 of this
appendix),
(3) A duct section that connects these two components and itself
contains the instrumentation for measuring the dry-bulb temperature
and water vapor content of the air leaving the outdoor coil
(sections 2.5.4, 2.5.5, and 2.5.6 of this appendix), and
(4) On the inlet side, a sampling device and temperature grid
(section 2.11.b of this appendix).
c. During the free outdoor air tests described in sections
3.11.1 and 3.11.1.1 of this appendix, measure the evaporator and
condenser temperatures or pressures. On both the outdoor coil and
the indoor coil, solder a thermocouple onto a return bend located at
or near the midpoint of each coil or at points not affected by vapor
superheat or liquid subcooling. Alternatively, if the test unit is
not sensitive to the refrigerant charge, install pressure gages to
the access valves or to ports created from tapping into the suction
and discharge lines according to sections 7.4.2 and 8.2.5 of ANSI/
ASHRAE 37-2009. Use this alternative approach when testing a unit
charged with a zeotropic refrigerant having a temperature glide in
excess of 1[emsp14][deg]F at the specified test conditions.
2.10.2 Compressor Calibration Method
Measure refrigerant pressures and temperatures to determine the
evaporator superheat and the enthalpy of the refrigerant that enters
and exits the indoor coil. Determine refrigerant flow rate or, when
the superheat of the refrigerant leaving the evaporator is less than
5[emsp14][deg]F, total capacity from separate calibration tests
conducted under identical operating conditions. When using this
method, install instrumentation and measure refrigerant properties
according to section 7.4.2 and 8.2.5 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3). If removing the
refrigerant before applying refrigerant lines and subsequently
recharging, use the steps in 7.4.2 of ANSI/ASHRAE 37-2009 in
addition to the methods of section 2.2.5 of this appendix to confirm
the refrigerant charge. Use refrigerant temperature and pressure
measuring instruments that meet the specifications given in sections
5.1.1 and 5.2 of ANSI/ASHRAE 37-2009.
2.10.3 Refrigerant Enthalpy Method
For this method, calculate space conditioning capacity by
determining the refrigerant enthalpy change for the indoor coil and
directly measuring the refrigerant flow rate. Use section 7.5.2 of
ANSI/ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3) for
the requirements for this method, including the additional
instrumentation requirements, and information on placing the flow
meter and a sight glass. Use refrigerant temperature, pressure, and
flow measuring instruments that meet the specifications given in
sections 5.1.1, 5.2, and 5.5.1 of ANSI/ASHRAE 37-2009. Refrigerant
flow measurement device(s), if used, must be either elevated at
least two feet from the test chamber floor or placed upon insulating
material having a total thermal resistance of at least R-12 and
extending at least one foot laterally beyond each side of the
device(s)' exposed surfaces.
2.11 Measurement of Test Room Ambient Conditions
Follow instructions for setting up air sampling device and
aspirating psychrometer as described in section 2.14 of this
appendix, unless otherwise instructed in this section.
a. If using a test set-up where air is ducted directly from the
conditioning apparatus to the indoor coil inlet (see Figure 2, Loop
Air-Enthalpy Test Method Arrangement, of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3)), add instrumentation
to permit measurement of the indoor test room dry-bulb temperature.
b. On the outdoor side, use one of the following two approaches,
except that approach (1) is required for all evaporatively-cooled
units and units that transfer condensate to the outdoor unit for
evaporation using condenser heat.
(1) Use sampling tree air collection on all air-inlet surfaces
of the outdoor unit.
(2) Use sampling tree air collection on one or more faces of the
outdoor unit and demonstrate air temperature uniformity as follows.
Install a grid of evenly-distributed thermocouples on each air-
permitting face on the inlet of the outdoor unit. Install the
thermocouples on the air sampling device, locate them individually
or attach them to a wire structure. If not installed on the air
sampling device, install the thermocouple grid 6 to 24 inches from
the unit. The thermocouples shall be evenly spaced across the coil
inlet surface and be installed to avoid sampling of discharge air or
blockage of air recirculation. The grid of thermocouples must
provide at least 16 measuring points per face or one measurement per
square foot of inlet face area, whichever is less. This grid must be
constructed and used as per section 5.3 of ANSI/ASHRAE 41.1-2013
(incorporated by reference, see Sec. 430.3). The maximum difference
between the average temperatures measured during the test period of
any two pairs of these individual thermocouples located at any of
the faces of the inlet of the outdoor unit, must not exceed 2.0
[deg]F, otherwise approach (1) must be used.
The air sampling devices shall be located at the geometric
center of each side; the branches may be oriented either parallel or
perpendicular to the longer edges of the air inlet area. The air
sampling devices in the outdoor air inlet location shall be sized
such that they cover at least 75% of the face area of the side of
the coil that they are measuring.
Air distribution at the test facility point of supply to the
unit shall be reviewed and may require remediation prior to the
beginning of testing. Mixing fans can be used to ensure adequate air
distribution in the test room. If used, mixing fans shall be
oriented such that they are pointed away from the air intake so that
the mixing fan exhaust does not affect the outdoor coil air volume
rate. Particular attention should be given to prevent the mixing
fans from affecting (enhancing or limiting) recirculation of
condenser fan exhaust air back through the unit. Any fan used to
enhance test room air mixing shall not cause air velocities in the
vicinity of the test unit to exceed 500 feet per minute.
The air sampling device may be larger than the face area of the
side being measured, however care shall be taken to prevent
discharge air from being sampled. If an air sampling device
dimension extends beyond the inlet area of the unit, holes shall be
blocked in the air sampling device to prevent sampling of discharge
air. Holes can be blocked to reduce the region of coverage of the
intake holes both in the direction of the trunk axis or
perpendicular to the trunk axis. For intake hole region reduction in
the direction of the trunk axis, block holes of one or more adjacent
pairs of branches (the branches of a pair connect opposite each
[[Page 1488]]
other at the same trunk location) at either the outlet end or the
closed end of the trunk. For intake hole region reduction
perpendicular to the trunk axis, block off the same number of holes
on each branch on both sides of the trunk.
A maximum of four (4) air sampling devices shall be connected to
each aspirating psychrometer. In order to proportionately divide the
flow stream for multiple air sampling devices for a given aspirating
psychrometer, the tubing or conduit conveying sampled air to the
psychrometer shall be of equivalent lengths for each air sampling
device. Preferentially, the air sampling device should be hard
connected to the aspirating psychrometer, but if space constraints
do not allow this, the assembly shall have a means of allowing a
flexible tube to connect the air sampling device to the aspirating
psychrometer. The tubing or conduit shall be insulated and routed to
prevent heat transfer to the air stream. Any surface of the air
conveying tubing in contact with surrounding air at a different
temperature than the sampled air shall be insulated with thermal
insulation with a nominal thermal resistance (R-value) of at least
19 hr [middot] ft\2\ [middot] [deg]F/Btu. Alternatively the conduit
may have lower thermal resistance if additional sensor(s) are used
to measure dry bulb temperature at the outlet of each air sampling
device. No part of the air sampling device or the tubing conducting
the sampled air to the sensors shall be within two inches of the
test chamber floor.
Pairs of measurements (e.g., dry bulb temperature and wet bulb
temperature) used to determine water vapor content of sampled air
shall be measured in the same location.
2.12 Measurement of Indoor Blower Speed
When required, measure fan speed using a revolution counter,
tachometer, or stroboscope that gives readings accurate to within
1.0 percent.
2.13 Measurement of Barometric Pressure
Determine the average barometric pressure during each test. Use
an instrument that meets the requirements specified in section 5.2
of ANSI/ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3).
2.14 Air Sampling Device and Aspirating Psycrhometer Requirements
Air temperature measurements shall be made in accordance with
ANSI/ASHRAE 41.1-2013, unless otherwise instructed in this section.
2.14.1 Air Sampling Device Requirements
The air sampling device is intended to draw in a sample of the
air at the critical locations of a unit under test. It shall be
constructed of stainless steel, plastic or other suitable, durable
materials. It shall have a main flow trunk tube with a series of
branch tubes connected to the trunk tube. Holes shall be on the side
of the sampler facing the upstream direction of the air source.
Other sizes and rectangular shapes can be used, and shall be scaled
accordingly with the following guidelines:
(1) Minimum hole density of 6 holes per square foot of area to
be sampled
(2) Sampler branch tube pitch (spacing) of 6 3 in
(3) Manifold trunk to branch diameter ratio having a minimum of
3:1 ratio
(4) Hole pitch (spacing) shall be equally distributed over the
branch (\1/2\ pitch from the closed end to the nearest hole)
(5) Maximum individual hole to branch diameter ratio of 1:2 (1:3
preferred)
The minimum average velocity through the air sampling device
holes shall be 2.5 ft/s as determined by evaluating the sum of the
open area of the holes as compared to the flow area in the
aspirating psychrometer.
2.14.2 Aspirating Psychrometer
The psychrometer consists of a flow section and a fan to draw
air through the flow section and measures an average value of the
sampled air stream. At a minimum, the flow section shall have a
means for measuring the dry bulb temperature (typically, a
resistance temperature device (RTD) and a means for measuring the
humidity (RTD with wetted sock, chilled mirror hygrometer, or
relative humidity sensor). The aspirating psychrometer shall include
a fan that either can be adjusted manually or automatically to
maintain required velocity across the sensors.
The psychrometer shall be made from suitable material which may
be plastic (such as polycarbonate), aluminum or other metallic
materials. All psychrometers for a given system being tested, shall
be constructed of the same material. Psychrometers shall be designed
such that radiant heat from the motor (for driving the fan that
draws sampled air through the psychrometer) does not affect sensor
measurements. For aspirating psychrometers, velocity across the wet
bulb sensor shall be 1000 200 ft/min. For all other
psychrometers, velocity shall be as specified by the sensor
manufacturer.
3. Testing Procedures
3.1 General Requirements
If, during the testing process, an equipment set-up adjustment
is made that would have altered the performance of the unit during
any already completed test, then repeat all tests affected by the
adjustment. For cyclic tests, instead of maintaining an air volume
rate, for each airflow nozzle, maintain the static pressure
difference or velocity pressure during an ON period at the same
pressure difference or velocity pressure as measured during the
steady-state test conducted at the same test conditions.
Use the testing procedures in this section to collect the data
used for calculating
(1) Performance metrics for central air conditioners and heat
pumps during the cooling season;
(2) Performance metrics for heat pumps during the heating
season; and
(3) Power consumption metric(s) for central air conditioners and
heat pumps during the off mode season(s).
3.1.1 Primary and Secondary Test Methods
For all tests, use the indoor air enthalpy method test apparatus
to determine the unit's space conditioning capacity. The procedure
and data collected, however, differ slightly depending upon whether
the test is a steady-state test, a cyclic test, or a frost
accumulation test. The following sections described these
differences. For the full-capacity cooling-mode test and (for a heat
pump) the full-capacity heating-mode test, use one of the acceptable
secondary methods specified in section 2.10 of this appendix to
determine indoor space conditioning capacity. Calculate this
secondary check of capacity according to section 3.11 of this
appendix. The two capacity measurements must agree to within 6
percent to constitute a valid test. For this capacity comparison,
use the Indoor Air Enthalpy Method capacity that is calculated in
section 7.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see
Sec. 430.3) (and, if testing a coil-only system, compare capacities
before making the after-test fan heat adjustments described in
section 3.3, 3.4, 3.7, and 3.10 of this appendix). However, include
the appropriate section 3.3 to 3.5 and 3.7 to 3.10 fan heat
adjustments within the indoor air enthalpy method capacities used
for the section 4 seasonal calculations of this appendix.
3.1.2 Manufacturer-Provided Equipment Overrides
Where needed, the manufacturer must provide a means for
overriding the controls of the test unit so that the compressor(s)
operates at the specified speed or capacity and the indoor blower
operates at the specified speed or delivers the specified air volume
rate.
3.1.3 Airflow Through the Outdoor Coil
For all tests, meet the requirements given in section 6.1.3.4 of
AHRI 210/240-2008 (incorporated by reference, see Sec. 430.3) when
obtaining the airflow through the outdoor coil.
3.1.3.1 Double-Ducted
For products intended to be installed with the outdoor airflow
ducted, the unit shall be installed with outdoor coil ductwork
installed per manufacturer installation instructions and shall
operate between 0.10 and 0.15 in H2O external static
pressure. External static pressure measurements shall be made in
accordance with ANSI/ASHRAE 37-2009 section 6.4 and 6.5.
3.1.4 Airflow Through the Indoor Coil
Airflow setting(s) shall be determined before testing begins.
Unless otherwise specified within this or its subsections, no
changes shall be made to the airflow setting(s) after initiation of
testing.
3.1.4.1 Cooling Full-Load Air Volume Rate
3.1.4.1.1. Cooling Full-Load Air Volume Rate for Ducted Units
Identify the certified cooling full-load air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified Cooling full-load air volume rate, use a value equal
to the certified cooling capacity of the unit times 400 scfm per
12,000 Btu/h. If there are no instructions for setting fan speed or
controls, use the as-shipped settings. Use the following procedure
to confirm and, if necessary, adjust the Cooling full-load air
volume rate and the fan speed or control settings to meet each test
procedure requirement:
a. For all ducted blower coil systems, except those having a
constant-air-volume-rate indoor blower:
[[Page 1489]]
Step (1) Operate the unit under conditions specified for the A
(for single-stage units) or A2 test using the certified
fan speed or controls settings, and adjust the exhaust fan of the
airflow measuring apparatus to achieve the certified Cooling full-
load air volume rate;
Step (2) Measure the external static pressure;
Step (3) If this external static pressure is equal to or greater
than the applicable minimum external static pressure cited in Table
4, the pressure requirement is satisfied; proceed to step 7 of this
section. If this external static pressure is not equal to or greater
than the applicable minimum external static pressure cited in Table
4, proceed to step 4 of this section;
Step (4) Increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until either
(i) The applicable Table 4 minimum is equaled or
(ii) The measured air volume rate equals 90 percent or less of
the Cooling full-load air volume rate, whichever occurs first;
Step (5) If the conditions of step 4 (i) of this section occur
first, the pressure requirement is satisfied; proceed to step 7 of
this section. If the conditions of step 4 (ii) of this section occur
first, proceed to step 6 of this section;
Step (6) Make an incremental change to the setup of the indoor
blower (e.g., next highest fan motor pin setting, next highest fan
motor speed) and repeat the evaluation process beginning above, at
step 1 of this section. If the indoor blower setup cannot be further
changed, increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until the applicable
Table 4 minimum is equaled; proceed to step 7 of this section;
Step (7) The airflow constraints have been satisfied. Use the
measured air volume rate as the Cooling full-load air volume rate.
Use the final fan speed or control settings for all tests that use
the Cooling full-load air volume rate.
b. For ducted blower coil systems with a constant-air-volume-
rate indoor blower. For all tests that specify the Cooling full-load
air volume rate, obtain an external static pressure as close to (but
not less than) the applicable Table 4 value that does not cause
automatic shutdown of the indoor blower or air volume rate variation
QVar, defined as follows, greater than 10 percent.
[GRAPHIC] [TIFF OMITTED] TR05JA17.008
where:
Qmax = maximum measured airflow value
Qmin = minimum measured airflow value
QVar = airflow variance, percent
Additional test steps as described in section 3.3.(e) of this
appendix are required if the measured external static pressure exceeds
the target value by more than 0.03 inches of water.
c. For coil-only indoor units. For the A or A2 Test,
(exclusively), the pressure drop across the indoor coil assembly must
not exceed 0.30 inches of water. If this pressure drop is exceeded,
reduce the air volume rate until the measured pressure drop equals the
specified maximum. Use this reduced air volume rate for all tests that
require the Cooling full-load air volume rate.
Table 4--Minimum External Static Pressure for Ducted Blower Coil Systems
------------------------------------------------------------------------
Minimum external resistance
\3\ (Inches of water)
-------------------------------
Rated Cooling \1\ or Heating \2\ Small-duct,
Capacity (Btu/h) high-velocity All other
systems \4\ systems
\5\
------------------------------------------------------------------------
Up Thru 28,800.......................... 1.10 0.10
29,000 to 42,500........................ 1.15 0.15
43,000 and Above........................ 1.20 0.20
------------------------------------------------------------------------
\1\ For air conditioners and air-conditioning heat pumps, the value
certified by the manufacturer for the unit's cooling capacity when
operated at the A or A2 Test conditions.
\2\ For heating-only heat pumps, the value certified by the manufacturer
for the unit's heating capacity when operated at the H1 or H12 Test
conditions.
\3\ For ducted units tested without an air filter installed, increase
the applicable tabular value by 0.08 inches of water.
\4\ See section 1.2 of this appendix, Definitions, to determine if the
equipment qualifies as a small-duct, high-velocity system.
\5\ If a closed-loop, air-enthalpy test apparatus is used on the indoor
side, limit the resistance to airflow on the inlet side of the blower
coil indoor unit to a maximum value of 0.1 inch of water. Impose the
balance of the airflow resistance on the outlet side of the indoor
blower.
d. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the full-load air volume rate with all
indoor blowers operating unless prevented by the controls of the unit.
In such cases, turn on the maximum number of indoor blowers permitted
by the unit's controls. Where more than one option exists for meeting
this ``on'' indoor blower requirement, which indoor blower(s) are
turned on must match that specified in the certification report.
Conduct section 3.1.4.1.1 setup steps for each indoor blower
separately. If two or more indoor blowers are connected to a common
duct as per section 2.4.1 of this appendix, temporarily divert their
air volume to the test room when confirming or adjusting the setup
configuration of individual indoor blowers. The allocation of the
system's full-load air volume rate assigned to each ``on'' indoor
blower must match that specified by the manufacturer in the
certification report.
3.1.4.1.2. Cooling Full-Load Air Volume Rate for Non-Ducted Units
For non-ducted units, the Cooling full-load air volume rate is the
air volume rate that results during each test when the unit is operated
at an external static pressure of zero inches of water.
3.1.4.2 Cooling Minimum Air Volume Rate
Identify the certified cooling minimum air volume rate and
certified instructions for setting fan speed or controls. If there is
no certified cooling minimum air volume rate, use the final indoor
blower control settings as determined when setting the cooling full-
load air volume rate, and readjust the exhaust fan of the airflow
measuring apparatus if necessary to reset to the cooling full load air
volume obtained in section 3.1.4.1 of this appendix. Otherwise,
calculate the target external static pressure and follow instructions
a, b, c, d, or e below. The target external static pressure,
[Delta]Pst_i, for any test ``i'' with a specified air volume
rate not equal to the Cooling full-load air volume rate is determined
as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.009
where:
[Delta]Pst_i = target minimum external static pressure
for test i;
[Delta]Pst_full = minimum external static pressure for
test A or A2 (Table 4);
Qi = air volume rate for test i; and
[[Page 1490]]
Qfull = Cooling full-load air volume rate as measured
after setting and/or adjustment as described in section 3.1.4.1.1 of
this appendix.
a. For a ducted blower coil system without a constant-air-volume
indoor blower, adjust for external static pressure as follows:
Step (1) Operate the unit under conditions specified for the B1
test using the certified fan speed or controls settings, and adjust
the exhaust fan of the airflow measuring apparatus to achieve the
certified cooling minimum air volume rate;
Step (2) Measure the external static pressure;
Step (3) If this pressure is equal to or greater than the
minimum external static pressure computed above, the pressure
requirement is satisfied; proceed to step 7 of this section. If this
pressure is not equal to or greater than the minimum external static
pressure computed above, proceed to step 4 of this section;
Step (4) Increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until either
(i) The pressure is equal to the minimum external static
pressure computed above or
(ii) The measured air volume rate equals 90 percent or less of
the cooling minimum air volume rate, whichever occurs first;
Step (5) If the conditions of step 4 (i) of this section occur
first, the pressure requirement is satisfied; proceed to step 7 of
this section. If the conditions of step 4 (ii) of this section occur
first, proceed to step 6 of this section;
Step (6) Make an incremental change to the setup of the indoor
blower (e.g., next highest fan motor pin setting, next highest fan
motor speed) and repeat the evaluation process beginning above, at
step 1 of this section. If the indoor blower setup cannot be further
changed, increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until it equals the
minimum external static pressure computed above; proceed to step 7
of this section;
Step (7) The airflow constraints have been satisfied. Use the
measured air volume rate as the cooling minimum air volume rate. Use
the final fan speed or control settings for all tests that use the
cooling minimum air volume rate.
b. For ducted units with constant-air-volume indoor blowers,
conduct all tests that specify the cooling minimum air volume rate--
(i.e., the A1, B1, C1,
F1, and G1 Tests)--at an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b of this appendix, greater than 10 percent, while
being as close to, but not less than the target minimum external
static pressure. Additional test steps as described in section
3.3(e) of this appendix are required if the measured external static
pressure exceeds the target value by more than 0.03 inches of water.
c. For ducted two-capacity coil-only systems, the cooling
minimum air volume rate is the higher of (1) the rate specified by
the installation instructions included with the unit by the
manufacturer or (2) 75 percent of the cooling full-load air volume
rate. During the laboratory tests on a coil-only (fanless) system,
obtain this cooling minimum air volume rate regardless of the
pressure drop across the indoor coil assembly.
d. For non-ducted units, the cooling minimum air volume rate is
the air volume rate that results during each test when the unit
operates at an external static pressure of zero inches of water and
at the indoor blower setting used at low compressor capacity (two-
capacity system) or minimum compressor speed (variable-speed
system). For units having a single-speed compressor and a variable-
speed variable-air-volume-rate indoor blower, use the lowest fan
setting allowed for cooling.
e. For ducted systems having multiple indoor blowers within a
single indoor section, operate the indoor blowers such that the
lowest air volume rate allowed by the unit's controls is obtained
when operating the lone single-speed compressor or when operating at
low compressor capacity while meeting the requirements of section
2.2.3.b of this appendix for the minimum number of blowers that must
be turned off. Using the target external static pressure and the
certified air volume rates, follow the procedures described in
section 3.1.4.2.a of this appendix if the indoor blowers are not
constant-air-volume indoor blowers or as described in section
3.1.4.2.b of this appendix if the indoor blowers are constant-air-
volume indoor blowers. The sum of the individual ``on'' indoor
blowers' air volume rates is the cooling minimum air volume rate for
the system.
3.1.4.3 Cooling Intermediate Air Volume Rate
Identify the certified cooling intermediate air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified cooling intermediate air volume rate, use the final
indoor blower control settings as determined when setting the
cooling full load air volume rate, and readjust the exhaust fan of
the airflow measuring apparatus if necessary to reset to the cooling
full load air volume obtained in section 3.1.4.1 of this appendix.
Otherwise, calculate target minimum external static pressure as
described in section 3.1.4.2 of this appendix, and set the air
volume rate as follows.
a. For a ducted blower coil system without a constant-air-volume
indoor blower, adjust for external static pressure as described in
section 3.1.4.2.a of this appendix for cooling minimum air volume
rate.
b. For a ducted blower coil system with a constant-air-volume
indoor blower, conduct the EV Test at an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b of this appendix, greater than 10 percent, while
being as close to, but not less than the target minimum external
static pressure. Additional test steps as described in section
3.3(e) of this appendix are required if the measured external static
pressure exceeds the target value by more than 0.03 inches of water.
c. For non-ducted units, the cooling intermediate air volume
rate is the air volume rate that results when the unit operates at
an external static pressure of zero inches of water and at the fan
speed selected by the controls of the unit for the EV
Test conditions.
3.1.4.4 Heating Full-Load Air Volume Rate
3.1.4.4.1. Ducted Heat Pumps Where the Heating and Cooling Full-Load
Air Volume Rates Are the Same
a. Use the Cooling full-load air volume rate as the heating
full-load air volume rate for:
(1) Ducted blower coil system heat pumps that do not have a
constant-air-volume indoor blower, and that operate at the same
airflow-control setting during both the A (or A2) and the
H1 (or H12) Tests;
(2) Ducted blower coil system heat pumps with constant-air-flow
indoor blowers that provide the same air flow for the A (or
A2) and the H1 (or H12) Tests; and
(3) Ducted heat pumps that are tested with a coil-only indoor
unit (except two-capacity northern heat pumps that are tested only
at low capacity cooling--see section 3.1.4.4.2 of this appendix).
b. For heat pumps that meet the above criteria ``1'' and ``3,''
no minimum requirements apply to the measured external or internal,
respectively, static pressure. Use the final indoor blower control
settings as determined when setting the Cooling full-load air volume
rate, and readjust the exhaust fan of the airflow measuring
apparatus if necessary to reset to the cooling full-load air volume
obtained in section 3.1.4.1 of this appendix. For heat pumps that
meet the above criterion ``2,'' test at an external static pressure
that does not cause an automatic shutdown of the indoor blower or
air volume rate variation QVar, defined in section
3.1.4.1.1.b of this appendix, greater than 10 percent, while being
as close to, but not less than, the same Table 4 minimum external
static pressure as was specified for the A (or A2)
cooling mode test. Additional test steps as described in section
3.9.1(c) of this appendix are required if the measured external
static pressure exceeds the target value by more than 0.03 inches of
water.
3.1.4.4.2. Ducted Heat Pumps Where the Heating and Cooling Full-Load
Air Volume Rates Are Different Due to Changes in Indoor Blower
Operation, i.e. Speed Adjustment by the System Controls
Identify the certified heating full-load air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified heating full-load air volume rate, use the final
indoor blower control settings as determined when setting the
cooling full-load air volume rate, and readjust the exhaust fan of
the airflow measuring apparatus if necessary to reset to the cooling
full load air volume obtained in section 3.1.4.1 of this appendix.
Otherwise, calculate target minimum external static pressure as
described in section 3.1.4.2 of this appendix and set the air volume
rate as follows.
a. For ducted blower coil system heat pumps that do not have a
constant-air-volume indoor blower, adjust for external static
pressure as described in section 3.1.4.2.a of this appendix for
cooling minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct all tests that specify the heating full-
[[Page 1491]]
load air volume rate at an external static pressure that does not
cause an automatic shutdown of the indoor blower or air volume rate
variation QVar, defined in section 3.1.4.1.1.b of this
appendix, greater than 10 percent, while being as close to, but not
less than the target minimum external static pressure. Additional
test steps as described in section 3.9.1(c) of this appendix are
required if the measured external static pressure exceeds the target
value by more than 0.03 inches of water.
c. When testing ducted, two-capacity blower coil system northern
heat pumps (see section 1.2 of this appendix, Definitions), use the
appropriate approach of the above two cases. For coil-only system
northern heat pumps, the heating full-load air volume rate is the
lesser of the rate specified by the manufacturer in the installation
instructions included with the unit or 133 percent of the cooling
full-load air volume rate. For this latter case, obtain the heating
full-load air volume rate regardless of the pressure drop across the
indoor coil assembly.
d. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the heating full-load air volume rate
using the same ``on'' indoor blowers as used for the Cooling full-
load air volume rate. Using the target external static pressure and
the certified air volume rates, follow the procedures as described
in section 3.1.4.4.2.a of this appendix if the indoor blowers are
not constant-air-volume indoor blowers or as described in section
3.1.4.4.2.b of this appendix if the indoor blowers are constant-air-
volume indoor blowers. The sum of the individual ``on'' indoor
blowers' air volume rates is the heating full load air volume rate
for the system.
3.1.4.4.3. Ducted Heating-Only Heat Pumps
Identify the certified heating full-load air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified heating full-load air volume rate, use a value equal
to the certified heating capacity of the unit times 400 scfm per
12,000 Btu/h. If there are no instructions for setting fan speed or
controls, use the as-shipped settings.
a. For all ducted heating-only blower coil system heat pumps,
except those having a constant-air-volume-rate indoor blower.
Conduct the following steps only during the first test, the H1 or
H12 Test:
Step (1) Adjust the exhaust fan of the airflow measuring
apparatus to achieve the certified heating full-load air volume
rate.
Step (2) Measure the external static pressure.
Step (3) If this pressure is equal to or greater than the Table
4 minimum external static pressure that applies given the heating-
only heat pump's rated heating capacity, the pressure requirement is
satisfied; proceed to step 7 of this section. If this pressure is
not equal to or greater than the applicable Table 4 minimum external
static pressure, proceed to step 4 of this section;
Step (4) Increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until either (i) the
pressure is equal to the applicable Table 4 minimum external static
pressure or (ii) the measured air volume rate equals 90 percent or
less of the heating full-load air volume rate, whichever occurs
first;
Step (5) If the conditions of step 4(i) of this section occur
first, the pressure requirement is satisfied; proceed to step 7 of
this section. If the conditions of step 4(ii) of this section occur
first, proceed to step 6 of this section;
Step (6) Make an incremental change to the setup of the indoor
blower (e.g., next highest fan motor pin setting, next highest fan
motor speed) and repeat the evaluation process beginning above, at
step 1 of this section. If the indoor blower setup cannot be further
changed, increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until it equals the
applicable Table 4 minimum external static pressure; proceed to step
7 of this section;
Step (7) The airflow constraints have been satisfied. Use the
measured air volume rate as the heating full-load air volume rate.
Use the final fan speed or control settings for all tests that use
the heating full-load air volume rate.
b. For ducted heating-only blower coil system heat pumps having
a constant-air-volume-rate indoor blower. For all tests that specify
the heating full-load air volume rate, obtain an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b of this appendix, greater than 10 percent, while
being as close to, but not less than, the applicable Table 4
minimum. Additional test steps as described in section 3.9.1(c) of
this appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For ducted heating-only coil-only system heat pumps in the H1
or H12 Test, (exclusively), the pressure drop across the
indoor coil assembly must not exceed 0.30 inches of water. If this
pressure drop is exceeded, reduce the air volume rate until the
measured pressure drop equals the specified maximum. Use this
reduced air volume rate for all tests that require the heating full-
load air volume rate.
3.1.4.4.4. Non-Ducted Heat Pumps, Including Non-Ducted Heating-Only
Heat Pumps
For non-ducted heat pumps, the heating full-load air volume rate
is the air volume rate that results during each test when the unit
operates at an external static pressure of zero inches of water.
3.1.4.5 Heating Minimum Air Volume Rate
3.1.4.5.1. Ducted Heat Pumps Where the Heating and Cooling Minimum Air
Volume Rates Are the Same
a. Use the cooling minimum air volume rate as the heating
minimum air volume rate for:
(1) Ducted blower coil system heat pumps that do not have a
constant-air-volume indoor blower, and that operate at the same
airflow-control setting during both the A1 and the
H11 tests;
(2) Ducted blower coil system heat pumps with constant-air-flow
indoor blowers installed that provide the same air flow for the
A1 and the H11 Tests; and
(3) Ducted coil-only system heat pumps.
b. For heat pumps that meet the above criteria ``1'' and ``3,''
no minimum requirements apply to the measured external or internal,
respectively, static pressure. Use the final indoor blower control
settings as determined when setting the cooling minimum air volume
rate, and readjust the exhaust fan of the airflow measuring
apparatus if necessary to reset to the cooling minimum air volume
rate obtained in section 3.1.4.2 of this appendix. For heat pumps
that meet the above criterion ``2,'' test at an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b of this appendix, greater than 10 percent, while
being as close to, but not less than, the same target minimum
external static pressure as was specified for the A1
cooling mode test. Additional test steps as described in section
3.9.1(c) of this appendix are required if the measured external
static pressure exceeds the target value by more than 0.03 inches of
water.
3.1.4.5.2. Ducted Heat Pumps Where the Heating and Cooling Minimum Air
Volume Rates Are Different Due to Changes in Indoor Blower Operation,
i.e. Speed Adjustment by the System Controls
Identify the certified heating minimum air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified heating minimum air volume rate, use the final
indoor blower control settings as determined when setting the
cooling minimum air volume rate, and readjust the exhaust fan of the
airflow measuring apparatus if necessary to reset to the cooling
minimum air volume obtained in section 3.1.4.2 of this appendix.
Otherwise, calculate the target minimum external static pressure as
described in section 3.1.4.2 of this appendix.
a. For ducted blower coil system heat pumps that do not have a
constant-air-volume indoor blower, adjust for external static
pressure as described in section 3.1.4.2.a of this appendix for
cooling minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct all tests that specify the heating
minimum air volume rate--(i.e., the H01, H11,
H21, and H31 Tests)--at an external static
pressure that does not cause an automatic shutdown of the indoor
blower while being as close to, but not less than the air volume
rate variation QVar, defined in section 3.1.4.1.1.b of
this appendix, greater than 10 percent, while being as close to, but
not less than the target minimum external static pressure.
Additional test steps as described in section 3.9.1.c of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For ducted two-capacity blower coil system northern heat
pumps, use the appropriate approach of the above two cases.
d. For ducted two-capacity coil-only system heat pumps, use the
cooling minimum air volume rate as the heating minimum air volume
rate. For ducted two-capacity coil-only system northern heat pumps,
use the cooling full-load air volume rate as the heating minimum air
volume rate.
[[Page 1492]]
For ducted two-capacity heating-only coil-only system heat pumps,
the heating minimum air volume rate is the higher of the rate
specified by the manufacturer in the test setup instructions
included with the unit or 75 percent of the heating full-load air
volume rate. During the laboratory tests on a coil-only system,
obtain the heating minimum air volume rate without regard to the
pressure drop across the indoor coil assembly.
e. For non-ducted heat pumps, the heating minimum air volume
rate is the air volume rate that results during each test when the
unit operates at an external static pressure of zero inches of water
and at the indoor blower setting used at low compressor capacity
(two-capacity system) or minimum compressor speed (variable-speed
system). For units having a single-speed compressor and a variable-
speed, variable-air-volume-rate indoor blower, use the lowest fan
setting allowed for heating.
f. For ducted systems with multiple indoor blowers within a
single indoor section, obtain the heating minimum air volume rate
using the same ``on'' indoor blowers as used for the cooling minimum
air volume rate. Using the target external static pressure and the
certified air volume rates, follow the procedures as described in
section 3.1.4.5.2.a of this appendix if the indoor blowers are not
constant-air-volume indoor blowers or as described in section
3.1.4.5.2.b of this appendix if the indoor blowers are constant-air-
volume indoor blowers. The sum of the individual ``on'' indoor
blowers' air volume rates is the heating full-load air volume rate
for the system.
3.1.4.6 Heating Intermediate Air Volume Rate
Identify the certified heating intermediate air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified heating intermediate air volume rate, use the final
indoor blower control settings as determined when setting the
heating full-load air volume rate, and readjust the exhaust fan of
the airflow measuring apparatus if necessary to reset to the cooling
full load air volume obtained in section 3.1.4.2 of this appendix.
Calculate the target minimum external static pressure as described
in section 3.1.4.2 of this appendix.
a. For ducted blower coil system heat pumps that do not have a
constant-air-volume indoor blower, adjust for external static
pressure as described in section 3.1.4.2.a of this appendix for
cooling minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct the H2V Test at an external
static pressure that does not cause an automatic shutdown of the
indoor blower or air volume rate variation QVar, defined
in section 3.1.4.1.1.b of this appendix, greater than 10 percent,
while being as close to, but not less than the target minimum
external static pressure. Additional test steps as described in
section 3.9.1(c) of this appendix are required if the measured
external static pressure exceeds the target value by more than 0.03
inches of water.
c. For non-ducted heat pumps, the heating intermediate air
volume rate is the air volume rate that results when the heat pump
operates at an external static pressure of zero inches of water and
at the fan speed selected by the controls of the unit for the
H2V Test conditions.
3.1.4.7 Heating Nominal Air Volume Rate
The manufacturer must specify the heating nominal air volume
rate and the instructions for setting fan speed or controls.
Calculate target minimum external static pressure as described in
section 3.1.4.2 of this appendix. Make adjustments as described in
section 3.1.4.6 of this appendix for heating intermediate air volume
rate so that the target minimum external static pressure is met or
exceeded.
3.1.5 Indoor Test Room Requirement When the Air Surrounding the Indoor
Unit Is Not Supplied From the Same Source as the Air Entering the
Indoor Unit
If using a test set-up where air is ducted directly from the air
reconditioning apparatus to the indoor coil inlet (see Figure 2,
Loop Air-Enthalpy Test Method Arrangement, of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3)), maintain the dry bulb
temperature within the test room within 5.0[emsp14][deg]F of the applicable sections 3.2 and 3.6 dry
bulb temperature test condition for the air entering the indoor
unit. Dew point shall be within 2[emsp14][deg]F of the required
inlet conditions.
3.1.6 Air Volume Rate Calculations
For all steady-state tests and for frost accumulation (H2,
H21, H22, H2V) tests, calculate the
air volume rate through the indoor coil as specified in sections
7.7.2.1 and 7.7.2.2 of ANSI/ASHRAE 37-2009. When using the outdoor
air enthalpy method, follow sections 7.7.2.1 and 7.7.2.2 of ANSI/
ASHRAE 37-2009 to calculate the air volume rate through the outdoor
coil. To express air volume rates in terms of standard air, use:
[GRAPHIC] [TIFF OMITTED] TR05JA17.010
Where:
Vis = air volume rate of standard (dry) air, (ft\3\/
min)da
Vimx = air volume rate of the air-water vapor mixture,
(ft\3\/min)mx
vn' = specific volume of air-water vapor mixture at the
nozzle, ft\3\ per lbm of the air-water vapor mixture
Wn = humidity ratio at the nozzle, lbm of water vapor per
lbm of dry air
0.075 = the density associated with standard (dry) air, (lbm/ft\3\)
vn = specific volume of the dry air portion of the
mixture evaluated at the dry-bulb temperature, vapor content, and
barometric pressure existing at the nozzle, ft\3\ per lbm of dry
air.
Note: In the first printing of ANSI/ASHRAE 37-2009, the second
IP equation for Qmi should read
[GRAPHIC] [TIFF OMITTED] TR05JA17.011
3.1.7 Test Sequence
Before making test measurements used to calculate performance,
operate the equipment for the ``break-in'' period specified in the
certification report, which may not exceed 20 hours. Each compressor
of the unit must undergo this ``break-in'' period. When testing a
ducted unit (except if a heating-only heat pump), conduct the A or
A2 Test first to establish the cooling full-load air
volume rate. For ducted heat pumps where the heating and cooling
full-load air volume rates are different, make the first heating
mode test one that requires the heating full-load air volume rate.
For ducted heating-only heat pumps, conduct the H1 or H12
Test first to establish the heating full-load air volume rate. When
conducting a cyclic test, always conduct it immediately after the
steady-state test that requires the same test conditions. For
variable-speed systems, the first test using the cooling minimum air
volume rate should precede the EV Test, and the first
test using the heating minimum air volume rate must precede the
H2V Test. The test laboratory makes all other decisions
on the test sequence.
3.1.8 Requirement for the Air Temperature Distribution Leaving the
Indoor Coil
For at least the first cooling mode test and the first heating
mode test, monitor the temperature distribution of the air leaving
the indoor coil using the grid of individual sensors described in
sections 2.5 and 2.5.4 of this appendix. For the 30-minute data
collection interval used to determine capacity, the maximum spread
among the outlet dry bulb temperatures from any data sampling must
not exceed 1.5[emsp14][deg]F. Install the mixing devices described
in section 2.5.4.2 of this appendix to minimize the temperature
spread.
3.1.9 Requirement for the Air Temperature Distribution Entering the
Outdoor Coil
Monitor the temperatures of the air entering the outdoor coil
using air sampling devices and/or temperature sensor grids,
maintaining the required tolerances, if applicable, as described in
section 2.11 of this appendix.
[[Page 1493]]
3.1.10 Control of Auxiliary Resistive Heating Elements
Except as noted, disable heat pump resistance elements used for
heating indoor air at all times, including during defrost cycles and
if they are normally regulated by a heat comfort controller. For
heat pumps equipped with a heat comfort controller, enable the heat
pump resistance elements only during the below-described, short
test. For single-speed heat pumps covered under section 3.6.1 of
this appendix, the short test follows the H1 or, if conducted, the
H1C Test. For two-capacity heat pumps and heat pumps covered under
section 3.6.2 of this appendix, the short test follows the
H12 Test. Set the heat comfort controller to provide the
maximum supply air temperature. With the heat pump operating and
while maintaining the heating full-load air volume rate, measure the
temperature of the air leaving the indoor-side beginning 5 minutes
after activating the heat comfort controller. Sample the outlet dry-
bulb temperature at regular intervals that span 5 minutes or less.
Collect data for 10 minutes, obtaining at least 3 samples. Calculate
the average outlet temperature over the 10-minute interval,
TCC.
3.2 Cooling Mode Tests for Different Types of Air Conditioners and
Heat Pumps
3.2.1 Tests for a System Having a Single-Speed Compressor and Fixed
Cooling Air Volume Rate
This set of tests is for single-speed-compressor units that do
not have a cooling minimum air volume rate or a cooling intermediate
air volume rate that is different than the cooling full load air
volume rate. Conduct two steady-state wet coil tests, the A and B
Tests. Use the two optional dry-coil tests, the steady-state C Test
and the cyclic D Test, to determine the cooling mode cyclic
degradation coefficient, CD\c\. If the two optional tests
are conducted but yield a tested CD\c\ that exceeds the
default CD\c\ or if the two optional tests are not
conducted, assign CD\c\ the default value of 0.25 (for
outdoor units with no match) or 0.20 (for all other systems). Table
5 specifies test conditions for these four tests.
Table 5--Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed Cooling Air Volume Rate
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A Test--required (steady, wet coil).... 80 67 95 \1\ 75 Cooling full-load.\2\
B Test--required (steady, wet coil).... 80 67 82 \1\ 65 Cooling full-load.\2\
C Test--optional (steady, dry coil).... 80 (\3\) 82 .............. Cooling full-load.\2\
D Test--optional (cyclic, dry coil).... 80 (\3\) 82 .............. (\4\).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1 of this appendix.
\3\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb
temperature of 57 [deg]F or less be used.)
\4\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C Test.
3.2.2 Tests for a Unit Having a Single-Speed Compressor Where the
Indoor Section Uses a Single Variable-Speed Variable-Air-Volume
Rate Indoor Blower or Multiple Indoor Blowers
3.2.2.1 Indoor Blower Capacity Modulation That Correlates With the
Outdoor Dry Bulb Temperature or Systems With a Single Indoor Coil but
Multiple Indoor Blowers
Conduct four steady-state wet coil tests: The A2,
A1, B2, and B1 tests. Use the two
optional dry-coil tests, the steady-state C1 test and the
cyclic D1 test, to determine the cooling mode cyclic
degradation coefficient, CD\c\. If the two optional tests
are conducted but yield a tested CDc that exceeds the
default CDc or if the two optional tests are not
conducted, assign CDc the default value of 0.20.
3.2.2.2 Indoor Blower Capacity Modulation Based on Adjusting the
Sensible to Total (S/T) Cooling Capacity Ratio
The testing requirements are the same as specified in section
3.2.1 of this appendix and Table 5. Use a cooling full-load air
volume rate that represents a normal installation. If performed,
conduct the steady-state C Test and the cyclic D Test with the unit
operating in the same S/T capacity control mode as used for the B
Test.
Table 6--Cooling Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.2.2.1 Indoor Unit Requirements
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet coil)... 80 67 95 \1\ 75 Cooling full-load.\2\
A1 Test--required (steady, wet coil)... 80 67 95 \1\ 75 Cooling minimum.\3\
B2 Test--required (steady, wet coil)... 80 67 82 \1\ 65 Cooling full-load.\2\
B1 Test--required (steady, wet coil)... 80 67 82 \1\ 65 Cooling minimum.\3\
C1 Test \4\--optional (steady, dry 80 (\4\) 82 .............. Cooling minimum.\3\
coil).
D1 Test \4\--optional (cyclic, dry 80 (\4\) 82 .............. (\5\).
coil).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1 of this appendix.
\3\ Defined in section 3.1.4.2 of this appendix.
\4\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb
temperature of 5 [deg]F or less be used.)
\5\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C1 Test.
[[Page 1494]]
3.2.3 Tests for a Unit Having a Two-Capacity Compressor (See Section
1.2 of This Appendix, Definitions)
a. Conduct four steady-state wet coil tests: the A2,
B2, B1, and F1 Tests. Use the two
optional dry-coil tests, the steady-state C1 Test and the
cyclic D1 Test, to determine the cooling-mode cyclic-
degradation coefficient, CD\c\. If the two optional tests
are conducted but yield a tested CDc that exceeds the
default CDc or if the two optional tests are not
conducted, assign CDc the default value of 0.20. Table 6
specifies test conditions for these six tests.
b. For units having a variable speed indoor blower that is
modulated to adjust the sensible to total (S/T) cooling capacity
ratio, use cooling full-load and cooling minimum air volume rates
that represent a normal installation. Additionally, if conducting
the dry-coil tests, operate the unit in the same S/T capacity
control mode as used for the B1 Test.
c. Test two-capacity, northern heat pumps (see section 1.2 of
this appendix, Definitions) in the same way as a single speed heat
pump with the unit operating exclusively at low compressor capacity
(see section 3.2.1 of this appendix and Table 5).
d. If a two-capacity air conditioner or heat pump locks out low-
capacity operation at higher outdoor temperatures, then use the two
dry-coil tests, the steady-state C2 Test and the cyclic
D2 Test, to determine the cooling-mode cyclic-degradation
coefficient that only applies to on/off cycling from high capacity,
CD\c\(k=2). If the two optional tests are conducted but
yield a tested CD\c\ (k = 2) that exceeds the default CD\c\ (k = 2)
or if the two optional tests are not conducted, assign CD\c\ (k = 2)
the default value. The default CD\c\(k=2) is the same
value as determined or assigned for the low-capacity cyclic-
degradation coefficient, CD\c\ [or equivalently,
CD\c\(k=1)].
Table 7--Cooling Mode Test Conditions for Units Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F) Compressor
Test description ------------------------------------------------------------------------ capacity Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet coil). 80 67 95 \1\ 75 High Cooling Full-Load.\2\
B2 Test--required (steady, wet coil). 80 67 82 \1\ 65 High Cooling Full-Load.\2\
B1 Test--required (steady, wet coil). 80 67 82 \1\ 65 Low Cooling Minimum.\3\
C2 Test--optional (steady, dry-coil). 80 (\4\) 82 ................ High Cooling Full-Load.\2\
D2 Test--optional (cyclic, dry-coil). 80 (\4\) 82 ................ High (\5\).
C1 Test--optional (steady, dry-coil). 80 (\4\) 82 ................ Low Cooling Minimum.\3\
D1 Test--optional (cyclic, dry-coil). 80 (\4\) 82 ................ Low (\6\).
F1 Test--required (steady, wet coil). 80 67 67 \1\ 53.5 Low Cooling Minimum.\3\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1 of this appendix.
\3\ Defined in section 3.1.4.2 of this appendix.
\4\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet-bulb
temperature of 57 [deg]F or less.
\5\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the C2 Test.
\6\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the C1 Test.
3.2.4 Tests for a Unit Having a Variable-Speed Compressor
a. Conduct five steady-state wet coil tests: The A2,
EV, B2, B1, and F1
Tests. Use the two optional dry-coil tests, the steady-state
G1 Test and the cyclic I1 Test, to determine
the cooling mode cyclic degradation coefficient, CD\c\.
If the two optional tests are conducted but yield a tested
CDc that exceeds the default CDc or if the two
optional tests are not conducted, assign CDc the default
value of 0.25. Table 8 specifies test conditions for these seven
tests. The compressor shall operate at the same cooling full speed,
measured by RPM or power input frequency (Hz), for both the
A2 and B2 tests. The compressor shall operate
at the same cooling minimum speed, measured by RPM or power input
frequency (Hz), for the B1, F1, G1,
and I1 tests. Determine the cooling intermediate
compressor speed cited in Table 8 using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.012
where a tolerance of plus 5 percent or the next higher inverter
frequency step from that calculated is allowed.
b. For units that modulate the indoor blower speed to adjust the
sensible to total (S/T) cooling capacity ratio, use cooling full-
load, cooling intermediate, and cooling minimum air volume rates
that represent a normal installation. Additionally, if conducting
the dry-coil tests, operate the unit in the same S/T capacity
control mode as used for the F1 Test.
c. For multiple-split air conditioners and heat pumps (except
where noted), the following procedures supersede the above
requirements: For all Table 8 tests specified for a minimum
compressor speed, at least one indoor unit must be turned off. The
manufacturer shall designate the particular indoor unit(s) that is
turned off. The manufacturer must also specify the compressor speed
used for the Table 8 EV Test, a cooling-mode intermediate
compressor speed that falls within \1/4\ and \3/4\ of the difference
between the full and minimum cooling-mode speeds. The manufacturer
should prescribe an intermediate speed that is expected to yield the
highest EER for the given EV Test conditions and
bracketed compressor speed range. The manufacturer can designate
that
[[Page 1495]]
one or more indoor units are turned off for the EV Test.
Table 8--Cooling Mode Test Condition for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description -------------------------------------------------------- Compressor speed Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet coil).... 80 67 95 \1\ 75 Cooling Full.............. Cooling Full-Load.\2\
B2 Test--required (steady, wet coil).... 80 67 82 \1\ 65 Cooling Full.............. Cooling Full-Load.\2\
EV Test--required (steady, wet coil).... 80 67 87 \1\ 69 Cooling Intermediate...... Cooling Intermediate.\3\
B1 Test--required (steady, wet coil).... 80 67 82 \1\ 65 Cooling Minimum........... Cooling Minimum.\4\
F1 Test--required (steady, wet coil).... 80 67 67 \1\ 53.5 Cooling Minimum........... Cooling Minimum.\4\
G1 Test \5\--optional (steady, dry-coil) 80 (\6\) 67 ............ Cooling Minimum........... Cooling Minimum.\4\
I1 Test \5\--optional (cyclic, dry-coil) 80 (\6\) 67 ............ Cooling Minimum........... (\6\).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1 of this appendix.
\3\ Defined in section 3.1.4.3 of this appendix.
\4\ Defined in section 3.1.4.2 of this appendix.
\5\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet bulb
temperature of 57 [deg]F or less.
\6\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the G1 Test.
3.2.5 Cooling Mode Tests for Northern Heat Pumps With Triple-Capacity
Compressors
Test triple-capacity, northern heat pumps for the cooling mode
in the same way as specified in section 3.2.3 of this appendix for
units having a two-capacity compressor.
3.2.6 Tests for an Air Conditioner or Heat Pump Having a Single Indoor
Unit Having Multiple Indoor Blowers and Offering Two Stages of
Compressor Modulation
Conduct the cooling mode tests specified in section 3.2.3 of
this appendix.
3.3 Test Procedures for Steady-State Wet Coil Cooling Mode Tests
(the A, A2, A1, B, B2, B1, EV, and F1 Tests)
a. For the pretest interval, operate the test room
reconditioning apparatus and the unit to be tested until maintaining
equilibrium conditions for at least 30 minutes at the specified
section 3.2 test conditions. Use the exhaust fan of the airflow
measuring apparatus and, if installed, the indoor blower of the test
unit to obtain and then maintain the indoor air volume rate and/or
external static pressure specified for the particular test.
Continuously record (see section 1.2 of this appendix, Definitions):
(1) The dry-bulb temperature of the air entering the indoor
coil,
(2) The water vapor content of the air entering the indoor coil,
(3) The dry-bulb temperature of the air entering the outdoor
coil, and
(4) For the section 2.2.4 of this appendix cases where its
control is required, the water vapor content of the air entering the
outdoor coil.
Refer to section 3.11 of this appendix for additional
requirements that depend on the selected secondary test method.
b. After satisfying the pretest equilibrium requirements, make
the measurements specified in Table 3 of ANSI/ASHRAE 37-2009 for the
indoor air enthalpy method and the user-selected secondary method.
Make said Table 3 measurements at equal intervals that span 5
minutes or less. Continue data sampling until reaching a 30-minute
period (e.g., seven consecutive 5-minute samples) where the test
tolerances specified in Table 9 are satisfied. For those
continuously recorded parameters, use the entire data set from the
30-minute interval to evaluate Table 9 compliance. Determine the
average electrical power consumption of the air conditioner or heat
pump over the same 30-minute interval.
c. Calculate indoor-side total cooling capacity and sensible
cooling capacity as specified in sections 7.3.3.1 and 7.3.3.3 of
ANSI/ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3). To
calculate capacity, use the averages of the measurements (e.g. inlet
and outlet dry bulb and wet bulb temperatures measured at the
psychrometers) that are continuously recorded for the same 30-minute
interval used as described above to evaluate compliance with test
tolerances. Do not adjust the parameters used in calculating
capacity for the permitted variations in test conditions. Evaluate
air enthalpies based on the measured barometric pressure. Use the
values of the specific heat of air given in section 7.3.3.1 of ANSI/
ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3) for
calculation of the sensible cooling capacities. Assign the average
total space cooling capacity, average sensible cooling capacity, and
electrical power consumption over the 30-minute data collection
interval to the variables Qc\k\(T), Qsc\k\(T)
and Ec\k\(T), respectively. For these three variables,
replace the ``T'' with the nominal outdoor temperature at which the
test was conducted. The superscript k is used only when testing
multi-capacity units.
Use the superscript k=2 to denote a test with the unit operating
at high capacity or full speed, k=1 to denote low capacity or
minimum speed, and k=v to denote the intermediate speed.
d. For coil-only system tests, decrease Qc\k\(T) by
[GRAPHIC] [TIFF OMITTED] TR05JA17.013
and increase Ec\k\(T) by,
[GRAPHIC] [TIFF OMITTED] TR05JA17.014
where VIs is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
[[Page 1496]]
Table 9--Test Operating and Test Condition Tolerances for Section 3.3
Steady-State Wet Coil Cooling Mode Tests and Section 3.4 Dry Coil
Cooling Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor dry-bulb, [deg]F
Entering temperature.......... 2.0 0.5
Leaving temperature........... 2.0 .................
Indoor wet-bulb, [deg]F
Entering temperature.......... 1.0 \2\ 0.3
Leaving temperature........... \2\ 1.0 .................
Outdoor dry-bulb, [deg]F
Entering temperature.......... 2.0 0.5
Leaving temperature........... \3\ 2.0 .................
Outdoor wet-bulb, [deg]F
Entering temperature.......... 1.0 \4\ 0.3
Leaving temperature........... \3\ 1.0 .................
External resistance to airflow, 0.05 \5\ 0.02
inches of water..................
Electrical voltage, % of rdg...... 2.0 1.5
Nozzle pressure drop, % of rdg.... 2.0 .................
------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
\2\ Only applies during wet coil tests; does not apply during steady-
state, dry coil cooling mode tests.
\3\ Only applies when using the outdoor air enthalpy method.
\4\ Only applies during wet coil cooling mode tests where the unit
rejects condensate to the outdoor coil.
\5\ Only applies when testing non-ducted units.
e. For air conditioners and heat pumps having a constant-air-
volume-rate indoor blower, the five additional steps listed below
are required if the average of the measured external static
pressures exceeds the applicable sections 3.1.4 minimum (or target)
external static pressure ([Delta]Pmin) by 0.03 inches of
water or more.
(1) Measure the average power consumption of the indoor blower
motor (Efan,1) and record the corresponding external
static pressure ([Delta]P1) during or immediately
following the 30-minute interval used for determining capacity.
(2) After completing the 30-minute interval and while
maintaining the same test conditions, adjust the exhaust fan of the
airflow measuring apparatus until the external static pressure
increases to approximately [Delta]P1 +
([Delta]P1-[Delta]Pmin).
(3) After re-establishing steady readings of the fan motor power
and external static pressure, determine average values for the
indoor blower power (Efan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
(4) Approximate the average power consumption of the indoor
blower motor at [Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TR05JA17.015
(5) Increase the total space cooling capacity,
Qc\k\(T), by the quantity (Efan,1-
Efan,min), when expressed on a Btu/h basis. Decrease the
total electrical power, Ec\k\(T), by the same fan power
difference, now expressed in watts.
3.4 Test Procedures for the Steady-State Dry-Coil Cooling-Mode
Tests (the C, C1, C2, and G1 Tests)
a. Except for the modifications noted in this section, conduct
the steady-state dry coil cooling mode tests as specified in section
3.3 of this appendix for wet coil tests. Prior to recording data
during the steady-state dry coil test, operate the unit at least one
hour after achieving dry coil conditions. Drain the drain pan and
plug the drain opening. Thereafter, the drain pan should remain
completely dry.
b. Denote the resulting total space cooling capacity and
electrical power derived from the test as Qss,dry and
Ess,dry. With regard to a section 3.3 deviation, do not
adjust Qss,dry for duct losses (i.e., do not apply
section 7.3.3.3 of ANSI/ASHRAE 37-2009). In preparing for the
section 3.5 cyclic tests of this appendix, record the average
indoor-side air volume rate, VI, specific heat of the air, Cp,a
(expressed on dry air basis), specific volume of the air at the
nozzles, v'n, humidity ratio at the nozzles,
Wn, and either pressure difference or velocity pressure
for the flow nozzles. For units having a variable-speed indoor
blower (that provides either a constant or variable air volume rate)
that will or may be tested during the cyclic dry coil cooling mode
test with the indoor blower turned off (see section 3.5 of this
appendix), include the electrical power used by the indoor blower
motor among the recorded parameters from the 30-minute test.
c. If the temperature sensors used to provide the primary
measurement of the indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the subsequent cyclic dry-
coil test are different, include measurements of the latter sensors
among the regularly sampled data. Beginning at the start of the 30-
minute data collection period, measure and compute the indoor-side
air dry-bulb temperature difference using both sets of
instrumentation, [Delta]T (Set SS) and [Delta]T (Set CYC), for each
equally spaced data sample. If using a consistent data sampling rate
that is less than 1 minute, calculate and record minutely averages
for the two temperature differences. If using a consistent sampling
rate of one minute or more, calculate and record the two temperature
differences from each data sample. After having recorded the seventh
(i=7) set of temperature differences, calculate the following ratio
using the first seven sets of values:
[GRAPHIC] [TIFF OMITTED] TR05JA17.016
Each time a subsequent set of temperature differences is
recorded (if sampling more frequently than every 5 minutes),
calculate FCD using the most recent seven sets of values.
Continue these calculations until the 30-minute period is completed
or until a value for FCD is calculated that falls outside
the allowable range of 0.94-1.06. If the latter occurs, immediately
suspend the test and identify the cause for the disparity in the two
temperature difference measurements. Recalibration of one or both
sets of instrumentation may be required. If all the values for
FCD are within the allowable range, save the final value
of the ratio from the 30-minute test as FCD*. If the
temperature sensors used to provide the primary measurement of the
indoor-side dry bulb temperature difference during the steady-
[[Page 1497]]
state dry-coil test and the subsequent cyclic dry-coil test are the
same, set FCD*= 1.
3.5 Test Procedures for the Cyclic Dry-Coil Cooling-Mode Tests (the
D, D1, D2, and I1 Tests)
After completing the steady-state dry-coil test, remove the
outdoor air enthalpy method test apparatus, if connected, and begin
manual OFF/ON cycling of the unit's compressor. The test set-up
should otherwise be identical to the set-up used during the steady-
state dry coil test. When testing heat pumps, leave the reversing
valve during the compressor OFF cycles in the same position as used
for the compressor ON cycles, unless automatically changed by the
controls of the unit. For units having a variable-speed indoor
blower, the manufacturer has the option of electing at the outset
whether to conduct the cyclic test with the indoor blower enabled or
disabled. Always revert to testing with the indoor blower disabled
if cyclic testing with the fan enabled is unsuccessful.
a. For all cyclic tests, the measured capacity must be adjusted
for the thermal mass stored in devices and connections located
between measured points. Follow the procedure outlined in section
7.4.3.4.5 of ASHRAE 116-2010 (incorporated by reference, see Sec.
430.3) to ensure any required measurements are taken.
b. For units having a single-speed or two-capacity compressor,
cycle the compressor OFF for 24 minutes and then ON for 6 minutes
([Delta][tau]cyc,dry = 0.5 hours). For units having a
variable-speed compressor, cycle the compressor OFF for 48 minutes
and then ON for 12 minutes ([Delta][tau]cyc,dry = 1.0
hours). Repeat the OFF/ON compressor cycling pattern until the test
is completed. Allow the controls of the unit to regulate cycling of
the outdoor fan. If an upturned duct is used, measure the dry-bulb
temperature at the inlet of the device at least once every minute
and ensure that its test operating tolerance is within 1.0 [deg]F
for each compressor OFF period.
c. Sections 3.5.1 and 3.5.2 of this appendix specify airflow
requirements through the indoor coil of ducted and non-ducted indoor
units, respectively. In all cases, use the exhaust fan of the
airflow measuring apparatus (covered under section 2.6 of this
appendix) along with the indoor blower of the unit, if installed and
operating, to approximate a step response in the indoor coil
airflow. Regulate the exhaust fan to quickly obtain and then
maintain the flow nozzle static pressure difference or velocity
pressure at the same value as was measured during the steady-state
dry coil test. The pressure difference or velocity pressure should
be within 2 percent of the value from the steady-state dry coil test
within 15 seconds after airflow initiation. For units having a
variable-speed indoor blower that ramps when cycling on and/or off,
use the exhaust fan of the airflow measuring apparatus to impose a
step response that begins at the initiation of ramp up and ends at
the termination of ramp down.
d. For units having a variable-speed indoor blower, conduct the
cyclic dry coil test using the pull-thru approach described below if
any of the following occur when testing with the fan operating:
(1) The test unit automatically cycles off;
(2) Its blower motor reverses; or
(3) The unit operates for more than 30 seconds at an external
static pressure that is 0.1 inches of water or more higher than the
value measured during the prior steady-state test.
For the pull-thru approach, disable the indoor blower and use
the exhaust fan of the airflow measuring apparatus to generate the
specified flow nozzles static pressure difference or velocity
pressure. If the exhaust fan cannot deliver the required pressure
difference because of resistance created by the unpowered indoor
blower, temporarily remove the indoor blower.
e. Conduct three complete compressor OFF/ON cycles with the test
tolerances given in Table 10 satisfied. Calculate the degradation
coefficient CD for each complete cycle. If all three
CD values are within 0.02 of the average CD
then stability has been achieved, and the highest CD
value of these three shall be used. If stability has not been
achieved, conduct additional cycles, up to a maximum of eight cycles
total, until stability has been achieved between three consecutive
cycles. Once stability has been achieved, use the highest
CD value of the three consecutive cycles that establish
stability. If stability has not been achieved after eight cycles,
use the highest CD from cycle one through cycle eight, or
the default CD, whichever is lower.
f. With regard to the Table 10 parameters, continuously record
the dry-bulb temperature of the air entering the indoor and outdoor
coils during periods when air flows through the respective coils.
Sample the water vapor content of the indoor coil inlet air at least
every 2 minutes during periods when air flows through the coil.
Record external static pressure and the air volume rate indicator
(either nozzle pressure difference or velocity pressure) at least
every minute during the interval that air flows through the indoor
coil. (These regular measurements of the airflow rate indicator are
in addition to the required measurement at 15 seconds after flow
initiation.) Sample the electrical voltage at least every 2 minutes
beginning 30 seconds after compressor start-up. Continue until the
compressor, the outdoor fan, and the indoor blower (if it is
installed and operating) cycle off.
g. For ducted units, continuously record the dry-bulb
temperature of the air entering (as noted above) and leaving the
indoor coil. Or if using a thermopile, continuously record the
difference between these two temperatures during the interval that
air flows through the indoor coil. For non-ducted units, make the
same dry-bulb temperature measurements beginning when the compressor
cycles on and ending when indoor coil airflow ceases.
h. Integrate the electrical power over complete cycles of length
[Delta][tau]cyc,dry. For ducted blower coil systems
tested with the unit's indoor blower operating for the cycling test,
integrate electrical power from indoor blower OFF to indoor blower
OFF. For all other ducted units and for non-ducted units, integrate
electrical power from compressor OFF to compressor OFF. (Some cyclic
tests will use the same data collection intervals to determine the
electrical energy and the total space cooling. For other units,
terminate data collection used to determine the electrical energy
before terminating data collection used to determine total space
cooling.)
Table 10--Test Operating and Test Condition Tolerances for Cyclic Dry
Coil Cooling Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor entering dry-bulb temperature,\2\ 2.0 0.5
[deg]F.................................
Indoor entering wet-bulb temperature, .............. (\3\)
[deg]F.................................
Outdoor entering dry-bulb 2.0 0.5
temperature,\2\ [deg]F.................
External resistance to airflow,\2\ 0.05 ..............
inches of water........................
Airflow nozzle pressure difference or 2.0 \4\ 2.0
velocity pressure,\2\ % of reading.....
Electrical voltage,\5\ % of rdg......... 2.0 1.5
------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
\2\ Applies during the interval that air flows through the indoor
(outdoor) coil except for the first 30 seconds after flow initiation.
For units having a variable-speed indoor blower that ramps, the
tolerances listed for the external resistance to airflow apply from 30
seconds after achieving full speed until ramp down begins.
\3\ Shall at no time exceed a wet-bulb temperature that results in
condensate forming on the indoor coil.
\4\ The test condition shall be the average nozzle pressure difference
or velocity pressure measured during the steady-state dry coil test.
\5\ Applies during the interval when at least one of the following--the
compressor, the outdoor fan, or, if applicable, the indoor blower--are
operating except for the first 30 seconds after compressor start-up.
[[Page 1498]]
If the Table 10 tolerances are satisfied over the complete
cycle, record the measured electrical energy consumption as
ecyc,dry and express it in units of watt-hours. Calculate
the total space cooling delivered, qcyc,dry, in units of
Btu using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.017
Where,
VI, Cp,a, vn' (or vn),
Wn, and FCD* are the values recorded during
the section 3.4 dry coil steady-state test and
Tal([tau]) = dry bulb temperature of the air entering the
indoor coil at time [tau], [deg]F.
Ta2([tau]) = dry bulb temperature of the air leaving the
indoor coil at time [tau], [deg]F.
[tau]1 = for ducted units, the elapsed time when airflow
is initiated through the indoor coil; for non-ducted units, the
elapsed time when the compressor is cycled on, hr.
[tau]2 = the elapsed time when indoor coil airflow
ceases, hr.
Adjust the total space cooling delivered, qcyc,dry,
according to calculation method outlined in section 7.4.3.4.5 of
ASHRAE 116-2010 (incorporated by reference, see Sec. 430.3).
3.5.1 Procedures When Testing Ducted Systems
The automatic controls that are installed in the test unit must
govern the OFF/ON cycling of the air moving equipment on the indoor
side (exhaust fan of the airflow measuring apparatus and the indoor
blower of the test unit). For ducted coil-only systems rated based
on using a fan time-delay relay, control the indoor coil airflow
according to the OFF delay listed by the manufacturer in the
certification report. For ducted units having a variable-speed
indoor blower that has been disabled (and possibly removed), start
and stop the indoor airflow at the same instances as if the fan were
enabled. For all other ducted coil-only systems, cycle the indoor
coil airflow in unison with the cycling of the compressor. If air
damper boxes are used, close them on the inlet and outlet side
during the OFF period. Airflow through the indoor coil should stop
within 3 seconds after the automatic controls of the test unit (act
to) de-energize the indoor blower. For ducted coil-only systems
(excluding the special case where a variable-speed fan is
temporarily removed), increase ecyc,dry by the quantity,
[GRAPHIC] [TIFF OMITTED] TR05JA17.018
and decrease qcyc,dry by,
[GRAPHIC] [TIFF OMITTED] TR05JA17.019
where VIs is the average indoor air volume rate from the
section 3.4 dry coil steady-state test and is expressed in units of
cubic feet per minute of standard air (scfm). For units having a
variable-speed indoor blower that is disabled during the cyclic
test, increase ecyc,dry and decrease qcyc,dry
based on:
a. The product of [[tau]2 - [tau]1] and the
indoor blower power measured during or following the dry coil
steady-state test; or,
b. The following algorithm if the indoor blower ramps its speed when
cycling.
(1) Measure the electrical power consumed by the variable-speed
indoor blower at a minimum of three operating conditions: At the
speed/air volume rate/external static pressure that was measured
during the steady-state test, at operating conditions associated
with the midpoint of the ramp-up interval, and at conditions
associated with the midpoint of the ramp-down interval. For these
measurements, the tolerances on the airflow volume or the external
static pressure are the same as required for the section 3.4 steady-
state test.
(2) For each case, determine the fan power from measurements
made over a minimum of 5 minutes.
(3) Approximate the electrical energy consumption of the indoor
blower if it had operated during the cyclic test using all three
power measurements. Assume a linear profile during the ramp
intervals. The manufacturer must provide the durations of the ramp-
up and ramp-down intervals. If the test setup instructions included
with the unit by the manufacturer specifies a ramp interval that
exceeds 45 seconds, use a 45-second ramp interval nonetheless when
estimating the fan energy.
3.5.2 Procedures When Testing Non-Ducted Indoor Units
Do not use airflow prevention devices when conducting cyclic
tests on non-ducted indoor units. Until the last OFF/ON compressor
cycle, airflow through the indoor coil must cycle off and on in
unison with the compressor. For the last OFF/ON compressor cycle--
the one used to determine ecyc,dry and
qcyc,dry--use the exhaust fan of the airflow measuring
apparatus and the indoor blower of the test unit to have indoor
airflow start 3 minutes prior to compressor cut-on and end three
minutes after compressor cutoff. Subtract the electrical energy used
by the indoor blower during the 3 minutes prior to compressor cut-on
from the integrated electrical energy, ecyc,dry. Add the
electrical energy used by the indoor blower during the 3 minutes
after compressor cutoff to the integrated cooling capacity,
qcyc,dry. For the case where the non-ducted indoor unit
uses a variable-speed indoor blower which is disabled during the
cyclic test, correct ecyc,dry and qcyc,dry
using the same approach as prescribed in section 3.5.1 of this
appendix for ducted units having a disabled variable-speed indoor
blower.
3.5.3 Cooling-Mode Cyclic-Degradation Coefficient Calculation
Use the two dry-coil tests to determine the cooling-mode cyclic-
degradation coefficient, CD\c\. Append ``(k=2)'' to the
coefficient if it corresponds to a two-capacity unit cycling at high
capacity. If the two optional tests are conducted but yield a tested
CD\c\ that exceeds the default CD\c\ or if the two optional tests
are not conducted, assign CD\c\ the default value of 0.25 for
variable-speed compressor systems and outdoor units with no match,
and 0.20 for all other systems. The default value for two-capacity
units cycling at high capacity, however, is the low-capacity
coefficient, i.e., CD\c\(k=2) = CD\c\.
Evaluate CD\c\ using the above results and those from the
section 3.4 dry-coil steady-state test.
[GRAPHIC] [TIFF OMITTED] TR05JA17.020
where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.021
the average energy efficiency ratio during the cyclic dry coil
cooling mode test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TR05JA17.022
[[Page 1499]]
the average energy efficiency ratio during the steady-state dry coil
cooling mode test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TR05JA17.023
the cooling load factor dimensionless
Round the calculated value for CD\c\ to the nearest 0.01.
If CD\c\ is negative, then set it equal to zero.
3.6 Heating Mode Tests for Different Types of Heat Pumps, Including
Heating-Only Heat Pumps
3.6.1 Tests for a Heat Pump Having a Single-Speed Compressor and Fixed
Heating Air Volume Rate
This set of tests is for single-speed-compressor heat pumps that
do not have a heating minimum air volume rate or a heating
intermediate air volume rate that is different than the heating full
load air volume rate. Conduct the optional high temperature cyclic
(H1C) test to determine the heating mode cyclic-degradation
coefficient, CD\h\. If this optional test is conducted
but yields a tested CD\h\ that exceeds the default
CD\h\ or if the optional test is not conducted, assign
CD\h\ the default value of 0.25. Test conditions for the
four tests are specified in Table 10.
Table 11--Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Blower, a Constant Air Volume Rate Indoor
Blower, or No Indoor Blower
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit temperature Air entering outdoor unit
([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------------------- Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H1 Test (required, steady).......... 70 60 \(max)\................ 47 43 Heating Full-load.\1\
H1C Test (optional, cyclic)......... 70 60 \(max)\................ 47 43 (\2\)
H2 Test (required).................. 70 60 \(max)\................ 35 33 Heating Full-load.\1\
H3 Test (required, steady).......... 70 60 \(max)\................ 17 15 Heating Full-load.\1\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4 of this appendix.
\2\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the H1 Test.
3.6.2 Tests for a Heat Pump Having a Single-Speed Compressor and a
Single Indoor Unit Having Either (1) a Variable Speed, Variable-Air-
Rate Indoor Blower Whose Capacity Modulation Correlates With Outdoor
Dry Bulb Temperature or (2) Multiple Indoor Blowers
Conduct five tests: Two high temperature tests (H12
and H11), one frost accumulation test (H22),
and two low temperature tests (H32 and H31).
Conducting an additional frost accumulation test (H21) is
optional. Conduct the optional high temperature cyclic
(H1C1) test to determine the heating mode cyclic-
degradation coefficient, CD\h\. If this optional test is
conducted but yields a tested CD\h\ that exceeds the
default CD\h\ or if the optional test is not conducted,
assign CD\h\ the default value of 0.25. Test conditions
for the seven tests are specified in Table 12. If the optional
H21 test is not performed, use the following equations to
approximate the capacity and electrical power of the heat pump at
the H21 test conditions:
[GRAPHIC] [TIFF OMITTED] TR05JA17.024
The quantities Qhk=2(47), Ehk=2(47), Qh\k=1\(47), and
Eh\k=1\(47) are determined from the H12 and
H11 tests and evaluated as specified in section 3.7 of
this appendix; the quantities Qhk=2(35) and Ehk=2(35) are determined
from the H22 test and evaluated as specified in section
3.9 of this appendix; and the quantities Qhk=2(17), Ehk=2(17),
Qh\k=1\(17), and Eh\k=1\(17), are determined from the H32
and H31 tests and evaluated as specified in section 3.10
of this appendix.
[[Page 1500]]
Table 12--Table Heating Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.6.2 Indoor Unit Requirements
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit temperature Air entering outdoor unit
([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------------------- Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H12 Test (required, steady)......... 70 60 \(max)\................ 47 43 Heating Full-load.\1\
H11 Test (required, steady)......... 70 60 \(max)\................ 47 43 Heating Minimum.\2\
H1C1 Test (optional, cyclic)........ 70 60 \(max)\................ 47 43 (\3\)
H22 Test (required)................. 70 60 \(max)\................ 35 33 Heating Full-load.\1\
H21 Test (optional)................. 70 60 \(max)\................ 35 33 Heating Minimum.\2\
H32 Test (required, steady)......... 70 60 \(max)\................ 17 15 Heating Full-load.\1\
H31 Test (required, steady)......... 70 60 \(max)\................ 17 15 Heating Minimum.\2\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4 of this appendix.
\2\ Defined in section 3.1.4.5 of this appendix.
\3\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the H11 test.
3.6.3 Tests for a Heat Pump Having a Two-Capacity Compressor (see
section 1.2 of this appendix, Definitions), Including Two-Capacity,
Northern Heat Pumps (see section 1.2 of this appendix, Definitions)
a. Conduct one maximum temperature test (H01), two
high temperature tests (H12and H11), one frost
accumulation test (H22), and one low temperature test
(H32). Conduct an additional frost accumulation test
(H21) and low temperature test (H31) if both
of the following conditions exist:
(1) Knowledge of the heat pump's capacity and electrical power
at low compressor capacity for outdoor temperatures of 37 [deg]F and
less is needed to complete the section 4.2.3 of this appendix
seasonal performance calculations; and
(2) The heat pump's controls allow low-capacity operation at
outdoor temperatures of 37 [deg]F and less.
If the above two conditions are met, an alternative to
conducting the H21 frost accumulation is to use the
following equations to approximate the capacity and electrical
power:
[GRAPHIC] [TIFF OMITTED] TR05JA17.306
Determine the quantities Qh\k=1\ (47) and Eh\k=1\ (47) from the
H11 test and evaluate them according to section 3.7 of
this appendix. Determine the quantities Qh\k=1\ (17) and Eh\k=1\
(17) from the H31 test and evaluate them according to
section 3.10 of this appendix.
b. Conduct the optional high temperature cyclic test
(H1C1) to determine the heating mode cyclic-degradation
coefficient, CD\h\. If this optional test is conducted
but yields a tested CD\h\ that exceeds the default
CD\h\ or if the optional test is not conducted, assign
CD\h\ the default value of 0.25. If a two-capacity heat
pump locks out low capacity operation at lower outdoor temperatures,
conduct the high temperature cyclic test (H1C 2) to
determine the high-capacity heating mode cyclic-degradation
coefficient, CD\h\ (k=2). If this optional test at high
capacity is conducted but yields a tested CD\h\ (k = 2)
that exceeds the default CD\h\ (k = 2) or if the optional
test is not conducted, assign CD\h\ the default value.
The default CD\h\ (k=2) is the same value as determined
or assigned for the low-capacity cyclic-degradation coefficient,
CD\h\ [or equivalently, CD\h\ (k=1)]. Table 13
specifies test conditions for these nine tests.
Table 13--Heating Mode Test Conditions for Units Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F) Compressor
Test description ---------------------------------------------------------------------- capacity Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady)... 70 60 \(max)\.......... 62 56.5 Low.............. Heating Minimum.\1\
H12 Test (required, steady)... 70 60 \(max)\.......... 47 43 High............. Heating Full-Load.\2\
H1C2 Test (optional \7\, 70 60 \(max)\.......... 47 43 High............. (\3\)
cyclic).
H11 Test (required)........... 70 60 \(max)\.......... 47 43 Low.............. Heating Minimum.\1\
H1C1 Test (optional, cyclic).. 70 60 \(max)\.......... 47 43 Low.............. (\4\)
H22 Test (required)........... 70 60 \(max)\.......... 35 33 High............. Heating Full-Load.\2\
H21 Test \5 6\ (required)..... 70 60 \(max)\.......... 35 33 Low.............. Heating Minimum.\1\
H32 Test (required, steady)... 70 60 \(max)\.......... 17 15 High............. Heating Full-Load.\2\
H31 Test \5\ (required, 70 60 \(max)\.......... 17 15 Low.............. Heating Minimum.\1\
steady).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5 of this appendix.
\2\ Defined in section 3.1.4.4 of this appendix.
\3\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H12 test.
\4\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H11 test.
\5\ Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 [deg]F is needed to
complete the section 4.2.3 HSPF calculations.
\6\ If table note #5 applies, the section 3.6.3 equations for Qh\k=1\ (35) and Eh\k=1\ (17) may be used in lieu of conducting the H21 test.
[[Page 1501]]
\7\ Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.
3.6.4 Tests for a Heat Pump Having a Variable-Speed Compressor
a. Conduct one maximum temperature test (H01), two
high temperature tests (H1N and H11), one
frost accumulation test (H2V), and one low temperature
test (H32). Conducting one or both of the following tests
is optional: An additional high temperature test (H12)
and an additional frost accumulation test (H22). If
desired, conduct the optional maximum temperature cyclic
(H0C1) test to determine the heating mode cyclic-
degradation coefficient, CD\h\. If this optional test is
conducted but yields a tested CD\h\ that exceeds the
default CD\h\ or if the optional test is not conducted,
assign CD\h\ the default value of 0.25. Test conditions
for the eight tests are specified in Table 14. The compressor shall
operate at the same heating full speed, measured by RPM or power
input frequency (Hz), for the H12, H22 and
H32 tests. For a cooling/heating heat pump, the
compressor shall operate for the H1N test at a speed,
measured by RPM or power input frequency (Hz), no lower than the
speed used in the A2 test if the tested H12
heating capacity is less than the tested cooling capacity in
A2 test. The compressor shall operate at the same heating
minimum speed, measured by RPM or power input frequency (Hz), for
the H01, H1C1, and H11 tests.
Determine the heating intermediate compressor speed cited in Table
14 using the heating mode full and minimum compressors speeds and:
[GRAPHIC] [TIFF OMITTED] TR05JA17.025
Where a tolerance on speed of plus 5 percent or the next higher
inverter frequency step from the calculated value is allowed.
b. If the H12 test is conducted, set the 47 [deg]F
capacity and power input values used for calculation of HSPF equal
to the measured values for that test:
[GRAPHIC] [TIFF OMITTED] TR05JA17.313
Where:
Qhcalck=2(47) and Ehcalck=2(47) are the
capacity and power input representing full-speed operation at 47
[deg]F for the HSPF calculations,
Qhk=2(47) is the capacity measured in the
H12 test, and
Ehk=2(47) is the power input measured in the
H12 test.
Evaluate the quantities Qhk=2(47) and from Ehk=2(47) according
to section 3.7.
Otherwise, if the H1N test is conducted using the
same compressor speed (RPM or power input frequency) as the
H32 test, set the 47[emsp14][deg]F capacity and power
input values used for calculation of HSPF equal to the measured
values for that test:
[GRAPHIC] [TIFF OMITTED] TR05JA17.307
Where:
Qhcalck=2(47) and Ehcalck=2(47) are the capacity and power input
representing full-speed operation at 47[emsp14][deg]F for the HSPF
calculations,
Qhk=N(47) is the capacity measured in the H1N test, and
Ehk=N(47) is the power input measured in the H1N test.
Evaluate the quantities Qhk=N(47) and from Ehk=N(47) according
to section 3.7.
Otherwise (if no high temperature test is conducted using the
same speed (RPM or power input frequency) as the H32
test), calculate the 47[emsp14][deg]F capacity and power input
values used for calculation of HSPF as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.308
Where:
Qhcalck=2(47) and Ehcalck=2(47) are the capacity and power input
representing full-speed operation at 47[emsp14][deg]F for the HSPF
calculations,
Qhk=2(17) is the capacity measured in the H32
test,
Ehk=2(17) is the power input measured in the
H32 test,
CSF is the capacity slope factor, equal to 0.0204/[deg]F for split
systems and 0.0262/[deg]F for single-package systems, and
PSF is the Power Slope Factor, equal to 0.00455/[deg]F.
c. If the H22 test is not done, use the following
equations to approximate the capacity and electrical power at the
H22 test conditions:
[GRAPHIC] [TIFF OMITTED] TR05JA17.309
Where:
Qhcalck=2(47) and Ehcalck=2(47) are the
capacity and power input representing full-speed operation at 47
[deg]F for the HSPF
[[Page 1502]]
calculations,calculated as described in section b above.
Qhk=2(17) and Ehk=2(17) are the capacity and
power input measured in the H32 test.
d. Determine the quantities Qhk=2(17) and Ehk=2(17) from the
H32 test, determine the quantities Qhk=2(5) and Ehk=2(5)
from the H42 test, and evaluate all four according to
section 3.10.
Table 14--Heating Mode Test Conditions for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit temperature Air entering outdoor unit
([deg]F) temperature ([deg]F) Heating air volume
Test description ------------------------------------------------------------------------- Compressor speed rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 test (required, steady)...... 70 60\(max)\.............. 62 56.5 Heating minimum........ Heating minimum.\1\
H12 test (optional, steady)...... 70 60\(max)\.............. 47 43 Heating full \4\....... Heating full-
load.\3\
H11 test (required, steady)...... 70 60\(max)\.............. 47 43 Heating minimum........ Heating minimum.\1\
H1N test (required, steady)...... 70 60\(max)\.............. 47 43 Heating full........... Heating full-
load.\3\
H1C1 test (optional, cyclic)..... 70 60\(max)\.............. 47 43 Heating minimum........ (\2\)
H22 test (optional).............. 70 60\(max)\.............. 35 33 Heating full \4\....... Heating full-
load.\3\
H2V test (required).............. 70 60\(max)\.............. 35 33 Heating intermediate... Heating
intermediate.\5\
H32 test (required, steady)...... 70 60\(max)\.............. 17 15 Heating full........... Heating full-
load.\3\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5 of this appendix.
\2\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured
during the H11 test.
\3\ Defined in section 3.1.4.4 of this appendix.
\4\ The same compressor speed used in the H32 test. The H12 test is not needed if the H1N test uses this same compressor speed.
\5\ Defined in section 3.1.4.6 of this appendix.
3.6.5 Additional Test for a Heat Pump Having a Heat Comfort Controller
Test any heat pump that has a heat comfort controller (see
section 1.2 of this appendix, Definitions) according to section
3.6.1, 3.6.2, or 3.6.3, whichever applies, with the heat comfort
controller disabled. Additionally, conduct the abbreviated test
described in section 3.1.10 of this appendix with the heat comfort
controller active to determine the system's maximum supply air
temperature. (Note: Heat pumps having a variable speed compressor
and a heat comfort controller are not covered in the test procedure
at this time.)
3.6.6 Heating Mode Tests for Northern Heat Pumps With Triple-Capacity
Compressors.
Test triple-capacity, northern heat pumps for the heating mode
as follows:
a. Conduct one maximum-temperature test (H01), two
high-temperature tests (H12 and H11), one
frost accumulation test (H22), two low-temperature tests
(H32, H33), and one minimum-temperature test
(H43). Conduct an additional frost accumulation test
(H21) and low-temperature test (H31) if both
of the following conditions exist: (1) Knowledge of the heat pump's
capacity and electrical power at low compressor capacity for outdoor
temperatures of 37[emsp14][deg]F and less is needed to complete the
section 4.2.6 seasonal performance calculations; and (2) the heat
pump's controls allow low-capacity operation at outdoor temperatures
of 37[emsp14][deg]F and less. If the above two conditions are met,
an alternative to conducting the H21 frost accumulation
test to determine Qh\k=1\(35) and Ehk=1(35) is to use the following
equations to approximate this capacity and electrical power:
[GRAPHIC] [TIFF OMITTED] TR05JA17.310
In evaluating the above equations, determine the quantities
Qhk=1(47) from the H11 test and evaluate them according
to section 3.7 of this appendix. Determine the quantities Qhk=1(17)
and Eh\k=1\(17) from the H31 test and evaluate them
according to section 3.10 of this appendix. Use the paired values of
Qh\k=1\(35) and Eh\k=1\(35) derived from conducting the
H21 frost accumulation test and evaluated as specified in
section 3.9.1 of this appendix or use the paired values calculated
using the above default equations, whichever contribute to a higher
Region IV HSPF based on the DHRmin.
b. Conducting a frost accumulation test (H23) with
the heat pump operating at its booster capacity is optional. If this
optional test is not conducted, determine Qh\k=3\(35) and Ehk=3(35)
using the following equations to approximate this capacity and
electrical power:
[GRAPHIC] [TIFF OMITTED] TR05JA17.311
Where:
[[Page 1503]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.026
Determine the quantities Qhk=2(47) and Ehk=2(47) from the
H12 test and evaluate them according to section 3.7 of
this appendix. Determine the quantities Qhk=2(35) and Ehk=2(35) from
the H22 test and evaluate them according to section 3.9.1
of this appendix. Determine the quantities Qhk=2(17) and Ehk=2(17)
from the H32 test, determine the quantities Qh\k=3\(17)
and Ehk=3(17) from the H33 test, and determine the
quantities Qhk=3(5) and Ehk=3(5) from the H43 test.
Evaluate all six quantities according to section 3.10 of this
appendix. Use the paired values of Qhk=3(35) and Ehk=3(35) derived
from conducting the H23 frost accumulation test and
calculated as specified in section 3.9.1 of this appendix or use the
paired values calculated using the above default equations,
whichever contribute to a higher Region IV HSPF2 based on the
DHRmin.
c. Conduct the optional high-temperature cyclic test
(H1C1) to determine the heating mode cyclic-degradation
coefficient, CD\h\. A default value for CD\h\
may be used in lieu of conducting the cyclic. The default value of
CD\h\ is 0.25. If a triple-capacity heat pump locks out
low capacity operation at lower outdoor temperatures, conduct the
high-temperature cyclic test (H1C2) to determine the
high-capacity heating mode cyclic-degradation coefficient,
CD\h\ (k=2). The default CD\h\ (k=2) is the
same value as determined or assigned for the low-capacity cyclic-
degradation coefficient, CD\h\ [or equivalently,
CD\h\ (k=1)]. Finally, if a triple-capacity heat pump
locks out both low and high capacity operation at the lowest outdoor
temperatures, conduct the low-temperature cyclic test
(H3C3) to determine the booster-capacity heating mode
cyclic-degradation coefficient, CD\h\ (k=3). The default
CD\h\ (k=3) is the same value as determined or assigned
for the high-capacity cyclic-degradation coefficient,
CD\h\ [or equivalently, CD\h\ (k=2)]. Table 15
specifies test conditions for all 13 tests.
Table 15--Heating Mode Test Conditions for Units With a Triple-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor
temperature [deg]F unit temperature [deg]F
Test description ---------------------------------------------------- Compressor capacity Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).............. 70 60\(max)\ 62 56.5 Low......................... Heating Minimum.\1\
H12 Test (required, steady).............. 70 60\(max)\ 47 43 High........................ Heating Full-Load.\2\
H1C2 Test (optional,\8\ cyclic).......... 70 60\(max)\ 47 43 High........................ (\3\).
H11 Test (required)...................... 70 60\(max)\ 47 43 Low......................... Heating Minimum.\1\
H1C1 Test (optional, cyclic)............. 70 60\(max)\ 47 43 Low......................... (\4\).
H23 Test (optional, steady).............. 70 60\(max)\ 35 33 Booster..................... Heating Full-Load.\2\
H22 Test (required)...................... 70 60\(max)\ 35 33 High........................ Heating Full-Load.\2\
H21 Test (required)...................... 70 60\(max)\ 35 33 Low......................... Heating Minimum.\1\
H33 Test (required, steady).............. 70 60\(max)\ 17 15 Booster..................... Heating Full-Load.\2\
H3C3 Test5 6 (optional, cyclic).......... 70 60\(max)\ 17 15 Booster..................... (\7\).
H32 Test (required, steady).............. 70 60\(max)\ 17 15 High........................ Heating Full-Load.\2\
H31 Test\5\ (required, steady)........... 70 60\(max)\ 17 15 Low......................... Heating Minimum.\1\
H43 Test (required, steady).............. 70 60\(max)\ 5 3\(max)\ Booster..................... Heating Full-Load.\2\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5 of this appendix.
\2\ Defined in section 3.1.4.4 of this appendix.
\3\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H12 test.
\4\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H11 test.
\5\ Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 [deg]F is needed to
complete the section 4.2.6 HSPF2 calculations.
\6\ If table note \5\ applies, the section 3.6.6 equations for Qh\k=1\(35) and Eh\k=1\(17) may be used in lieu of conducting the H21 test.
\7\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H33 test.
\8\ Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.
3.6.7 Tests for a Heat Pump Having a Single Indoor Unit Having Multiple
Indoor Blowers and Offering Two Stages of Compressor Modulation
Conduct the heating mode tests specified in section 3.6.3 of
this appendix.
3.7 Test Procedures for Steady-State Maximum Temperature and High
Temperature Heating Mode Tests (the H01, H1, H12, H11, and H1N
Tests)
a. For the pretest interval, operate the test room
reconditioning apparatus and the heat pump until equilibrium
conditions are maintained for at least 30 minutes at the specified
section 3.6 test conditions. Use the exhaust fan of the airflow
measuring apparatus and, if installed, the indoor blower of the heat
pump to obtain and then maintain the indoor air volume rate and/or
the external static pressure specified for the particular test.
Continuously record the dry-bulb temperature of the air entering the
indoor coil, and the dry-bulb temperature and water vapor content of
the air entering the outdoor coil. Refer to section 3.11 of this
appendix for additional requirements that depend on the selected
secondary test method. After satisfying the pretest equilibrium
requirements, make the measurements specified in Table 3 of ANSI/
ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3) for the
indoor air enthalpy method and the user-selected secondary method.
Make said Table 3 measurements at equal intervals that span 5
minutes or less. Continue data sampling until a 30-minute period
(e.g., seven consecutive 5-minute samples) is reached where the test
tolerances specified in Table 16 are satisfied. For those
continuously recorded parameters,
[[Page 1504]]
use the entire data set for the 30-minute interval when evaluating
Table 16 compliance. Determine the average electrical power
consumption of the heat pump over the same 30-minute interval.
Table 16--Test Operating and Test Condition Tolerances for Section 3.7
and Section 3.10 Steady-State Heating Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor dry-bulb, [deg]F:
Entering temperature.......... 2.0 0.5
Leaving temperature........... 2.0 .................
Indoor wet-bulb, [deg]F:
Entering temperature.......... 1.0 .................
Leaving temperature........... 1.0 .................
Outdoor dry-bulb, [deg]F:
Entering temperature.......... 2.0 0.5
Leaving temperature........... \2\ 2.0 .................
Outdoor wet-bulb, [deg]F:
Entering temperature.......... 1.0 0.3
Leaving temperature........... \2\ 1.0 .................
External resistance to airflow, 0.05 \3\ 0.02
inches of water..................
Electrical voltage, % of rdg...... 2.0 1.5
Nozzle pressure drop, % of rdg.... 2.0 .................
------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
\2\ Only applies when the Outdoor Air Enthalpy Method is used.
\3\ Only applies when testing non-ducted units.
b. Calculate indoor-side total heating capacity as specified in
sections 7.3.4.1 and 7.3.4.3 of ANSI/ASHRAE 37-2009 (incorporated by
reference, see Sec. 430.3). To calculate capacity, use the averages
of the measurements (e.g. inlet and outlet dry bulb temperatures
measured at the psychrometers) that are continuously recorded for
the same 30-minute interval used as described above to evaluate
compliance with test tolerances. Do not adjust the parameters used
in calculating capacity for the permitted variations in test
conditions. Assign the average space heating capacity and electrical
power over the 30-minute data collection interval to the variables
Qh\k\ and Eh\k\(T) respectively. The ``T'' and superscripted ``k''
are the same as described in section 3.3 of this appendix.
Additionally, for the heating mode, use the superscript to denote
results from the optional H1N test, if conducted.
c. For coil-only system heat pumps, increase Qh\k\(T) by
[GRAPHIC] [TIFF OMITTED] TR05JA17.028
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
During the 30-minute data collection interval of a high temperature
test, pay attention to preventing a defrost cycle. Prior to this
time, allow the heat pump to perform a defrost cycle if
automatically initiated by its own controls. As in all cases, wait
for the heat pump's defrost controls to automatically terminate the
defrost cycle. Heat pumps that undergo a defrost should operate in
the heating mode for at least 10 minutes after defrost termination
prior to beginning the 30-minute data collection interval. For some
heat pumps, frost may accumulate on the outdoor coil during a high
temperature test. If the indoor coil leaving air temperature or the
difference between the leaving and entering air temperatures
decreases by more than 1.5[emsp14][deg]F over the 30-minute data
collection interval, then do not use the collected data to determine
capacity. Instead, initiate a defrost cycle. Begin collecting data
no sooner than 10 minutes after defrost termination. Collect 30
minutes of new data during which the Table 16 test tolerances are
satisfied. In this case, use only the results from the second 30-
minute data collection interval to evaluate Qh\k\(47) and Eh\k\(47).
d. If conducting the cyclic heating mode test, which is
described in section 3.8 of this appendix, record the average
indoor-side air volume rate, Vi, specific heat of the air,
Cp,a (expressed on dry air basis), specific volume of the
air at the nozzles, vn' (or vn), humidity
ratio at the nozzles, Wn, and either pressure difference
or velocity pressure for the flow nozzles. If either or both of the
below criteria apply, determine the average, steady-state,
electrical power consumption of the indoor blower motor
(Efan,1):
(1) The section 3.8 cyclic test will be conducted and the heat
pump has a variable-speed indoor blower that is expected to be
disabled during the cyclic test; or
(2) The heat pump has a (variable-speed) constant-air volume-
rate indoor blower and during the steady-state test the average
external static pressure ([Delta]P1) exceeds the
applicable section 3.1.4.4 minimum (or targeted) external static
pressure ([Delta]Pmin) by 0.03 inches of water or more.
Determine Efan,1 by making measurements during the
30-minute data collection interval, or immediately following the
test and prior to changing the test conditions. When the above ``2''
criteria applies, conduct the following four steps after determining
Efan,1 (which corresponds to [Delta]P1):
(i) While maintaining the same test conditions, adjust the
exhaust fan of the airflow measuring apparatus until the external
static pressure increases to approximately [Delta]P1 +
([Delta]P1 - [Delta]Pmin).
(ii) After re-establishing steady readings for fan motor power
and external static pressure, determine average values for the
indoor blower power (Efan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
(iii) Approximate the average power consumption of the indoor
blower motor if the 30-minute test had been conducted at
[Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TR05JA17.029
[[Page 1505]]
(iv) Decrease the total space heating capacity, Qhk(T), by the
quantity (Efan,1 - Efan,min), when expressed
on a Btu/h basis. Decrease the total electrical power, Ehk(T) by the
same fan power difference, now expressed in watts.
e. If the temperature sensors used to provide the primary
measurement of the indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the subsequent cyclic dry-
coil test are different, include measurements of the latter sensors
among the regularly sampled data. Beginning at the start of the 30-
minute data collection period, measure and compute the indoor-side
air dry-bulb temperature difference using both sets of
instrumentation, [Delta]T (Set SS) and [Delta]T (Set CYC), for each
equally spaced data sample. If using a consistent data sampling rate
that is less than 1 minute, calculate and record minutely averages
for the two temperature differences. If using a consistent sampling
rate of one minute or more, calculate and record the two temperature
differences from each data sample. After having recorded the seventh
(i=7) set of temperature differences, calculate the following ratio
using the first seven sets of values:
[GRAPHIC] [TIFF OMITTED] TR05JA17.030
Each time a subsequent set of temperature differences is recorded
(if sampling more frequently than every 5 minutes), calculate FCD
using the most recent seven sets of values. Continue these
calculations until the 30-minute period is completed or until a
value for FCD is calculated that falls outside the allowable range
of 0.94-1.06. If the latter occurs, immediately suspend the test and
identify the cause for the disparity in the two temperature
difference measurements. Recalibration of one or both sets of
instrumentation may be required. If all the values for FCD are
within the allowable range, save the final value of the ratio from
the 30-minute test as FCD*. If the temperature sensors used to
provide the primary measurement of the indoor-side dry bulb
temperature difference during the steady-state dry-coil test and the
subsequent cyclic dry-coil test are the same, set FCD*= 1.
3.8 Test Procedures for the Cyclic Heating Mode Tests (the H0C1,
H1C, H1C1 and H1C2 Tests)
a. Except as noted below, conduct the cyclic heating mode test
as specified in section 3.5 of this appendix. As adapted to the
heating mode, replace section 3.5 references to ``the steady-state
dry coil test'' with ``the heating mode steady-state test conducted
at the same test conditions as the cyclic heating mode test.'' Use
the test tolerances in Table 17 rather than Table 10. Record the
outdoor coil entering wet-bulb temperature according to the
requirements given in section 3.5 of this appendix for the outdoor
coil entering dry-bulb temperature. Drop the subscript ``dry'' used
in variables cited in section 3.5 of this appendix when referring to
quantities from the cyclic heating mode test. Determine the total
space heating delivered during the cyclic heating test,
qcyc, as specified in section 3.5 of this appendix except
for making the following changes:
(1) When evaluating Equation 3.5-1, use the values of Vi,
Cp,a,vn', (or vn), and
Wn that were recorded during the section 3.7 steady-state
test conducted at the same test conditions.
(2) Calculate [Gamma] using
[GRAPHIC] [TIFF OMITTED] TR05JA17.031
where FCD* is the value recorded during the section 3.7 steady-state
test conducted at the same test condition.
b. For ducted coil-only system heat pumps (excluding the special
case where a variable-speed fan is temporarily removed), increase
qcyc by the amount calculated using Equation 3.5-3.
Additionally, increase ecyc by the amount calculated
using Equation 3.5-2. In making these calculations, use the average
indoor air volume rate (Vis) determined from the section
3.7 steady-state heating mode test conducted at the same test
conditions.
c. For non-ducted heat pumps, subtract the electrical energy
used by the indoor blower during the 3 minutes after compressor
cutoff from the non-ducted heat pump's integrated heating capacity,
qcyc.
d. If a heat pump defrost cycle is manually or automatically
initiated immediately prior to or during the OFF/ON cycling, operate
the heat pump continuously until 10 minutes after defrost
termination. After that, begin cycling the heat pump immediately or
delay until the specified test conditions have been re-established.
Pay attention to preventing defrosts after beginning the cycling
process. For heat pumps that cycle off the indoor blower during a
defrost cycle, make no effort here to restrict the air movement
through the indoor coil while the fan is off. Resume the OFF/ON
cycling while conducting a minimum of two complete compressor OFF/ON
cycles before determining qcyc and ecyc.
3.8.1 Heating Mode Cyclic-Degradation Coefficient Calculation
Use the results from the required cyclic test and the required
steady-state test that were conducted at the same test conditions to
determine the heating mode cyclic-degradation coefficient
CD\h\. Add ``(k=2)'' to the coefficient if it corresponds
to a two-capacity unit cycling at high capacity. For the below
calculation of the heating mode cyclic degradation coefficient, do
not include the duct loss correction from section 7.3.3.3 of ANSI/
ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3) in
determining Qh\k\(Tcyc) (or qcyc). If the
optional cyclic test is conducted but yields a tested
CD\h\ that exceeds the default CD\h\ or if the
optional test is not conducted, assign CD\h\ the default
value of 0.25. The default value for two-capacity units cycling at
high capacity, however, is the low-capacity coefficient, i.e.,
CD\h\ (k=2) = CD\h\. The tested
CD\h\ is calculated as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.032
where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.033
the average coefficient of performance during the cyclic heating
mode test, dimensionless.
[[Page 1506]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.034
the average coefficient of performance during the steady-state
heating mode test conducted at the same test conditions--i.e., same
outdoor dry bulb temperature, Tcyc, and speed/capacity,
k, if applicable--as specified for the cyclic heating mode test,
dimensionless.
[GRAPHIC] [TIFF OMITTED] TR05JA17.035
the heating load factor, dimensionless.
Tcyc = the nominal outdoor temperature at which the
cyclic heating mode test is conducted, 62 or 47 [deg]F.
[Delta][tau]cyc = the duration of the OFF/ON intervals;
0.5 hours when testing a heat pump having a single-speed or two-
capacity compressor and 1.0 hour when testing a heat pump having a
variable-speed compressor.
Round the calculated value for CD\h\ to the nearest
0.01. If CD\h\ is negative, then set it equal to zero.
Table 17--Test Operating and Test Condition Tolerances for Cyclic
Heating Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor entering dry-bulb 2.0 0.5
temperature,\2\ [deg]F...........
Indoor entering wet-bulb 1.0 .................
temperature,\2\ [deg]F...........
Outdoor entering dry-bulb 2.0 0.5
temperature,\2\ [deg]F...........
Outdoor entering wet-bulb 2.0 1.0
temperature,\2\ [deg]F...........
External resistance to air- 0.05 .................
flow,\2\ inches of water.........
Airflow nozzle pressure difference 2.0 \3\ 2.0
or velocity pressure,\2\% of
reading..........................
Electrical voltage,\4\ % of rdg... 2.0 1.5
------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
\2\ Applies during the interval that air flows through the indoor
(outdoor) coil except for the first 30 seconds after flow initiation.
For units having a variable-speed indoor blower that ramps, the
tolerances listed for the external resistance to airflow shall apply
from 30 seconds after achieving full speed until ramp down begins.
\3\ The test condition shall be the average nozzle pressure difference
or velocity pressure measured during the steady-state test conducted
at the same test conditions.
\4\ Applies during the interval that at least one of the following--the
compressor, the outdoor fan, or, if applicable, the indoor blower--are
operating, except for the first 30 seconds after compressor start-up.
3.9 Test Procedures for Frost Accumulation Heating Mode Tests (the
H2, H22, H2V, and H21 tests)
a. Confirm that the defrost controls of the heat pump are set as
specified in section 2.2.1 of this appendix. Operate the test room
reconditioning apparatus and the heat pump for at least 30 minutes
at the specified section 3.6 test conditions before starting the
``preliminary'' test period. The preliminary test period must
immediately precede the ``official'' test period, which is the
heating and defrost interval over which data are collected for
evaluating average space heating capacity and average electrical
power consumption.
b. For heat pumps containing defrost controls which are likely
to cause defrosts at intervals less than one hour, the preliminary
test period starts at the termination of an automatic defrost cycle
and ends at the termination of the next occurring automatic defrost
cycle. For heat pumps containing defrost controls which are likely
to cause defrosts at intervals exceeding one hour, the preliminary
test period must consist of a heating interval lasting at least one
hour followed by a defrost cycle that is either manually or
automatically initiated. In all cases, the heat pump's own controls
must govern when a defrost cycle terminates.
c. The official test period begins when the preliminary test
period ends, at defrost termination. The official test period ends
at the termination of the next occurring automatic defrost cycle.
When testing a heat pump that uses a time-adaptive defrost control
system (see section 1.2 of this appendix, Definitions), however,
manually initiate the defrost cycle that ends the official test
period at the instant indicated by instructions provided by the
manufacturer. If the heat pump has not undergone a defrost after 6
hours, immediately conclude the test and use the results from the
full 6-hour period to calculate the average space heating capacity
and average electrical power consumption.
For heat pumps that turn the indoor blower off during the
defrost cycle, take steps to cease forced airflow through the indoor
coil and block the outlet duct whenever the heat pump's controls
cycle off the indoor blower. If it is installed, use the outlet
damper box described in section 2.5.4.1 of this appendix to affect
the blocked outlet duct.
d. Defrost termination occurs when the controls of the heat pump
actuate the first change in converting from defrost operation to
normal heating operation. Defrost initiation occurs when the
controls of the heat pump first alter its normal heating operation
in order to eliminate possible accumulations of frost on the outdoor
coil.
e. To constitute a valid frost accumulation test, satisfy the
test tolerances specified in Table 18 during both the preliminary
and official test periods. As noted in Table 18, test operating
tolerances are specified for two sub-intervals:
(1) When heating, except for the first 10 minutes after the
termination of a defrost cycle (sub-interval H, as described in
Table 18) and
(2) When defrosting, plus these same first 10 minutes after
defrost termination (sub-interval D, as described in Table 18).
Evaluate compliance with Table 18 test condition tolerances and the
majority of the test operating tolerances using the averages from
measurements recorded only during sub-interval H. Continuously
record the dry bulb temperature of the air entering the indoor coil,
and the dry bulb temperature and water vapor content of the air
entering the outdoor coil. Sample the remaining parameters listed in
Table 18 at equal intervals that span 5 minutes or less.
f. For the official test period, collect and use the following
data to calculate average space heating capacity and electrical
power. During heating and defrosting intervals when the controls of
the heat pump have the indoor blower on, continuously record the
[[Page 1507]]
dry-bulb temperature of the air entering (as noted above) and
leaving the indoor coil. If using a thermopile, continuously record
the difference between the leaving and entering dry-bulb
temperatures during the interval(s) that air flows through the
indoor coil. For coil-only system heat pumps, determine the
corresponding cumulative time (in hours) of indoor coil airflow,
[Delta][tau]a. Sample measurements used in calculating
the air volume rate (refer to sections 7.7.2.1 and 7.7.2.2 of ANSI/
ASHRAE 37-2009) at equal intervals that span 10 minutes or less.
(Note: In the first printing of ANSI/ASHRAE 37-2009, the second IP
equation for Qmi should read:) Record the electrical
energy consumed, expressed in watt-hours, from defrost termination
to defrost termination, eDEF\k\(35), as well as the
corresponding elapsed time in hours, [Delta][tau]FR.
Table 18--Test Operating and Test Condition Tolerances for Frost Accumulation Heating Mode Tests
----------------------------------------------------------------------------------------------------------------
Test operating tolerance \1\ Test condition
-------------------------------- tolerance \1\
Sub-interval H Sub-interval D Sub-interval
\2\ \3\ H \2\
----------------------------------------------------------------------------------------------------------------
Indoor entering dry-bulb temperature, [deg]F.................... 2.0 \4\ 4.0 0.5
Indoor entering wet-bulb temperature, [deg]F.................... 1.0 .............. ..............
Outdoor entering dry-bulb temperature, [deg]F................... 2.0 10.0 1.0
Outdoor entering wet-bulb temperature, [deg]F................... 1.5 .............. 0.5
External resistance to airflow, inches of water................. 0.05 .............. \5\ 0.02
Electrical voltage, % of rdg.................................... 2.0 .............. 1.5
----------------------------------------------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
\2\ Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a
defrost cycle.
\3\ Applies during a defrost cycle and during the first 10 minutes after the termination of a defrost cycle when
the heat pump is operating in the heating mode.
\4\ For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies
during the 10 minute interval that follows defrost termination.
\5\ Only applies when testing non-ducted heat pumps.
3.9.1 Average Space Heating Capacity and Electrical Power Calculations
a. Evaluate average space heating capacity, Qh\k\(35), when
expressed in units of Btu per hour, using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.036
Where,
Vi = the average indoor air volume rate measured during sub-interval
H, cfm.
Cp,a = 0.24 + 0.444 [middot] Wn, the constant
pressure specific heat of the air-water vapor mixture that flows
through the indoor coil and is expressed on a dry air basis, Btu/
lbmda [middot] [deg]F.
vn' = specific volume of the air-water vapor mixture at
the nozzle, ft\3\/lbmmx.
Wn = humidity ratio of the air-water vapor mixture at the
nozzle, lbm of water vapor per lbm of dry air.
[Delta][tau]FR = [tau]2 - [tau]1,
the elapsed time from defrost termination to defrost termination,
hr.
[GRAPHIC] [TIFF OMITTED] TR05JA17.312
Tal([tau]) = dry bulb temperature of the air entering the
indoor coil at elapsed time [tau], [deg]F; only recorded when indoor
coil airflow occurs; assigned the value of zero during periods (if
any) where the indoor blower cycles off.
Ta2([tau]) = dry bulb temperature of the air leaving the
indoor coil at elapsed time [tau], [deg]F; only recorded when indoor
coil airflow occurs; assigned the value of zero during periods (if
any) where the indoor blower cycles off.
[tau]1 = the elapsed time when the defrost termination
occurs that begins the official test period, hr.
[tau]2 = the elapsed time when the next automatically
occurring defrost termination occurs, thus ending the official test
period, hr.
vn = specific volume of the dry air portion of the
mixture evaluated at the dry-bulb temperature, vapor content, and
barometric pressure existing at the nozzle, ft\3\ per lbm of dry
air.
To account for the effect of duct losses between the outlet of
the indoor unit and the section 2.5.4 dry-bulb temperature grid,
adjust Qh\k\(35) in accordance with section 7.3.4.3 of ANSI/ASHRAE
37-2009 (incorporated by reference, see Sec. 430.3).
b. Evaluate average electrical power, Eh\k\(35), when expressed
in units of watts, using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.037
For coil-only system heat pumps, increase Qh\k\(35) by,
[GRAPHIC] [TIFF OMITTED] TR05JA17.038
and increase Eh\k\(35) by,
[GRAPHIC] [TIFF OMITTED] TR05JA17.039
where Vis is the average indoor air volume rate measured
during the frost accumulation heating mode test and is expressed in
units of cubic feet per minute of standard air (scfm).
c. For heat pumps having a constant-air-volume-rate indoor
blower, the five additional steps listed below are required if the
average of the external static pressures measured during sub-
interval H exceeds the applicable section 3.1.4.4, 3.1.4.5, or
3.1.4.6 minimum (or targeted) external static pressure
([Delta]Pmin) by 0.03 inches of water or more:
(1) Measure the average power consumption of the indoor blower
motor (Efan,1) and record the corresponding external
[[Page 1508]]
static pressure ([Delta]P1) during or immediately
following the frost accumulation heating mode test. Make the
measurement at a time when the heat pump is heating, except for the
first 10 minutes after the termination of a defrost cycle.
(2) After the frost accumulation heating mode test is completed
and while maintaining the same test conditions, adjust the exhaust
fan of the airflow measuring apparatus until the external static
pressure increases to approximately [Delta]P1 +
([Delta]P1 - [Delta]Pmin).
(3) After re-establishing steady readings for the fan motor
power and external static pressure, determine average values for the
indoor blower power (Efan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
(4) Approximate the average power consumption of the indoor
blower motor had the frost accumulation heating mode test been
conducted at [Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TR05JA17.040
(5) Decrease the total heating capacity, Qh\k\(35), by the
quantity [(Efan,1-Efan,min) [middot]
([Delta][tau] a/[Delta][tau] FR], when
expressed on a Btu/h basis. Decrease the total electrical power,
Eh\k\(35), by the same quantity, now expressed in watts.
3.9.2 Demand Defrost Credit
a. Assign the demand defrost credit, Fdef, that is
used in section 4.2 of this appendix to the value of 1 in all cases
except for heat pumps having a demand-defrost control system (see
section 1.2 of this appendix, Definitions). For such qualifying heat
pumps, evaluate Fdef using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.041
where:
[Delta][tau]def = the time between defrost terminations
(in hours) or 1.5, whichever is greater. A value of 6 must be
assigned to [Delta][tau]def if this limit is reached
during a frost accumulation test and the heat pump has not completed
a defrost cycle.
[Delta][tau]max = maximum time between defrosts as
allowed by the controls (in hours) or 12, whichever is less, as
provided in the certification report.
b. For two-capacity heat pumps and for section 3.6.2 units,
evaluate the above equation using the [Delta][tau]def
that applies based on the frost accumulation test conducted at high
capacity and/or at the heating full-load air volume rate. For
variable-speed heat pumps, evaluate [Delta][tau]def based
on the required frost accumulation test conducted at the
intermediate compressor speed.
3.10 Test Procedures for Steady-State Low Temperature Heating Mode
Tests (the H3, H32, and H31 Tests)
Except for the modifications noted in this section, conduct the
low temperature heating mode test using the same approach as
specified in section 3.7 of this appendix for the maximum and high
temperature tests. After satisfying the section 3.7 requirements for
the pretest interval but before beginning to collect data to
determine Qh\k\(17) and Eh\k\(17), conduct a defrost cycle. This
defrost cycle may be manually or automatically initiated. The
defrost sequence must be terminated by the action of the heat pump's
defrost controls. Begin the 30-minute data collection interval
described in section 3.7 of this appendix, from which Qh\k\(17) and
Eh\k\(17) are determined, no sooner than 10 minutes after defrost
termination. Defrosts should be prevented over the 30-minute data
collection interval.
3.11 Additional Requirements for the Secondary Test Methodst
3.11.1 If Using the Outdoor Air Enthalpy Method as the Secondary Test
Method
a. For all cooling mode and heating mode tests, first conduct a
test without the outdoor air-side test apparatus described in
section 2.10.1 of this appendix connected to the outdoor unit
(``free outdoor air'' test).
b. For the first section 3.2 steady-state cooling mode test and
the first section 3.6 steady-state heating mode test, conduct a
second test in which the outdoor-side apparatus is connected
(``ducted outdoor air'' test). No other cooling mode or heating mode
tests require the ducted outdoor air test so long as the unit
operates the outdoor fan during all cooling mode steady-state tests
at the same speed and all heating mode steady-state tests at the
same speed. If using more than one outdoor fan speed for the cooling
mode steady-state tests, however, conduct the ducted outdoor air
test for each cooling mode test where a different fan speed is first
used. This same requirement applies for the heating mode tests.
3.11.1.1 Free Outdoor Air Test
a. For the free outdoor air test, connect the indoor air-side
test apparatus to the indoor coil; do not connect the outdoor air-
side test apparatus. Allow the test room reconditioning apparatus
and the unit being tested to operate for at least one hour. After
attaining equilibrium conditions, measure the following quantities
at equal intervals that span 5 minutes or less:
(1) The section 2.10.1 evaporator and condenser temperatures or
pressures;
(2) Parameters required according to the indoor air enthalpy
method.
Continue these measurements until a 30-minute period (e.g.,
seven consecutive 5-minute samples) is obtained where the Table 9 or
Table 16, whichever applies, test tolerances are satisfied.
b. For cases where a ducted outdoor air test is not required per
section 3.11.1.b of this appendix, the free outdoor air test
constitutes the ``official'' test for which validity is not based on
comparison with a secondary test.
c. For cases where a ducted outdoor air test is required per
section 3.11.1.b of this appendix, the following conditions must be
met for the free outdoor air test to constitute a valid ``official''
test:
(1) Achieve the energy balance specified in section 3.1.1 of
this appendix for the ducted outdoor air test (i.e., compare the
capacities determined using the indoor air enthalpy method and the
outdoor air enthalpy method).
(2) The capacities determined using the indoor air enthalpy
method from the ducted outdoor air and free outdoor tests must agree
within 2 percent.
3.11.1.2 Ducted Outdoor Air Test
a. The test conditions and tolerances for the ducted outdoor air
test are the same as specified for the free outdoor air test
described in Section 3.11.1.1 of this appendix.
b. After collecting 30 minutes of steady-state data during the
free outdoor air test, connect the outdoor air-side test apparatus
to the unit for the ducted outdoor air test. Adjust the exhaust fan
of the outdoor airflow measuring apparatus until averages for the
evaporator and condenser temperatures, or the saturated temperatures
corresponding to the measured pressures, agree within 0.5 [deg]F of the averages achieved during the free outdoor
air test. Collect 30 minutes of steady-state data after re-
establishing equilibrium conditions.
c. During the ducted outdoor air test, at intervals of 5 minutes
or less, measure the parameters required according to the indoor air
enthalpy method and the outdoor air enthalpy method for the
prescribed 30 minutes.
d. For cooling mode ducted outdoor air tests, calculate capacity
based on outdoor air-enthalpy measurements as specified in sections
7.3.3.2 and 7.3.3.3 of ANSI/ASHRAE 37-2009 (incorporated by
reference, see
[[Page 1509]]
Sec. 430.3). For heating mode ducted tests, calculate heating
capacity based on outdoor air-enthalpy measurements as specified in
sections 7.3.4.2 and 7.3.3.4.3 of the same ANSI/ASHRAE Standard.
Adjust the outdoor-side capacity according to section 7.3.3.4 of
ANSI/ASHRAE 37-2009 to account for line losses when testing split
systems. As described in section 8.6.2 of ANSI/ASHRAE 37-2009, use
the outdoor air volume rate as measured during the ducted outdoor
air tests to calculate capacity for checking the agreement with the
capacity calculated using the indoor air enthalpy method.
3.11.2 If Using the Compressor Calibration Method as the Secondary Test
Method
a. Conduct separate calibration tests using a calorimeter to
determine the refrigerant flow rate. Or for cases where the
superheat of the refrigerant leaving the evaporator is less than
5[emsp14][deg]F, use the calorimeter to measure total capacity
rather than refrigerant flow rate. Conduct these calibration tests
at the same test conditions as specified for the tests in this
appendix. Operate the unit for at least one hour or until obtaining
equilibrium conditions before collecting data that will be used in
determining the average refrigerant flow rate or total capacity.
Sample the data at equal intervals that span 5 minutes or less.
Determine average flow rate or average capacity from data sampled
over a 30-minute period where the Table 9 (cooling) or the Table 16
(heating) tolerances are satisfied. Otherwise, conduct the
calibration tests according to sections 5, 6, 7, and 8 of ASHRAE
23.1-2010 (incorporated by reference, see Sec. 430.3); sections 5,
6, 7, 8, 9, and 11 of ASHRAE 41.9-2011 (incorporated by reference,
see Sec. 430.3); and section 7.4 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3).
b. Calculate space cooling and space heating capacities using
the compressor calibration method measurements as specified in
section 7.4.5 and 7.4.6 respectively, of ANSI/ASHRAE 37-2009.
3.11.3 If Using the Refrigerant-Enthalpy Method as the Secondary Test
Method
Conduct this secondary method according to section 7.5 of ANSI/
ASHRAE 37-2009. Calculate space cooling and heating capacities using
the refrigerant-enthalpy method measurements as specified in
sections 7.5.4 and 7.5.5, respectively, of the same ASHRAE Standard.
3.12 Rounding of Space Conditioning Capacities for Reporting
Purposes
a. When reporting rated capacities, round them off as specified
in Sec. 430.23 (for a single unit) and in 10 CFR 429.16 (for a
sample).
b. For the capacities used to perform the calculations in
section 4 of this appendix, however, round only to the nearest
integer.
3.13 Laboratory Testing to Determine Off Mode Average Power Ratings
Voltage tolerances: As a percentage of reading, test operating
tolerance shall be 2.0 percent and test condition tolerance shall be
1.5 percent (see section 1.2 of this appendix for definitions of
these tolerances).
Conduct one of the following tests: If the central air
conditioner or heat pump lacks a compressor crankcase heater,
perform the test in section 3.13.1 of this appendix; if the central
air conditioner or heat pump has a compressor crankcase heater that
lacks controls and is not self-regulating, perform the test in
section 3.13.1 of this appendix; if the central air conditioner or
heat pump has a crankcase heater with a fixed power input controlled
with a thermostat that measures ambient temperature and whose
sensing element temperature is not affected by the heater, perform
the test in section 3.13.1 of this appendix; if the central air
conditioner or heat pump has a compressor crankcase heater equipped
with self-regulating control or with controls for which the sensing
element temperature is affected by the heater, perform the test in
section 3.13.2 of this appendix.
3.13.1 This Test Determines the Off Mode Average Power Rating for
Central Air Conditioners and Heat Pumps That Lack a Compressor
Crankcase Heater, or Have a Compressor Crankcase Heating System That
Can Be Tested Without Control of Ambient Temperature During the Test.
This Test Has No Ambient Condition Requirements
a. Test Sample Set-up and Power Measurement: For coil-only
systems, provide a furnace or modular blower that is compatible with
the system to serve as an interface with the thermostat (if used for
the test) and to provide low-voltage control circuit power. Make all
control circuit connections between the furnace (or modular blower)
and the outdoor unit as specified by the manufacturer's installation
instructions. Measure power supplied to both the furnace or modular
blower and power supplied to the outdoor unit. Alternatively,
provide a compatible transformer to supply low-voltage control
circuit power, as described in section 2.2.d of this appendix.
Measure transformer power, either supplied to the primary winding or
supplied by the secondary winding of the transformer, and power
supplied to the outdoor unit. For blower coil and single-package
systems, make all control circuit connections between components as
specified by the manufacturer's installation instructions, and
provide power and measure power supplied to all system components.
b. Configure Controls: Configure the controls of the central air
conditioner or heat pump so that it operates as if connected to a
building thermostat that is set to the OFF position. Use a
compatible building thermostat if necessary to achieve this
configuration. For a thermostat-controlled crankcase heater with a
fixed power input, bypass the crankcase heater thermostat if
necessary to energize the heater.
c. Measure P2x: If the unit has a crankcase heater time delay,
make sure that time delay function is disabled or wait until delay
time has passed. Determine the average power from non-zero value
data measured over a 5-minute interval of the non-operating central
air conditioner or heat pump and designate the average power as P2x,
the heating season total off mode power.
d. Measure Px for coil-only split systems and for blower coil
split systems for which a furnace or a modular blower is the
designated air mover: Disconnect all low-voltage wiring for the
outdoor components and outdoor controls from the low-voltage
transformer. Determine the average power from non-zero value data
measured over a 5-minute interval of the power supplied to the
(remaining) low-voltage components of the central air conditioner or
heat pump, or low-voltage power, Px. This power measurement does not
include line power supplied to the outdoor unit. It is the line
power supplied to the air mover, or, if a compatible transformer is
used instead of an air mover, it is the line power supplied to the
transformer primary coil. If a compatible transformer is used
instead of an air mover and power output of the low-voltage
secondary circuit is measured, Px is zero.
e. Calculate P2: Set the number of compressors equal to the
unit's number of single-stage compressors plus 1.75 times the unit's
number of compressors that are not single-stage.
For single-package systems and blower coil split systems for
which the designated air mover is not a furnace or modular blower,
divide the heating season total off mode power (P2x) by the number
of compressors to calculate P2, the heating season per-compressor
off mode power. Round P2 to the nearest watt. The expression for
calculating P2 is as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.042
For coil-only split systems and blower coil split systems for
which a furnace or a modular blower is the designated air mover,
subtract the low-voltage power (Px) from the heating season total
off mode power (P2x) and divide by the number of compressors to
calculate P2, the heating season per-compressor off mode power.
Round P2 to the nearest watt. The expression for calculating P2 is
as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.043
f. Shoulder-season per-compressor off mode power, P1: If the
system does not have a crankcase heater, has a crankcase heater
without controls that is not self-regulating, or has a value for the
crankcase heater turn-on temperature (as certified in the DOE
Compliance Certification Database) that is higher than 71 [deg]F, P1
is equal to P2.
Otherwise, de-energize the crankcase heater (by removing the
thermostat bypass or otherwise disconnecting only the power supply
to the crankcase heater) and repeat the measurement as described in
section 3.13.1.c of this appendix. Designate the measured average
power as P1x, the shoulder season total off mode power.
Determine the number of compressors as described in section
3.13.1.e of this appendix.
For single-package systems and blower coil systems for which the
designated air mover is not a furnace or modular blower, divide the
shoulder season total off mode power (P1x) by the number of
compressors to calculate P1, the shoulder season per-compressor off
mode power. Round P1 to the nearest watt. The expression for
calculating P1 is as follows:
[[Page 1510]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.044
For coil-only split systems and blower coil split systems for
which a furnace or a modular blower is the designated air mover,
subtract the low-voltage power (Px) from the shoulder season total
off mode power (P1x) and divide by the number of compressors to
calculate P1, the shoulder season per-compressor off mode power.
Round P1 to the nearest watt. The expression for calculating P1 is
as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.045
3.13.2 This Test Determines the Off Mode Average Power Rating for
Central Air Conditioners and Heat Pumps for Which Ambient Temperature
Can Affect the Measurement of Crankcase Heater Power
a. Test Sample Set-up and Power Measurement: Set up the test and
measurement as described in section 3.13.1.a of this appendix.
b. Configure Controls: Position a temperature sensor to measure
the outdoor dry-bulb temperature in the air between 2 and 6 inches
from the crankcase heater control temperature sensor or, if no such
temperature sensor exists, position it in the air between 2 and 6
inches from the crankcase heater. Utilize the temperature
measurements from this sensor for this portion of the test
procedure. Configure the controls of the central air conditioner or
heat pump so that it operates as if connected to a building
thermostat that is set to the OFF position. Use a compatible
building thermostat if necessary to achieve this configuration.
Conduct the test after completion of the B, B1, or
B2 test. Alternatively, start the test when the outdoor
dry-bulb temperature is at 82 [deg]F and the temperature of the
compressor shell (or temperature of each compressor's shell if there
is more than one compressor) is at least 81 [deg]F. Then adjust the
outdoor temperature at a rate of change of no more than 20 [deg]F
per hour and achieve an outdoor dry-bulb temperature of 72 [deg]F.
Maintain this temperature within 2 [deg]F while making
the power measurement, as described in section 3.13.2.c of this
appendix.
c. Measure P1x: If the unit has a crankcase heater time delay,
make sure that time delay function is disabled or wait until delay
time has passed. Determine the average power from non-zero value
data measured over a 5-minute interval of the non-operating central
air conditioner or heat pump and designate the average power as P1x,
the shoulder season total off mode power. For units with crankcase
heaters which operate during this part of the test and whose
controls cycle or vary crankcase heater power over time, the test
period shall consist of three complete crankcase heater cycles or 18
hours, whichever comes first. Designate the average power over the
test period as P1x, the shoulder season total off mode power.
d. Reduce outdoor temperature: Approach the target outdoor dry-
bulb temperature by adjusting the outdoor temperature at a rate of
change of no more than 20 [deg]F per hour. This target temperature
is five degrees Fahrenheit less than the temperature specified by
the manufacturer in the DOE Compliance Certification Database at
which the crankcase heater turns on. Maintain the target temperature
within 2 [deg]F while making the power measurement, as
described in section 3.13.2.e of this appendix.
e. Measure P2x: If the unit has a crankcase heater time delay,
make sure that time delay function is disabled or wait until delay
time has passed. Determine the average non-zero power of the non-
operating central air conditioner or heat pump over a 5-minute
interval and designate it as P2x, the heating season total off mode
power. For units with crankcase heaters whose controls cycle or vary
crankcase heater power over time, the test period shall consist of
three complete crankcase heater cycles or 18 hours, whichever comes
first. Designate the average power over the test period as P2x, the
heating season total off mode power.
f. Measure Px for coil-only split systems and for blower coil
split systems for which a furnace or modular blower is the
designated air mover: Disconnect all low-voltage wiring for the
outdoor components and outdoor controls from the low-voltage
transformer. Determine the average power from non-zero value data
measured over a 5-minute interval of the power supplied to the
(remaining) low-voltage components of the central air conditioner or
heat pump, or low-voltage power, Px.. This power measurement does
not include line power supplied to the outdoor unit. It is the line
power supplied to the air mover, or, if a compatible transformer is
used instead of an air mover, it is the line power supplied to the
transformer primary coil. If a compatible transformer is used
instead of an air mover and power output of the low-voltage
secondary circuit is measured, Px is zero.
g. Calculate P1:
Set the number of compressors equal to the unit's number of
single-stage compressors plus 1.75 times the unit's number of
compressors that are not single-stage.
For single-package systems and blower coil split systems for
which the air mover is not a furnace or modular blower, divide the
shoulder season total off mode power (P1x) by the number of
compressors to calculate P1, the shoulder season per-compressor off
mode power. Round to the nearest watt. The expression for
calculating P1 is as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.046
For coil-only split systems and blower coil split systems for
which a furnace or a modular blower is the designated air mover,
subtract the low-voltage power (Px) from the shoulder season total
off mode power (P1x) and divide by the number of compressors to
calculate P1, the shoulder season per-compressor off mode power.
Round to the nearest watt. The expression for calculating P1 is as
follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.047
h. Calculate P2:
Determine the number of compressors as described in section
3.13.2.g of this appendix.
For single-package systems and blower coil split systems for
which the air mover is not a furnace, divide the heating season
total off mode power (P2x) by the number of compressors to calculate
P2, the heating season per-compressor off mode power. Round to the
nearest watt. The expression for calculating P2 is as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.048
For coil-only split systems and blower coil split systems for
which a furnace or a modular blower is the designated air mover,
subtract the low-voltage power (Px) from the heating season total
off mode power (P2x) and divide by the number of compressors to
calculate P2, the heating season per-compressor off mode power.
Round to the nearest watt. The expression for calculating P2 is as
follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.049
4. Calculations of Seasonal Performance Descriptors
4.1 Seasonal Energy Efficiency Ratio (SEER) Calculations. SEER must
be calculated as follows: For equipment covered under sections
4.1.2, 4.1.3, and 4.1.4 of this appendix, evaluate the seasonal
energy efficiency ratio,
[GRAPHIC] [TIFF OMITTED] TR05JA17.050
[[Page 1511]]
where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.051
Tj = the outdoor bin temperature, [deg]F. Outdoor
temperatures are grouped or ``binned.'' Use bins of 5 [deg]F with
the 8 cooling season bin temperatures being 67, 72, 77, 82, 87, 92,
97, and 102 [deg]F.
j = the bin number. For cooling season calculations, j ranges from 1
to 8.
Additionally, for sections 4.1.2, 4.1.3, and 4.1.4 of this
appendix, use a building cooling load, BL(Tj). When
referenced, evaluate BL(Tj) for cooling using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.052
where:
Qck=2(95) = the space cooling capacity
determined from the A2 test and calculated as specified
in section 3.3 of this appendix, Btu/h.
1.1 = sizing factor, dimensionless.
The temperatures 95 [deg]F and 65 [deg]F in the building load
equation represent the selected outdoor design temperature and the
zero-load base temperature, respectively.
4.1.1 SEER Calculations for a Blower Coil System Having a Single-Speed
Compressor and Either a Fixed-Speed Indoor Blower or a Constant-Air-
Volume-Rate Indoor Blower, or a Coil-Only System Air Conditioner or
Heat Pump
a. Evaluate the seasonal energy efficiency ratio, expressed in
units of Btu/watt-hour, using:
SEER = PLF(0.5) * EERB
where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.053
PLF(0.5) = 1 - 0.5 [middot] CD\c\, the part-load
performance factor evaluated at a cooling load factor of 0.5,
dimensionless.
b. Refer to section 3.3 of this appendix regarding the
definition and calculation of Qc(82) and
Ec(82). Evaluate the cooling mode cyclic degradation
factor CD\c\ as specified in section 3.5.3 of this
appendix.
4.1.2 SEER Calculations for an Air Conditioner or Heat Pump Having a
Single-Speed Compressor and a Variable-Speed Variable-Air-Volume-Rate
Indoor Blower
4.1.2.1 Units Covered by Section 3.2.2.1 of This Appendix Where Indoor
Blower Capacity Modulation Correlates With the Outdoor Dry Bulb
Temperature
The manufacturer must provide information on how the indoor air
volume rate or the indoor blower speed varies over the outdoor
temperature range of 67[emsp14][deg]F to 102[emsp14][deg]F.
Calculate SEER using Equation 4.1-1. Evaluate the quantity
qc(Tj)/N in Equation 4.1-1 using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.054
where:
[[Page 1512]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.055
Qc(Tj) = the space cooling capacity of the
test unit when operating at outdoor temperature, Tj, Btu/
h.
nj/N = fractional bin hours for the cooling season; the
ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless.
a. For the space cooling season, assign nj/N as
specified in Table 19. Use Equation 4.1-2 to calculate the building
load, BL(Tj). Evaluate Qc(Tj)
using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.056
where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.057
the space cooling capacity of the test unit at outdoor temperature
Tj if operated at the cooling minimum air volume rate,
Btu/h.
[GRAPHIC] [TIFF OMITTED] TR05JA17.058
the space cooling capacity of the test unit at outdoor temperature
Tj if operated at the Cooling full-load air volume rate,
Btu/h.
b. For units where indoor blower speed is the primary control
variable, FPc\k=1\ denotes the fan speed used during the
required A1 and B1 tests (see section 3.2.2.1
of this appendix), FPck=2 denotes the fan speed used
during the required A2 and B2 tests, and
FPc(Tj) denotes the fan speed used by the unit
when the outdoor temperature equals Tj. For units where
indoor air volume rate is the primary control variable, the three
FPc's are similarly defined only now being expressed in
terms of air volume rates rather than fan speeds. Refer to sections
3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 of this appendix regarding the
definitions and calculations of Qc\k=1\(82),
Qc\k=1\(95), Qck=2(82), and
Qck=2(95).
[GRAPHIC] [TIFF OMITTED] TR05JA17.059
where:
PLFj = 1 - CD\c\ [middot] [1 -
X(Tj)], the part load factor, dimensionless.
Ec(Tj) = the electrical power consumption of
the test unit when operating at outdoor temperature Tj,
W.
c. The quantities X(Tj) and nj/N are the
same quantities as used in Equation 4.1.2-1. Evaluate the cooling
mode cyclic degradation factor CD\c\ as specified in
section 3.5.3 of this appendix.
d. Evaluate Ec(Tj) using,
[[Page 1513]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.060
e. The parameters FPc\k=1\, and FPck=2,
and FPc(Tj) are the same quantities that are
used when evaluating Equation 4.1.2-2. Refer to sections 3.2.2.1,
3.1.4 to 3.1.4.2, and 3.3 of this appendix regarding the definitions
and calculations of Ec\k=1\(82), Ec\k=1\(95),
Eck=2(82), and Eck=2(95).
4.1.2.2 Units Covered by Section 3.2.2.2 of This Appendix Where
Indoor Blower Capacity Modulation Is Used To Adjust the Sensible to
Total Cooling Capacity Ratio. Calculate SEER as specified in section
4.1.1 of this appendix.
4.1.3 SEER Calculations for an Air Conditioner or Heat Pump Having a
Two-Capacity Compressor
Calculate SEER using Equation 4.1-1. Evaluate the space cooling
capacity, Qc\k=1\ (Tj), and electrical power
consumption, Ec\k=1\ (Tj), of the test unit
when operating at low compressor capacity and outdoor temperature
Tj using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.061
[GRAPHIC] [TIFF OMITTED] TR05JA17.062
where Qc\k=1\ (82) and Ec\k=1\ (82) are
determined from the B1 test, Qc\k=1\ (67) and
Ec\k=1\ (67) are determined from the F1 test,
and all four quantities are calculated as specified in section 3.3
of this appendix. Evaluate the space cooling capacity,
Qck=2 (Tj), and electrical power consumption,
Eck=2 (Tj), of the test unit when operating at
high compressor capacity and outdoor temperature Tj
using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.063
[GRAPHIC] [TIFF OMITTED] TR05JA17.064
where Qck=2(95) and Eck=2(95) are determined
from the A2 test, Qck=2(82), and
Eck=2(82), are determined from the B2test, and
all are calculated as specified in section 3.3 of this appendix.
The calculation of Equation 4.1-1 quantities
qc(Tj)/N and ec(Tj)/N
differs depending on whether the test unit would operate at low
capacity (section 4.1.3.1 of this appendix), cycle between low and
high capacity (section 4.1.3.2 of this appendix), or operate at high
capacity (sections 4.1.3.3 and 4.1.3.4 of this appendix) in
responding to the building load. For units that lock out low
capacity operation at higher outdoor temperatures, the outdoor
temperature at which the unit locks out must be that specified by
the manufacturer in the certification report so that the appropriate
equations are used. Use Equation 4.1-2 to calculate the building
load, BL(Tj), for each temperature bin.
4.1.3.1 Steady-State Space Cooling Capacity at Low Compressor Capacity
Is Greater Than or Equal to the Building Cooling Load at Temperature
Tj, Qc\k=1\(Tj) >=BL(Tj)
[[Page 1514]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.065
where:
X\k=1\(Tj) = BL(Tj)/
Qc\k=1\(Tj), the cooling mode low capacity
load factor for temperature bin j, dimensionless.
PLFj = 1 - CD\c\ [middot] [1 -
X\k=1\(Tj)], the part load factor, dimensionless.
[GRAPHIC] [TIFF OMITTED] TR05JA17.066
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qc\k=1\(Tj) and
Ec\k=1\(Tj). Evaluate the cooling mode cyclic
degradation factor CD\c\ as specified in section 3.5.3 of
this appendix.
Table 19--Distribution of Fractional Hours Within Cooling Season Temperature Bins
----------------------------------------------------------------------------------------------------------------
Fraction of of
Bin Representative total
Bin number, j temperature temperature temperature
range [deg]F for bin [deg]F bin hours, nj/
N
----------------------------------------------------------------------------------------------------------------
1............................................................... 65-69 67 0.214
2............................................................... 70-74 72 0.231
3............................................................... 75-79 77 0.216
4............................................................... 80-84 82 0.161
5............................................................... 85-89 87 0.104
6............................................................... 90-94 92 0.052
7............................................................... 95-99 97 0.018
8............................................................... 100-104 102 0.004
----------------------------------------------------------------------------------------------------------------
4.1.3.2 Unit Alternates Between High (k=2) and Low (k=1) Compressor
Capacity To Satisfy the Building Cooling Load at Temperature
Tj, Qc\k=1\(Tj) BL(Tj)
Qck=2(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.067
[GRAPHIC] [TIFF OMITTED] TR05JA17.068
[[Page 1515]]
Xk=2(Tj) = 1 - X\k=1\(Tj), the cooling mode,
high capacity load factor for temperature bin j, dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qc\k=1\(Tj) and
Ec\k=1\(Tj). Use Equations 4.1.3-3 and 4.1.3-
4, respectively, to evaluate Qck=2(Tj) and
Eck=2(Tj).
4.1.3.3 Unit Only Operates at High (k=2) Compressor Capacity at
Temperature Tj and Its Capacity Is Greater Than the Building
Cooling Load, BL(Tj) Qck=2(Tj). This
section applies to units that lock out low compressor capacity
operation at higher outdoor temperatures.
[GRAPHIC] [TIFF OMITTED] TR05JA17.069
where:
Xk=2(Tj) = BL(Tj)/
Qck=2(Tj), the cooling mode high capacity load
factor for temperature bin j, dimensionless.
PLFj = 1 - CDc(k = 2) * [1 - Xk=2(Tj) the part
load factor, dimensionless.
[GRAPHIC] [TIFF OMITTED] TR05JA17.070
4.1.3.4 Unit Must Operate Continuously at High (k=2) Compressor
Capacity at Temperature Tj, BL(Tj)
>=Qck=2(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.071
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. Use Equations 4.1.3-3 and 4.1.3-4,
respectively, to evaluate Qck=2(Tj) and
Eck=2(Tj).
4.1.4 SEER Calculations for an Air Conditioner or Heat Pump Having a
Variable-Speed Compressor
Calculate SEER using Equation 4.1-1. Evaluate the space cooling
capacity, Qc\k=1\(Tj), and electrical power
consumption, Ec\k=1\(Tj), of the test unit
when operating at minimum compressor speed and outdoor temperature
Tj. Use,
[GRAPHIC] [TIFF OMITTED] TR05JA17.072
[GRAPHIC] [TIFF OMITTED] TR05JA17.073
where Qc\k=1\(82) and Ec\k=1\(82) are
determined from the B1 test, Qc\k=1\(67) and
Ec\k=1\(67) are determined from the F1 test, and all four
quantities are calculated as specified in section 3.3 of this
appendix.
Evaluate the space cooling capacity,
Qck=2(Tj), and electrical power consumption,
Eck=2(Tj), of the test unit when operating at
full compressor speed and outdoor temperature Tj. Use
Equations 4.1.3-3 and 4.1.3-4, respectively, where
Qck=2(95) and Eck=2(95) are determined from
the A2 test, Qck=2(82) and
Eck=2(82) are determined from the B2 test, and
all four quantities are calculated as specified in section 3.3 of
this appendix. Calculate the space cooling capacity,
Qc\k=v\(Tj), and electrical power consumption,
Ec\k=v\(Tj), of the test unit when operating
at outdoor temperature Tj and the intermediate compressor
speed used during the section 3.2.4 (and Table 8) EV test
of this appendix using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.074
[GRAPHIC] [TIFF OMITTED] TR05JA17.075
[[Page 1516]]
where Qc\k=v\(87) and Ec\k=v\(87) are
determined from the EV test and calculated as specified
in section 3.3 of this appendix. Approximate the slopes of the k=v
intermediate speed cooling capacity and electrical power input
curves, MQ and ME, as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.076
Use Equations 4.1.4-1 and 4.1.4-2, respectively, to calculate
Qc\k=1\(87) and Ec\k=1\(87).
4.1.4.1 Steady-State Space Cooling Capacity When Operating at Minimum
Compressor Speed Is Greater Than or Equal to the Building Cooling Load
at Temperature Tj, Qc\k=1\(Tj)
>=BL(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.077
where:
X\k=1\(Tj) = BL(Tj)/
Qc\k=1\(Tj), the cooling mode minimum speed
load factor for temperature bin j, dimensionless.
PLFj = 1 - CD\c\ [middot] [1 -
X\k=1\(Tj)], the part load factor, dimensionless.
nj/N = fractional bin hours for the cooling season; the
ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qc\k=l\ (Tj) and
Ec\k=l\ (Tj). Evaluate the cooling mode cyclic
degradation factor CD\c\ as specified in section 3.5.3 of
this appendix.
4.1.4.2 Unit Operates at an Intermediate Compressor Speed (k=i) In
Order To Match the Building Cooling Load at Temperature
Tj,Qc\k=1\(Tj) BL(Tj)
Qck=2(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.078
where:
Qc\k=i\(Tj) = BL(Tj), the space
cooling capacity delivered by the unit in matching the building load
at temperature Tj, Btu/h. The matching occurs with the
unit operating at compressor speed k = i.
[GRAPHIC] [TIFF OMITTED] TR05JA17.079
EER\k=i\(Tj) = the steady-state energy efficiency ratio
of the test unit when operating at a compressor speed of k = i and
temperature Tj, Btu/h per W.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. For each temperature bin where the
unit operates at an intermediate compressor speed, determine the
energy efficiency ratio EER\k=i\(Tj) using,
EER\k=i\(Tj) = A + B [middot] Tj + C
[middot] Tj\2\.
For each unit, determine the coefficients A, B, and C by
conducting the following calculations once:
[GRAPHIC] [TIFF OMITTED] TR05JA17.080
[[Page 1517]]
where:
T1 = the outdoor temperature at which the unit, when
operating at minimum compressor speed, provides a space cooling
capacity that is equal to the building load
(Qck=l(Tl) = BL(T1)),
[deg]F. Determine T1 by equating Equations 4.1.3-1 and
4.1-2 and solving for outdoor temperature.
Tv = the outdoor temperature at which the unit, when
operating at the intermediate compressor speed used during the
section 3.2.4 EV test of this appendix, provides a space
cooling capacity that is equal to the building load
(Qck=v(Tv) = BL(Tv)),
[deg]F. Determine Tv by equating Equations 4.1.4-3 and
4.1-2 and solving for outdoor temperature.
T2 = the outdoor temperature at which the unit, when
operating at full compressor speed, provides a space cooling
capacity that is equal to the building load
(Qck=2(T2) = BL(T2)),
[deg]F. Determine T2 by equating Equations 4.1.3-3 and
4.1-2 and solving for outdoor temperature.
[GRAPHIC] [TIFF OMITTED] TR05JA17.081
4.1.4.3 Unit Must Operate Continuously at Full (k=2) Compressor Speed
at Temperature Tj, BL(Tj)
>=Qck=2(Tj). Evaluate the Equation
4.1-1 Quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.082
as specified in section 4.1.3.4 of this appendix with the
understanding that Qck=2(Tj) and
Eck=2(Tj) correspond to full
compressor speed operation and are derived from the results of the
tests specified in section 3.2.4 of this appendix.
4.1.5 SEER Calculations for an Air Conditioner or Heat Pump Having a
Single Indoor Unit With Multiple Indoor Blowers
Calculate SEER using Eq. 4.1-1, where qc(Tj)/N and
ec(Tj)/N are evaluated as specified in the applicable
subsection.
4.1.5.1 For Multiple Indoor Blower Systems That Are Connected to a
Single, Single-Speed Outdoor Unit
a. Calculate the space cooling capacity, Qck=1(Tj),
and electrical power consumption, Eck=1(Tj), of the test
unit when operating at the cooling minimum air volume rate and
outdoor temperature Tj using the equations given in
section 4.1.2.1 of this appendix. Calculate the space cooling
capacity, Qck=2(Tj), and electrical power consumption,
Eck=2(Tj), of the test unit when operating at the cooling
full-load air volume rate and outdoor temperature Tj
using the equations given in section 4.1.2.1 of this appendix. In
evaluating the section 4.1.2.1 equations, determine the quantities
Qck=1(82) and Eck=1(82) from the B1 test,
Qck=1(95) and Eck=1(95) from the Al test,
Qck=2(82) and Eck=2(82) from the B2 test,
andQck=2(95) and Eck=2(95) from the A2 test.
Evaluate all eight quantities as specified in section 3.3 of this
appendix. Refer to section 3.2.2.1 and Table 6 of this appendix for
additional information on the four referenced laboratory tests.
b. Determine the cooling mode cyclic degradation coefficient,
CDc, as per sections 3.2.2.1 and 3.5 to 3.5.3 of this
appendix. Assign this same value to CDc(K=2).
c. Except for using the above values of Qck=1(Tj),
Eck=1(Tj), Eck=2(Tj), Qck=2(Tj),
CDc, and CDc (K=2), calculate the quantities
qc(Tj)/N and ec(Tj)/N as
specified in section 4.1.3.1 of this appendix for cases where
Qck=1(Tj) >=BL(Tj). For all other outdoor bin
temperatures, Tj, calculate qc(Tj)/N and
ec(Tj)/N as specified in section 4.1.3.3 of this appendix
if Qck=2(Tj) >BL (Tj) or as specified in
section 4.1.3.4 of this appendix if Qck=2(Tj)
<=BL(Tj).
4.1.5.2 Unit Operates at an Intermediate Compressor Speed (k=i) In
Order To Match the Building Cooling Load at Temperature
Tj,Qck=1(Tj)
j) ck=2(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.083
where,
Qck=i(Tj) = BL(Tj), the
space cooling capacity delivered by the unit in matching the
building load at temperature Tj, Btu/h. The matching
occurs with the unit operating at compressor speed k = i.
[GRAPHIC] [TIFF OMITTED] TR05JA17.084
[[Page 1518]]
EERk=i(Tj), the steady-state energy efficiency
ratio of the test unit when operating at a compressor speed of k = i
and temperature Tj, Btu/h per W.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. For each temperature bin where the
unit operates at an intermediate compressor speed, determine the
energy efficiency ratio EERk=i(Tj) using the
following equations,
For each temperature bin where
Qck=1(Tj) j)
ck=v(Tj),
[GRAPHIC] [TIFF OMITTED] TR05JA17.085
For each temperature bin where
Qck=v(Tj) <=BL(Tj)
ck=2(Tj),
[GRAPHIC] [TIFF OMITTED] TR05JA17.086
Where:
EERk=1(Tj) is the steady-state energy
efficiency ratio of the test unit when operating at minimum
compressor speed and temperature Tj, Btu/h per W, calculated using
capacity Qck=1(Tj) calculated using
Equation 4.1.4-1 and electrical power consumption
Eck=1(Tj) calculated using Equation
4.1.4-2;
EERk=v(Tj) is the steady-state
energy efficiency ratio of the test unit when operating at
intermediate compressor speed and temperature Tj, Btu/h per W,
calculated using capacity Qck=v(Tj)
calculated using Equation 4.1.4-3 and electrical power consumption
Eck=v(Tj) calculated using Equation
4.1.4-4;
EERk=2(Tj) is the steady-state energy
efficiency ratio of the test unit when operating at full compressor
speed and temperature Tj, Btu/h per W, calculated using capacity
Qck=2(Tj) and electrical power
consumption Eck=2(Tj), both
calculated as described in section 4.1.4; and
BL(Tj) is the building cooling load at temperature
Tj, Btu/h.
4.2 Heating Seasonal Performance Factor (HSPF) Calculations
Unless an approved alternative efficiency determination method
is used, as set forth in 10 CFR 429.70(e), HSPF must be calculated
as follows: Six generalized climatic regions are depicted in Figure
1 and otherwise defined in Table 20. For each of these regions and
for each applicable standardized design heating requirement,
evaluate the heating seasonal performance factor using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.087
where:
e2(Tj)/N = The ratio of the electrical energy consumed by
the heat pump during periods of the space heating season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
heating season (N), W. For heat pumps having a heat comfort
controller, this ratio may also include electrical energy used by
resistive elements to maintain a minimum air delivery temperature
(see 4.2.5).
RH(Tj)/N = The ratio of the electrical energy used for
resistive space heating during periods when the outdoor temperature
fell within the range represented by bin temperature Tj
to the total number of hours in the heating season (N), W. Except as
noted in section 4.2.5 of this appendix, resistive space heating is
modeled as being used to meet that portion of the building load that
the heat pump does not meet because of insufficient capacity or
because the heat pump automatically turns off at the lowest outdoor
temperatures. For heat pumps having a heat comfort controller, all
or part of the electrical energy used by resistive heaters at a
particular bin temperature may be reflected in eh(Tj)/N
(see section 4.2.5 of this appendix).
Tj = the outdoor bin temperature, [deg]F. Outdoor
temperatures are ``binned'' such that calculations are only
performed based one temperature within the bin. Bins of 5 [deg]F are
used.
nj/N= Fractional bin hours for the heating season; the
ratio of the number of hours during the heating season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
heating season, dimensionless. Obtain nj/N values from
Table 20.
j = the bin number, dimensionless.
J = for each generalized climatic region, the total number of
temperature bins, dimensionless. Referring to Table 20, J is the
highest bin number (j) having a nonzero entry for the fractional bin
hours for the generalized climatic region of interest.
Fdef = the demand defrost credit described in section
3.9.2 of this appendix, dimensionless.
BL(Tj) = the building space conditioning load
corresponding to an outdoor temperature of Tj; the
heating season building load also depends on the generalized
climatic region's outdoor design temperature and the design heating
requirement, Btu/h.
Table 20--Generalized Climatic Region Information
----------------------------------------------------------------------------------------------------------------
Region No.
-----------------------------------------------------------------------------
I II III IV V VI
----------------------------------------------------------------------------------------------------------------
Heating Load Hours, HLH........... 750 1,250 1,750 2,250 2,750 *2,750
Outdoor Design Temperature, TOD... 37 27 17 5 -10 30
----------------------------------------------------------------------------------------------------------------
[[Page 1519]]
j Tj ([deg]F) Fractional Bin Hours, nj/N
----------------------------------------------------------------------------------------------------------------
1 62.............................. .291 .215 .153 .132 .106 .113
2 57.............................. .239 .189 .142 .111 .092 .206
3 52.............................. .194 .163 .138 .103 .086 .215
4 47.............................. .129 .143 .137 .093 .076 .204
5 42.............................. .081 .112 .135 .100 .078 .141
6 37.............................. .041 .088 .118 .109 .087 .076
7 32.............................. .019 .056 .092 .126 .102 .034
8 27.............................. .005 .024 .047 .087 .094 .008
9 22.............................. .001 .008 .021 .055 .074 .003
10 17............................. 0 .002 .009 .036 .055 0
11 12............................. 0 0 .005 .026 .047 0
12 7.............................. 0 0 .002 .013 .038 0
13 2.............................. 0 0 .001 .006 .029 0
14 -3............................. 0 0 0 .002 .018 0
15 -8............................. 0 0 0 .001 .010 0
16 -13............................ 0 0 0 0 .005 0
17 -18............................ 0 0 0 0 .002 0
18 -23............................ 0 0 0 0 .001 0
----------------------------------------------------------------------------------------------------------------
* Pacific Coast Region.
Evaluate the building heating load using
[GRAPHIC] [TIFF OMITTED] TR05JA17.088
Where:
TOD = the outdoor design temperature, [deg]F. An outdoor
design temperature is specified for each generalized climatic region
in Table 20.
C = 0.77, a correction factor which tends to improve the agreement
between calculated and measured building loads, dimensionless.
DHR = the design heating requirement (see section 1.2 of this
appendix, Definitions), Btu/h.
Calculate the minimum and maximum design heating requirements
for each generalized climatic region as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.089
where Qh\k\(47) is expressed in units of Btu/h and otherwise defined
as follows:
a. For a single-speed heat pump tested as per section 3.6.1 of
this appendix, Qh\k\(47) = Qh(47), the space heating capacity
determined from the H1 test.
b. For a section 3.6.2 single-speed heat pump or a two-capacity
heat pump not covered by item d, Qh\k\(47) = Qhk=2(47), the space
heating capacity determined from the H1 or H12 test.
c. For a variable-speed heat pump, Qh\k\(47) = Qhk=N(47), the
space heating capacity determined from the H1N test.
d. For two-capacity, northern heat pumps (see section 1.2 of
this appendix, Definitions), Q\k\h(47) = Q\k=1\h(47), the space
heating capacity determined from the H11 test.
For all heat pumps, HSPF accounts for the heating delivered and
the energy consumed by auxiliary resistive elements when operating
below the balance point. This condition occurs when the building
load exceeds the space heating capacity of the heat pump condenser.
For HSPF calculations
[[Page 1520]]
for all heat pumps, see either section 4.2.1, 4.2.2, 4.2.3, or 4.2.4
of this appendix, whichever applies.
For heat pumps with heat comfort controllers (see section 1.2 of
this appendix, Definitions), HSPF also accounts for resistive
heating contributed when operating above the heat-pump-plus-comfort-
controller balance point as a result of maintaining a minimum supply
temperature. For heat pumps having a heat comfort controller, see
section 4.2.5 of this appendix for the additional steps required for
calculating the HSPF.
Table 21--Standardized Design Heating Requirements
[Btu/h]
------------------------------------------------------------------------
-------------------------------------------------------------------------
5,000
10,000
15,000
20,000
25,000
30,000
35,000
40,000
50,000
60,000
70,000
80,000
90,000
100,000
110,000
130,000
------------------------------------------------------------------------
4.2.1 Additional Steps for Calculating the HSPF of a Blower Coil System
Heat Pump Having a Single-Speed Compressor and Either a Fixed-Speed
Indoor Blower or a Constant-Air-Volume-Rate Indoor Blower Installed, or
a Coil-Only System Heat Pump
[GRAPHIC] [TIFF OMITTED] TR05JA17.090
[GRAPHIC] [TIFF OMITTED] TR05JA17.091
Where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.092
whichever is less; the heating mode load factor for temperature bin
j, dimensionless.
Qh(Tj) = the space heating capacity of the heat pump when
operating at outdoor temperature Tj, Btu/h.
Eh(Tj) = the electrical power consumption of the heat
pump when operating at outdoor temperature Tj, W.
[delta](Tj) = the heat pump low temperature cut-out
factor, dimensionless.
PLFj = 1 - CD\h\ [middot] [1 -
X(Tj)] the part load factor, dimensionless.
Use Equation 4.2-2 to determine BL(Tj). Obtain
fractional bin hours for the heating season, nj/N, from
Table 20. Evaluate the heating mode cyclic degradation factor
CD\h\ as specified in section 3.8.1 of this appendix.
Determine the low temperature cut-out factor using
[GRAPHIC] [TIFF OMITTED] TR05JA17.093
Where:
Toff = the outdoor temperature when the compressor is
automatically shut off, [deg]F. (If no such temperature exists,
Tj is always greater than Toff and
Ton).
Ton = the outdoor temperature when the compressor is
automatically turned back on, if applicable, following an automatic
shut-off, [deg]F.
Calculate Qh(Tj) and Eh(Tj) using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.094
[[Page 1521]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.095
where Qh(47) and Eh(47) are determined from the H1 test and
calculated as specified in section 3.7 of this appendix; Qh(35) and
Eh(35) are determined from the H2 test and calculated as specified
in section 3.9.1 of this appendix; and Qh(17) and Eh(17) are
determined from the H3 test and calculated as specified in section
3.10 of this appendix.
4.2.2 Additional Steps for Calculating the HSPF of a Heat Pump Having a
Single-Speed Compressor and a Variable-Speed, Variable-Air-Volume-Rate
Indoor Blower
The manufacturer must provide information about how the indoor
air volume rate or the indoor blower speed varies over the outdoor
temperature range of 65[emsp14][deg]F to -23[emsp14][deg]F.
Calculate the quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.096
in Equation 4.2-1 as specified in section 4.2.1 of this appendix
with the exception of replacing references to the H1C test and
section 3.6.1 of this appendix with the H1C1 test and
section 3.6.2 of this appendix. In addition, evaluate the space
heating capacity and electrical power consumption of the heat pump
Qh(Tj) and Eh(Tj) using
[GRAPHIC] [TIFF OMITTED] TR05JA17.097
[GRAPHIC] [TIFF OMITTED] TR05JA17.098
where the space heating capacity and electrical power consumption at
both low capacity (k=1) and high capacity (k=2) at outdoor
temperature Tj are determined using
[GRAPHIC] [TIFF OMITTED] TR05JA17.099
[GRAPHIC] [TIFF OMITTED] TR05JA17.100
For units where indoor blower speed is the primary control
variable, FPhk=1 denotes the fan speed used during the required
H11 and H31 tests (see Table 12), FPhk=2
denotes the fan speed used during the required H12,
H22, and H32 tests, and FPh(Tj)
denotes the fan speed used by the unit when the outdoor temperature
equals Tj. For units where indoor air volume rate is the
primary control variable, the three FPh's are similarly defined only
now being expressed in terms of air volume rates rather than fan
speeds. Determine Qhk=1(47) and Ehk=1(47) from the H11
test, and Qhk=2(47) and Ehk=2(47) from the H12 test.
Calculate all four quantities as specified in section 3.7 of this
appendix. Determine Qhk=1(35) and Ehk=1(35) as specified in section
3.6.2 of this appendix; determine Qhk=2(35) and Ehk=2(35) and from
the H22 test and the calculation specified in section 3.9
of this appendix. Determine Qhk=1(17) and Ehk=1(17) from the
H31 test, and Qhk=2(17) and Ehk=2(17) from the
H32 test. Calculate all four quantities as specified in
section 3.10 of this appendix.
[[Page 1522]]
4.2.3 Additional Steps for Calculating the HSPF of a Heat Pump Having a
Two-Capacity Compressor
The calculation of the Equation 4.2-1 quantities differ
depending upon whether the heat pump would operate at low capacity
(section 4.2.3.1 of this appendix), cycle between low and high
capacity (section 4.2.3.2 of this appendix), or operate at high
capacity (sections 4.2.3.3 and 4.2.3.4 of this appendix) in
responding to the building load. For heat pumps that lock out low
capacity operation at low outdoor temperatures, the outdoor
temperature at which the unit locks out must be that specified by
the manufacturer in the certification report so that the appropriate
equations can be selected.
[GRAPHIC] [TIFF OMITTED] TR05JA17.101
a. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at low compressor
capacity and outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TR05JA17.102
b. Evaluate the space heating capacity and electrical power
consumption (Qhk=2(Tj) and Ehk=2 (Tj)) of the
heat pump when operating at high compressor capacity and outdoor
temperature Tj by solving Equations 4.2.2-3 and 4.2.2-4,
respectively, for k=2. Determine Qhk=1(62) and Ehk=1(62) from the
H01 test, Qhk=1(47) and Ehk=1(47) from the H11
test, and Qhk=2(47) and Ehk=2(47) from the H12 test.
Calculate all six quantities as specified in section 3.7 of this
appendix. Determine Qhk=2(35) and Ehk=2(35) from the H22
test and, if required as described in section 3.6.3 of this
appendix, determine Qhk=1(35) and Ehk=1(35) from the H21
test. Calculate the required 35[emsp14][deg]F quantities as
specified in section 3.9 of this appendix. Determine Qhk=2(17) and
Ehk=2(17) from the H32 test and, if required as described
in section 3.6.3 of this appendix, determine Qhk=1(17) and Ehk=1(17)
from the H31 test. Calculate the required
17[emsp14][deg]F quantities as specified in section 3.10 of this
appendix.
4.2.3.1 Steady-State Space Heating Capacity When Operating at Low
Compressor Capacity is Greater Than or Equal to the Building Heating
Load at Temperature Tj, Qhk=1(Tj)
>=BL(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.103
[GRAPHIC] [TIFF OMITTED] TR05JA17.104
Where:
Xk=1(Tj) = BL(Tj)/Qhk=1(Tj), the
heating mode low capacity load factor for temperature bin j,
dimensionless.
PLFj = 1 - CD\h\ [middot] [ 1 -
Xk=1(Tj) ], the part load factor, dimensionless.
[delta]'(Tj) = the low temperature cutoff factor,
dimensionless.
Evaluate the heating mode cyclic degradation factor
CD\h\ as specified in section 3.8.1 of this appendix.
Determine the low temperature cut-out factor using
[GRAPHIC] [TIFF OMITTED] TR05JA17.105
[[Page 1523]]
where Toff and Ton are defined in section
4.2.1 of this appendix. Use the calculations given in section
4.2.3.3 of this appendix, and not the above, if:
a. The heat pump locks out low capacity operation at low outdoor
temperatures and
b. Tj is below this lockout threshold temperature.
4.2.3.2 Heat Pump Alternates Between High (k=2) and Low (k=1)
Compressor Capacity To Satisfy the Building Heating Load at a
Temperature Tj, Qhk=1(Tj) j)
j)
[GRAPHIC] [TIFF OMITTED] TR05JA17.106
Xk=2(Tj) = 1 - Xk=1(Tj) the heating mode, high
capacity load factor for temperature bin j,
dimensionless.
Determine the low temperature cut-out factor,
[delta]'(Tj), using Equation 4.2.3-3.
4.2.3.3 Heat Pump Only Operates at High (k=2) Compressor Capacity at
Temperature Tj and its Capacity Is Greater Than the Building
Heating Load, BL(Tj) j)
This section applies to units that lock out low compressor
capacity operation at low outdoor temperatures.
[GRAPHIC] [TIFF OMITTED] TR05JA17.107
Where:
Xk=2(Tj)= BL(Tj)/Qhk=2(Tj).
PLFj = 1 - CDh(k = 2) * [1 - Xk=1(Tj)
If the H1C2 test described in section 3.6.3 and Table
13 of this appendix is not conducted, set CD\h\ (k=2)
equal to the default value specified in section 3.8.1 of this
appendix.
Determine the low temperature cut-out factor,
[delta](Tj), using Equation 4.2.3-3.
4.2.3.4 Heat Pump Must Operate Continuously at High (k=2) Compressor
Capacity at Temperature Tj, BL(Tj)
>=Qhk=2(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.108
[[Page 1524]]
4.2.4 Additional Steps for Calculating the HSPF of a Heat Pump Having a
Variable-Speed Compressor
Calculate HSPF using Equation 4.2-1. Evaluate the space heating
capacity, Qhk=1(Tj), and electrical power consumption,
Ehk=1(Tj), of the heat pump when operating at minimum
compressor speed and outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TR05JA17.109
[GRAPHIC] [TIFF OMITTED] TR05JA17.110
where Qhk=1(62) and Ehk=1(62) are determined from the H01
test, Qhk=1(47) and Ehk=1(47) are determined from the H11
test, and all four quantities are calculated as specified in section
3.7 of this appendix.
Evaluate the space heating capacity, Qhk=2(Tj), and
electrical power consumption, Ehk=2(Tj), of the heat pump
when operating at full compressor speed and outdoor temperature
Tj by solving Equations 4.2.2-3 and 4.2.2-4,
respectively, for k=2. For Equation 4.2.2-3, use
Qhcalck=2(47) to represent Qhk=2(47), and for Equation
4.2.2-4, use Ehcalck=2(47) to represent
Ehcalck=2(47)--evaluate Qhcalck=2(47) and
Ehcalck=2(47) as specified in section 3.6.4b of this
appendix.
[GRAPHIC] [TIFF OMITTED] TR05JA17.111
[GRAPHIC] [TIFF OMITTED] TR05JA17.112
where Qh\k=v\(35) and Eh\k=v\(35) are determined from the
H2V test and calculated as specified in section 3.9 of
this appendix. Approximate the slopes of the k=v intermediate speed
heating capacity and electrical power input curves, MQ
and ME, as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.113
[[Page 1525]]
4.2.4.1 Steady-State Space Heating Capacity When Operating at Minimum
Compressor Speed Is Greater Than or Equal to the Building Heating Load
at Temperature Tj, Qhk=1(Tj >=BL(Tj)
Evaluate the Equation 4.2-1 quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.114
as specified in section 4.2.3.1 of this appendix. Except now use
Equations 4.2.4-1 and 4.2.4-2 to evaluate Qhk=1(Tj) and
Ehk=1(Tj), respectively, and replace section 4.2.3.1
references to ``low capacity'' and section 3.6.3 of this appendix
with ``minimum speed'' and section 3.6.4 of this appendix. Also, the
last sentence of section 4.2.3.1 of this appendix does not apply.
4.2.4.2 Heat Pump Operates at an Intermediate Compressor Speed (k=i) in
Order To Match the Building Heating Load at a Temperature
Tj, Qhk=1(Tj) j)
j)
[GRAPHIC] [TIFF OMITTED] TR05JA17.115
and [delta](Tj) is evaluated using Equation 4.2.3-3
while,
Qh\k=i\(Tj) = BL(Tj), the space heating
capacity delivered by the unit in matching the building load at
temperature (Tj), Btu/h. The matching occurs with the
heat pump operating at compressor speed k=i.
COP\k=i\(Tj) = the steady-state coefficient of
performance of the heat pump when operating at compressor speed k=i
and temperature Tj, dimensionless.
For each temperature bin where the heat pump operates at an
intermediate compressor speed, determine COP\k=i\(Tj)
using the following equations,
For each temperature bin where Qhk=1(Tj)
j) j),
[GRAPHIC] [TIFF OMITTED] TR05JA17.116
For each temperature bin where Qh\k=v\(Tj)
<=BL(Tj) j),
[GRAPHIC] [TIFF OMITTED] TR05JA17.117
Where:
COPhk=1(Tj) is the steady-state coefficient of
performance of the heat pump when operating at minimum compressor
speed and temperature Tj, dimensionless, calculated using capacity
Qhk=1(Tj) calculated using Equation 4.2.4-1 and
electrical power consumption Ehk=1(Tj) calculated using
Equation 4.2.4-2;
COPh\k=v\(Tj) is the steady-state coefficient of
performance of the heat pump when operating at intermediate
compressor speed and temperature Tj, dimensionless, calculated using
capacity Qh\k=v\(Tj) calculated using Equation 4.2.4-3
and electrical power consumption Eh\k=v\(Tj) calculated
using Equation 4.2.4-4;
COPhk=2(Tj) is the steady-state coefficient of
performance of the heat pump when operating at full compressor speed
and temperature Tj, dimensionless, calculated using capacity
Qhk=2(Tj) and electrical power consumption
Ehk=2(Tj), both calculated as described in section 4.2.4;
and
BL(Tj) is the building heating load at temperature
Tj, Btu/h.
4.2.4.3 Heat Pump Must Operate Continuously at Full (k=2) Compressor
Speed at Temperature Tj, BL(Tj)
>=Qhk=2(Tj)
Evaluate the Equation 4.2-1 Quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.118
as specified in section 4.2.3.4 of this appendix with the
understanding that Qhk=2(Tj) and Ehk=2(Tj)
correspond to full compressor speed operation and are derived from
the results of the specified section 3.6.4 tests of this appendix.
4.2.5 Heat Pumps Having a Heat Comfort Controller
Heat pumps having heat comfort controllers, when set to maintain
a typical minimum air delivery temperature, will cause the heat pump
condenser to operate less because of a greater contribution from the
resistive elements. With a conventional heat pump, resistive heating
is only initiated if the heat pump condenser cannot meet the
building load (i.e., is delayed until a second stage call from the
indoor thermostat). With a heat comfort controller, resistive
heating can occur even though the heat pump condenser has adequate
capacity to meet the building load (i.e., both on during a first
stage call from the indoor thermostat). As a result, the outdoor
temperature where the heat pump compressor no longer cycles (i.e.,
starts to run continuously), will be lower than if the heat pump did
not have the heat comfort controller.
[[Page 1526]]
4.2.5.1 Blower Coil System Heat Pump Having a Heat Comfort Controller:
Additional Steps for Calculating the HSPF of a Heat Pump Having a
Single-Speed Compressor and Either a Fixed-Speed Indoor Blower or a
Constant-Air-Volume-Rate Indoor Blower Installed, or a Coil-Only System
Heat Pump
Calculate the space heating capacity and electrical power of the
heat pump without the heat comfort controller being active as
specified in section 4.2.1 of this appendix (Equations 4.2.1-4 and
4.2.1-5) for each outdoor bin temperature, Tj, that is
listed in Table 20. Denote these capacities and electrical powers by
using the subscript ``hp'' instead of ``h.'' Calculate the mass flow
rate (expressed in pounds-mass of dry air per hour) and the specific
heat of the indoor air (expressed in Btu/lbmda [middot]
[deg]F) from the results of the H1 test using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.119
where Vis, Vimx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 20, calculate
the nominal temperature of the air leaving the heat pump condenser
coil using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.120
Evaluate eh(Tj/N), RH(Tj)/N,
X(Tj), PLFj, and [delta](Tj) as
specified in section 4.2.1 of this appendix. For each bin
calculation, use the space heating capacity and electrical power
from Case 1 or Case 2, whichever applies.
Case 1. For outdoor bin temperatures where
To(Tj) is equal to or greater than
TCC (the maximum supply temperature determined according
to section 3.1.9 of this appendix), determine Qh(Tj) and
Eh(Tj) as specified in section 4.2.1 of this appendix
(i.e., Qh(Tj) = Qhp(Tj) and
Ehp(Tj) = Ehp(Tj)).
Note: Even though To(Tj) >=Tcc,
resistive heating may be required; evaluate Equation 4.2.1-2 for all
bins.
Case 2. For outdoor bin temperatures where
To(Tj) >Tcc, determine
Qh(Tj) and Eh(Tj) using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.121
Note: Even though To(Tj) Tcc,
additional resistive heating may be required; evaluate Equation
4.2.1-2 for all bins.
4.2.5.2 Heat Pump Having a Heat Comfort Controller: Additional Steps
for Calculating the HSPF of a Heat Pump Having a Single-Speed
Compressor and a Variable-Speed, Variable-Air-Volume-Rate Indoor Blower
Calculate the space heating capacity and electrical power of the
heat pump without the heat comfort controller being active as
specified in section 4.2.2 of this appendix (Equations 4.2.2-1 and
4.2.2-2) for each outdoor bin temperature, Tj, that is
listed in Table 20. Denote these capacities and electrical powers by
using the subscript ``hp'' instead of ``h.'' Calculate the mass flow
rate (expressed in pounds-mass of dry air per hour) and the specific
heat of the indoor air (expressed in Btu/lbmda [middot]
[deg]F) from the results of the H12 test using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.122
where ViS, Vimx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 20, calculate
the nominal temperature of the air leaving the heat pump condenser
coil using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.123
Evaluate eh(Tj)/N, RH(Tj)/N,
X(Tj), PLFj, and [delta](Tj) as
specified in section 4.2.1 of this appendix with the exception of
replacing references to the H1C test and section 3.6.1 of this
appendix with the H1C1 test and section 3.6.2 of this
appendix. For each bin calculation, use the space heating capacity
and electrical power from Case 1 or Case 2, whichever applies.
Case 1. For outdoor bin temperatures where
To(Tj) is equal to or greater than
TCC
[[Page 1527]]
(the maximum supply temperature determined according to section
3.1.9 of this appendix), determine Qh(Tj) and
Eh(Tj) as specified in section 4.2.2 of this appendix
(i.e. Qh(Tj) = Qhp(Tj) and
Eh(Tj) = Ehp(Tj)). Note: Even
though To(Tj) >=TCC, resistive
heating may be required; evaluate Equation 4.2.1-2 for all bins.
Case 2. For outdoor bin temperatures where
To(Tj) TCC, determine
Qh(Tj) and Eh(Tj) using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.124
Note: Even though To(Tj) Tcc,
additional resistive heating may be required; evaluate Equation
4.2.1-2 for all bins.
4.2.5.3 Heat Pumps Having a Heat Comfort Controller: Additional Steps
for Calculating the HSPF of a Heat Pump Having a Two-Capacity
Compressor
Calculate the space heating capacity and electrical power of the
heat pump without the heat comfort controller being active as
specified in section 4.2.3 of this appendix for both high and low
capacity and at each outdoor bin temperature, Tj, that is
listed in Table 20. Denote these capacities and electrical powers by
using the subscript ``hp'' instead of ``h.'' For the low capacity
case, calculate the mass flow rate (expressed in pounds-mass of dry
air per hour) and the specific heat of the indoor air (expressed in
Btu/lbmda [middot] [deg]F) from the results of the
H11 test using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.125
where Vis, Vimx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 20, calculate
the nominal temperature of the air leaving the heat pump condenser
coil when operating at low capacity using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.126
Repeat the above calculations to determine the mass flow rate
(mdak=2) and the specific heat of the indoor air
(Cp,dak=2) when operating at high capacity by using the
results of the H12 test. For each outdoor bin temperature
listed in Table 20, calculate the nominal temperature of the air
leaving the heat pump condenser coil when operating at high capacity
using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.127
Evaluate eh(Tj)/N, RH(Tj)/N,
Xk=1(Tj), and/or
Xk=2(Tj), PLFj, and
[delta]'(Tj) or [delta]''(Tj) as specified in
section 4.2.3.1. 4.2.3.2, 4.2.3.3, or 4.2.3.4 of this appendix,
whichever applies, for each temperature bin. To evaluate these
quantities, use the low-capacity space heating capacity and the low-
capacity electrical power from Case 1 or Case 2, whichever applies;
use the high-capacity space heating capacity and the high-capacity
electrical power from Case 3 or Case 4, whichever applies.
Case 1. For outdoor bin temperatures where
Tok=1(Tj) is equal to or greater
than TCC (the maximum supply temperature determined
according to section 3.1.9 of this appendix), determine
Qhk=1(Tj) and Ehk=1(Tj)
as specified in section 4.2.3 of this appendix (i.e.,
Qhk=1(Tj) =
Qhpk=1(Tj) and
Ehk=1(Tj) =
Ehpk=1(Tj).
Note: Even though Tok=1(Tj)
>=TCC, resistive heating may be required; evaluate
RH(Tj)/N for all bins.
Case 2. For outdoor bin temperatures where
Tok=1(Tj) TCC, determine
Qhk=1(Tj) and Ehk=1(Tj)
using,
[[Page 1528]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.128
Note: Even though Tok=1(Tj)
>=Tcc, additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
Case 3. For outdoor bin temperatures where
Tok=2(Tj) is equal to or greater
than TCC, determine Qhk=2(Tj) and
Ehk=2(Tj) as specified in section 4.2.3 of
this appendix (i.e., Qhk=2(Tj) =
Qhpk=2(Tj) and
Ehk=2(Tj) =
Ehpk=2(Tj)).
Note: Even though Tok=2(Tj)
CC, resistive heating may be required; evaluate
RH(Tj)/N for all bins.
Case 4. For outdoor bin temperatures where
Tok=2(Tj) CC,
determine Qhk=2(Tj) and
Ehk=2(Tj) using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.129
Note: Even though Tok=2(Tj)
cc, additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
4.2.5.4 Heat Pumps Having a Heat Comfort Controller: Additional Steps
for Calculating the HSPF of a Heat Pump Having a Variable-Speed
Compressor. [Reserved]
4.2.6 Additional Steps for Calculating the HSPF of a Heat Pump Having a
Triple-Capacity Compressor
The only triple-capacity heat pumps covered are triple-capacity,
northern heat pumps. For such heat pumps, the calculation of the Eq.
4.2-1 quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.130
differ depending on whether the heat pump would cycle on and off at
low capacity (section 4.2.6.1 of this appendix), cycle on and off at
high capacity (section 4.2.6.2 of this appendix), cycle on and off
at booster capacity (section 4.2.6.3 of this appendix), cycle
between low and high capacity (section 4.2.6.4 of this appendix),
cycle between high and booster capacity (section 4.2.6.5 of this
appendix), operate continuously at low capacity (4.2.6.6 of this
appendix), operate continuously at high capacity (section 4.2.6.7 of
this appendix), operate continuously at booster capacity (section
4.2.6.8 of this appendix), or heat solely using resistive heating
(also section 4.2.6.8 of this appendix) in responding to the
building load. As applicable, the manufacturer must supply
information regarding the outdoor temperature range at which each
stage of compressor capacity is active. As an informative example,
data may be submitted in this manner: At the low (k=1) compressor
capacity, the outdoor temperature range of operation is
40[emsp14][deg]F <= T <= 65[emsp14][deg]F; At the high (k=2)
compressor capacity, the outdoor temperature range of operation is
20[emsp14][deg]F <= T <= 50[emsp14][deg]F; At the booster (k=3)
compressor capacity, the outdoor temperature range of operation is -
20[emsp14][deg]F <= T <= 30[emsp14][deg]F.
a. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at low compressor
capacity and outdoor temperature Tj using the equations given in
section 4.2.3 of this appendix for Qhk=1(Tj)
and Ehk=1 (Tj)) In evaluating the section
4.2.3 equations, Determine Qhk=1(62) and
Ehk=1(62) from the H01 test,
Qhk=1(47) and Ehk=1(47) from the
H11 test, and Qhk=2(47) and
Ehk=2(47) from the H12 test. Calculate all
four quantities as specified in section 3.7 of this appendix. If, in
accordance with section 3.6.6 of this appendix, the H31
test is conducted, calculate Qhk=1(17) and
Ehk=1(17) as specified in section 3.10 of this appendix
and determine Qhk=1(35) and Ehk=1(35) as
specified in section 3.6.6 of this appendix.
b. Evaluate the space heating capacity and electrical power
consumption (Qhk=2(Tj) and Ehk=2
(Tj)) of the heat pump when operating at high compressor
capacity and outdoor temperature Tj by solving Equations 4.2.2-3 and
4.2.2-4, respectively, for k=2. Determine Qhk=1(62) and
Ehk=1(62) from the H01 test,
Qhk=1(47) and Ehk=1(47) from the
H11 test, and Qhk=2(47) and
Ehk=2(47) from the H12 test, evaluated as
specified in section 3.7 of this appendix. Determine the equation
input for Qhk=2(35) and Ehk=2(35) from the
H22, evaluated as specified in section 3.9.1 of this
appendix. Also, determine Qhk=2(17) and
Ehk=2(17) from the H32 test, evaluated as
specified in section 3.10 of this appendix.
c. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at booster compressor
capacity and outdoor temperature Tj using
[[Page 1529]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.131
Determine Qhk=3(17) and Ehk=3(17) from the
H33 test and determine Qhk=2(5) and
Ehk=3(5) from the H43 test. Calculate all four
quantities as specified in section 3.10 of this appendix. Determine
the equation input for Qhk=3(35) and Ehk=3(35)
as specified in section 3.6.6 of this appendix. 4.2.6.1 Steady-State
Space Heating Capacity when Operating at Low Compressor Capacity is
Greater than or Equal to the Building Heating Load at Temperature
Tj, Qhk=1(Tj) >=BL(Tj).,
and the heat pump permits low compressor capacity at Tj.
Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.132
using Eqs. 4.2.3-1 and 4.2.3-2, respectively. Determine the equation
inputs Xk=1(Tj), PLFj, and
[delta]'(Tj) as specified in section 4.2.3.1 of this
appendix. In calculating the part load factor, PLFj, use
the low-capacity cyclic-degradation coefficient CD\h\,
[or equivalently, CDh(k=1)] determined in
accordance with section 3.6.6 of this appendix.
4.2.6.2 Heat Pump Only Operates at High (k=2) Compressor Capacity at
Temperature Tj and Its Capacity Is Greater Than or Equal to
the Building Heating Load, BL(Tj)
k=2(Tj)
Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.133
as specified in section 4.2.3.3 of this appendix. Determine the
equation inputs Xk=2(Tj), PLFj, and
[delta]'(Tj) as specified in section 4.2.3.3 of this
appendix. In calculating the part load factor, PLFj, use
the high-capacity cyclic-degradation coefficient,
CD\h\(k=2) determined in accordance with section 3.6.6 of
this appendix.
4.2.6.3 Heat Pump Only Operates at High (k=3) Compressor Capacity at
Temperature Tj and Its Capacity Is Greater Than or Equal to
the Building Heating Load, BL(Tj)
<=Qhk=3(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.134
where:
Xk=3(Tj) = BL(Tj)/Qhk=3 (Tj) and PLFj = 1-CDh (k = 3) * [1-Xk=3 (Tj)
Determine the low temperature cut-out factor,
[delta]'(Tj), using Eq. 4.2.3-3. Use the booster-capacity
cyclic-degradation coefficient, CD\h\(k=3) determined in
accordance with section 3.6.6 of this appendix.
4.2.6.4 Heat Pump Alternates Between High (k=2) and Low (k=1)
Compressor Capacity to Satisfy the Building Heating Load at a
Temperature Tj, Qhk=1(Tj)
j) k=2(Tj)
Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.135
[[Page 1530]]
as specified in section 4.2.3.2 of this appendix. Determine the
equation inputs Xk=1(Tj),
Xk=2(Tj), and [delta]'(Tj) as
specified in section 4.2.3.2 of this appendix.
4.2.6.5 Heat Pump Alternates Between High (k=2) and Booster (k=3)
Compressor Capacity To Satisfy the Building Heating Load at a
Temperature Tj, Qhk=2(Tj)
j) k=3(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.136
and Xk=3(Tj) = Xk=2(Tj)
= the heating mode, booster capacity load factor for temperature bin
j, dimensionless. Determine the low temperature cut-out factor,
[delta]'(Tj), using Eq. 4.2.3-3.
4.2.6.6 Heat Pump Only Operates at Low (k=1) Capacity at Temperature
Tj and Its Capacity Is Less Than the Building Heating Load,
BL(Tj) > Qhk=1(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.137
where the low temperature cut-out factor, [delta]'(Tj), is
calculated using Eq. 4.2.3-3.
4.2.6.7 Heat Pump Only Operates at High (k=2) Capacity at Temperature
Tj and Its Capacity Is Less Than the Building Heating Load, BL(Tj) >
Qhk=2(Tj)
Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.138
as specified in section 4.2.3.4 of this appendix. Calculate
[delta]''(Tj) using the equation given in section 4.2.3.4 of this
appendix.
4.2.6.8 Heat Pump Only Operates at Booster (k=3) Capacity at
Temperature Tj and Its Capacity Is Less Than the Building Heating Load,
BL(Tj) > Qhk=3(Tj) or the System
Converts to Using Only Resistive Heating
[GRAPHIC] [TIFF OMITTED] TR05JA17.139
where [delta]''(Tj) is calculated as specified in section 4.2.3.4 of
this appendix if the heat pump is operating at its booster
compressor capacity. If the heat pump system converts to using only
resistive heating at outdoor temperature Tj, set
[delta]'(Tj) equal to zero.
4.2.7 Additional Steps for Calculating the HSPF of a Heat Pump Having a
Single Indoor Unit With Multiple Indoor Blowers
The calculation of the Eq. 4.2-1 quantities eh(Tj)/N
and RH(Tj)/N are evaluated as specified in the applicable
subsection.
4.2.7.1 For Multiple Indoor Blower Heat Pumps That Are Connected to a
Singular, Single-Speed Outdoor Unit
a. Calculate the space heating capacity, Qhk=1(Tj),
and electrical power consumption, Ehk=1(Tj), of the heat
pump when operating at the heating minimum air volume rate and
outdoor temperature Tj using Eqs. 4.2.2-3 and 4.2.2-4,
respectively. Use these same equations to calculate the space
heating capacity, Qhk=2(Tj) and electrical power
consumption, Ehk=2(Tj), of the test unit when operating
at the heating full-load air volume rate and outdoor temperature
Tj. In evaluating Eqs. 4.2.2-3 and 4.2.2- 4, determine
the quantities Qhk=1(47) and Ehk=1(47) from
the H11 test; determine Qhk=2 (47) and
Ehk=2(47) from the H12 test. Evaluate all four
quantities according to section 3.7 of this appendix. Determine the
quantities Qhk=1(35) and Ehk=1(35) as
specified in section 3.6.2 of this appendix. Determine
Qhk=2(35) and Ehk=2(35) from the
H22 frost accumulation test as calculated according to
section 3.9.1 of this appendix. Determine the quantities
Qhk=1(17) and Ehk=1(17) from the
H31 test, and Qhk=2(17) and
Ehk=2(17) from the H32 test. Evaluate all four
quantities according to section 3.10 of this appendix. Refer to
section 3.6.2 and Table 12 of this appendix for additional
information on the referenced laboratory tests.
b. Determine the heating mode cyclic degradation coefficient,
CDh, as per sections
[[Page 1531]]
3.6.2 and 3.8 to 3.8.1 of this appendix. Assign this same value to
CDh(k = 2).
c. Except for using the above values of Qhk=1(Tj),
Ehk=1(Tj),Qhk=2(Tj),Ehk=2(Tj), CDh,
and CDh(k = 2), calculate the quantities eh(Tj)/N as
specified in section 4.2.3.1 of this appendix for cases where
Qhk=1(Tj) >= BL(Tj). For all other outdoor bin
temperatures, Tj, calculate eh(Tj)/N and RHh(Tj)/N as
specified in section 4.2.3.3 of this appendix if
Qhk=2(Tj) > BL(Tj) or as specified in section 4.2.3.4 of
this appendix if Qhk=2(Tj) <= BL(Tj).
4.2.7.2 For Multiple Indoor Blower Heat Pumps Connected to Either a
Single Outdoor Unit With a Two-capacity Compressor or to Two Separate
Single-Speed Outdoor Units of Identical Model, calculate the quantities
eh(Tj)/N and RH(Tj)/N as specified in section
4.2.3 of this appendix.
4.3 Calculations of Off-mode Power Consumption
For central air conditioners and heat pumps with a cooling
capacity of:
Less than 36,000 Btu/h, determine the off mode represented
value, PW,OFF, with the following equation:
[GRAPHIC] [TIFF OMITTED] TR05JA17.140
greater than or equal to 36,000 Btu/h, calculate the capacity
scaling factor according to:
[GRAPHIC] [TIFF OMITTED] TR05JA17.141
where QC(95) is the total cooling capacity at the A or A2
test condition, and determine the off mode represented value,
PW,OFF, with the following equation:
[GRAPHIC] [TIFF OMITTED] TR05JA17.142
4.4 Rounding of SEER and HSPF for Reporting Purposes
After calculating SEER according to section 4.1 of this appendix
and HSPF according to section 4.2 of this appendix round the values
off as specified per Sec. 430.23(m) of title 10 of the Code of
Federal Regulations.
[GRAPHIC] [TIFF OMITTED] TR05JA17.143
[[Page 1532]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.144
Table 22--Representative Cooling and Heating Load Hours for Each
Generalized Climatic Region
------------------------------------------------------------------------
Cooling load Heating load
Climatic region hours CLHR hours HLHR
------------------------------------------------------------------------
I....................................... 2,400 750
II...................................... 1,800 1,250
III..................................... 1,200 1,750
IV...................................... 800 2,250
Rating Values........................... 1,000 2,080
V....................................... 400 2,750
VI...................................... 200 2,750
------------------------------------------------------------------------
4.5 Calculations of the SHR, Which Should Be Computed for Different
Equipment Configurations and Test Conditions Specified in Table 23
Table 23--Applicable Test Conditions For Calculation of the Sensible Heat Ratio
----------------------------------------------------------------------------------------------------------------
Reference
Equipment configuration table Number SHR computation with Computed values
of appendix M results from
----------------------------------------------------------------------------------------------------------------
Units Having a Single-Speed 4 B Test............... SHR(B).
Compressor and a Fixed-Speed
Indoor blower, a Constant Air
Volume Rate Indoor blower, or No
Indoor blower.
Units Having a Single-Speed 5 B2 and B1 Tests...... SHR(B1), SHR(B2).
Compressor That Meet the section
3.2.2.1 Indoor Unit Requirements.
Units Having a Two-Capacity 6 B2 and B1 Tests...... SHR(B1), SHR(B2).
Compressor.
Units Having a Variable-Speed 7 B2 and B1 Tests...... SHR(B1), SHR(B2).
Compressor.
----------------------------------------------------------------------------------------------------------------
The SHR is defined and calculated as follows:
[[Page 1533]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.145
Where both the total and sensible cooling capacities are determined
from the same cooling mode test and calculated from data collected
over the same 30-minute data collection interval.
4.6 Calculations of the Energy Efficiency Ratio (EER).
Calculate the energy efficiency ratio using.
[GRAPHIC] [TIFF OMITTED] TR05JA17.146
where Qck(T) and Eck(T) are the space cooling capacity and
electrical power consumption determined from the 30-minute data
collection interval of the same steady-state wet coil cooling mode
test and calculated as specified in section 3.3 of this appendix.
Add the letter identification for each steady-state test as a
subscript (e.g., EERA2) to differentiate among the resulting EER
values.
0
10. Add appendix M1 to subpart B of part 430 to read as follows:
Appendix M1 to Subpart B of Part 430--Uniform Test Method for Measuring
the Energy Consumption of Central Air Conditioners and Heat Pumps
Prior to January 1, 2023, any representations, including
compliance certifications, made with respect to the energy use,
power, or efficiency of central air conditioners and central air
conditioning heat pumps must be based on the results of testing
pursuant to appendix M of this subpart.
On or after January 1, 2023, any representations, including
compliance certifications, made with respect to the energy use,
power, or efficiency of central air conditioners and central air
conditioning heat pumps must be based on the results of testing
pursuant to this appendix.
1 Scope and Definitions
1.1 Scope
This test procedure provides a method of determining SEER2,
EER2, HSPF2 and PW,OFF for central air conditioners and
central air conditioning heat pumps including the following
categories:
(h) Split-system air conditioners, including single-split,
multi-head mini-split, multi-split (including VRF), and multi-
circuit systems
(i) Split-system heat pumps, including single-split, multi-head
mini-split, multi-split (including VRF), and multi-circuit systems
(j) Single-package air conditioners
(k) Single-package heat pumps
(l) Small-duct, high-velocity systems (including VRF)
(m) Space-constrained products--air conditioners
(n) Space-constrained products--heat pumps
For the purposes of this appendix, the Department of Energy
incorporates by reference specific sections of several industry
standards, as listed in Sec. 430.3. In cases where there is a
conflict, the language of the test procedure in this appendix takes
precedence over the incorporated standards.
All section references refer to sections within this appendix
unless otherwise stated.
1.2 Definitions
Airflow-control settings are programmed or wired control system
configurations that control a fan to achieve discrete, differing
ranges of airflow--often designated for performing a specific
function (e.g., cooling, heating, or constant circulation)--without
manual adjustment other than interaction with a user-operable
control (i.e., a thermostat) that meets the manufacturer
specifications for installed-use. For the purposes of this appendix,
manufacturer specifications for installed-use are those found in the
product literature shipped with the unit.
Air sampling device is an assembly consisting of a manifold with
several branch tubes with multiple sampling holes that draws an air
sample from a critical location from the unit under test (e.g.
indoor air inlet, indoor air outlet, outdoor air inlet, etc.).
Airflow prevention device denotes a device that prevents airflow
via natural convection by mechanical means, such as an air damper
box, or by means of changes in duct height, such as an upturned
duct.
Aspirating psychrometer is a piece of equipment with a monitored
airflow section that draws uniform airflow through the measurement
section and has probes for measurement of air temperature and
humidity.
Blower coil indoor unit means an indoor unit either with an
indoor blower housed with the coil or with a separate designated air
mover such as a furnace or a modular blower (as defined in appendix
AA to this subpart).
Blower coil system refers to a split system that includes one or
more blower coil indoor units.
Cased coil means a coil-only indoor unit with external
cabinetry.
Ceiling-mount blower coil system means a split system for which
a) the outdoor unit has a certified cooling capacity less than or
equal to 36,000 Btu/h; b) the indoor unit(s) is/are shipped with
manufacturer-supplied installation instructions that specify to
secure the indoor unit only to the ceiling, within a furred-down
space, or above a dropped ceiling of the conditioned space, with
return air directly to the bottom of the unit without ductwork, or
through the furred-down space, or optional insulated return air
plenum that is shipped with the indoor unit; c) the installed height
of the indoor unit is no more than 12 inches (not including
condensate drain lines) and the installed depth (in the direction of
airflow) of the indoor unit is no more than 30 inches; and d) supply
air is discharged horizontally.
Coefficient of Performance (COP) means the ratio of the average
rate of space heating delivered to the average rate of electrical
energy consumed by the heat pump. Determine these rate quantities
from a single test or, if derived via interpolation, determine at a
single set of operating conditions. COP is a dimensionless quantity.
When determined for a ducted coil-only system, COP must be
calculated using the default values for heat output and power input
of a fan motor specified in sections 3.7 and 3.9.1 of this appendix.
Coil-only indoor unit means an indoor unit that is distributed
in commerce without an indoor blower or separate designated air
mover. A coil-only indoor unit installed in the field relies on a
separately installed furnace or a modular blower for indoor air
movement.
[[Page 1534]]
Coil-only system means a system that includes only (one or more)
coil-only indoor units.
Condensing unit removes the heat absorbed by the refrigerant to
transfer it to the outside environment and consists of an outdoor
coil, compressor(s), and air moving device.
Constant-air-volume-rate indoor blower means a fan that varies
its operating speed to provide a fixed air-volume-rate from a ducted
system.
Continuously recorded, when referring to a dry bulb measurement,
dry bulb temperature used for test room control, wet bulb
temperature, dew point temperature, or relative humidity
measurements, means that the specified value must be sampled at
regular intervals that are equal to or less than 15 seconds.
Cooling load factor (CLF) means the ratio having as its
numerator the total cooling delivered during a cyclic operating
interval consisting of one ON period and one OFF period, and as its
denominator the total cooling that would be delivered, given the
same ambient conditions, had the unit operated continuously at its
steady-state, space-cooling capacity for the same total time (ON +
OFF) interval.
Crankcase heater means any electrically powered device or
mechanism for intentionally generating heat within and/or around the
compressor sump volume. Crankcase heater control may be achieved
using a timer or may be based on a change in temperature or some
other measurable parameter, such that the crankcase heater is not
required to operate continuously. A crankcase heater without
controls operates continuously when the compressor is not operating.
Cyclic Test means a test where the unit's compressor is cycled
on and off for specific time intervals. A cyclic test provides half
the information needed to calculate a degradation coefficient.
Damper box means a short section of duct having an air damper
that meets the performance requirements of section 2.5.7 of this
appendix.
Degradation coefficient (CD) means a parameter used in
calculating the part load factor. The degradation coefficient for
cooling is denoted by CD\c\. The degradation coefficient
for heating is denoted by CD\h\.
Demand-defrost control system means a system that defrosts the
heat pump outdoor coil-only when measuring a predetermined
degradation of performance. The heat pump's controls either:
(1) Monitor one or more parameters that always vary with the
amount of frost accumulated on the outdoor coil (e.g., coil to air
differential temperature, coil differential air pressure, outdoor
fan power or current, optical sensors) at least once for every ten
minutes of compressor ON-time when space heating; or
(2) Operate as a feedback system that measures the length of the
defrost period and adjusts defrost frequency accordingly. In all
cases, when the frost parameter(s) reaches a predetermined value,
the system initiates a defrost. In a demand-defrost control system,
defrosts are terminated based on monitoring a parameter(s) that
indicates that frost has been eliminated from the coil. (Note:
Systems that vary defrost intervals according to outdoor dry-bulb
temperature are not demand-defrost systems.) A demand-defrost
control system, which otherwise meets the requirements, may allow
time-initiated defrosts if, and only if, such defrosts occur after 6
hours of compressor operating time.
Design heating requirement (DHR) predicts the space heating load
of a residence when subjected to outdoor design conditions.
Estimates for the minimum and maximum DHR are provided for six
generalized U.S. climatic regions in section 4.2 of this appendix.
Dry-coil tests are cooling mode tests where the wet-bulb
temperature of the air supplied to the indoor unit is maintained low
enough that no condensate forms on the evaporator coil.
Ducted system means an air conditioner or heat pump that is
designed to be permanently installed equipment and delivers
conditioned air to the indoor space through a duct(s). The air
conditioner or heat pump may be either a split-system or a single-
package unit.
Energy efficiency ratio (EER) means the ratio of the average
rate of space cooling delivered to the average rate of electrical
energy consumed by the air conditioner or heat pump. Determine these
rate quantities from a single test or, if derived via interpolation,
determine at a single set of operating conditions. EER is expressed
in units of
[GRAPHIC] [TIFF OMITTED] TR05JA17.147
When determined for a ducted coil-only system, EER must include,
from this appendix, the section 3.3 and 3.5.1 default values for the
heat output and power input of a fan motor. The represented value of
EER determined in accordance with appendix M1 is EER2.
Evaporator coil means an assembly that absorbs heat from an
enclosed space and transfers the heat to a refrigerant.
Heat pump means a kind of central air conditioner that utilizes
an indoor conditioning coil, compressor, and refrigerant-to-outdoor
air heat exchanger to provide air heating, and may also provide air
cooling, air dehumidifying, air humidifying, air circulating, and
air cleaning.
Heat pump having a heat comfort controller means a heat pump
with controls that can regulate the operation of the electric
resistance elements to assure that the air temperature leaving the
indoor section does not fall below a specified temperature. Heat
pumps that actively regulate the rate of electric resistance heating
when operating below the balance point (as the result of a second
stage call from the thermostat) but do not operate to maintain a
minimum delivery temperature are not considered as having a heat
comfort controller.
Heating load factor (HLF) means the ratio having as its
numerator the total heating delivered during a cyclic operating
interval consisting of one ON period and one OFF period, and its
denominator the heating capacity measured at the same test
conditions used for the cyclic test, multiplied by the total time
interval (ON plus OFF) of the cyclic-test.
Heating season means the months of the year that require
heating, e.g., typically, and roughly, October through April.
Heating seasonal performance factor 2 (HSPF2) means the total
space heating required during the heating season, expressed in Btu,
divided by the total electrical energy consumed by the heat pump
system during the same season, expressed in watt-hours. The HSPF2
used to evaluate compliance with 10 CFR 430.32(c) is based on Region
IV and the sampling plan stated in 10 CFR 429.16(a). HSPF2 is
determined in accordance with appendix M1.
Independent coil manufacturer (ICM) means a manufacturer that
manufactures indoor units but does not manufacture single-package
units or outdoor units.
Indoor unit means a separate assembly of a split system that
includes--
(a) An arrangement of refrigerant-to-air heat transfer coil(s)
for transfer of heat between the refrigerant and the indoor air,
(b) A condensate drain pan, and may or may not include,
(c) Sheet metal or plastic parts not part of external cabinetry
to direct/route airflow over the coil(s),
(d) A cooling mode expansion device,
(e) External cabinetry, and
(f) An integrated indoor blower (i.e. a device to move air
including its associated motor). A separate designated air mover
that may be a furnace or a modular blower (as defined in appendix AA
to the subpart) may be considered to be part of the indoor unit. A
service coil is not an indoor unit.
Low-static blower coil system means a ducted multi-split or
multi-head mini-split system for which all indoor units produce
greater than 0.01 in. wc. and a maximum of 0.35 in. wc. external
static pressure when operated at the cooling full-load air volume
rate not exceeding 400 cfm per rated ton of cooling.
Mid-static blower coil system means a ducted multi-split or
multi-head mini-split system for which all indoor units produce
greater than 0.20 in. wc. and a maximum of 0.65 in. wc. when
operated at the cooling full-load air volume rate not exceeding 400
cfm per rated ton of cooling.
Minimum-speed-limiting variable-speed heat pump means a heat
pump for which the compressor speed (represented by revolutions per
minute or motor power input frequency) is higher than its value for
operation in a 47[emsp14][deg]F ambient temperature for any bin
temperature Tj for which the calculated heating load is
less than the calculated intermediate-speed capacity.
Mobile home blower coil system means a split system that
contains an outdoor unit and an indoor unit that meet the following
criteria:
(1) Both the indoor and outdoor unit are shipped with
manufacturer-supplied installation instructions that specify
installation only in a mobile home with the home and equipment
complying with HUD Manufactured Home Construction Safety Standard 24
CFR part 3280;
(2) The indoor unit cannot exceed 0.40 in. wc. when operated at
the cooling full-load air
[[Page 1535]]
volume rate not exceeding 400 cfm per rated ton of cooling; and
(3) The indoor and outdoor unit each must bear a label in at
least \1/4\ inch font that reads ``For installation only in HUD
manufactured home per Construction Safety Standard 24 CFR part
3280.''
Mobile home coil-only system means a coil-only split system that
includes an outdoor unit and coil-only indoor unit that meet the
following criteria:
(1) The outdoor unit is shipped with manufacturer-supplied
installation instructions that specify installation only for mobile
homes that comply with HUD Manufactured Home Construction Safety
Standard 24 CFR part 3280,
(2) The coil-only indoor unit is shipped with manufacturer-
supplied installation instructions that specify installation only in
or with a mobile home furnace, modular blower, or designated air
mover that complies with HUD Manufactured Home Construction Safety
Standard 24 CFR part 3280, and has dimensions no greater than 20''
wide, 34'' high and 21'' deep, and
(3) The coil-only indoor unit and outdoor unit each has a label
in at least \1/4\ inch font that reads ``For installation only in
HUD manufactured home per Construction Safety Standard 24 CFR part
3280.''
Multi-head mini-split system means a split system that has one
outdoor unit and that has two or more indoor units connected with a
single refrigeration circuit. The indoor units operate in unison in
response to a single indoor thermostat.
Multiple-circuit (or multi-circuit) system means a split system
that has one outdoor unit and that has two or more indoor units
installed on two or more refrigeration circuits such that each
refrigeration circuit serves a compressor and one and only one
indoor unit, and refrigerant is not shared from circuit to circuit.
Multiple-split (or multi-split) system means a split system that
has one outdoor unit and two or more coil-only indoor units and/or
blower coil indoor units connected with a single refrigerant
circuit. The indoor units operate independently and can condition
multiple zones in response to at least two indoor thermostats or
temperature sensors. The outdoor unit operates in response to
independent operation of the indoor units based on control input of
multiple indoor thermostats or temperature sensors, and/or based on
refrigeration circuit sensor input (e.g., suction pressure).
Nominal capacity means the capacity that is claimed by the
manufacturer on the product name plate. Nominal cooling capacity is
approximate to the air conditioner cooling capacity tested at A or
A2 condition. Nominal heating capacity is approximate to
the heat pump heating capacity tested in the H1N test.
Non-ducted indoor unit means an indoor unit that is designed to
be permanently installed, mounted on room walls and/or ceilings, and
that directly heats or cools air within the conditioned space.
Normalized Gross Indoor Fin Surface (NGIFS) means the gross fin
surface area of the indoor unit coil divided by the cooling capacity
measured for the A or A2 Test, whichever applies.
Off-mode power consumption means the power consumption when the
unit is connected to its main power source but is neither providing
cooling nor heating to the building it serves.
Off-mode season means, for central air conditioners other than
heat pumps, the shoulder season and the entire heating season; and
for heat pumps, the shoulder season only.
Outdoor unit means a separate assembly of a split system that
transfers heat between the refrigerant and the outdoor air, and
consists of an outdoor coil, compressor(s), an air moving device,
and in addition for heat pumps, may include a heating mode expansion
device, reversing valve, and/or defrost controls.
Outdoor unit manufacturer (OUM) means a manufacturer of single-
package units, outdoor units, and/or both indoor units and outdoor
units.
Part-load factor (PLF) means the ratio of the cyclic EER (or COP
for heating) to the steady-state EER (or COP), where both EERs (or
COPs) are determined based on operation at the same ambient
conditions.
Seasonal energy efficiency ratio 2 (SEER2) means the total heat
removed from the conditioned space during the annual cooling season,
expressed in Btu's, divided by the total electrical energy consumed
by the central air conditioner or heat pump during the same season,
expressed in watt-hours. SEER2 is determined in accordance with
appendix M1.
Service coil means an arrangement of refrigerant-to-air heat
transfer coil(s), condensate drain pan, sheet metal or plastic parts
to direct/route airflow over the coil(s), which may or may not
include external cabinetry and/or a cooling mode expansion device,
distributed in commerce solely for replacing an uncased coil or
cased coil that has already been placed into service, and that has
been labeled ``for indoor coil replacement only'' on the nameplate
and in manufacturer technical and product literature. The model
number for any service coil must include some mechanism (e.g., an
additional letter or number) for differentiating a service coil from
a coil intended for an indoor unit.
Shoulder season means the months of the year in between those
months that require cooling and those months that require heating,
e.g., typically, and roughly, April through May, and September
through October.
Single-package unit means any central air conditioner or heat
pump that has all major assemblies enclosed in one cabinet.
Single-split system means a split system that has one outdoor
unit and one indoor unit connected with a single refrigeration
circuit.
Small-duct, high-velocity system means a split system for which
all indoor units are blower coil indoor units that produce at least
1.2 inches (of water column) of external static pressure when
operated at the full-load air volume rate certified by the
manufacturer of at least 220 scfm per rated ton of cooling.
Split system means any central air conditioner or heat pump that
has at least two separate assemblies that are connected with
refrigerant piping when installed. One of these assemblies includes
an indoor coil that exchanges heat with the indoor air to provide
heating or cooling, while one of the others includes an outdoor coil
that exchanges heat with the outdoor air. Split systems may be
either blower coil systems or coil-only systems.
Standard Air means dry air having a mass density of 0.075 lb/
ft\3\.
Steady-state test means a test where the test conditions are
regulated to remain as constant as possible while the unit operates
continuously in the same mode.
Temperature bin means the 5[emsp14][deg]F increments that are
used to partition the outdoor dry-bulb temperature ranges of the
cooling (>=65[emsp14][deg]F) and heating (<65[emsp14][deg]F)
seasons.
Test condition tolerance means the maximum permissible
difference between the average value of the measured test parameter
and the specified test condition.
Test operating tolerance means the maximum permissible range
that a measurement may vary over the specified test interval. The
difference between the maximum and minimum sampled values must be
less than or equal to the specified test operating tolerance.
Tested combination means a multi-head mini-split, multi-split,
or multi-circuit system having the following features:
(1) The system consists of one outdoor unit with one or more
compressors matched with between two and five indoor units;
(2) The indoor units must:
(i) Collectively, have a nominal cooling capacity greater than
or equal to 95 percent and less than or equal to 105 percent of the
nominal cooling capacity of the outdoor unit;
(ii) Each represent the highest sales volume model family, if
this is possible while meeting all the requirements of this section.
If this is not possible, one or more of the indoor units may
represent another indoor model family in order that all the other
requirements of this section are met.
(iii) Individually not have a nominal cooling capacity greater
than 50 percent of the nominal cooling capacity of the outdoor unit,
unless the nominal cooling capacity of the outdoor unit is 24,000
Btu/h or less;
(iv) Operate at fan speeds consistent with manufacturer's
specifications; and
(v) All be subject to the same minimum external static pressure
requirement while able to produce the same external static pressure
at the exit of each outlet plenum when connected in a manifold
configuration as required by the test procedure.
(3) Where referenced, ``nominal cooling capacity'' means, for
indoor units, the highest cooling capacity listed in published
product literature for 95[emsp14][deg]F outdoor dry bulb temperature
and 80[emsp14][deg]F dry bulb, 67[emsp14][deg]F wet bulb indoor
conditions, and for outdoor units, the lowest cooling capacity
listed in published product literature for these conditions. If
incomplete or no operating conditions are published, use the highest
(for indoor units) or lowest (for outdoor units) such cooling
capacity available for sale.
Time-adaptive defrost control system is a demand-defrost control
system that measures the length of the prior defrost period(s) and
uses that information to automatically determine when to initiate
the next defrost cycle.
[[Page 1536]]
Time-temperature defrost control systems initiate or evaluate
initiating a defrost cycle only when a predetermined cumulative
compressor ON-time is obtained. This predetermined ON-time is
generally a fixed value (e.g., 30, 45, 90 minutes) although it may
vary based on the measured outdoor dry-bulb temperature. The ON-time
counter accumulates if controller measurements (e.g., outdoor
temperature, evaporator temperature) indicate that frost formation
conditions are present, and it is reset/remains at zero at all other
times. In one application of the control scheme, a defrost is
initiated whenever the counter time equals the predetermined ON-
time. The counter is reset when the defrost cycle is completed.
In a second application of the control scheme, one or more
parameters are measured (e.g., air and/or refrigerant temperatures)
at the predetermined, cumulative, compressor ON-time. A defrost is
initiated only if the measured parameter(s) falls within a
predetermined range. The ON-time counter is reset regardless of
whether or not a defrost is initiated. If systems of this second
type use cumulative ON-time intervals of 10 minutes or less, then
the heat pump may qualify as having a demand defrost control system
(see definition).
Triple-capacity, northern heat pump means a heat pump that
provides two stages of cooling and three stages of heating. The two
common stages for both the cooling and heating modes are the low
capacity stage and the high capacity stage. The additional heating
mode stage is the booster capacity stage, which offers the highest
heating capacity output for a given set of ambient operating
conditions.
Triple-split system means a split system that is composed of
three separate assemblies: An outdoor fan coil section, a blower
coil indoor unit, and an indoor compressor section.
Two-capacity (or two-stage) compressor system means a central
air conditioner or heat pump that has a compressor or a group of
compressors operating with only two stages of capacity. For such
systems, low capacity means the compressor(s) operating at low
stage, or at low load test conditions. The low compressor stage that
operates for heating mode tests may be the same or different from
the low compressor stage that operates for cooling mode tests. For
such systems, high capacity means the compressor(s) operating at
high stage, or at full load test conditions.
Two-capacity, northern heat pump means a heat pump that has a
factory or field-selectable lock-out feature to prevent space
cooling at high-capacity. Two-capacity heat pumps having this
feature will typically have two sets of ratings, one with the
feature disabled and one with the feature enabled. The heat pump is
a two-capacity northern heat pump only when this feature is enabled
at all times. The certified indoor coil model number must reflect
whether the ratings pertain to the lockout enabled option via the
inclusion of an extra identifier, such as ``+LO''. When testing as a
two-capacity, northern heat pump, the lockout feature must remain
enabled for all tests.
Uncased coil means a coil-only indoor unit without external
cabinetry.
Variable refrigerant flow (VRF) system means a multi-split
system with at least three compressor capacity stages, distributing
refrigerant through a piping network to multiple indoor blower coil
units each capable of individual zone temperature control, through
proprietary zone temperature control devices and a common
communications network. Note: Single-phase VRF systems less than
65,000 Btu/h are central air conditioners and central air
conditioning heat pumps.
Variable-speed compressor system means a central air conditioner
or heat pump that has a compressor that uses a variable-speed drive
to vary the compressor speed to achieve variable capacities. Wall-
mount blower coil system means a split system air conditioner or
heat pump for which:
(a) The outdoor unit has a certified cooling capacity less than
or equal to 36,000 Btu/h;
(b) The indoor unit(s) is/are shipped with manufacturer-supplied
installation instructions that specify mounting only by:
(1) Securing the back side of the unit to a wall within the
conditioned space, or
(2) Securing the unit to adjacent wall studs or in an enclosure,
such as a closet, such that the indoor unit's front face is flush
with a wall in the conditioned space;
(c) Has front air return without ductwork and is not capable of
horizontal air discharge; and
(d) Has a height no more than 45 inches, a depth (perpendicular
to the wall) no more than 22 inches (including tubing connections),
and a width no more than 24 inches (parallel to the wall).
Wet-coil test means a test conducted at test conditions that
typically cause water vapor to condense on the test unit evaporator
coil.
2 Testing Overview and Conditions
(A) Test VRF systems using AHRI 1230-2010 (incorporated by
reference, see Sec. 430.3) and appendix M. Where AHRI 1230-2010
refers to the appendix C therein substitute the provisions of this
appendix. In cases where there is a conflict, the language of the
test procedure in this appendix takes precedence over AHRI 1230-
2010.
For definitions use section 1 of appendix M and section 3 of
AHRI 1230-2010. For rounding requirements, refer to Sec. 430.23(m).
For determination of certified ratings, refer to Sec. 429.16 of
this chapter.
For test room requirements, refer to section 2.1 of this
appendix. For test unit installation requirements refer to sections
2.2.a, 2.2.b, 2.2.c, 2.2.1, 2.2.2, 2.2.3.a, 2.2.3.c, 2.2.4, 2.2.5,
and 2.4 to 2.12 of this appendix, and sections 5.1.3 and 5.1.4 of
AHRI 1230-2010. The ``manufacturer's published instructions,'' as
stated in section 8.2 of ANSI/ASHRAE 37-2009 (incorporated by
reference, see Sec. 430.3) and ``manufacturer's installation
instructions'' discussed in this appendix mean the manufacturer's
installation instructions that come packaged with or appear in the
labels applied to the unit. This does not include online manuals.
Installation instructions that appear in the labels applied to the
unit take precedence over installation instructions that are shipped
with the unit.
For general requirements for the test procedure, refer to
section 3.1 of this appendix, except for sections 3.1.3 and 3.1.4,
which are requirements for indoor air volume and outdoor air volume.
For indoor air volume and outdoor air volume requirements, refer
instead to section 6.1.5 (except where section 6.1.5 refers to Table
8, refer instead to Table 4 of this appendix) and 6.1.6 of AHRI
1230-2010.
For the test method, refer to sections 3.3 to 3.5 and 3.7 to
3.13 of this appendix. For cooling mode and heating mode test
conditions, refer to section 6.2 of AHRI 1230-2010. For calculations
of seasonal performance descriptors, refer to section 4 of this
appendix.
(B) For systems other than VRF, only a subset of the sections
listed in this test procedure apply when testing and determining
represented values for a particular unit. Table 1 shows the sections
of the test procedure that apply to each system. This table is meant
to assist manufacturers in finding the appropriate sections of the
test procedure; the appendix sections rather than the table provide
the specific requirements for testing, and given the varied nature
of available units, manufacturers are responsible for determining
which sections apply to each unit tested based on the model
characteristics. To use this table, first refer to the sections
listed under ``all units''. Then refer to additional requirements
based on:
(1) System configuration(s),
(2) The compressor staging or modulation capability, and
(3) Any special features.
Testing requirements for space-constrained products do not
differ from similar equipment that is not space-constrained and thus
are not listed separately in this table. Air conditioners and heat
pumps are not listed separately in this table, but heating
procedures and calculations apply only to heat pumps.
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2.1 Test Room Requirements.
a. Test using two side-by-side rooms: An indoor test room and an
outdoor test room. For multiple-split, single-zone-multi-coil or
multi-circuit air conditioners and heat pumps, however, use as many
indoor test rooms as needed to accommodate the total number of
indoor units. These rooms must comply with the requirements
specified in sections 8.1.2 and 8.1.3 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3).
b. Inside these test rooms, use artificial loads during cyclic
tests and frost accumulation tests, if needed, to produce stabilized
room air temperatures. For one room, select an electric resistance
heater(s) having a heating capacity that is approximately equal to
the heating capacity of the test unit's condenser. For the second
room, select a heater(s) having a capacity that is close to the
sensible cooling capacity of the test unit's evaporator. Cycle the
heater located in the same room as the test unit evaporator coil ON
and OFF when the test unit cycles ON and OFF. Cycle the heater
located in the same room as the test unit condensing coil ON and OFF
when the test unit cycles OFF and ON.
2.2 Test Unit Installation Requirements.
a. Install the unit according to section 8.2 of ANSI/ASHRAE 37-
2009 (incorporated by reference, see Sec. 430.3), subject to the
following additional requirements:
(1) When testing split systems, follow the requirements given in
section 6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see
Sec. 430.3). For the vapor refrigerant line(s), use the insulation
included with the unit; if no insulation is provided, use insulation
meeting the specifications for the insulation in the installation
instructions included with the unit by the manufacturer; if no
insulation is included with the unit and the installation
instructions do not contain provisions for insulating the line(s),
fully insulate the vapor refrigerant line(s) with vapor proof
insulation having an inside diameter that matches the refrigerant
tubing and a nominal thickness of at least 0.5 inches. For the
liquid refrigerant line(s), use the insulation included with the
unit; if no insulation is provided, use insulation meeting the
specifications for the insulation in the installation instructions
included with the unit by the manufacturer; if no insulation is
included with the unit and the installation instructions do not
contain provisions for insulating the line(s), leave the liquid
refrigerant line(s) exposed to the air for air conditioners and heat
pumps that heat and cool; or, for heating-only heat pumps, insulate
the liquid refrigerant line(s) with insulation having an inside
diameter that matches the refrigerant tubing and a nominal thickness
of at least 0.5 inches. However, these requirements do not take
priority over instructions for application of insulation for the
purpose of improving refrigerant temperature measurement accuracy as
required by sections 2.10.2 and 2.10.3 of this appendix. Insulation
must be the same for the cooling and heating tests.
(2) When testing split systems, if the indoor unit does not ship
with a cooling mode expansion device, test the system using the
device as specified in the installation instructions provided with
the indoor unit. If none is specified, test the system using a fixed
orifice or piston type expansion device that is sized appropriately
for the system.
(3) When testing triple-split systems (see section 1.2 of this
appendix, Definitions), use the tubing length specified in section
6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see Sec.
430.3) to connect the outdoor coil, indoor compressor section, and
indoor coil while still meeting the requirement of exposing 10 feet
of the tubing to outside conditions;
(4) When testing split systems having multiple indoor coils,
connect each indoor blower coil unit to the outdoor unit using:
(a) 25 feet of tubing, or
(b) Tubing furnished by the manufacturer, whichever is longer.
(5) When testing split systems having multiple indoor coils,
expose at least 10 feet of the system interconnection tubing to the
outside conditions. If they are needed to make a secondary
measurement of capacity or for verification of refrigerant charge,
install refrigerant pressure measuring instruments as described in
section 8.2.5 of ANSI/ASHRAE 37-2009 (incorporated by reference, see
Sec. 430.3). Section 2.10 of this appendix specifies which
secondary methods require refrigerant pressure measurements and
section 2.2.5.5 of this appendix discusses use of pressure
measurements to verify charge. At a minimum, insulate the low-
pressure line(s) of a split system with insulation having an inside
diameter that matches the refrigerant tubing and a nominal thickness
of 0.5 inch.
b. For units designed for both horizontal and vertical
installation or for both up-flow and down-flow vertical
installations, use the orientation for testing specified by the
manufacturer in the certification report. Conduct testing with the
following installed:
(1) The most restrictive filter(s);
(2) Supplementary heating coils; and
(3) Other equipment specified as part of the unit, including all
hardware used by a heat comfort controller if so equipped (see
section 1 of this appendix, Definitions). For small-duct, high-
velocity systems, configure all balance dampers or restrictor
devices on or inside the unit to fully open or lowest restriction.
c. Testing a ducted unit without having an indoor air filter
installed is permissible as long as the minimum external static
pressure requirement is adjusted as stated in Table 4, note 3 (see
section 3.1.4 of this appendix). Except as noted in section 3.1.10
of this appendix, prevent the indoor air supplementary heating coils
from operating during all tests. For uncased coils, create an
enclosure using 1 inch fiberglass foil-faced ductboard having a
nominal density of 6 pounds per cubic foot. Or alternatively,
construct an enclosure using sheet metal or a similar material and
insulating material having a thermal resistance (``R'' value)
between 4 and 6 hr [middot] ft\2\ [middot] [deg]F/Btu. Size the
enclosure and seal between the coil and/or drainage pan and the
interior of the enclosure as specified in installation instructions
shipped with the unit. Also seal between the plenum and inlet and
outlet ducts.
d. When testing a coil-only system, install a toroidal-type
transformer to power the system's low-voltage components, complying
with any additional requirements for the transformer mentioned in
the installation manuals included with the unit by the system
manufacturer. If the installation manuals do not provide
specifications for the transformer, use a transformer having the
following features:
(1) A nominal volt-amp rating such that the transformer is
loaded between 25 and 90 percent of this rating for the highest
level of power measured during the off mode test (section 3.13 of
this appendix);
(2) Designed to operate with a primary input of 230 V, single
phase, 60 Hz; and
(3) That provides an output voltage that is within the specified
range for each low-voltage component. Include the power consumption
of the components connected to the transformer as part of the total
system power consumption during the off mode tests; do not include
the power consumed by the transformer when no load is connected to
it.
e. Test an outdoor unit with no match (i.e., that is not
distributed in commerce with any indoor units) using a coil-only
indoor unit with a single cooling air volume rate whose coil has:
(1) Round tubes of outer diameter no less than 0.375 inches, and
(2) A normalized gross indoor fin surface (NGIFS) no greater
than 1.0 square inch per British thermal unit per hour (sq. in./Btu/
hr). NGIFS is calculated as follows:
NGIFS = 2 x Lf x Wf x Nf / Qc(95)
where,
Lf = Indoor coil fin length in inches, also height of the
coil transverse to the tubes.
Wf = Indoor coil fin width in inches, also depth of the
coil.
Nf = Number of fins.
Qc = the measured space cooling capacity of the tested outdoor unit/
indoor unit combination as determined from the A2 or A
Test whichever applies, Btu/h.
f. If the outdoor unit or the outdoor portion of a single-
package unit has a drain pan heater to prevent freezing of defrost
water, energize the heater, subject to control to de-energize it
when not needed by the heater's thermostat or the unit's control
system, for all tests.
g. If pressure measurement devices are connected to a cooling/
heating heat pump refrigerant circuit, the refrigerant charge
Mt that could potentially transfer out of the connected
pressure measurement systems (transducers, gauges, connections, and
lines) between operating modes must be less than 2 percent of the
factory refrigerant charge listed on the nameplate of the outdoor
unit. If the outdoor unit nameplate has no listed refrigerant
charge, or the heat pump is shipped without a refrigerant charge,
use a factory refrigerant charge equal to 30 ounces per ton of
certified cooling capacity. Use Equation 2.2-1 to calculate
Mt for heat pumps that have a single expansion device
located in the outdoor unit to serve each indoor unit, and use
Equation 2.2-2 to calculate Mt for heat pumps that have
two expansion devices per indoor unit.
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where:
Vi (i=2,3,4 . . .) = the internal volume of the pressure
measurement system (pressure lines, fittings, and gauge and/or
transducer) at the location i (as indicated in Table 2), (cubic
inches)
fi (i=5,6) = 0 if the pressure measurement system is
pitched upwards from the pressure tap location to the gauge or
transducer, 1 if it is not.
r = the density associated with liquid refrigerant at 100 [deg]F
bubble point conditions (ounces per cubic inch)
Table 2--Pressure Measurement Locations
------------------------------------------------------------------------
Location
------------------------------------------------------------------------
Compressor Discharge............................................. 1
Between Outdoor Coil and Outdoor Expansion Valve(s).............. 2
Liquid Service Valve............................................. 3
Indoor Coil Inlet................................................ 4
Indoor Coil Outlet............................................... 5
Common Suction Port (i.e., vapor service valve).................. 6
Compressor Suction............................................... 7
------------------------------------------------------------------------
Calculate the internal volume of each pressure measurement
system using internal volume reported for pressure transducers and
gauges in product literature, if available. If such information is
not available, use the value of 0.1 cubic inch internal volume for
each pressure transducer, and 0.2 cubic inches for each pressure
gauge.
In addition, for heat pumps that have a single expansion device
located in the outdoor unit to serve each indoor unit, the internal
volume of the pressure system at location 2 (as indicated in Table
2) must be no more than 1 cubic inches. Once the pressure
measurement lines are set up, no change should be made until all
tests are finished.
2.2.1 Defrost Control Settings
Set heat pump defrost controls at the normal settings which most
typify those encountered in generalized climatic region IV. (Refer
to Figure 1 and Table 20 of section 4.2 of this appendix for
information on region IV.) For heat pumps that use a time-adaptive
defrost control system (see section 1.2 of this appendix,
Definitions), the manufacturer must specify in the certification
report the frosting interval to be used during frost accumulation
tests and provide the procedure for manually initiating the defrost
at the specified time.
2.2.2 Special Requirements for Units Having a Multiple-Speed Outdoor
Fan
Configure the multiple-speed outdoor fan according to the
installation manual included with the unit by the manufacturer, and
thereafter, leave it unchanged for all tests. The controls of the
unit must regulate the operation of the outdoor fan during all lab
tests except dry coil cooling mode tests. For dry coil cooling mode
tests, the outdoor fan must operate at the same speed used during
the required wet coil test conducted at the same outdoor test
conditions.
2.2.3 Special Requirements for Multi-Split Air Conditioners and Heat
Pumps and Ducted Systems Using a Single Indoor Section Containing
Multiple Indoor Blowers That Would Normally Operate Using Two or More
Indoor Thermostats
Because these systems will have more than one indoor blower and
possibly multiple outdoor fans and compressor systems, references in
this test procedure to a singular indoor blower, outdoor fan, and/or
compressor means all indoor blowers, all outdoor fans, and all
compressor systems that are energized during the test.
a. Additional requirements for multi-split air conditioners and
heat pumps. For any test where the system is operated at part load
(i.e., one or more compressors ``off'', operating at the
intermediate or minimum compressor speed, or at low compressor
capacity), the manufacturer must designate in the certification
report the indoor coil(s) that are not providing heating or cooling
during the test. For variable-speed systems, the manufacturer must
designate in the certification report at least one indoor unit that
is not providing heating or cooling for all tests conducted at
minimum compressor speed. For all other part-load tests, the
manufacturer must choose to turn off zero, one, two, or more indoor
units. The chosen configuration must remain unchanged for all tests
conducted at the same compressor speed/capacity. For any indoor coil
that is not providing heating or cooling during a test, cease forced
airflow through this indoor coil and block its outlet duct.
b. Additional requirements for ducted split systems with a
single indoor unit containing multiple indoor blowers (or for
single-package units with an indoor section containing multiple
indoor blowers) where the indoor blowers are designed to cycle on
and off independently of one another and are not controlled such
that all indoor blowers are modulated to always operate at the same
air volume rate or speed. For any test where the system is operated
at its lowest capacity--i.e., the lowest total air volume rate
allowed when operating the single-speed compressor or when operating
at low compressor capacity--turn off indoor blowers accounting for
at least one-third of the full-load air volume rate unless prevented
by the controls of the unit. In such cases, turn off as many indoor
blowers as permitted by the unit's controls. Where more than one
option exists for meeting this ``off'' requirement, the manufacturer
must indicate in its certification report which indoor blower(s) are
turned off. The chosen configuration shall remain unchanged for all
tests conducted at the same lowest capacity configuration. For any
indoor coil turned off during a test, cease forced airflow through
any outlet duct connected to a switched-off indoor blower.
c. For test setups where the laboratory's physical limitations
require use of more than the required line length of 25 feet as
listed in section 2.2.a.(4) of this appendix, then the actual
refrigerant line length used by the laboratory may exceed the
required length and the refrigerant line length correction factors
in Table 4 of AHRI 1230-2010 are applied to the cooling capacity
measured for each cooling mode test.
2.2.4 Wet-Bulb Temperature Requirements for the Air Entering the Indoor
and Outdoor Coils
2.2.4.1 Cooling Mode Tests
For wet-coil cooling mode tests, regulate the water vapor
content of the air entering the indoor unit so that the wet-bulb
temperature is as listed in Tables 5 to 8. As noted in these same
tables, achieve a wet-bulb temperature during dry-coil cooling mode
tests that results in no condensate forming on the indoor coil.
Controlling the water vapor content of the air entering the outdoor
side of the unit is not required for cooling mode tests except when
testing:
(1) Units that reject condensate to the outdoor coil during wet
coil tests. Tables 5-8 list the applicable wet-bulb temperatures.
(2) Single-package units where all or part of the indoor section
is located in the outdoor test room. The average dew point
temperature of the air entering the outdoor coil during wet coil
tests must be within 3.0 [deg]F of the average dew point
temperature of the air entering the indoor coil over the 30-minute
data collection interval described in section 3.3 of this appendix.
For dry coil tests on such units, it may be necessary to limit the
moisture content of the air entering the outdoor coil of the unit to
meet the requirements of section 3.4 of this appendix.
2.2.4.2 Heating Mode Tests
For heating mode tests, regulate the water vapor content of the
air entering the outdoor unit to the applicable wet-bulb temperature
listed in Tables 12 to 15. The wet-bulb temperature entering the
indoor side of the heat pump must not exceed 60 [deg]F.
Additionally, if the Outdoor Air Enthalpy test method (section
2.10.1 of this appendix) is used while testing a single-package heat
pump where all or part of the outdoor section is located in the
indoor test room, adjust the wet-bulb temperature for the air
entering the indoor side to yield an indoor-side dew point
temperature that is as close as reasonably possible to the dew point
temperature of the outdoor-side entering air.
[[Page 1542]]
2.2.5 Additional Refrigerant Charging Requirements
2.2.5.1 Instructions to Use for Charging
a. Where the manufacturer's installation instructions contain
two sets of refrigerant charging criteria, one for field
installations and one for lab testing, use the field installation
criteria.
b. For systems consisting of an outdoor unit manufacturer's
outdoor section and indoor section with differing charging
procedures, adjust the refrigerant charge per the outdoor
installation instructions.
c. For systems consisting of an outdoor unit manufacturer's
outdoor unit and an independent coil manufacturer's indoor unit with
differing charging procedures, adjust the refrigerant charge per the
indoor unit's installation instructions. If instructions are
provided only with the outdoor unit or are provided only with an
independent coil manufacturer's indoor unit, then use the provided
instructions.
2.2.5.2 Test(s) to Use for Charging
a. Use the tests or operating conditions specified in the
manufacturer's installation instructions for charging. The
manufacturer's installation instructions may specify use of tests
other than the A or A2 test for charging, but, unless the
unit is a heating-only heat pump, determine the air volume rate by
the A or A2 test as specified in section 3.1 of this
appendix.
b. If the manufacturer's installation instructions do not
specify a test or operating conditions for charging or there are no
manufacturer's instructions, use the following test(s):
(1) For air conditioners or cooling and heating heat pumps, use
the A or A2 test.
(2) For cooling and heating heat pumps that do not operate in
the H1 or H12 test (e.g. due to shut down by the unit
limiting devices) when tested using the charge determined at the A
or A2 test, and for heating-only heat pumps, use the H1
or H12 test.
2.2.5.3 Parameters to Set and Their Target Values
a. Consult the manufacturer's installation instructions
regarding which parameters (e.g., superheat) to set and their target
values. If the instructions provide ranges of values, select target
values equal to the midpoints of the provided ranges.
b. In the event of conflicting information between charging
instructions (i.e., multiple conditions given for charge adjustment
where all conditions specified cannot be met), follow the following
hierarchy.
(1) For fixed orifice systems:
(i) Superheat
(ii) High side pressure or corresponding saturation or dew-point
temperature
(iii) Low side pressure or corresponding saturation or dew-point
temperature
(iv) Low side temperature
(v) High side temperature
(vi) Charge weight
(2) For expansion valve systems:
(i) Subcooling
(ii) High side pressure or corresponding saturation or dew-point
temperature
(iii) Low side pressure or corresponding saturation or dew-point
temperature
(iv) Approach temperature (difference between temperature of
liquid leaving condenser and condenser average inlet air
temperature)
(v) Charge weight
c. If there are no installation instructions and/or they do not
provide parameters and target values, set superheat to a target
value of 12[emsp14][deg]F for fixed orifice systems or set
subcooling to a target value of 10[emsp14][deg]F for expansion valve
systems.
2.2.5.4 Charging Tolerances
a. If the manufacturer's installation instructions specify
tolerances on target values for the charging parameters, set the
values within these tolerances.
b. Otherwise, set parameter values within the following test
condition tolerances for the different charging parameters:
11. Superheat: +/- 2.0[emsp14][deg]F
12. Subcooling: +/- 2.0[emsp14][deg]F
13. High side pressure or corresponding saturation or dew point
temperature: +/- 4.0 psi or +/- 1.0[emsp14][deg]F
14. Low side pressure or corresponding saturation or dew point
temperature: +/- 2.0 psi or +/- 0.8[emsp14][deg]F
15. High side temperature: +/- 2.0[emsp14][deg]F
16. Low side temperature: +/- 2.0[emsp14][deg]F
17. Approach temperature: +/- 1.0[emsp14][deg]F
18. Charge weight: +/- 2.0 ounce
2.2.5.5 Special Charging Instructions
a. Cooling and Heating Heat Pumps
If, using the initial charge set in the A or A2 test,
the conditions are not within the range specified in manufacturer's
installation instructions for the H1 or H12 test, make as
small as possible an adjustment to obtain conditions for this test
in the specified range. After this adjustment, recheck conditions in
the A or A2 test to confirm that they are still within
the specified range for the A or A2 test.
b. Single-Package Systems
i. Unless otherwise directed by the manufacturer's installation
instructions, install one or more refrigerant line pressure gauges
during the setup of the unit, located depending on the parameters
used to verify or set charge, as described:
(1) Install a pressure gauge at the location of the service
valve on the liquid line if charging is on the basis of subcooling,
or high side pressure or corresponding saturation or dew point
temperature;
(2) Install a pressure gauge at the location of the service
valve on the suction line if charging is on the basis of superheat,
or low side pressure or corresponding saturation or dew point
temperature.
ii. Use methods for installing pressure gauge(s) at the required
location(s) as indicated in manufacturer's instructions if
specified.
2.2.5.6 Near-Azeotropic and Zeotropic Refrigerants
Perform charging of near-azeotropic and zeotropic refrigerants
only with refrigerant in the liquid state.
2.2.5.7 Adjustment of Charge Between Tests
After charging the system as described in this test procedure,
use the set refrigerant charge for all tests used to determine
performance. Do not adjust the refrigerant charge at any point
during testing. If measurements indicate that refrigerant charge has
leaked during the test, repair the refrigerant leak, repeat any
necessary set-up steps, and repeat all tests.
2.3 Indoor Air Volume Rates
If a unit's controls allow for overspeeding the indoor blower
(usually on a temporary basis), take the necessary steps to prevent
overspeeding during all tests.
2.3.1 Cooling Tests
a. Set indoor blower airflow-control settings (e.g., fan motor
pin settings, fan motor speed) according to the requirements that
are specified in section 3.1.4 of this appendix.
b. Express the Cooling full-load air volume rate, the Cooling
Minimum Air Volume Rate, and the Cooling Intermediate Air Volume
Rate in terms of standard air.
2.3.2 Heating Tests
a. Set indoor blower airflow-control settings (e.g., fan motor
pin settings, fan motor speed) according to the requirements that
are specified in section 3.1.4 of this appendix.
b. Express the heating full-load air volume rate, the heating
minimum air volume rate, the heating intermediate air volume rate,
and the heating nominal air volume rate in terms of standard air.
2.4 Indoor Coil Inlet and Outlet Duct Connections
Insulate and/or construct the outlet plenum as described in
section 2.4.1 of this appendix and, if installed, the inlet plenum
described in section 2.4.2 of this appendix with thermal insulation
having a nominal overall resistance (R-value) of at least 19
hr[middot]ft\2\ [deg]F/Btu.
2.4.1 Outlet Plenum for the Indoor Unit
a. Attach a plenum to the outlet of the indoor coil. (Note: For
some packaged systems, the indoor coil may be located in the outdoor
test room.)
b. For systems having multiple indoor coils, or multiple indoor
blowers within a single indoor section, attach a plenum to each
indoor coil or indoor blower outlet. In order to reduce the number
of required airflow measurement apparatuses (section 2.6 of this
appendix), each such apparatus may serve multiple outlet plenums
connected to a single common duct leading to the apparatus. More
than one indoor test room may be used, which may use one or more
common ducts leading to one or more airflow measurement apparatuses
within each test room that contains multiple indoor coils. At the
plane where each plenum enters a common duct, install an adjustable
airflow damper and use it to equalize the static pressure in each
plenum. The outlet air temperature grid(s) (section 2.5.4 of this
appendix) and airflow measuring apparatus shall be located
downstream of the inlet(s) to the common duct(s). For multiple-
circuit (or multi-circuit) systems for which each indoor coil outlet
is measured separately and its outlet plenum is not connected to a
common duct connecting multiple outlet plenums,
[[Page 1543]]
install the outlet air temperature grid and airflow measuring
apparatus at each outlet plenum.
c. For small-duct, high-velocity systems, install an outlet
plenum that has a diameter that is equal to or less than the value
listed in Table 3. The limit depends only on the Cooling full-load
air volume rate (see section 3.1.4.1.1 of this appendix) and is
effective regardless of the flange dimensions on the outlet of the
unit (or an air supply plenum adapter accessory, if installed in
accordance with the manufacturer's installation instructions).
d. Add a static pressure tap to each face of the (each) outlet
plenum, if rectangular, or at four evenly distributed locations
along the circumference of an oval or round plenum. Create a
manifold that connects the four static pressure taps. Figure 9 of
ANSI/ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3)
shows allowed options for the manifold configuration. The cross-
sectional dimensions of plenum must be equal to the dimensions of
the indoor unit outlet. See Figures 7a, 7b, and 7c of ANSI/ASHRAE
37-2009 for the minimum length of the (each) outlet plenum and the
locations for adding the static pressure taps for ducted blower coil
indoor units and single-package systems. See Figure 8 of ANSI/ASHRAE
37-2009 for coil-only indoor units.
Table 3--Size of Outlet Plenum for Small-Duct High-Velocity Indoor Units
------------------------------------------------------------------------
Maximum diameter*
Cooling full-load air volume rate (scfm) of outlet plenum
(inches)
------------------------------------------------------------------------
<=500................................................ 6
501 to 700........................................... 7
701 to 900........................................... 8
901 to 1100.......................................... 9
1101 to 1400......................................... 10
1401 to 1750......................................... 11
------------------------------------------------------------------------
* If the outlet plenum is rectangular, calculate its equivalent diameter
using (4A/P,) where A is the cross-sectional area and P is the
perimeter of the rectangular plenum, and compare it to the listed
maximum diameter.
2.4.2 Inlet Plenum for the Indoor Unit
Install an inlet plenum when testing a coil-only indoor unit, a
ducted blower coil indoor unit, or a single-package system. See
Figures 7b and 7c of ANSI/ASHRAE 37-2009 for cross-sectional
dimensions, the minimum length of the inlet plenum, and the
locations of the static-pressure taps for ducted blower coil indoor
units and single-package systems. See Figure 8 of ANSI/ASHRAE 37-
2009 for coil-only indoor units. The inlet plenum duct size shall
equal the size of the inlet opening of the air-handling (blower
coil) unit or furnace. For a ducted blower coil indoor unit the set
up may omit the inlet plenum if an inlet airflow prevention device
is installed with a straight internally unobstructed duct on its
outlet end with a minimum length equal to 1.5 times the square root
of the cross-sectional area of the indoor unit inlet. See section
2.1.5.2 of this appendix for requirements for the locations of
static pressure taps built into the inlet airflow prevention device.
For all of these arrangements, make a manifold that connects the
four static-pressure taps using one of the three configurations
specified in section 2.4.1.d. of this appendix. Never use an inlet
plenum when testing a non-ducted system.
2.5 Indoor Coil Air Property Measurements and Airflow Prevention
Devices.
Follow instructions for indoor coil air property measurements as
described in section 2.14 of this appendix, unless otherwise
instructed in this section.
a. Measure the dry-bulb temperature and water vapor content of
the air entering and leaving the indoor coil. If needed, use an air
sampling device to divert air to a sensor(s) that measures the water
vapor content of the air. See section 5.3 of ANSI/ASHRAE 41.1-2013
(incorporated by reference, see Sec. 430.3) for guidance on
constructing an air sampling device. No part of the air sampling
device or the tubing transferring the sampled air to the sensor must
be within two inches of the test chamber floor, and the transfer
tubing must be insulated. The sampling device may also be used for
measurement of dry bulb temperature by transferring the sampled air
to a remotely located sensor(s). The air sampling device and the
remotely located temperature sensor(s) may be used to determine the
entering air dry bulb temperature during any test. The air sampling
device and the remotely located sensor(s) may be used to determine
the leaving air dry bulb temperature for all tests except:
(1) Cyclic tests; and
(2) Frost accumulation tests.
b. Install grids of temperature sensors to measure dry bulb
temperatures of both the entering and leaving airstreams of the
indoor unit. These grids of dry bulb temperature sensors may be used
to measure average dry bulb temperature entering and leaving the
indoor unit in all cases (as an alternative to the dry bulb sensor
measuring the sampled air). The leaving airstream grid is required
for measurement of average dry bulb temperature leaving the indoor
unit for cyclic tests and frost accumulation tests. The grids are
also required to measure the air temperature distribution of the
entering and leaving airstreams as described in sections 3.1.8 of
this appendix. Two such grids may be applied as a thermopile, to
directly obtain the average temperature difference rather than
directly measuring both entering and leaving average temperatures.
c. Use of airflow prevention devices. Use an inlet and outlet
air damper box, or use an inlet upturned duct and an outlet air
damper box when conducting one or both of the cyclic tests listed in
sections 3.2 and 3.6 of this appendix on ducted systems. If not
conducting any cyclic tests, an outlet air damper box is required
when testing ducted and non-ducted heat pumps that cycle off the
indoor blower during defrost cycles and there is no other means for
preventing natural or forced convection through the indoor unit when
the indoor blower is off. Never use an inlet damper box or an inlet
upturned duct when testing non-ducted indoor units. An inlet
upturned duct is a length of ductwork installed upstream from the
inlet such that the indoor duct inlet opening, facing upwards, is
sufficiently high to prevent natural convection transfer out of the
duct. If an inlet upturned duct is used, install a dry bulb
temperature sensor near the inlet opening of the indoor duct at a
centerline location not higher than the lowest elevation of the duct
edges at the inlet, and ensure that any pair of 5-minute averages of
the dry bulb temperature at this location, measured at least every
minute during the compressor OFF period of the cyclic test, do not
differ by more than 1.0[emsp14][deg]F.
2.5.1 Test Set-Up on the Inlet Side of the Indoor Coil: for Cases Where
the Inlet Airflow Prevention Device is Installed
a. Install an airflow prevention device as specified in section
2.5.1.1 or 2.5.1.2 of this appendix, whichever applies.
b. For an inlet damper box, locate the grid of entering air dry-
bulb temperature sensors, if used, and the air sampling device, or
the sensor used to measure the water vapor content of the inlet air,
at a location immediately upstream of the damper box inlet. For an
inlet upturned duct, locate the grid of entering air dry-bulb
temperature sensors, if used, and the air sampling device, or the
sensor used to measure the water vapor content of the inlet air, at
a location at least one foot downstream from the beginning of the
insulated portion of the duct but before the static pressure
measurement.
2.5.1.1 If the section 2.4.2 inlet plenum is installed,
construct the airflow prevention device having a cross-sectional
flow area equal to or greater than the flow area of the inlet
plenum. Install the airflow prevention device upstream of the inlet
plenum and construct ductwork connecting it to the inlet plenum. If
needed, use an adaptor plate or a transition duct section to connect
the airflow prevention device with the inlet plenum. Insulate the
ductwork and inlet plenum with thermal insulation that has a nominal
overall resistance (R-value) of at least 19 hr [middot] ft\2\
[middot] [deg]F/Btu.
2.5.1.2 If the section 2.4.2 inlet plenum is not installed,
construct the airflow prevention device having a cross-sectional
flow area equal to or greater than the flow area of the air inlet of
the indoor unit. Install the airflow prevention device immediately
upstream of the inlet of the indoor unit. If needed, use an adaptor
plate or a short transition duct section to connect the airflow
prevention device with the unit's air inlet. Add static pressure
taps at the center of each face of a rectangular airflow prevention
device, or at four evenly distributed locations along the
circumference of an oval or round airflow prevention device. Locate
the pressure taps at a distance from the indoor unit inlet equal to
0.5 times the square root of the cross sectional area of the indoor
unit inlet. This location must be between the damper and the inlet
of the indoor unit, if a damper is used. Make a manifold that
connects the four static pressure taps using one of the
configurations shown in Figure 9 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3). Insulate the ductwork
with thermal insulation that has a nominal overall resistance (R-
value) of at least 19 hr[middot]ft\2\[middot][deg]F/Btu.
[[Page 1544]]
2.5.2 Test Set-Up on the Inlet Side of the Indoor Unit: for Cases Where
No Airflow Prevention Device is Installed
If using the section 2.4.2 inlet plenum and a grid of dry bulb
temperature sensors, mount the grid at a location upstream of the
static pressure taps described in section 2.4.2 of this appendix,
preferably at the entrance plane of the inlet plenum. If the section
2.4.2 inlet plenum is not used (i.e. for non-ducted units) locate a
grid approximately 6 inches upstream of the indoor unit inlet. In
the case of a system having multiple non-ducted indoor units, do
this for each indoor unit. Position an air sampling device, or the
sensor used to measure the water vapor content of the inlet air,
immediately upstream of the (each) entering air dry-bulb temperature
sensor grid. If a grid of sensors is not used, position the entering
air sampling device (or the sensor used to measure the water vapor
content of the inlet air) as if the grid were present.
2.5.3 Indoor Coil Static Pressure Difference Measurement
Fabricate pressure taps meeting all requirements described in
section 6.5.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see
Sec. 430.3) and illustrated in Figure 2A of AMCA 210-2007
(incorporated by reference, see Sec. 430.3), however, if adhering
strictly to the description in section 6.5.2 of ANSI/ASHRAE 37-2009,
the minimum pressure tap length of 2.5 times the inner diameter of
Figure 2A of AMCA 210-2007 is waived. Use a differential pressure
measuring instrument that is accurate to within 0.01
inches of water and has a resolution of at least 0.01 inches of
water to measure the static pressure difference between the indoor
coil air inlet and outlet. Connect one side of the differential
pressure instrument to the manifolded pressure taps installed in the
outlet plenum. Connect the other side of the instrument to the
manifolded pressure taps located in either the inlet plenum or
incorporated within the airflow prevention device. For non-ducted
systems that are tested with multiple outlet plenums, measure the
static pressure within each outlet plenum relative to the
surrounding atmosphere.
2.5.4 Test Set-Up on the Outlet Side of the Indoor Coil
a. Install an interconnecting duct between the outlet plenum
described in section 2.4.1 of this appendix and the airflow
measuring apparatus described below in section 2.6 of this appendix.
The cross-sectional flow area of the interconnecting duct must be
equal to or greater than the flow area of the outlet plenum or the
common duct used when testing non-ducted units having multiple
indoor coils. If needed, use adaptor plates or transition duct
sections to allow the connections. To minimize leakage, tape joints
within the interconnecting duct (and the outlet plenum). Construct
or insulate the entire flow section with thermal insulation having a
nominal overall resistance (R-value) of at least 19
hr[middot]ft\2\[middot] [deg]F/Btu.
b. Install a grid(s) of dry-bulb temperature sensors inside the
interconnecting duct. Also, install an air sampling device, or the
sensor(s) used to measure the water vapor content of the outlet air,
inside the interconnecting duct. Locate the dry-bulb temperature
grid(s) upstream of the air sampling device (or the in-duct
sensor(s) used to measure the water vapor content of the outlet
air). Turn off the sampler fan motor during the cyclic tests. Air
leaving an indoor unit that is sampled by an air sampling device for
remote water-vapor-content measurement must be returned to the
interconnecting duct at a location:
(1) Downstream of the air sampling device;
(2) On the same side of the outlet air damper as the air
sampling device; and
(3) Upstream of the section 2.6 airflow measuring apparatus.
2.5.4.1 Outlet Air Damper Box Placement and Requirements
If using an outlet air damper box (see section 2.5 of this
appendix), the leakage rate from the combination of the outlet
plenum, the closed damper, and the duct section that connects these
two components must not exceed 20 cubic feet per minute when a
negative pressure of 1 inch of water column is maintained at the
plenum's inlet.
2.5.4.2 Procedures to Minimize Temperature Maldistribution
Use these procedures if necessary to correct temperature
maldistributions. Install a mixing device(s) upstream of the outlet
air, dry-bulb temperature grid (but downstream of the outlet plenum
static pressure taps). Use a perforated screen located between the
mixing device and the dry-bulb temperature grid, with a maximum open
area of 40 percent. One or both items should help to meet the
maximum outlet air temperature distribution specified in section
3.1.8 of this appendix. Mixing devices are described in sections
5.3.2 and 5.3.3 of ANSI/ASHRAE 41.1-2013 and section 5.2.2 of ASHRAE
41.2-1987 (RA 1992) (incorporated by reference, see Sec. 430.3).
2.5.4.3 Minimizing Air Leakage
For small-duct, high-velocity systems, install an air damper
near the end of the interconnecting duct, just prior to the
transition to the airflow measuring apparatus of section 2.6 of this
appendix. To minimize air leakage, adjust this damper such that the
pressure in the receiving chamber of the airflow measuring apparatus
is no more than 0.5 inch of water higher than the surrounding test
room ambient. If applicable, in lieu of installing a separate
damper, use the outlet air damper box of sections 2.5 and 2.5.4.1 of
this appendix if it allows variable positioning. Also apply these
steps to any conventional indoor blower unit that creates a static
pressure within the receiving chamber of the airflow measuring
apparatus that exceeds the test room ambient pressure by more than
0.5 inches of water column.
2.5.5 Dry Bulb Temperature Measurement
a. Measure dry bulb temperatures as specified in sections 4,
5.3, 6, and 7 of ANSI/ASHRAE 41.1-2013 (incorporated by reference,
see Sec. 430.3).
b. Distribute the sensors of a dry-bulb temperature grid over
the entire flow area. The required minimum is 9 sensors per grid.
2.5.6 Water Vapor Content Measurement
Determine water vapor content by measuring dry-bulb temperature
combined with the air wet-bulb temperature, dew point temperature,
or relative humidity. If used, construct and apply wet-bulb
temperature sensors as specified in sections 4, 5, 6, 7.2, 7.3, and
7.4 of ASHRAE 41.6-2014 (incorporated by reference, see Sec.
430.3). The temperature sensor (wick removed) must be accurate to
within 0.2[emsp14][deg]F. If used, apply dew point
hygrometers as specified in sections 4, 5, 6, 7.1, and 7.4 of ASHRAE
41.6-2014. The dew point hygrometers must be accurate to within
0.4[emsp14][deg]F when operated at conditions that
result in the evaluation of dew points above 35[emsp14][deg]F. If
used, a relative humidity (RH) meter must be accurate to within
0.7% RH. Other means to determine the psychrometric
state of air may be used as long as the measurement accuracy is
equivalent to or better than the accuracy achieved from using a wet-
bulb temperature sensor that meets the above specifications.
2.5.7 Air Damper Box Performance Requirements
If used (see section 2.5 of this appendix), the air damper
box(es) must be capable of being completely opened or completely
closed within 10 seconds for each action.
2.6 Airflow Measuring Apparatus
a. Fabricate and operate an airflow measuring apparatus as
specified in section 6.2 and 6.3 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3). Place the static
pressure taps and position the diffusion baffle (settling means)
relative to the chamber inlet as indicated in Figure 12 of AMCA 210-
07 and/or Figure 14 of ASHRAE 41.2-1987 (RA 1992) (incorporated by
reference, see Sec. 430.3). When measuring the static pressure
difference across nozzles and/or velocity pressure at nozzle throats
using electronic pressure transducers and a data acquisition system,
if high frequency fluctuations cause measurement variations to
exceed the test tolerance limits specified in section 9.2 and Table
2 of ANSI/ASHRAE 37-2009, dampen the measurement system such that
the time constant associated with response to a step change in
measurement (time for the response to change 63% of the way from the
initial output to the final output) is no longer than five seconds.
b. Connect the airflow measuring apparatus to the
interconnecting duct section described in section 2.5.4 of this
appendix. See sections 6.1.1, 6.1.2, and 6.1.4, and Figures 1, 2,
and 4 of ANSI/ASHRAE 37-2009; and Figures D1, D2, and D4 of AHRI
210/240-2008 (incorporated by reference, see Sec. 430.3) with
Addendum 1 and 2 for illustrative examples of how the test apparatus
may be applied within a complete laboratory set-up. Instead of
following one of these examples, an alternative set-up may be used
to handle the air leaving the airflow measuring apparatus and to
supply properly conditioned air to the test unit's inlet. The
alternative set-up, however, must not interfere with the prescribed
means for measuring airflow rate, inlet and outlet air temperatures,
inlet and outlet water vapor contents, and external static
pressures, nor create abnormal
[[Page 1545]]
conditions surrounding the test unit. (Note: Do not use an enclosure
as described in section 6.1.3 of ANSI/ASHRAE 37-2009 when testing
triple-split units.)
2.7 Electrical Voltage Supply
Perform all tests at the voltage specified in section 6.1.3.2 of
AHRI 210/240-2008 (incorporated by reference, see Sec. 430.3) for
``Standard Rating Tests.'' If either the indoor or the outdoor unit
has a 208V or 200V nameplate voltage and the other unit has a 230V
nameplate rating, select the voltage supply on the outdoor unit for
testing. Otherwise, supply each unit with its own nameplate voltage.
Measure the supply voltage at the terminals on the test unit using a
volt meter that provides a reading that is accurate to within 1.0 percent of the measured quantity.
2.8 Electrical Power and Energy Measurements
a. Use an integrating power (watt-hour) measuring system to
determine the electrical energy or average electrical power supplied
to all components of the air conditioner or heat pump (including
auxiliary components such as controls, transformers, crankcase
heater, integral condensate pump on non-ducted indoor units, etc.).
The watt-hour measuring system must give readings that are accurate
to within 0.5 percent. For cyclic tests, this accuracy
is required during both the ON and OFF cycles. Use either two
different scales on the same watt-hour meter or two separate watt-
hour meters. Activate the scale or meter having the lower power
rating within 15 seconds after beginning an OFF cycle. Activate the
scale or meter having the higher power rating within 15 seconds
prior to beginning an ON cycle. For ducted blower coil systems, the
ON cycle lasts from compressor ON to indoor blower OFF. For ducted
coil-only systems, the ON cycle lasts from compressor ON to
compressor OFF. For non-ducted units, the ON cycle lasts from indoor
blower ON to indoor blower OFF. When testing air conditioners and
heat pumps having a variable-speed compressor, avoid using an
induction watt/watt-hour meter.
b. When performing section 3.5 and/or 3.8 cyclic tests on non-
ducted units, provide instrumentation to determine the average
electrical power consumption of the indoor blower motor to within
1.0 percent. If required according to sections 3.3, 3.4,
3.7, 3.9.1 of this appendix, and/or 3.10 of this appendix, this same
instrumentation requirement (to determine the average electrical
power consumption of the indoor blower motor to within 1.0 percent) applies when testing air conditioners and heat
pumps having a variable-speed constant-air-volume-rate indoor blower
or a variable-speed, variable-air-volume-rate indoor blower.
2.9 Time Measurements
Make elapsed time measurements using an instrument that yields
readings accurate to within 0.2 percent.
2.10 Test Apparatus for the Secondary Space Conditioning Capacity
Measurement
For all tests, use the indoor air enthalpy method to measure the
unit's capacity. This method uses the test set-up specified in
sections 2.4 to 2.6 of this appendix. In addition, for all steady-
state tests, conduct a second, independent measurement of capacity
as described in section 3.1.1 of this appendix. For split systems,
use one of the following secondary measurement methods: outdoor air
enthalpy method, compressor calibration method, or refrigerant
enthalpy method. For single-package units, use either the outdoor
air enthalpy method or the compressor calibration method as the
secondary measurement.
2.10.1 Outdoor Air Enthalpy Method
a. To make a secondary measurement of indoor space conditioning
capacity using the outdoor air enthalpy method, do the following:
(1) Measure the electrical power consumption of the test unit;
(2) Measure the air-side capacity at the outdoor coil; and
(3) Apply a heat balance on the refrigerant cycle.
b. The test apparatus required for the outdoor air enthalpy
method is a subset of the apparatus used for the indoor air enthalpy
method. Required apparatus includes the following:
(1) On the outlet side, an outlet plenum containing static
pressure taps (sections 2.4, 2.4.1, and 2.5.3 of this appendix),
(2) An airflow measuring apparatus (section 2.6 of this
appendix),
(3) A duct section that connects these two components and itself
contains the instrumentation for measuring the dry-bulb temperature
and water vapor content of the air leaving the outdoor coil
(sections 2.5.4, 2.5.5, and 2.5.6 of this appendix), and
(4) On the inlet side, a sampling device and temperature grid
(section 2.11.b of this appendix).
c. During the free outdoor air tests described in sections
3.11.1 and 3.11.1.1 of this appendix, measure the evaporator and
condenser temperatures or pressures. On both the outdoor coil and
the indoor coil, solder a thermocouple onto a return bend located at
or near the midpoint of each coil or at points not affected by vapor
superheat or liquid subcooling. Alternatively, if the test unit is
not sensitive to the refrigerant charge, install pressure gages to
the access valves or to ports created from tapping into the suction
and discharge lines according to sections 7.4.2 and 8.2.5 of ANSI/
ASHRAE 37-2009. Use this alternative approach when testing a unit
charged with a zeotropic refrigerant having a temperature glide in
excess of 1[emsp14][deg]F at the specified test conditions.
2.10.2 Compressor Calibration Method
Measure refrigerant pressures and temperatures to determine the
evaporator superheat and the enthalpy of the refrigerant that enters
and exits the indoor coil. Determine refrigerant flow rate or, when
the superheat of the refrigerant leaving the evaporator is less than
5[emsp14][deg]F, total capacity from separate calibration tests
conducted under identical operating conditions. When using this
method, install instrumentation and measure refrigerant properties
according to section 7.4.2 and 8.2.5 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3). If removing the
refrigerant before applying refrigerant lines and subsequently
recharging, use the steps in 7.4.2 of ANSI/ASHRAE 37-2009 in
addition to the methods of section 2.2.5 of this appendix to confirm
the refrigerant charge. Use refrigerant temperature and pressure
measuring instruments that meet the specifications given in sections
5.1.1 and 5.2 of ANSI/ASHRAE 37-2009.
2.10.3 Refrigerant Enthalpy Method
For this method, calculate space conditioning capacity by
determining the refrigerant enthalpy change for the indoor coil and
directly measuring the refrigerant flow rate. Use section 7.5.2 of
ANSI/ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3) for
the requirements for this method, including the additional
instrumentation requirements, and information on placing the flow
meter and a sight glass. Use refrigerant temperature, pressure, and
flow measuring instruments that meet the specifications given in
sections 5.1.1, 5.2, and 5.5.1 of ANSI/ASHRAE 37-2009. Refrigerant
flow measurement device(s), if used, must be either elevated at
least two feet from the test chamber floor or placed upon insulating
material having a total thermal resistance of at least R-12 and
extending at least one foot laterally beyond each side of the
device(s)' exposed surfaces.
2.11 Measurement of Test Room Ambient Conditions
Follow instructions for setting up air sampling device and
aspirating psychrometer as described in section 2.14 of this
appendix, unless otherwise instructed in this section.
a. If using a test set-up where air is ducted directly from the
conditioning apparatus to the indoor coil inlet (see Figure 2, Loop
Air-Enthalpy Test Method Arrangement, of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3)), add instrumentation
to permit measurement of the indoor test room dry-bulb temperature.
b. On the outdoor side, use one of the following two approaches,
except that approach (1) is required for all evaporatively cooled
units and units that transfer condensate to the outdoor unit for
evaporation using condenser heat.
(1) Use sampling tree air collection on all air-inlet surfaces
of the outdoor unit.
(2) Use sampling tree air collection on one or more faces of the
outdoor unit and demonstrate air temperature uniformity as follows.
Install a grid of evenly distributed thermocouples on each air-
permitting face on the inlet of the outdoor unit. Install the
thermocouples on the air sampling device, locate them individually
or attach them to a wire structure. If not installed on the air
sampling device, install the thermocouple grid 6 to 24 inches from
the unit. Evenly space the thermocouples across the coil inlet
surface and install them to avoid sampling of discharge air or
blockage of air recirculation. The grid of thermocouples must
provide at least 16 measuring points per face or one measurement per
square foot of inlet face
[[Page 1546]]
area, whichever is less. Construct this grid and use as per section
5.3 of ANSI/ASHRAE 41.1-2013 (incorporated by reference, see Sec.
430.3). The maximum difference between the average temperatures
measured during the test period of any two pairs of these individual
thermocouples located at any of the faces of the inlet of the
outdoor unit, must not exceed 2.0[emsp14][deg]F, otherwise use
approach (1).
Locate the air sampling devices at the geometric center of each
side; the branches may be oriented either parallel or perpendicular
to the longer edges of the air inlet area. Size the air sampling
devices in the outdoor air inlet location such that they cover at
least 75% of the face area of the side of the coil that they are
measuring.
Review air distribution at the test facility point of supply to
the unit and remediate as necessary prior to the beginning of
testing. Mixing fans can be used to ensure adequate air distribution
in the test room. If used, orient mixing fans such that they are
pointed away from the air intake so that the mixing fan exhaust does
not affect the outdoor coil air volume rate. Particular attention
should be given to prevent the mixing fans from affecting (enhancing
or limiting) recirculation of condenser fan exhaust air back through
the unit. Any fan used to enhance test room air mixing shall not
cause air velocities in the vicinity of the test unit to exceed 500
feet per minute.
The air sampling device may be larger than the face area of the
side being measured. Take care, however, to prevent discharge air
from being sampled. If an air sampling device dimension extends
beyond the inlet area of the unit, block holes in the air sampling
device to prevent sampling of discharge air. Holes can be blocked to
reduce the region of coverage of the intake holes both in the
direction of the trunk axis or perpendicular to the trunk axis. For
intake hole region reduction in the direction of the trunk axis,
block holes of one or more adjacent pairs of branches (the branches
of a pair connect opposite each other at the same trunk location) at
either the outlet end or the closed end of the trunk. For intake
hole region reduction perpendicular to the trunk axis, block off the
same number of holes on each branch on both sides of the trunk.
Connect a maximum of four (4) air sampling devices to each
aspirating psychrometer. In order to proportionately divide the flow
stream for multiple air sampling devices for a given aspirating
psychrometer, the tubing or conduit conveying sampled air to the
psychrometer must be of equivalent lengths for each air sampling
device. Preferentially, the air sampling device should be hard
connected to the aspirating psychrometer, but if space constraints
do not allow this, the assembly shall have a means of allowing a
flexible tube to connect the air sampling device to the aspirating
psychrometer. Insulate and route the tubing or conduit to prevent
heat transfer to the air stream. Insulate any surface of the air
conveying tubing in contact with surrounding air at a different
temperature than the sampled air with thermal insulation with a
nominal thermal resistance (R-value) of at least 19 hr
ft\2\ [deg]F/Btu. Alternatively the conduit may have lower
thermal resistance if additional sensor(s) are used to measure dry
bulb temperature at the outlet of each air sampling device. No part
of the air sampling device or the tubing conducting the sampled air
to the sensors may be within two inches of the test chamber floor.
Take pairs of measurements (e.g. dry bulb temperature and wet
bulb temperature) used to determine water vapor content of sampled
air in the same location.
2.12 Measurement of Indoor Blower Speed
When required, measure fan speed using a revolution counter,
tachometer, or stroboscope that gives readings accurate to within
1.0 percent.
2.13 Measurement of Barometric Pressure
Determine the average barometric pressure during each test. Use
an instrument that meets the requirements specified in section 5.2
of ANSI/ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3).
2.14 Air Sampling Device and Aspirating Psychrometer Requirements
Make air temperature measurements in accordance with ANSI/ASHRAE
41.1-2013 (incorporated by reference, see Sec. 430.3), unless
otherwise instructed in this section.
2.14.1 Air Sampling Device Requirements
The air sampling device is intended to draw in a sample of the
air at the critical locations of a unit under test. Construct the
device from stainless steel, plastic or other suitable, durable
materials. It shall have a main flow trunk tube with a series of
branch tubes connected to the trunk tube. Holes must be on the side
of the sampler facing the upstream direction of the air source. Use
other sizes and rectangular shapes, and scale them accordingly with
the following guidelines:
1. Minimum hole density of 6 holes per square foot of area to be
sampled.
2. Sampler branch tube pitch (spacing) of 6 3 in.
3. Manifold trunk to branch diameter ratio having a minimum of
3:1 ratio.
4. Distribute hole pitch (spacing) equally over the branch (\1/
2\ pitch from the closed end to the nearest hole).
5. Maximum individual hole to branch diameter ratio of 1:2 (1:3
preferred).
The minimum average velocity through the air sampling device
holes must be 2.5 ft/s as determined by evaluating the sum of the
open area of the holes as compared to the flow area in the
aspirating psychrometer.
2.14.2 Aspirating Psychrometer
The psychrometer consists of a flow section and a fan to draw
air through the flow section and measures an average value of the
sampled air stream. At a minimum, the flow section shall have a
means for measuring the dry bulb temperature (typically, a
resistance temperature device (RTD) and a means for measuring the
humidity (RTD with wetted sock, chilled mirror hygrometer, or
relative humidity sensor). The aspirating psychrometer shall include
a fan that either can be adjusted manually or automatically to
maintain required velocity across the sensors.
Construct the psychrometer using suitable material which may be
plastic (such as polycarbonate), aluminum or other metallic
materials. Construct all psychrometers for a given system being
tested, using the same material. Design the psychrometers such that
radiant heat from the motor (for driving the fan that draws sampled
air through the psychrometer) does not affect sensor measurements.
For aspirating psychrometers, velocity across the wet bulb sensor
must be 1000 200 ft/min. For all other psychrometers,
velocity must be as specified by the sensor manufacturer.
3 Testing Procedures
3.1 General Requirements
If, during the testing process, an equipment set-up adjustment
is made that would have altered the performance of the unit during
any already completed test, then repeat all tests affected by the
adjustment. For cyclic tests, instead of maintaining an air volume
rate, for each airflow nozzle, maintain the static pressure
difference or velocity pressure during an ON period at the same
pressure difference or velocity pressure as measured during the
steady-state test conducted at the same test conditions.
Use the testing procedures in this section to collect the data
used for calculating
(1) Performance metrics for central air conditioners and heat
pumps during the cooling season;
(2) Performance metrics for heat pumps during the heating
season; and
(3) Power consumption metric(s) for central air conditioners and
heat pumps during the off mode season(s).
3.1.1 Primary and Secondary Test Methods
For all tests, use the indoor air enthalpy method test apparatus
to determine the unit's space conditioning capacity. The procedure
and data collected, however, differ slightly depending upon whether
the test is a steady-state test, a cyclic test, or a frost
accumulation test. The following sections described these
differences. For full-capacity cooling-mode test and (for a heat
pump) the full-capacity heating-mode test, use one of the acceptable
secondary methods specified in section 2.10 of this appendix to
determine indoor space conditioning capacity. Calculate this
secondary check of capacity according to section 3.11 of this
appendix. The two capacity measurements must agree to within 6
percent to constitute a valid test. For this capacity comparison,
use the Indoor Air Enthalpy Method capacity that is calculated in
section 7.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see
Sec. 430.3) (and, if testing a coil-only system, compare capacities
before making the after-test fan heat adjustments described in
section 3.3, 3.4, 3.7, and 3.10 of this appendix). However, include
the appropriate section 3.3 to 3.5 and 3.7 to 3.10 fan heat
adjustments within the indoor air enthalpy method capacities used
for the section 4 seasonal calculations of this appendix.
3.1.2 Manufacturer-Provided Equipment Overrides
Where needed, the manufacturer must provide a means for
overriding the controls of the test unit so that the compressor(s)
operates at the specified speed or capacity
[[Page 1547]]
and the indoor blower operates at the specified speed or delivers
the specified air volume rate.
3.1.3 Airflow Through the Outdoor Coil
For all tests, meet the requirements given in section 6.1.3.4 of
AHRI 210/240-2008 (incorporated by reference, see Sec. 430.3) when
obtaining the airflow through the outdoor coil.
3.1.3.1 Double-Ducted
For products intended to be installed with the outdoor airflow
ducted, install the unit with outdoor coil ductwork installed per
manufacturer installation instructions. The unit must operate
between 0.10 and 0.15 in H2O external static pressure.
Make external static pressure measurements in accordance with ANSI/
ASHRAE 37-2009 section 6.4 and 6.5.
3.1.4 Airflow Through the Indoor Coil
Determine airflow setting(s) before testing begins. Unless
otherwise specified within this or its subsections, make no changes
to the airflow setting(s) after initiation of testing.
3.1.4.1 Cooling Full-Load Air Volume Rate
3.1.4.1.1 Cooling Full-Load Air Volume Rate for Ducted Units
Identify the certified Cooling full-load air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified Cooling full-load air volume rate, use a value equal
to the certified cooling capacity of the unit times 400 scfm per
12,000 Btu/h. If there are no instructions for setting fan speed or
controls, use the as-shipped settings. Use the following procedure
to confirm and, if necessary, adjust the Cooling full-load air
volume rate and the fan speed or control settings to meet each test
procedure requirement:
a. For all ducted blower coil systems, except those having a
constant-air-volume-rate indoor blower:
Step (1) Operate the unit under conditions specified for the A
(for single-stage units) or A2 test using the certified
fan speed or controls settings, and adjust the exhaust fan of the
airflow measuring apparatus to achieve the certified Cooling full-
load air volume rate;
Step (2) Measure the external static pressure;
Step (3) If this external static pressure is equal to or greater
than the applicable minimum external static pressure cited in Table
4, the pressure requirement is satisfied; proceed to step 7 of this
section. If this external static pressure is not equal to or greater
than the applicable minimum external static pressure cited in Table
4, proceed to step 4 of this section;
Step (4) Increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until either
(i) The applicable Table 4 minimum is equaled or
(ii) The measured air volume rate equals 90 percent or less of
the Cooling full-load air volume rate, whichever occurs first;
Step (5) If the conditions of step 4 (i) of this section occur
first, the pressure requirement is satisfied; proceed to step 7 of
this section. If the conditions of step 4 (ii) of this section occur
first, proceed to step 6 of this section;
Step (6) Make an incremental change to the setup of the indoor
blower (e.g., next highest fan motor pin setting, next highest fan
motor speed) and repeat the evaluation process beginning above, at
step 1 of this section. If the indoor blower setup cannot be further
changed, increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until the applicable
Table 4 minimum is equaled; proceed to step 7 of this section;
Step (7) The airflow constraints have been satisfied. Use the
measured air volume rate as the Cooling full-load air volume rate.
Use the final fan speed or control settings for all tests that use
the Cooling full-load air volume rate.
b. For ducted blower coil systems with a constant-air-volume-
rate indoor blower. For all tests that specify the Cooling full-load
air volume rate, obtain an external static pressure as close to (but
not less than) the applicable Table 4 value that does not cause
automatic shutdown of the indoor blower or air volume rate variation
QVar, defined as follows, greater than 10 percent.
[GRAPHIC] [TIFF OMITTED] TR05JA17.153
Where:
Qmax = maximum measured airflow value
Qmin = minimum measured airflow value
QVar = airflow variance, percent
Additional test steps as described in section 3.3.e of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For coil-only indoor units. For the A or A2 Test,
(exclusively), the pressure drop across the indoor coil assembly
must not exceed 0.30 inches of water. If this pressure drop is
exceeded, reduce the air volume rate until the measured pressure
drop equals the specified maximum. Use this reduced air volume rate
for all tests that require the Cooling full-load air volume rate.
Table 4--Minimum External Static Pressure for Ducted Blower Coil Systems
------------------------------------------------------------------------
Minimum
external
Product variety static
pressure (in.
wc.)
------------------------------------------------------------------------
Conventional (i.e., all central air conditioners and 0.50
heat pumps not otherwise listed in this table).........
Ceiling-mount and Wall-mount............................ 0.30
Mobile Home............................................. 0.30
Low Static.............................................. 0.10
Mid Static.............................................. 0.30
Small Duct, High Velocity............................... 1.15
Space-constrained....................................... 0.30
------------------------------------------------------------------------
\1\ For ducted units tested without an air filter installed, increase
the applicable tabular value by 0.08 inches of water.
\2\ See section 1.2, Definitions, to determine for which Table 4 product
variety and associated minimum external static pressure requirement
equipment qualifies.
\3\ If a closed-loop, air-enthalpy test apparatus is used on the indoor
side, limit the resistance to airflow on the inlet side of the indoor
blower coil to a maximum value of 0.1 inch of water.
d. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the full-load air volume rate with all
indoor blowers operating unless prevented by the controls of the
unit. In such cases, turn on the maximum number of indoor blowers
permitted by the unit's controls. Where more than one option exists
for meeting this ``on'' indoor blower requirement, which indoor
blower(s) are turned on must match that specified in the
certification report. Conduct section 3.1.4.1.1 setup steps for each
indoor blower separately. If two or more indoor blowers are
connected to a common duct as per section 2.4.1 of this appendix,
temporarily divert their air volume to the test room when confirming
or adjusting the setup configuration of individual indoor blowers.
The allocation of the system's full-load air volume rate assigned to
each ``on'' indoor blower must match that specified by the
manufacturer in the certification report.
3.1.4.1.2 Cooling Full-Load Air Volume Rate for Non-Ducted Units
For non-ducted units, the Cooling full-load air volume rate is
the air volume rate that results during each test when the unit is
operated at an external static pressure of zero inches of water.
3.1.4.2 Cooling Minimum Air Volume Rate
Identify the certified cooling minimum air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified cooling minimum air volume rate, use the final
indoor blower control settings as determined when setting the
cooling full-load air volume rate, and readjust the exhaust fan of
the airflow measuring apparatus if necessary to reset to the cooling
full load air volume obtained in section 3.1.4.1 of this appendix.
Otherwise, calculate the target external static pressure and follow
instructions a, b, c, d, or e of this section. The target external
static pressure, [Delta]Pst_i, for any test ``i'' with a
specified air volume rate not equal to the Cooling full-load air
volume rate is determined as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.154
[[Page 1548]]
Where:
[Delta]Pst_i = target minimum external static pressure
for test i;
[Delta]Pst_full = minimum external static pressure for
test A or A2 (Table 4);
Qi = air volume rate for test i; and
Qfull = Cooling full-load air volume rate as measured
after setting and/or adjustment as described in section 3.1.4.1.1 of
this appendix.
a. For a ducted blower coil system without a constant-air-volume
indoor blower, adjust for external static pressure as follows:
Step (1) Operate the unit under conditions specified for the
B1 test using the certified fan speed or controls
settings, and adjust the exhaust fan of the airflow measuring
apparatus to achieve the certified cooling minimum air volume rate;
Step (2) Measure the external static pressure;
Step (3) If this pressure is equal to or greater than the
minimum external static pressure computed above, the pressure
requirement is satisfied; proceed to step 7 of this section. If this
pressure is not equal to or greater than the minimum external static
pressure computed above, proceed to step 4 of this section;
Step (4) Increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until either
(i) The pressure is equal to the minimum external static
pressure computed above or
(ii) The measured air volume rate equals 90 percent or less of
the cooling minimum air volume rate, whichever occurs first;
Step (5) If the conditions of step 4 (i) of this section occur
first, the pressure requirement is satisfied; proceed to step 7 of
this section. If the conditions of step 4 (ii) of this section occur
first, proceed to step 6 of this section;
Step (6) Make an incremental change to the setup of the indoor
blower (e.g., next highest fan motor pin setting, next highest fan
motor speed) and repeat the evaluation process beginning above, at
step 1 of this section. If the indoor blower setup cannot be further
changed, increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until it equals the
minimum external static pressure computed above; proceed to step 7
of this section;
Step (7) The airflow constraints have been satisfied. Use the
measured air volume rate as the cooling minimum air volume rate. Use
the final fan speed or control settings for all tests that use the
cooling minimum air volume rate.
b. For ducted units with constant-air-volume indoor blowers,
conduct all tests that specify the cooling minimum air volume rate--
(i.e., the A1, B1, C1,
F1, and G1 Tests)--at an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b of this appendix, greater than 10 percent, while
being as close to, but not less than the target minimum external
static pressure. Additional test steps as described in section 3.3.e
of this appendix are required if the measured external static
pressure exceeds the target value by more than 0.03 inches of water.
c. For ducted two-capacity coil-only systems, the cooling
minimum air volume rate is the higher of--
(1) The rate specified by the installation instructions included
with the unit by the manufacturer; or
(2) 75 percent of the cooling full-load air volume rate. During
the laboratory tests on a coil-only (fanless) system, obtain this
cooling minimum air volume rate regardless of the pressure drop
across the indoor coil assembly.
d. For non-ducted units, the cooling minimum air volume rate is
the air volume rate that results during each test when the unit
operates at an external static pressure of zero inches of water and
at the indoor blower setting used at low compressor capacity (two-
capacity system) or minimum compressor speed (variable-speed
system). For units having a single-speed compressor and a variable-
speed variable-air-volume-rate indoor blower, use the lowest fan
setting allowed for cooling.
e. For ducted systems having multiple indoor blowers within a
single indoor section, operate the indoor blowers such that the
lowest air volume rate allowed by the unit's controls is obtained
when operating the lone single-speed compressor or when operating at
low compressor capacity while meeting the requirements of section
2.2.3.2 of this appendix for the minimum number of blowers that must
be turned off. Using the target external static pressure and the
certified air volume rates, follow the procedures described in
section 3.1.4.2.a of this appendix if the indoor blowers are not
constant-air-volume indoor blowers or as described in section
3.1.4.2.b of this appendix if the indoor blowers are not constant-
air-volume indoor blowers. The sum of the individual ``on'' indoor
blowers' air volume rates is the cooling minimum air volume rate for
the system.
3.1.4.3 Cooling Intermediate Air Volume Rate
Identify the certified cooling intermediate air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified cooling intermediate air volume rate, use the final
indoor blower control settings as determined when setting the
cooling full load air volume rate, and readjust the exhaust fan of
the airflow measuring apparatus if necessary to reset to the cooling
full load air volume obtained in section 3.1.4.1 of this appendix.
Otherwise, calculate target minimum external static pressure as
described in section 3.1.4.2 of this appendix, and set the air
volume rate as follows.
a. For a ducted blower coil system without a constant-air-volume
indoor blower, adjust for external static pressure as described in
section 3.1.4.2.a of this appendix for cooling minimum air volume
rate.
b. For a ducted blower coil system with a constant-air-volume
indoor blower, conduct the EV Test at an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b of this appendix, greater than 10 percent, while
being as close to, but not less than the target minimum external
static pressure. Additional test steps as described in section 3.3.e
of this appendix are required if the measured external static
pressure exceeds the target value by more than 0.03 inches of water.
c. For non-ducted units, the cooling intermediate air volume
rate is the air volume rate that results when the unit operates at
an external static pressure of zero inches of water and at the fan
speed selected by the controls of the unit for the EV
Test conditions.
3.1.4.4 Heating Full-Load Air Volume Rate
3.1.4.4.1 Ducted Heat Pumps Where the Heating and Cooling Full-Load Air
Volume Rates Are the Same
a. Use the Cooling full-load air volume rate as the heating
full-load air volume rate for:
(1) Ducted blower coil system heat pumps that do not have a
constant-air-volume indoor blower, and that operate at the same
airflow-control setting during both the A (or A2) and the
H1 (or H12) Tests;
(2) Ducted blower coil system heat pumps with constant-air-flow
indoor blowers that provide the same airflow for the A (or
A2) and the H1 (or H12) Tests; and
(3) Ducted heat pumps that are tested with a coil-only indoor
unit (except two-capacity northern heat pumps that are tested only
at low capacity cooling--see section 3.1.4.4.2 of this appendix).
b. For heat pumps that meet the above criteria ``1'' and ``3,''
no minimum requirements apply to the measured external or internal,
respectively, static pressure. Use the final indoor blower control
settings as determined when setting the Cooling full-load air volume
rate, and readjust the exhaust fan of the airflow measuring
apparatus if necessary to reset to the cooling full-load air volume
obtained in section 3.1.4.1 of this appendix. For heat pumps that
meet the above criterion ``2,'' test at an external static pressure
that does not cause an automatic shutdown of the indoor blower or
air volume rate variation QVar, defined in section
3.1.4.1.1.b of this appendix, greater than 10 percent, while being
as close to, but not less than, the same Table 4 minimum external
static pressure as was specified for the A (or A2)
cooling mode test. Additional test steps as described in section
3.9.1.c of this appendix are required if the measured external
static pressure exceeds the target value by more than 0.03 inches of
water.
3.1.4.4.2 Ducted Heat Pumps Where the Heating and Cooling Full-Load Air
Volume Rates Are Different Due to Changes in Indoor Blower Operation,
i.e. Speed Adjustment by the System Controls
Identify the certified heating full-load air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified heating full-load air volume rate, use the final
indoor blower control settings as determined when setting the
cooling full-load air volume rate, and readjust the exhaust fan of
the airflow measuring apparatus if necessary to reset to the cooling
full-load air volume obtained in section 3.1.4.1 of this appendix.
Otherwise, calculate the target minimum external static pressure as
described in section 3.1.4.2 of this appendix and set the air volume
rate as follows.
a. For ducted blower coil system heat pumps that do not have a
constant-air-
[[Page 1549]]
volume indoor blower, adjust for external static pressure as
described in section 3.1.4.2.a of this appendix for cooling minimum
air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct all tests that specify the heating full-
load air volume rate at an external static pressure that does not
cause an automatic shutdown of the indoor blower or air volume rate
variation QVar, defined in section 3.1.4.1.1.b of this
appendix, greater than 10 percent, while being as close to, but not
less than the target minimum external static pressure. Additional
test steps as described in section 3.9.1.c of this appendix are
required if the measured external static pressure exceeds the target
value by more than 0.03 inches of water.
c. When testing ducted, two-capacity blower coil system northern
heat pumps (see section 1.2 of this appendix, Definitions), use the
appropriate approach of the above two cases. For coil-only system
northern heat pumps, the heating full-load air volume rate is the
lesser of the rate specified by the manufacturer in the installation
instructions included with the unit or 133 percent of the cooling
full-load air volume rate. For this latter case, obtain the heating
full-load air volume rate regardless of the pressure drop across the
indoor coil assembly.
d. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the heating full-load air volume rate
using the same ``on'' indoor blowers as used for the Cooling full-
load air volume rate. Using the target external static pressure and
the certified air volume rates, follow the procedures as described
in section 3.1.4.4.2.a of this appendix if the indoor blowers are
not constant-air-volume indoor blowers or as described in section
3.1.4.4.2.b of this appendix if the indoor blowers are constant-air-
volume indoor blowers. The sum of the individual ``on'' indoor
blowers' air volume rates is the heating full-load air volume rate
for the system.
3.1.4.4.3 Ducted Heating-Only Heat Pumps
Identify the certified heating full-load air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified heating full-load air volume rate, use a value equal
to the certified heating capacity of the unit times 400 scfm per
12,000 Btu/h. If there are no instructions for setting fan speed or
controls, use the as-shipped settings.
a. For all ducted heating-only blower coil system heat pumps,
except those having a constant-air-volume-rate indoor blower.
Conduct the following steps only during the first test, the H1 or
H12 test:
Step (1) Adjust the exhaust fan of the airflow measuring
apparatus to achieve the certified heating full-load air volume
rate.
Step (2) Measure the external static pressure.
Step (3) If this pressure is equal to or greater than the Table
4 minimum external static pressure that applies given the heating-
only heat pump's rated heating capacity, the pressure requirement is
satisfied; proceed to step 7 of this section. If this pressure is
not equal to or greater than the applicable Table 4 minimum external
static pressure, proceed to step 4 of this section;
Step (4) Increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until either--
(i) The pressure is equal to the applicable Table 4 minimum
external static pressure; or
(ii) The measured air volume rate equals 90 percent or less of
the heating full-load air volume rate, whichever occurs first;
Step (5) If the conditions of step 4 (i) of this section occur
first, the pressure requirement is satisfied; proceed to step 7 of
this section. If the conditions of step 4 (ii) of this section occur
first, proceed to step 6 of this section;
Step (6) Make an incremental change to the setup of the indoor
blower (e.g., next highest fan motor pin setting, next highest fan
motor speed) and repeat the evaluation process beginning above, at
step 1 of this section. If the indoor blower setup cannot be further
changed, increase the external static pressure by adjusting the
exhaust fan of the airflow measuring apparatus until it equals the
applicable Table 4 minimum external static pressure; proceed to step
7 of this section;
Step (7) The airflow constraints have been satisfied. Use the
measured air volume rate as the heating full-load air volume rate.
Use the final fan speed or control settings for all tests that use
the heating full-load air volume rate.
b. For ducted heating-only blower coil system heat pumps having
a constant-air-volume-rate indoor blower. For all tests that specify
the heating full-load air volume rate, obtain an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b of this section, greater than 10 percent, while
being as close to, but not less than, the applicable Table 4
minimum. Additional test steps as described in section 3.9.1.c of
this appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For ducted heating-only coil-only system heat pumps in the H1
or H12 Test, (exclusively), the pressure drop across the
indoor coil assembly must not exceed 0.30 inches of water. If this
pressure drop is exceeded, reduce the air volume rate until the
measured pressure drop equals the specified maximum. Use this
reduced air volume rate for all tests that require the heating full-
load air volume rate.
3.1.4.4.4 Non-Ducted Heat Pumps, Including Non-Ducted Heating-Only Heat
Pumps
For non-ducted heat pumps, the heating full-load air volume rate
is the air volume rate that results during each test when the unit
operates at an external static pressure of zero inches of water.
3.1.4.5 Heating Minimum Air Volume Rate
3.1.4.5.1 Ducted Heat Pumps Where the Heating and Cooling Minimum Air
Volume Rates are the Same
a. Use the cooling minimum air volume rate as the heating
minimum air volume rate for:
(1) Ducted blower coil system heat pumps that do not have a
constant-air-volume indoor blower, and that operates at the same
airflow-control setting during both the A1 and the
H11 tests;
(2) Ducted blower coil system heat pumps with constant-air-flow
indoor blowers installed that provide the same airflow for the
A1 and the H11 Tests; and
(3) Ducted coil-only system heat pumps.
b. For heat pumps that meet the above criteria ``1'' and ``3,''
no minimum requirements apply to the measured external or internal,
respectively, static pressure. Use the final indoor blower control
settings as determined when setting the cooling minimum air volume
rate, and readjust the exhaust fan of the airflow measuring
apparatus if necessary to reset to the cooling minimum air volume
rate obtained in section 3.1.4.2 of this appendix. For heat pumps
that meet the above criterion ``2,'' test at an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b, greater than 10 percent, while being as close
to, but not less than, the same target minimum external static
pressure as was specified for the A1 cooling mode test.
Additional test steps as described in section 3.9.1.c of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
3.1.4.5.2 Ducted Heat Pumps Where the Heating and Cooling Minimum Air
Volume Rates Are Different Due to Indoor Blower Operation, i.e. Speed
Adjustment by the System Controls
Identify the certified heating minimum air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified heating minimum air volume rate, use the final
indoor blower control settings as determined when setting the
cooling minimum air volume rate, and readjust the exhaust fan of the
airflow measuring apparatus if necessary to reset to the cooling
minimum air volume obtained in section 3.1.4.2 of this appendix.
Otherwise, calculate the target minimum external static pressure as
described in section 3.1.4.2 of this appendix.
a. For ducted blower coil system heat pumps that do not have a
constant-air-volume indoor blower, adjust for external static
pressure as described in section 3.1.4.2.a of this appendix for
cooling minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct all tests that specify the heating
minimum air volume rate--(i.e., the H01, H11,
H21, and H31 Tests)--at an external static
pressure that does not cause an automatic shutdown of the indoor
blower while being as close to, but not less than the air volume
rate variation QVar, defined in section 3.1.4.1.1.b of
this appendix, greater than 10 percent, while being as close to, but
not less than the target minimum external static pressure.
Additional test steps as described in section 3.9.1.c of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
[[Page 1550]]
c. For ducted two-capacity blower coil system northern heat
pumps, use the appropriate approach of the above two cases.
d. For ducted two-capacity coil-only system heat pumps, use the
cooling minimum air volume rate as the heating minimum air volume
rate. For ducted two-capacity coil-only system northern heat pumps,
use the cooling full-load air volume rate as the heating minimum air
volume rate. For ducted two-capacity heating-only coil-only system
heat pumps, the heating minimum air volume rate is the higher of the
rate specified by the manufacturer in the test setup instructions
included with the unit or 75 percent of the heating full-load air
volume rate. During the laboratory tests on a coil-only system,
obtain the heating minimum air volume rate without regard to the
pressure drop across the indoor coil assembly.
e. For non-ducted heat pumps, the heating minimum air volume
rate is the air volume rate that results during each test when the
unit operates at an external static pressure of zero inches of water
and at the indoor blower setting used at low compressor capacity
(two-capacity system) or minimum compressor speed (variable-speed
system). For units having a single-speed compressor and a variable-
speed, variable-air-volume-rate indoor blower, use the lowest fan
setting allowed for heating.
f. For ducted systems with multiple indoor blowers within a
single indoor section, obtain the heating minimum air volume rate
using the same ``on'' indoor blowers as used for the cooling minimum
air volume rate. Using the target external static pressure and the
certified air volume rates, follow the procedures as described in
section 3.1.4.5.2.a of this appendix if the indoor blowers are not
constant-air-volume indoor blowers or as described in section
3.1.4.5.2.b of this appendix if the indoor blowers are constant-air-
volume indoor blowers. The sum of the individual ``on'' indoor
blowers' air volume rates is the heating full-load air volume rate
for the system.
3.1.4.6 Heating Intermediate Air Volume Rate
Identify the certified heating intermediate air volume rate and
certified instructions for setting fan speed or controls. If there
is no certified heating intermediate air volume rate, use the final
indoor blower control settings as determined when setting the
heating full-load air volume rate, and readjust the exhaust fan of
the airflow measuring apparatus if necessary to reset to the cooling
full-load air volume obtained in section 3.1.4.2 of this appendix.
Calculate the target minimum external static pressure as described
in section 3.1.4.2 of this appendix.
a. For ducted blower coil system heat pumps that do not have a
constant-air-volume indoor blower, adjust for external static
pressure as described in section 3.1.4.2.a of this appendix for
cooling minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct the H2V Test at an external
static pressure that does not cause an automatic shutdown of the
indoor blower or air volume rate variation QVar, defined
in section 3.1.4.1.1.b of this appendix, greater than 10 percent,
while being as close to, but not less than the target minimum
external static pressure. Additional test steps as described in
section 3.9.1.c of this appendix are required if the measured
external static pressure exceeds the target value by more than 0.03
inches of water.
c. For non-ducted heat pumps, the heating intermediate air
volume rate is the air volume rate that results when the heat pump
operates at an external static pressure of zero inches of water and
at the fan speed selected by the controls of the unit for the
H2V Test conditions.
3.1.4.7 Heating Nominal Air Volume Rate
The manufacturer must specify the heating nominal air volume
rate and the instructions for setting fan speed or controls.
Calculate target minimum external static pressure as described in
section 3.1.4.2 of this appendix. Make adjustments as described in
section 3.14.6 of this appendix for heating intermediate air volume
rate so that the target minimum external static pressure is met or
exceeded.
3.1.5 Indoor Test Room Requirement When the Air Surrounding the Indoor
Unit is Not Supplied From the Same Source as the Air Entering the
Indoor Unit
If using a test set-up where air is ducted directly from the air
reconditioning apparatus to the indoor coil inlet (see Figure 2,
Loop Air-Enthalpy Test Method Arrangement, of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3)), maintain the dry bulb
temperature within the test room within 5.0[emsp14][deg]F of the applicable sections 3.2 and 3.6 dry
bulb temperature test condition for the air entering the indoor
unit. Dew point must be within 2[emsp14][deg]F of the required inlet
conditions.
3.1.6 Air Volume Rate Calculations
For all steady-state tests and for frost accumulation (H2,
H21, H22, H2V) tests, calculate the
air volume rate through the indoor coil as specified in sections
7.7.2.1 and 7.7.2.2 of ANSI/ASHRAE 37-2009. When using the outdoor
air enthalpy method, follow sections 7.7.2.1 and 7.7.2.2 of ANSI/
ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3) to
calculate the air volume rate through the outdoor coil. To express
air volume rates in terms of standard air, use:
[GRAPHIC] [TIFF OMITTED] TR05JA17.155
Where:
Vis = air volume rate of standard (dry) air, (ft\3\/
min)da
Vimx = air volume rate of the air-water vapor mixture,
(ft\3\/min)mx
vn' = specific volume of air-water vapor mixture at the
nozzle, ft\3\ per lbm of the air-water vapor mixture
Wn = humidity ratio at the nozzle, lbm of water vapor per
lbm of dry air
0.075 = the density associated with standard (dry) air, (lbm/ft\3\)
vn = specific volume of the dry air portion of the
mixture evaluated at the dry-bulb temperature, vapor content, and
barometric pressure existing at the nozzle, ft\3\ per lbm of dry
air.
(Note: In the first printing of ANSI/ASHRAE 37-2009, the second
IP equation for Qmi should read,
[GRAPHIC] [TIFF OMITTED] TR05JA17.156
3.1.7 Test Sequence
Before making test measurements used to calculate performance,
operate the equipment for the ``break-in'' period specified in the
certification report, which may not exceed 20 hours. Each compressor
of the unit must undergo this ``break-in'' period. When testing a
ducted unit (except if a heating-only heat pump), conduct the A or
A2 Test first to establish the cooling full-load air
volume rate. For ducted heat pumps where the heating and cooling
full-load air volume rates are different, make the first heating
mode test one that requires the heating full-load air volume rate.
For ducted heating-only heat pumps, conduct the H1 or H12
Test first to establish the heating full-load air volume rate. When
conducting a cyclic test, always conduct it immediately after the
steady-state test that requires the same test conditions. For
variable-speed systems, the first test using the cooling minimum air
volume rate should precede the EV Test, and the first
test using the heating minimum air volume rate must precede the
H2V Test. The test laboratory makes all other decisions
on the test sequence.
3.1.8 Requirement for the Air Temperature Distribution Leaving the
Indoor Coil
For at least the first cooling mode test and the first heating
mode test, monitor the temperature distribution of the air leaving
the indoor coil using the grid of individual sensors described in
sections 2.5 and 2.5.4 of this appendix. For the 30-minute data
collection interval used to determine capacity, the maximum spread
among the outlet dry bulb temperatures from any data sampling must
not exceed 1.5[emsp14][deg]F. Install the mixing devices described
in section 2.5.4.2 of this appendix to minimize the temperature
spread.
[[Page 1551]]
3.1.9 Requirement for the Air Temperature Distribution Entering the
Outdoor Coil
Monitor the Temperatures of the Air Entering the Outdoor Coil
Using Air Sampling Devices and/or Temperature Sensor Grids,
Maintaining the Required Tolerances, if Applicable, as Described in
section 2.11 of this appendix
3.1.10 Control of Auxiliary Resistive Heating Elements
Except as noted, disable heat pump resistance elements used for
heating indoor air at all times, including during defrost cycles and
if they are normally regulated by a heat comfort controller. For
heat pumps equipped with a heat comfort controller, enable the heat
pump resistance elements only during the below-described, short
test. For single-speed heat pumps covered under section 3.6.1 of
this appendix, the short test follows the H1 or, if conducted, the
H1C Test. For two-capacity heat pumps and heat pumps covered under
section 3.6.2 of this appendix, the short test follows the
H12 Test. Set the heat comfort controller to provide the
maximum supply air temperature. With the heat pump operating and
while maintaining the heating full-load air volume rate, measure the
temperature of the air leaving the indoor-side beginning 5 minutes
after activating the heat comfort controller. Sample the outlet dry-
bulb temperature at regular intervals that span 5 minutes or less.
Collect data for 10 minutes, obtaining at least 3 samples. Calculate
the average outlet temperature over the 10-minute interval,
TCC.
3.2 Cooling Mode Tests for Different Types of Air Conditioners and
Heat Pumps
3.2.1 Tests for a System Having a Single-Speed Compressor and Fixed
Cooling Air Volume Rate
This set of tests is for single-speed-compressor units that do
not have a cooling minimum air volume rate or a cooling intermediate
air volume rate that is different than the cooling full load air
volume rate. Conduct two steady-state wet coil tests, the A and B
Tests. Use the two optional dry-coil tests, the steady-state C Test
and the cyclic D Test, to determine the cooling mode cyclic
degradation coefficient, CD\c\. If the two optional tests
are conducted but yield a tested CD\c\ that exceeds the
default CD\c\ or if the two optional tests are not
conducted, assign CD\c\ the default value of 0.25 (for
outdoor units with no match) or 0.2 (for all other systems). Table 5
specifies test conditions for these four tests.
Table 5--Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed Cooling Air Volume Rate
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A Test--required (steady, wet coil)....... 80 67 95 \1\ 75 Cooling full-load \2\.
B Test--required (steady, wet coil)....... 80 67 82 \1\ 65 Cooling full-load \2\.
C Test--optional (steady, dry coil)....... 80 (\3\) 82 .............. Cooling full-load \2\.
D Test--optional (cyclic, dry coil)....... 80 (\3\) 82 .............. (\4\).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1 of this appendix.
\3\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb
temperature of 57[emsp14][deg]F or less be used.)
\4\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C Test.
3.2.2 Tests for a Unit Having a Single-Speed Compressor Where the
Indoor Section Uses a Single Variable-Speed Variable-Air-Volume Rate
Indoor Blower or Multiple Indoor Blowers
3.2.2.1 Indoor Blower Capacity Modulation That Correlates With the
Outdoor Dry Bulb Temperature or Systems With a Single Indoor Coil but
Multiple Indoor Blowers
Conduct four steady-state wet coil tests: The A2,
A1, B2, and B1 tests. Use the two
optional dry-coil tests, the steady-state C1 test and the
cyclic D1 test, to determine the cooling mode cyclic
degradation coefficient, CD\c\. If the two optional tests
are conducted but yield a tested CD\c\ that exceeds the
default CD\c\ or if the two optional tests are not
conducted, assign CD\c\ the default value of 0.2.
3.2.2.2 Indoor Blower Capacity Modulation Based on Adjusting the
Sensible to Total (S/T) Cooling Capacity Ratio
The testing requirements are the same as specified in section
3.2.1 of this appendix and Table 5. Use a cooling full-load air
volume rate that represents a normal installation. If performed,
conduct the steady-state C Test and the cyclic D Test with the unit
operating in the same S/T capacity control mode as used for the B
Test.
Table 6--Cooling Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.2.2.1
Indoor Unit Requirements
----------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F) Cooling air
Test description ---------------------------------------------------------------- volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
----------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet 80 67 95 \1\ 75 Cooling full-
coil). load \2\.
A1 Test--required (steady, wet 80 67 95 \1\ 75 Cooling minimum
coil). \3\.
B2 Test--required (steady, wet 80 67 82 \1\ 65 Cooling full-
coil). load \2\.
B1 Test--required (steady, wet 80 67 82 \1\ 65 Cooling minimum
coil). \3\.
C1 Test\4\--optional (steady, 80 (\4\) 82 .............. Cooling minimum
dry coil). \3\.
D1 Test\4\--optional (cyclic, 80 (\4\) 82 .............. (\5\).
dry coil).
----------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1 of this appendix.
\3\ Defined in section 3.1.4.2 of this appendix.
[[Page 1552]]
\4\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is
recommended that an indoor wet-bulb temperature of 57[emsp14][deg]F or less be used.)
\5\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the
same pressure difference or velocity pressure as measured during the C1 Test.
3.2.3 Tests for a Unit Having a Two-Capacity Compressor. (See Section
1.2 of This Appendix, Definitions)
a. Conduct four steady-state wet coil tests: the A2,
B2, B1, and F1 Tests. Use the two
optional dry-coil tests, the steady-state C1 Test and the
cyclic D1 Test, to determine the cooling-mode cyclic-
degradation coefficient, CD\c\. If the two optional tests
are conducted but yield a tested CD\c\ that exceeds the
default CD\c\ or if the two optional tests are not
conducted, assign CD\c\ the default value of 0.2. Table 7
specifies test conditions for these six tests.
b. For units having a variable-speed indoor blower that is
modulated to adjust the sensible to total (S/T) cooling capacity
ratio, use cooling full-load and cooling minimum air volume rates
that represent a normal installation. Additionally, if conducting
the dry-coil tests, operate the unit in the same S/T capacity
control mode as used for the B1 Test.
c. Test two-capacity, northern heat pumps (see section 1.2 of
this appendix, Definitions) in the same way as a single speed heat
pump with the unit operating exclusively at low compressor capacity
(see section 3.2.1 of this appendix and Table 5).
d. If a two-capacity air conditioner or heat pump locks out low-
capacity operation at higher outdoor temperatures, then use the two
dry-coil tests, the steady-state C2 Test and the cyclic
D2 Test, to determine the cooling-mode cyclic-degradation
coefficient that only applies to on/off cycling from high capacity,
CD\c\(k=2). If the two optional tests are conducted but
yield a tested CD\c\(k = 2) that exceeds the default
CD\c\(k = 2) or if the two optional tests are not
conducted, assign CD\c\(k = 2) the default value. The
default CD\c\(k=2) is the same value as determined or
assigned for the low-capacity cyclic-degradation coefficient,
CD\c\ [or equivalently, CD\c\(k=1)].
Table 7--Cooling Mode Test Conditions for Units Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Compressor capacity Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet 80 67 95 \1\ 75 High............... Cooling Full-Load.\2\
coil).
B2 Test--required (steady, wet 80 67 82 \1\ 65 High............... Cooling Full-Load.\2\
coil).
B1 Test--required (steady, wet 80 67 82 \1\ 65 Low................ Cooling Minimum.\3\
coil).
C2 Test--optional (steady, dry- 80 (\4\) 82 .............. High............... Cooling Full-Load.\2\
coil).
D2 Test--optional (cyclic, dry- 80 (\4\) 82 .............. High............... (\5\).
coil).
C1 Test--optional (steady, dry- 80 (\4\) 82 .............. Low................ Cooling Minimum.\3\
coil).
D1 Test--optional (cyclic, dry- 80 (\4\) 82 .............. Low................ (\6\).
coil).
F1 Test--required (steady, wet 80 67 67 \1\ 53.5 Low................ Cooling Minimum.\3\
coil).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1 of this appendix.
\3\ Defined in section 3.1.4.2 of this appendix.
\4\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet-bulb
temperature of 57[emsp14][deg]F or less.
\5\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the C2 Test.
\6\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the C1 Test.
3.2.4 Tests for a Unit Having a Variable-Speed Compressor
a. Conduct five steady-state wet coil tests: The A2,
EV, B2, B1, and F1
Tests. Use the two optional dry-coil tests, the steady-state
G1 Test and the cyclic I1 Test, to determine
the cooling mode cyclic degradation coefficient, CD\c\.
If the two optional tests are conducted but yield a tested
CD\c\ that exceeds the default CD\c\ or if the
two optional tests are not conducted, assign CD\c\ the
default value of 0.25. Table 8 specifies test conditions for these
seven tests. The compressor shall operate at the same cooling full
speed, measured by RPM or power input frequency (Hz), for both the
A2 and B2 tests. The compressor shall operate
at the same cooling minimum speed, measured by RPM or power input
frequency (Hz), for the B1, F1, G1,
and I1 tests. Determine the cooling intermediate
compressor speed cited in Table 8 using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.157
where a tolerance of plus 5 percent or the next higher inverter
frequency step from that calculated is allowed.
b. For units that modulate the indoor blower speed to adjust the
sensible to total (S/T) cooling capacity ratio, use cooling full-
load, cooling intermediate, and cooling minimum air volume rates
that represent a normal installation. Additionally, if conducting
the dry-coil tests, operate the unit
[[Page 1553]]
in the same S/T capacity control mode as used for the F1
Test.
c. For multiple-split air conditioners and heat pumps (except
where noted), the following procedures supersede the above
requirements: For all Table 8 tests specified for a minimum
compressor speed, turn off at least one indoor unit. The
manufacturer shall designate the particular indoor unit(s) that is
turned off. The manufacturer must also specify the compressor speed
used for the Table 8 EV Test, a cooling-mode intermediate
compressor speed that falls within \1/4\ and \3/4\ of the difference
between the full and minimum cooling-mode speeds. The manufacturer
should prescribe an intermediate speed that is expected to yield the
highest EER for the given EV Test conditions and
bracketed compressor speed range. The manufacturer can designate
that one or more indoor units are turned off for the EV
Test.
Table 8--Cooling Mode Test Condition for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Compressor speed Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet 80 67 95 \1\ 75 Cooling Full....... Cooling Full-Load.\2\
coil).
B2 Test--required (steady, wet 80 67 82 \1\ 65 Cooling Full....... Cooling Full-Load.\2\
coil).
EV Test--required (steady, wet 80 67 87 \1\ 69 Cooling Cooling Intermediate.\3\
coil). Intermediate.
B1 Test--required (steady, wet 80 67 82 \1\ 65 Cooling Minimum.... Cooling Minimum.\4\
coil).
F1 Test--required (steady, wet 80 67 67 \1\ 53.5 Cooling Minimum.... Cooling Minimum.\4\
coil).
G1 Test \5\--optional (steady, 80 (\6\) 67 .............. Cooling Minimum.... Cooling Minimum.\4\
dry-coil).
I1 Tes t\5\--optional (cyclic, 80 (\6\) 67 .............. Cooling Minimum.... (\6\).
dry-coil).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1 of this appendix.
\3\ Defined in section 3.1.4.3 of this appendix.
\4\ Defined in section 3.1.4.2 of this appendix.
\5\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet bulb
temperature of 57[emsp14][deg]F or less.
\6\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the G1 Test.
3.2.5 Cooling Mode Tests for Northern Heat Pumps With Triple-Capacity
Compressors
Test triple-capacity, northern heat pumps for the cooling mode
in the same way as specified in section 3.2.3 of this appendix for
units having a two-capacity compressor.
3.2.6 Tests for an Air Conditioner or Heat Pump Having a Single Indoor
Unit Having Multiple Indoor Blowers and Offering Two Stages of
Compressor Modulation
Conduct the cooling mode tests specified in section 3.2.3 of
this appendix.
3.3 Test Procedures for Steady-State Wet Coil Cooling Mode Tests (the
A, A2, A1, B, B2, B1,
EV, and F1 Tests)
a. For the pretest interval, operate the test room
reconditioning apparatus and the unit to be tested until maintaining
equilibrium conditions for at least 30 minutes at the specified
section 3.2 test conditions. Use the exhaust fan of the airflow
measuring apparatus and, if installed, the indoor blower of the test
unit to obtain and then maintain the indoor air volume rate and/or
external static pressure specified for the particular test.
Continuously record (see section 1.2 of this appendix, Definitions):
(1) The dry-bulb temperature of the air entering the indoor
coil,
(2) The water vapor content of the air entering the indoor coil,
(3) The dry-bulb temperature of the air entering the outdoor
coil, and
(4) For the section 2.2.4 of this appendix cases where its
control is required, the water vapor content of the air entering the
outdoor coil.
Refer to section 3.11 of this appendix for additional
requirements that depend on the selected secondary test method.
b. After satisfying the pretest equilibrium requirements, make
the measurements specified in Table 3 of ANSI/ASHRAE 37-2009 for the
indoor air enthalpy method and the user-selected secondary method.
Make said Table 3 measurements at equal intervals that span 5
minutes or less. Continue data sampling until reaching a 30-minute
period (e.g., seven consecutive 5-minute samples) where the test
tolerances specified in Table 9 are satisfied. For those
continuously recorded parameters, use the entire data set from the
30-minute interval to evaluate Table 9 compliance. Determine the
average electrical power consumption of the air conditioner or heat
pump over the same 30-minute interval.
c. Calculate indoor-side total cooling capacity and sensible
cooling capacity as specified in sections 7.3.3.1 and 7.3.3.3 of
ANSI/ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3). To
calculate capacity, use the averages of the measurements (e.g. inlet
and outlet dry bulb and wet bulb temperatures measured at the
psychrometers) that are continuously recorded for the same 30-minute
interval used as described above to evaluate compliance with test
tolerances. Do not adjust the parameters used in calculating
capacity for the permitted variations in test conditions. Evaluate
air enthalpies based on the measured barometric pressure. Use the
values of the specific heat of air given in section 7.3.3.1 of ANSI/
ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3) for
calculation of the sensible cooling capacities. Assign the average
total space cooling capacity, average sensible cooling capacity, and
electrical power consumption over the 30-minute data collection
interval to the variables Qc\k\(T), Qsc\k\(T)
and Ec\k\(T), respectively. For these three variables,
replace the ``T'' with the nominal outdoor temperature at which the
test was conducted. The superscript k is used only when testing
multi-capacity units. Use the superscript k=2 to denote a test with
the unit operating at high capacity or full speed, k=1 to denote low
capacity or minimum speed, and k=v to denote the intermediate speed.
d. For mobile home and space-constrained ducted coil-only system
tests, decrease Qc\k\(T) by
[[Page 1554]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.158
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
For non-mobile, non-space-constrained home ducted coil-only
system tests, decrease Qc\k\(T) by
[GRAPHIC] [TIFF OMITTED] TR05JA17.159
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
Table 9--Test Operating and Test Condition Tolerances for Section 3.3
Steady-State Wet Coil Cooling Mode Tests and Section 3.4 Dry Coil
Cooling Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor dry-bulb, [deg]F
Entering temperature................ 2.0 0.5
Leaving temperature................. 2.0 ..............
Indoor wet-bulb, [deg]F
Entering temperature................ 1.0 \2\ 0.3
Leaving temperature................. \2\ 1.0 ..............
Outdoor dry-bulb, [deg]F
Entering temperature................ 2.0 0.5
Leaving temperature................. \3\ 2.0 ..............
Outdoor wet-bulb, [deg]F
Entering temperature................ 1.0 \4\ 0.3
Leaving temperature................. \3\ 1.0 ..............
External resistance to airflow, inches 0.05 \5\ 0.02
of water...............................
Electrical voltage, % of reading........ 2.0 1.5
Nozzle pressure drop, % of reading...... 2.0 ..............
------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
\2\ Only applies during wet coil tests; does not apply during steady-
state, dry coil cooling mode tests.
\3\ Only applies when using the outdoor air enthalpy method.
\4\ Only applies during wet coil cooling mode tests where the unit
rejects condensate to the outdoor coil.
\5\ Only applies when testing non-ducted units.
e. For air conditioners and heat pumps having a constant-air-
volume-rate indoor blower, the five additional steps listed below
are required if the average of the measured external static
pressures exceeds the applicable sections 3.1.4 minimum (or target)
external static pressure ([Delta]Pmin) by 0.03 inches of
water or more.
(1) Measure the average power consumption of the indoor blower
motor (Efan,1) and record the corresponding external
static pressure ([Delta]P1) during or immediately
following the 30-minute interval used for determining capacity.
(2) After completing the 30-minute interval and while
maintaining the same test conditions, adjust the exhaust fan of the
airflow measuring apparatus until the external static pressure
increases to approximately [Delta]P1 +
([Delta]P1 - [Delta]Pmin).
(3) After re-establishing steady readings of the fan motor power
and external static pressure, determine average values for the
indoor blower power (Efan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
(4) Approximate the average power consumption of the indoor
blower motor at [Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TR05JA17.160
(5) Increase the total space cooling capacity,
Qc\k\(T), by the quantity (Efan,1 -
Efan,min), when expressed on a Btu/h basis. Decrease the
total electrical power, Ec\k\(T), by the same fan power
difference, now expressed in watts.
3.4 Test Procedures for the Steady-State Dry-Coil Cooling-Mode Tests
(the C, C1, C2, and G1 Tests)
a. Except for the modifications noted in this section, conduct
the steady-state dry coil cooling mode tests as specified in section
3.3 of this appendix for wet coil tests. Prior to recording data
during the steady-state dry coil test, operate the unit at least one
hour after achieving dry coil conditions. Drain the drain pan and
plug the drain opening. Thereafter, the drain pan should remain
completely dry.
b. Denote the resulting total space cooling capacity and
electrical power derived from the test as Qss,dry and
Ess,dry. With regard to a section 3.3 deviation, do not
adjust Qss,dry for duct losses (i.e., do not apply
section 7.3.3.3 of ANSI/ASHRAE 37-2009). In preparing for the
section 3.5 cyclic tests of this appendix, record the average
indoor-side air volume rate, Vi, specific heat of the air, Cp,a
[[Page 1555]]
(expressed on dry air basis), specific volume of the air at the
nozzles, v'n, humidity ratio at the nozzles,
Wn, and either pressure difference or velocity pressure
for the flow nozzles. For units having a variable-speed indoor
blower (that provides either a constant or variable air volume rate)
that will or may be tested during the cyclic dry coil cooling mode
test with the indoor blower turned off (see section 3.5 of this
appendix), include the electrical power used by the indoor blower
motor among the recorded parameters from the 30-minute test.
c. If the temperature sensors used to provide the primary
measurement of the indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the subsequent cyclic dry-
coil test are different, include measurements of the latter sensors
among the regularly sampled data. Beginning at the start of the 30-
minute data collection period, measure and compute the indoor-side
air dry-bulb temperature difference using both sets of
instrumentation, [Delta]T (Set SS) and [Delta]T (Set CYC), for each
equally spaced data sample. If using a consistent data sampling rate
that is less than 1 minute, calculate and record minutely averages
for the two temperature differences. If using a consistent sampling
rate of one minute or more, calculate and record the two temperature
differences from each data sample. After having recorded the seventh
(i=7) set of temperature differences, calculate the following ratio
using the first seven sets of values:
[GRAPHIC] [TIFF OMITTED] TR05JA17.161
Each time a subsequent set of temperature differences is recorded
(if sampling more frequently than every 5 minutes), calculate FCD
using the most recent seven sets of values. Continue these
calculations until the 30-minute period is completed or until a
value for FCD is calculated that falls outside the allowable range
of 0.94-1.06. If the latter occurs, immediately suspend the test and
identify the cause for the disparity in the two temperature
difference measurements. Recalibration of one or both sets of
instrumentation may be required. If all the values for FCD are
within the allowable range, save the final value of the ratio from
the 30-minute test as FCD*. If the temperature sensors used to
provide the primary measurement of the indoor-side dry bulb
temperature difference during the steady-state dry-coil test and the
subsequent cyclic dry-coil test are the same, set FCD*= 1.
3.5 Test Procedures for the Cyclic Dry-Coil Cooling-Mode Tests (the D,
D1, D2, and I1 Tests)
After completing the steady-state dry-coil test, remove the
outdoor air enthalpy method test apparatus, if connected, and begin
manual OFF/ON cycling of the unit's compressor. The test set-up
should otherwise be identical to the set-up used during the steady-
state dry coil test. When testing heat pumps, leave the reversing
valve during the compressor OFF cycles in the same position as used
for the compressor ON cycles, unless automatically changed by the
controls of the unit. For units having a variable-speed indoor
blower, the manufacturer has the option of electing at the outset
whether to conduct the cyclic test with the indoor blower enabled or
disabled. Always revert to testing with the indoor blower disabled
if cyclic testing with the fan enabled is unsuccessful.
a. For all cyclic tests, the measured capacity must be adjusted
for the thermal mass stored in devices and connections located
between measured points. Follow the procedure outlined in section
7.4.3.4.5 of ASHRAE 116-2010 (incorporated by reference, see Sec.
430.3) to ensure any required measurements are taken.
b. For units having a single-speed or two-capacity compressor,
cycle the compressor OFF for 24 minutes and then ON for 6 minutes
([Delta][tau]cyc,dry = 0.5 hours). For units having a
variable-speed compressor, cycle the compressor OFF for 48 minutes
and then ON for 12 minutes ([Delta][tau]cyc,dry = 1.0
hours). Repeat the OFF/ON compressor cycling pattern until the test
is completed. Allow the controls of the unit to regulate cycling of
the outdoor fan. If an upturned duct is used, measure the dry-bulb
temperature at the inlet of the device at least once every minute
and ensure that its test operating tolerance is within
1.0[emsp14][deg]F for each compressor OFF period.
c. Sections 3.5.1 and 3.5.2 of this appendix specify airflow
requirements through the indoor coil of ducted and non-ducted indoor
units, respectively. In all cases, use the exhaust fan of the
airflow measuring apparatus (covered under section 2.6 of this
appendix) along with the indoor blower of the unit, if installed and
operating, to approximate a step response in the indoor coil
airflow. Regulate the exhaust fan to quickly obtain and then
maintain the flow nozzle static pressure difference or velocity
pressure at the same value as was measured during the steady-state
dry coil test. The pressure difference or velocity pressure should
be within 2 percent of the value from the steady-state dry coil test
within 15 seconds after airflow initiation. For units having a
variable-speed indoor blower that ramps when cycling on and/or off,
use the exhaust fan of the airflow measuring apparatus to impose a
step response that begins at the initiation of ramp up and ends at
the termination of ramp down.
d. For units having a variable-speed indoor blower, conduct the
cyclic dry coil test using the pull-thru approach described below if
any of the following occur when testing with the fan operating:
(1) The test unit automatically cycles off;
(2) Its blower motor reverses; or
(3) The unit operates for more than 30 seconds at an external
static pressure that is 0.1 inches of water or more higher than the
value measured during the prior steady-state test.
For the pull-thru approach, disable the indoor blower and use
the exhaust fan of the airflow measuring apparatus to generate the
specified flow nozzles static pressure difference or velocity
pressure. If the exhaust fan cannot deliver the required pressure
difference because of resistance created by the unpowered indoor
blower, temporarily remove the indoor blower.
e. Conduct three complete compressor OFF/ON cycles with the test
tolerances given in Table 10 satisfied. Calculate the degradation
coefficient CD for each complete cycle. If all three
CD values are within 0.02 of the average CD
then stability has been achieved, use the highest CD
value of these three. If stability has not been achieved, conduct
additional cycles, up to a maximum of eight cycles, until stability
has been achieved between three consecutive cycles. Once stability
has been achieved, use the highest CD value of the three
consecutive cycles that establish stability. If stability has not
been achieved after eight cycles, use the highest CD from
cycle one through cycle eight, or the default CD,
whichever is lower.
f. With regard to the Table 10 parameters, continuously record
the dry-bulb temperature of the air entering the indoor and outdoor
coils during periods when air flows through the respective coils.
Sample the water vapor content of the indoor coil inlet air at least
every 2 minutes during periods when air flows through the coil.
Record external static pressure and the air volume rate indicator
(either nozzle pressure difference or velocity pressure) at least
every minute during the interval that air flows through the indoor
coil. (These regular measurements of the airflow rate indicator are
in addition to the required measurement at 15 seconds after flow
initiation.) Sample the electrical voltage at least every 2 minutes
beginning 30 seconds after compressor start-up. Continue until the
compressor, the outdoor fan, and the indoor blower (if it is
installed and operating) cycle off.
g. For ducted units, continuously record the dry-bulb
temperature of the air entering (as noted above) and leaving the
indoor coil. Or if using a thermopile, continuously record the
difference between these two temperatures during the interval that
air flows through the indoor coil. For non-ducted units, make the
same dry-bulb temperature measurements beginning when the compressor
cycles on and ending when indoor coil airflow ceases.
h. Integrate the electrical power over complete cycles of length
[Delta][tau]cyc,dry. For ducted blower coil systems
tested with the unit's indoor blower operating for the cycling test,
integrate electrical power from indoor blower OFF to indoor blower
OFF. For all other ducted units and for non-ducted units, integrate
electrical power from compressor OFF to compressor OFF. (Some cyclic
tests will use the same data collection intervals to determine the
electrical energy and the total space cooling. For other units,
terminate data collection used to determine the electrical energy
before terminating data collection used to determine total space
cooling.)
[[Page 1556]]
Table 10--Test Operating and Test Condition Tolerances for Cyclic Dry
Coil Cooling Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor entering dry-bulb temperature,\2\ 2.0 0.5
[deg]F.................................
Indoor entering wet-bulb temperature, .............. (\3\)
[deg]F.................................
Outdoor entering dry-bulb 2.0 0.5
temperature,\2\ [deg]F.................
External resistance to airflow,\2\ 0.05 ..............
inches of water........................
Airflow nozzle pressure difference or 2.0 \4\ 2.0
velocity pressure,\2\% of reading......
Electrical voltage,\5\ % of reading..... 2.0 1.5
------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
\2\ Applies during the interval that air flows through the indoor
(outdoor) coil except for the first 30 seconds after flow initiation.
For units having a variable-speed indoor blower that ramps, the
tolerances listed for the external resistance to airflow apply from 30
seconds after achieving full speed until ramp down begins.
\3\ Shall at no time exceed a wet-bulb temperature that results in
condensate forming on the indoor coil.
\4\ The test condition must be the average nozzle pressure difference or
velocity pressure measured during the steady-state dry coil test.
\5\ Applies during the interval when at least one of the following--the
compressor, the outdoor fan, or, if applicable, the indoor blower--are
operating except for the first 30 seconds after compressor start-up.
If the Table 10 tolerances are satisfied over the complete
cycle, record the measured electrical energy consumption as
ecyc,dry and express it in units of watt-hours. Calculate
the total space cooling delivered, qcyc,dry, in units of
Btu using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.162
Where,
V i, Cp,a, vn' (or vn),
Wn, and FCD* are the values recorded during the section
3.4 dry coil steady-state test and
Tal([tau]) = dry bulb temperature of the air entering the
indoor coil at time [tau], [deg]F.
Ta2([tau]) = dry bulb temperature of the air leaving the
indoor coil at time [tau], [deg]F.
[tau]1 = for ducted units, the elapsed time when airflow
is initiated through the indoor coil; for non-ducted units, the
elapsed time when the compressor is cycled on, hr.
[tau]2 = the elapsed time when indoor coil airflow
ceases, hr.
Adjust the total space cooling delivered, qcyc,dry,
according to calculation method outlined in section 7.4.3.4.5 of
ASHRAE 116-2010 (incorporated by reference, see Sec. 430.3).
3.5.1 Procedures When Testing Ducted Systems
The automatic controls that are installed in the test unit must
govern the OFF/ON cycling of the air moving equipment on the indoor
side (exhaust fan of the airflow measuring apparatus and the indoor
blower of the test unit). For ducted coil-only systems rated based
on using a fan time-delay relay, control the indoor coil airflow
according to the OFF delay listed by the manufacturer in the
certification report. For ducted units having a variable-speed
indoor blower that has been disabled (and possibly removed), start
and stop the indoor airflow at the same instances as if the fan were
enabled. For all other ducted coil-only systems, cycle the indoor
coil airflow in unison with the cycling of the compressor. If air
damper boxes are used, close them on the inlet and outlet side
during the OFF period. Airflow through the indoor coil should stop
within 3 seconds after the automatic controls of the test unit (act
to) de-energize the indoor blower. For mobile home and space-
constrained ducted coil-only systems increase ecyc,dry by
the quantity,
[GRAPHIC] [TIFF OMITTED] TR05JA17.163
[GRAPHIC] [TIFF OMITTED] TR05JA17.164
where V is is the average indoor air volume rate from the
section 3.4 dry coil steady-state test and is expressed in units of
cubic feet per minute of standard air (scfm). For ducted non-mobile,
non-space-constrained home coil-only units increase
ecyc,dry by the quantity,
[GRAPHIC] [TIFF OMITTED] TR05JA17.165
[GRAPHIC] [TIFF OMITTED] TR05JA17.166
[[Page 1557]]
where V is is the average indoor air volume rate from the
section 3.4 dry coil steady-state test and is expressed in units of
cubic feet per minute of standard air (scfm). For units having a
variable-speed indoor blower that is disabled during the cyclic
test, increase ecyc,dry and decrease qcyc,dry
based on:
a. The product of [[tau]2 - [tau] 1] and
the indoor blower power measured during or following the dry coil
steady-state test; or,
b. The following algorithm if the indoor blower ramps its speed
when cycling.
(1) Measure the electrical power consumed by the variable-speed
indoor blower at a minimum of three operating conditions: at the
speed/air volume rate/external static pressure that was measured
during the steady-state test, at operating conditions associated
with the midpoint of the ramp-up interval, and at conditions
associated with the midpoint of the ramp-down interval. For these
measurements, the tolerances on the airflow volume or the external
static pressure are the same as required for the section 3.4 steady-
state test.
(2) For each case, determine the fan power from measurements
made over a minimum of 5 minutes.
(3) Approximate the electrical energy consumption of the indoor
blower if it had operated during the cyclic test using all three
power measurements. Assume a linear profile during the ramp
intervals. The manufacturer must provide the durations of the ramp-
up and ramp-down intervals. If the test setup instructions included
with the unit by the manufacturer specifies a ramp interval that
exceeds 45 seconds, use a 45-second ramp interval nonetheless when
estimating the fan energy.
3.5.2 Procedures When Testing Non-Ducted Indoor Units
Do not use airflow prevention devices when conducting cyclic
tests on non-ducted indoor units. Until the last OFF/ON compressor
cycle, airflow through the indoor coil must cycle off and on in
unison with the compressor. For the last OFF/ON compressor cycle--
the one used to determine ecyc,dry and
qcyc,dry--use the exhaust fan of the airflow measuring
apparatus and the indoor blower of the test unit to have indoor
airflow start 3 minutes prior to compressor cut-on and end three
minutes after compressor cutoff. Subtract the electrical energy used
by the indoor blower during the 3 minutes prior to compressor cut-on
from the integrated electrical energy, ecyc,dry. Add the
electrical energy used by the indoor blower during the 3 minutes
after compressor cutoff to the integrated cooling capacity,
qcyc,dry. For the case where the non-ducted indoor unit
uses a variable-speed indoor blower which is disabled during the
cyclic test, correct ecyc,dry and qcyc,dry
using the same approach as prescribed in section 3.5.1 of this
appendix for ducted units having a disabled variable-speed indoor
blower.
3.5.3 Cooling-Mode Cyclic-Degradation Coefficient Calculation
Use the two dry-coil tests to determine the cooling-mode cyclic-
degradation coefficient, CD\c\. Append ``(k=2)'' to the
coefficient if it corresponds to a two-capacity unit cycling at high
capacity. If the two optional tests are conducted but yield a tested
CD\c\ that exceeds the default CD\c\ or if the
two optional tests are not conducted, assign CD\c\ the
default value of 0.25 for variable-speed compressor systems and
outdoor units with no match, and 0.20 for all other systems. The
default value for two-capacity units cycling at high capacity,
however, is the low-capacity coefficient, i.e.,
CD\c\(k=2) = CD\c\. Evaluate CD\c\
using the above results and those from the section 3.4 dry-coil
steady-state test.
[GRAPHIC] [TIFF OMITTED] TR05JA17.167
Where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.168
the average energy efficiency ratio during the cyclic dry coil
cooling mode test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TR05JA17.169
the average energy efficiency ratio during the steady-state dry coil
cooling mode test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TR05JA17.170
the cooling load factor dimensionless
Round the calculated value for CD\c\ to the nearest
0.01. If CD\c\ is negative, then set it equal to zero.
3.6 Heating Mode Tests for Different Types of Heat Pumps, Including
Heating-Only Heat Pumps
3.6.1 Tests for a Heat Pump Having a Single-Speed Compressor and Fixed
Heating Air Volume Rate
This set of tests is for single-speed-compressor heat pumps that
do not have a heating minimum air volume rate or a heating
intermediate air volume rate that is different than the heating full
load air volume rate. Conducting a very low temperature test (H4) is
optional. Conduct the optional high temperature cyclic (H1C) test to
determine the heating mode cyclic-degradation coefficient,
CD\h\. If this optional test is conducted but yields a
tested CD\h\ that exceeds the default CD\h\ or
if the optional test is not conducted, assign CD\h\ the
default value of 0.25. Test conditions for the five tests are
specified in Table 11 of this section.
Table 11--Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Blower, a Constant Air Volume Rate Indoor
Blower, or Coil-Only
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit temperature Air entering outdoor unit temperature
([deg]F) ([deg]F)
Test description ---------------------------------------------------------------------------------- Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H1 Test (required, steady)....... 70 60\(max)\.............. 47 43..................... Heating Full-load.\1\
H1C Test (optional, cyclic)...... 70 60\(max)\.............. 47 43..................... (\2\).
H2 Test (required)............... 70 60\(max)\.............. 35 33..................... Heating Full-load.\1\
H3 Test (required, steady)....... 70 60\(max)\.............. 17 15..................... Heating Full-load.\1\
H4 Test (optional, steady)....... 70 60\(max)\.............. 5 3\(max)\............... Heating Full-load.\1\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4 of this appendix.
\2\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the H1 Test.
3.6.2 Tests for a Heat Pump Having a Single-Speed Compressor and a
Single Indoor Unit Having Either (1) a Variable-Speed, Variable-Air-
Rate Indoor Blower Whose Capacity Modulation Correlates With Outdoor
Dry Bulb Temperature or (2) Multiple Indoor Blowers
Conduct five tests: Two high temperature tests (H12
and H11), one frost accumulation test (H22),
and two low temperature tests (H32 and H31).
Conducting an additional frost accumulation test (H21)
and a very low temperature test (H42) is optional.
Conduct the optional high temperature cyclic (H1C1) test
to determine the heating mode cyclic-degradation coefficient,
CD\h\. If this optional test is conducted but yields a
tested CD\h\ that exceeds the default CD\h\ or
if the optional test is not conducted, assign CD\h\ the
default value of 0.25. Test conditions for the seven tests are
specified in Table 12. If the optional H21 test is not
performed, use the following equations to approximate the capacity
and electrical power of the heat pump at the H21 test
conditions:
[[Page 1558]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.171
where,
[GRAPHIC] [TIFF OMITTED] TR05JA17.172
The quantities Q hk=2(47), E hk=2(47), Q hk=1(47), and E hk=1(47)
are determined from the H12 and H11 tests and
evaluated as specified in section 3.7 of this appendix; the
quantities Q hk=2(35) and E hk=2(35) are determined from the
H22 test and evaluated as specified in section 3.9 of
this appendix; and the quantities Q hk=2(17), E hk=2(17), Q
hk=1(17), and E hk=1(17), are determined from the H32 and
H31 tests and evaluated as specified in section 3.10 of
this appendix.
Table 12--Heating Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.6.2 Indoor Unit Requirements
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit temperature Air entering outdoor unit temperature
([deg]F) ([deg]F)
Test description ---------------------------------------------------------------------------------- Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H12 Test (required, steady)...... 70 60\(max)\.............. 47 43..................... Heating Full-load.\1\
H11 Test (required, steady)...... 70 60\(max)\.............. 47 43..................... Heating Minimum.\2\
H1C1 Test (optional, cyclic)..... 70 60\(max)\.............. 47 43..................... (\3\).
H22 Test (required).............. 70 60\(max)\.............. 35 33..................... Heating Full-load.\1\
H21 Test (optional).............. 70 60\(max)\.............. 35 33..................... Heating Minimum.\2\
H32 Test (required, steady)...... 70 60\(max)\.............. 17 15..................... Heating Full-load.\1\
H31 Test (required, steady)...... 70 60\(max)\.............. 17 15..................... Heating Minimum.\2\
H42 Test (optional, steady)...... 70 60\(max)\.............. 5 3\(max)\............... Heating Full-load.\1\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4 of this appendix.
\2\ Defined in section 3.1.4.5 of this appendix.
\3\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the H11 test.
3.6.3 Tests for a Heat Pump Having a Two-Capacity Compressor (see
Section 1.2 of This Appendix, Definitions), Including Two-Capacity,
Northern Heat Pumps (see Section 1.2 of This Appendix, Definitions)
a. Conduct one maximum temperature test (H01), two
high temperature tests (H12 and H11), one
frost accumulation test (H22), and one low temperature
test (H32). Conducting a very low temperature test
(H42) is optional. Conduct an additional frost
accumulation test (H21) and low temperature test
(H31) if both of the following conditions exist:
(1) Knowledge of the heat pump's capacity and electrical power
at low compressor capacity for outdoor temperatures of 37 [deg]F and
less is needed to complete the section 4.2.3 of this appendix
seasonal performance calculations; and
(2) The heat pump's controls allow low-capacity operation at
outdoor temperatures of 37 [deg]F and less.
If the two conditions in a.(1) and a.(2) of this section are
met, an alternative to conducting the H21 frost
accumulation is to use the following equations to approximate the
capacity and electrical power:
[GRAPHIC] [TIFF OMITTED] TR05JA17.173
Determine the quantities Qhk=1 (47) and Ehk=1 (47) from the
H11 test and evaluate them according to section 3.7 of
this appendix. Determine the quantities Qhk=1 (17) and Ehk=1 (17)
from the H31 test and evaluate them according to section
3.10 of this appendix.
b. Conduct the optional high temperature cyclic test
(H1C1) to determine the heating mode cyclic-degradation
coefficient, CDh. If this optional test is
conducted but yields a tested CDh that exceeds
the default CDh or if the optional test is not
conducted, assign CDh the default value of
0.25. If a two-capacity heat pump locks out low capacity operation
at lower outdoor temperatures, conduct the high temperature cyclic
test (H1C2) to determine the high-capacity heating mode
cyclic-degradation coefficient, CDh (k=2). If
this optional test at high capacity is conducted but yields a tested
CDh (k = 2) that exceeds the default
CDh (k = 2) or if the optional test is not
conducted, assign CDh the default value. The
default CDh (k=2) is the same value as
determined or assigned for the low-capacity cyclic-degradation
coefficient,
[[Page 1559]]
CDh [or equivalently,
CDh (k=1)]. Table 13 specifies test conditions
for these nine tests.
Table 13--Heating Mode Test Conditions for Units Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description --------------------------------------------------------------------- Compressor capacity Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).. 70 60 \(max)\......... 62 56.5 Low................ Heating Minimum.\1\
H12 Test (required, steady).. 70 60 \(max)\......... 47 43 High............... Heating Full-Load.\2\
H1C2 Test (optional \7\, 70 60 \(max)\......... 47 43 High............... (\3\)
cyclic).
H11 Test (required).......... 70 60 \(max)\......... 47 43 Low................ Heating Minimum.\1\
H1C1 Test (optional, cyclic). 70 60 \(max)\......... 47 43 Low................ (\4\)
H22 Test (required).......... 70 60 \(max)\......... 35 33 High............... Heating Full-Load.\2\
H21 Test 5 6 (required)...... 70 60 \(max)\......... 35 33 Low................ Heating Minimum.\1\
H32 Test (required, steady).. 70 60 \(max)\......... 17 15 High............... Heating Full-Load.\2\
H31 Test \5\ (required, 70 60 \(max)\......... 17 15 Low................ Heating Minimum.\1\
steady).
H42 Test (Optional, steady).. 70 60 \(max)\......... 5 3 \(max)\ High............... Heating Full-Load.\2\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5 of this appendix.
\2\ Defined in section 3.1.4.4 of this appendix.
\3\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H12 test.
\4\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H11 test.
\5\ Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37[emsp14][deg]F is needed
to complete the section 4.2.3 HSPF2 calculations.
\6\ If table note #5 applies, the section 3.6.3 equations for Qhk=1 (35) and Ehk=1 (17) may be used in lieu of conducting the H21 test.
\7\ Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.
3.6.4 Tests for a Heat Pump Having a Variable-Speed Compressor
a. Conduct one maximum temperature test (H01), two
high temperature tests (H1N and H11), one
frost accumulation test (H2V), and one low temperature
test (H32). Conducting one or more of the following tests
is optional: An additional high temperature test (H12),
an additional frost accumulation test (H22), and a very
low temperature test (H42). Conduct the optional high
temperature cyclic (H1C1) test to determine the heating
mode cyclic-degradation coefficient, CDh. If
this optional test is conducted but yields a tested
CDh that exceeds the default
CDh or if the optional test is not conducted,
assign CDh the default value of 0.25. Test
conditions for the nine tests are specified in Table 14. The
compressor shall operate at the same heating full speed, measured by
RPM or power input frequency (Hz), as the maximum speed at which the
system controls would operate the compressor in normal operation in
17[emsp14][deg]F ambient temperature, for the H12,
H22 and H32 Tests. The compressor shall
operate for the H1N test at the maximum speed at which
the system controls would operate the compressor in normal operation
in 47[emsp14][deg]F ambient temperature. The compressor shall
operate at the same heating minimum speed, measured by RPM or power
input frequency (Hz), for the H01, H1C1, and
H11 Tests. Determine the heating intermediate compressor
speed cited in Table 14 using the heating mode full and minimum
compressors speeds and:
[GRAPHIC] [TIFF OMITTED] TR05JA17.174
Where a tolerance of plus 5 percent or the next higher inverter
frequency step from that calculated is allowed.
b. If one of the high temperature tests (H12 or
H1N) is conducted using the same compressor speed (RPM or
power input frequency) as the H32 test, set the
47[emsp14][deg]F capacity and power input values used for
calculation of HSPF2 equal to the measured values for that test:
[GRAPHIC] [TIFF OMITTED] TR05JA17.175
Where:
Qhcalck=2(47) and Ehcalck=2(47) are the
capacity and power input representing full-speed operation at
47[emsp14][deg]F for the HSPF2 calculations,
Qhk=2(47) is the capacity measured in the high
temperature test (H12 or H1N) which used the
same compressor speed as the H32 test, and
Ehk=2(47) is the power input measured in the high
temperature test (H12 or H1N) which used the
same compressor speed as the H32 test.
Evaluate the quantities Qhk=2(47) and from
Ehk=2(47) according to section 3.7.
Otherwise (if no high temperature test is conducted using the
same speed (RPM or power input frequency) as the H32
test), calculate the 47[emsp14][deg]F capacity and power input
values used for calculation of HSPF2 as follows:
[[Page 1560]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.176
Where:
Qhcalck=2(47) and Ehcalck=2(47) are the
capacity and power input representing full-speed operation at
47[emsp14][deg]F for the HSPF2 calculations,
Qhk=2(17) is the capacity measured in the H32
test,
Ehk=2(17) is the power input measured in the
H32 test,
CSF is the capacity slope factor, equal to 0.0204/[deg]F for split
systems and 0.0262/[deg]F for single-package systems, and
PSF is the Power Slope Factor, equal to 0.00455/[deg]F.
c. If the H22 test is not done, use the following
equations to approximate the capacity and electrical power at the
H22 test conditions:
[GRAPHIC] [TIFF OMITTED] TR05JA17.177
Where:
Qhcalck=2(47) and Ehcalck=2(47) are the
capacity and power input representing full-speed operation at
47[emsp14][deg]F for the HSPF2 calculations, calculated as described
in section b above.
Qhk=2(17) and Ehk=2(17) are the capacity and power input
measured in the H32 test.
d. Determine the quantities Qhk=2(17) and Ehk=2(17) from the
H32 test, determine the quantities Qhk=2(5) and Ehk=2(5)
from the H42 test, and evaluate all four according to
section 3.10.
Table 14--Heating Mode Test Conditions for Units Having a Variable-Speed Compressor
------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Compressor speed Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------
H01 test (required, steady)............ 70 60 \(max)\ 62 56.5 Heating Minimum............................ Heating Minimum.\1\
H12 test (optional, steady)............ 70 60 \(max)\ 47 43 Heating Full \4\........................... Heating Full-Load.\3\
H11 test (required, steady)............ 70 60\(max)\ 47 43 Heating Minimum............................ Heating Minimum.\1\
H1N test (required, steady)............ 70 60\(max)\ 47 43 Heating Full \5\........................... Heating Full-Load.\3\
H1C1 test (optional, cyclic)........... 70 60\(max)\ 47 43 Heating Minimum............................ (\2\)
H22 test (optional).................... 70 60 \(max)\ 35 33 Heating Full \4\........................... Heating Full-Load.\3\
H2V test (required).................... 70 60 \(max)\ 35 33 Heating Intermediate....................... Heating Intermediate.\6\
H32 test (required, steady)............ 70 60 \(max)\ 17 15 Heating Full \4\........................... Heating Full-Load.\3\
H42 test (optional, steady)............ 70 60 \(max)\ 5 3 \(max)\ Heating Full............................... Heating Full-Load.\3\
------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5 of this appendix.
\2\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H11 test.
\3\ Defined in section 3.1.4.4 of this appendix.
\4\ Maximum speed that the system controls would operate the compressor in normal operation in 17[emsp14][deg]F ambient temperature. The H12 test is not needed if the H1N test uses this same
compressor speed.
\5\ Maximum speed that the system controls would operate the compressor in normal operation in 47[emsp14][deg]F ambient temperature.
\6\ Defined in section 3.1.4.6 of this appendix.
e. For multiple-split heat pumps (only), the following
procedures supersede the above requirements. For all Table 14 tests
specified for a minimum compressor speed, turn off at least one
indoor unit. The manufacturer shall designate the particular indoor
unit(s) that is turned off. The manufacturer must also specify the
compressor speed used for the Table 14 H2V test, a
heating mode intermediate compressor speed that falls within \1/4\
and \3/4\ of the difference between the full and minimum heating
mode speeds. The manufacturer should prescribe an intermediate speed
that is expected to yield the highest COP for the given
H2V test conditions and bracketed compressor speed range.
The manufacturer can designate that one or more specific indoor
units are turned off for the H2V test.
3.6.5 Additional Test for a Heat Pump Having a Heat Comfort Controller
Test any heat pump that has a heat comfort controller (see
section 1.2 of this appendix, Definitions) according to section
3.6.1, 3.6.2, or 3.6.3, whichever applies, with the heat
[[Page 1561]]
comfort controller disabled. Additionally, conduct the abbreviated
test described in section 3.1.9 of this appendix with the heat
comfort controller active to determine the system's maximum supply
air temperature. ( Note: heat pumps having a variable-speed
compressor and a heat comfort controller are not covered in the test
procedure at this time.)
3.6.6 Heating Mode Tests for Northern Heat Pumps with Triple-Capacity
Compressors
Test triple-capacity, northern heat pumps for the heating mode
as follows:
a. Conduct one maximum temperature test (H01), two
high temperature tests (H12 and H11), one
frost accumulation test (H22), two low temperature tests
(H32, H33), and one very low temperature test
(H43). Conduct an additional frost accumulation test
(H21) and low temperature test (H31) if both
of the following conditions exist: (1) Knowledge of the heat pump's
capacity and electrical power at low compressor capacity for outdoor
temperatures of 37[emsp14][deg]F and less is needed to complete the
section 4.2.6 seasonal performance calculations; and (2) the heat
pump's controls allow low capacity operation at outdoor temperatures
of 37[emsp14][deg]F and less. If the above two conditions are met,
an alternative to conducting the H21 frost accumulation
test to determine Qhk=1(35) and Ehk=1(35) is to use the following
equations to approximate this capacity and electrical power:
[GRAPHIC] [TIFF OMITTED] TR05JA17.178
In evaluating the above equations, determine the quantities
Qhk=1(47) from the H11 test and evaluate them according
to section 3.7 of this appendix. Determine the quantities Qhk=1(17)
and Ehk=1(17) from the H31 test and evaluate them
according to section 3.10 of this appendix. Use the paired values of
Qhk=1(35) and Ehk=1(35) derived from conducting the H21
frost accumulation test and evaluated as specified in section 3.9.1
of this appendix or use the paired values calculated using the above
default equations, whichever contribute to a higher Region IV HSPF2
based on the DHRmin.
b. Conducting a frost accumulation test (H23) with
the heat pump operating at its booster capacity is optional. If this
optional test is not conducted, determine Qhk=3(35) and
Ehk=3(35) using the following equations to approximate
this capacity and electrical power:
[GRAPHIC] [TIFF OMITTED] TR05JA17.179
Where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.180
Determine the quantities Qhk=2(47) and
Ehk=2(47) from the H12 test and evaluate them
according to section 3.7 of this appendix. Determine the quantities
Qhk=2(35) and Ehk=2(35) from the
H22 test and evaluate them according to section 3.9.1 of
this appendix. Determine the quantities Qhk=2(17) and
Ehk=2(17) from the H32 test, determine the
quantities Qhk=3(17) and Ehk=3(17) from the
H33 test, and determine the quantities
Qhk=3(5) and Ehk=3(5) from the H43
test. Evaluate all six quantities according to section 3.10 of this
appendix. Use the paired values of Qhk=3(35) and
Ehk=3(35) derived from conducting the H23
frost accumulation test and calculated as specified in section 3.9.1
of this appendix or use the paired values calculated using the above
default equations, whichever contribute to a higher Region IV HSPF2
based on the DHRmin.
c. Conduct the optional high temperature cyclic test
(H1C1) to determine the heating mode cyclic-degradation
coefficient, CD\h\. A default value for CD\h\
of 0.25 may be used in lieu of conducting the cyclic. If a triple-
capacity heat pump locks out low capacity operation at lower outdoor
temperatures, conduct the high temperature cyclic test
(H1C2) to determine the high capacity heating mode
cyclic-degradation coefficient, CD\h\ (k=2). The default
CD\h\ (k=2) is the same value as determined or assigned
for the low-capacity cyclic-degradation coefficient,
CD\h\ [or equivalently, CD\h\ (k=1)]. Finally,
if a triple-capacity heat pump locks out both low and high capacity
operation at the lowest outdoor temperatures, conduct the low
temperature cyclic test (H3C3) to determine the booster-
capacity heating mode cyclic-degradation coefficient,
CD\h\ (k=3). The default CD\h\ (k=3) is the
same value as determined or assigned for the high capacity cyclic-
degradation coefficient, CD\h\ [or equivalently,
CD\h\ (k=2)]. Table 15 specifies test conditions for all
13 tests.
[[Page 1562]]
Table 15--Heating Mode Test Conditions for Units With a Triple-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor
temperature [deg]F unit temperature [deg]F
Test description ---------------------------------------------------- Compressor capacity Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady)......... 70 60\(max)\ 62 56.5 Low...................... Heating Minimum \1\
H12 Test (required, steady)......... 70 60\(max)\ 47 43 High..................... Heating Full-Load \2\
H1C2 Test (optional,\8\ cyclic)..... 70 60\(max)\ 47 43 High..................... (\3\)
H11 Test (required)................. 70 60\(max)\ 47 43 Low...................... Heating Minimum \1\
H1C1 Test (optional, cyclic)........ 70 60\(max)\ 47 43 Low...................... (\4\)
H23 Test (optional, steady)......... 70 60\(max)\ 35 33 Booster.................. Heating Full-Load \2\
H22 Test (required)................. 70 60\(max)\ 35 33 High..................... Heating Full-Load \2\
H21 Test (required)................. 70 60\(max)\ 35 33 Low...................... Heating Minimum \1\
H33 Test (required, steady)......... 70 60\(max)\ 17 15 Booster.................. Heating Full-Load \2\
H3C3 Test5 6 (optional, cyclic)..... 70 60\(max)\ 17 15 Booster.................. (\7\)
H32 Test (required, steady)......... 70 60\(max)\ 17 15 High..................... Heating Full-Load \2\
H31 Test \5\ (required, steady)..... 70 60\(max)\ 17 15 Low...................... Heating Minimum \1\
H43 Test (required, steady)......... 70 60\(max)\ 5 3\(max)\ Booster.................. Heating Full-Load \2\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5 of this appendix.
\2\ Defined in section 3.1.4.4 of this appendix.
\3\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H12 test.
\4\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H11 test.
\5\ Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37[deg]F is needed to
complete the section 4.2.6 HSPF2 calculations.
\6\ If table note \5\ applies, the section 3.6.6 equations for Qhk=1(35) and Ehk=1(17) may be used in lieu of conducting the H21 test.
\7\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H33 test.
\8\ Required only if the heat pump locks out low capacity operation at lower outdoor temperatures
3.6.7 Tests for a Heat Pump Having a Single Indoor Unit Having Multiple
Indoor Blowers and Offering Two Stages of Compressor Modulation.
Conduct the Heating Mode Tests Specified in Section 3.6.3 of this
Appendix
3.7 Test Procedures for Steady-State Maximum Temperature and High
Temperature Heating Mode Tests (the H01, H1,
H12, H11, and H1N tests)
a. For the pretest interval, operate the test room
reconditioning apparatus and the heat pump until equilibrium
conditions are maintained for at least 30 minutes at the specified
section 3.6 test conditions. Use the exhaust fan of the airflow
measuring apparatus and, if installed, the indoor blower of the heat
pump to obtain and then maintain the indoor air volume rate and/or
the external static pressure specified for the particular test.
Continuously record the dry-bulb temperature of the air entering the
indoor coil, and the dry-bulb temperature and water vapor content of
the air entering the outdoor coil. Refer to section 3.11 of this
appendix for additional requirements that depend on the selected
secondary test method. After satisfying the pretest equilibrium
requirements, make the measurements specified in Table 3 of ANSI/
ASHRAE 37-2009 (incorporated by reference, see Sec. 430.3) for the
indoor air enthalpy method and the user-selected secondary method.
Make said Table 3 measurements at equal intervals that span 5
minutes or less. Continue data sampling until a 30-minute period
(e.g., seven consecutive 5-minute samples) is reached where the test
tolerances specified in Table 16 are satisfied. For those
continuously recorded parameters, use the entire data set for the
30-minute interval when evaluating Table 16 compliance. Determine
the average electrical power consumption of the heat pump over the
same 30-minute interval.
Table 16--Test Operating and Test Condition Tolerances for Section 3.7
and Section 3.10 Steady-State Heating Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor dry-bulb, [deg]F: .............. ..............
Entering temperature................ 2.0 0.5
Leaving temperature................. 2.0 ..............
Indoor wet-bulb, [deg]F: .............. ..............
Entering temperature................ 1.0 ..............
Leaving temperature................. 1.0 ..............
Outdoor dry-bulb, [deg]F: .............. ..............
Entering temperature................ 2.0 0.5
Leaving temperature................. \2\2.0 ..............
Outdoor wet-bulb, [deg]F: .............. ..............
Entering temperature................ 1.0 0.3
Leaving temperature................. \2\ 1.0 ..............
External resistance to airflow, inches 0.05 \3\ 0.02
of water...............................
Electrical voltage, % of reading........ 2.0 1.5
Nozzle pressure drop, % of reading...... 2.0 ..............
------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
\2\ Only applies when the Outdoor Air Enthalpy Method is used.
\3\ Only applies when testing non-ducted units.
[[Page 1563]]
b. Calculate indoor-side total heating capacity as specified in
sections 7.3.4.1 and 7.3.4.3 of ANSI/ASHRAE 37-2009 (incorporated by
reference, see Sec. 430.3). To calculate capacity, use the averages
of the measurements (e.g. inlet and outlet dry bulb temperatures
measured at the psychrometers) that are continuously recorded for
the same 30-minute interval used as described above to evaluate
compliance with test tolerances. Do not adjust the parameters used
in calculating capacity for the permitted variations in test
conditions. Assign the average space heating capacity and electrical
power over the 30-minute data collection interval to the variables
Qh\k\ and Eh\k\(T) respectively. The ``T'' and superscripted ``k''
are the same as described in section 3.3 of this appendix.
Additionally, for the heating mode, use the superscript to denote
results from the optional H1N test, if conducted.
c. For mobile home and space-constrained coil-only system heat
pumps, increase Qh\k\(T) by
[GRAPHIC] [TIFF OMITTED] TR05JA17.181
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
For non-mobile home, non-space-constrained coil-only system heat
pumps, increase Qh\k\(T) by
[GRAPHIC] [TIFF OMITTED] TR05JA17.182
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
During the 30-minute data collection interval of a high temperature
test, pay attention to preventing a defrost cycle. Prior to this
time, allow the heat pump to perform a defrost cycle if
automatically initiated by its own controls. As in all cases, wait
for the heat pump's defrost controls to automatically terminate the
defrost cycle. Heat pumps that undergo a defrost cycle should
operate in the heating mode for at least 10 minutes after defrost
termination prior to beginning the 30-minute data collection
interval. For some heat pumps, frost may accumulate on the outdoor
coil during a high temperature test. If the indoor coil leaving air
temperature or the difference between the leaving and entering air
temperatures decreases by more than 1.5[emsp14][deg]F over the 30-
minute data collection interval, then do not use the collected data
to determine capacity. Instead, initiate a defrost cycle. Begin
collecting data no sooner than 10 minutes after defrost termination.
Collect 30 minutes of new data during which the Table 16 test
tolerances are satisfied. In this case, use only the results from
the second 30-minute data collection interval to evaluate Qh\k\(47)
and Eh\k\(47).
d. If conducting the cyclic heating mode test, which is
described in section 3.8 of this appendix, record the average
indoor-side air volume rate, Vi, specific heat of the air,
Cp,a (expressed on dry air basis), specific volume of the
air at the nozzles, vn' (or vn), humidity
ratio at the nozzles, Wn, and either pressure difference
or velocity pressure for the flow nozzles. If either or both of the
below criteria apply, determine the average, steady-state,
electrical power consumption of the indoor blower motor
(Efan,1):
(1) The section 3.8 cyclic test will be conducted and the heat
pump has a variable-speed indoor blower that is expected to be
disabled during the cyclic test; or
(2) The heat pump has a (variable-speed) constant-air volume-
rate indoor blower and during the steady-state test the average
external static pressure ([Delta]P1) exceeds the
applicable section 3.1.4.4 minimum (or targeted) external static
pressure ([Delta]Pmin) by 0.03 inches of water or more.
Determine Efan,1 by making measurements during the
30-minute data collection interval, or immediately following the
test and prior to changing the test conditions. When the above ``2''
criteria applies, conduct the following four steps after determining
Efan,1 (which corresponds to [Delta]P1):
(i) While maintaining the same test conditions, adjust the
exhaust fan of the airflow measuring apparatus until the external
static pressure increases to approximately [Delta]P1 +
([Delta]P1 - [Delta]Pmin).
(ii) After re-establishing steady readings for fan motor power
and external static pressure, determine average values for the
indoor blower power (Efan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
(iii) Approximate the average power consumption of the indoor
blower motor if the 30-minute test had been conducted at
[Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TR05JA17.183
(iv) Decrease the total space heating capacity, Qh\k\(T), by the
quantity (Efan,1 - Efan,min), when expressed
on a Btu/h basis. Decrease the total electrical power, Eh\k\(T) by
the same fan power difference, now expressed in watts.
e. If the temperature sensors used to provide the primary
measurement of the indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the subsequent cyclic dry-
coil test are different, include measurements of the latter sensors
among the regularly sampled data. Beginning at the start of the 30-
minute data collection period, measure and compute the indoor-side
air dry-bulb temperature difference using both sets of
instrumentation, [Delta]T (Set SS) and [Delta]T (Set CYC), for each
equally spaced data sample. If using a consistent data sampling rate
that is less than 1 minute, calculate and record minutely averages
for the two temperature differences. If using a consistent sampling
rate of one minute or more, calculate and record the two temperature
differences from each data sample. After having recorded the seventh
(i=7) set of temperature differences, calculate the following ratio
using the first seven sets of values:
[GRAPHIC] [TIFF OMITTED] TR05JA17.184
Each time a subsequent set of temperature differences is recorded
(if sampling more frequently than every 5 minutes), calculate
FCD using the most recent seven sets of values. Continue
these calculations until the 30-minute period is completed or until
a value for FCD is calculated that falls outside the
allowable range of 0.94-1.06. If the latter occurs, immediately
suspend the test and identify the cause for the disparity in the two
temperature difference measurements. Recalibration of one or both
sets of instrumentation may be required. If all the values for
FCD are within the allowable range, save the final value
of the ratio from the 30-minute test as FCD*. If the
temperature sensors used to provide the primary measurement of the
indoor-side dry bulb temperature difference during the steady-state
dry-coil test and the subsequent cyclic dry-coil test are the same,
set FCD*= 1.
3.8 Test Procedures for the Cyclic Heating Mode Tests (the
H0C1, H1C, H1C1 and H1C2 Tests).
a. Except as noted below, conduct the cyclic heating mode test
as specified in section 3.5 of this appendix. As adapted to the
heating mode, replace section 3.5 references to ``the steady-state
dry coil test'' with ``the heating mode steady-state test conducted
at the same test conditions as the cyclic heating mode test.'' Use
the test tolerances in Table 17 rather than Table 10. Record the
outdoor coil entering wet-bulb temperature according to the
requirements given in section 3.5 of this appendix for the outdoor
coil entering dry-bulb temperature. Drop the subscript ``dry'' used
in variables cited in section 3.5 of this appendix when referring to
quantities from the cyclic heating
[[Page 1564]]
mode test. If available, use electric resistance heaters (see
section 2.1 of this appendix) to minimize the variation in the inlet
air temperature. Determine the total space heating delivered during
the cyclic heating test, qcyc, as specified in section
3.5 of this appendix except for making the following changes:
(1) When evaluating Equation 3.5-1, use the values of Vi,
Cp,a,vn', (or vn), and
Wn that were recorded during the section 3.7 steady-state
test conducted at the same test conditions.
(2) Calculate
[GRAPHIC] [TIFF OMITTED] TR05JA17.185
where FCD* is the value recorded during the section 3.7
steady-state test conducted at the same test condition.
b. For ducted coil-only system heat pumps (excluding the special
case where a variable-speed fan is temporarily removed), increase
qcyc by the amount calculated using Equation 3.5-3.
Additionally, increase ecyc by the amount calculated
using Equation 3.5-2. In making these calculations, use the average
indoor air volume rate (Vis) determined from the section
3.7 steady-state heating mode test conducted at the same test
conditions.
c. For non-ducted heat pumps, subtract the electrical energy
used by the indoor blower during the 3 minutes after compressor
cutoff from the non-ducted heat pump's integrated heating capacity,
qcyc.
d. If a heat pump defrost cycle is manually or automatically
initiated immediately prior to or during the OFF/ON cycling, operate
the heat pump continuously until 10 minutes after defrost
termination. After that, begin cycling the heat pump immediately or
delay until the specified test conditions have been re-established.
Pay attention to preventing defrosts after beginning the cycling
process. For heat pumps that cycle off the indoor blower during a
defrost cycle, make no effort here to restrict the air movement
through the indoor coil while the fan is off. Resume the OFF/ON
cycling while conducting a minimum of two complete compressor OFF/ON
cycles before determining qcyc and ecyc.
3.8.1 Heating Mode Cyclic-Degradation Coefficient Calculation
Use the results from the required cyclic test and the required
steady-state test that were conducted at the same test conditions to
determine the heating mode cyclic-degradation coefficient CDh. Add
``(k=2)'' to the coefficient if it corresponds to a two-capacity
unit cycling at high capacity. For the below calculation of the
heating mode cyclic degradation coefficient, do not include the duct
loss correction from section 7.3.3.3 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3) in determining
Qh\k\(Tcyc) (or qcyc). If the optional cyclic
test is conducted but yields a tested CDh that exceeds the default
CDh or if the optional test is not conducted, assign CDh the default
value of 0.25. The default value for two-capacity units cycling at
high capacity, however, is the low-capacity coefficient, i.e., CDh
(k=2) = CDh. The tested CDh is calculated as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.186
Where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.187
the average coefficient of performance during the cyclic heating
mode test, dimensionless.
[GRAPHIC] [TIFF OMITTED] TR05JA17.188
the average coefficient of performance during the steady-state
heating mode test conducted at the same test conditions--i.e., same
outdoor dry bulb temperature, Tcyc, and speed/capacity,
k, if applicable--as specified for the cyclic heating mode test,
dimensionless.
[GRAPHIC] [TIFF OMITTED] TR05JA17.189
the heating load factor, dimensionless.
Tcyc = the nominal outdoor temperature at which the
cyclic heating mode test is conducted, 62 or 47[emsp14][deg]F.
[Delta][tau]cyc = the duration of the OFF/ON intervals;
0.5 hours when testing a heat pump having a single-speed or two-
capacity compressor and 1.0 hour when testing a heat pump having a
variable-speed compressor.
Round the calculated value for CDh to the nearest 0.01. If CDh
is negative, then set it equal to zero.
[[Page 1565]]
Table 17--Test Operating and Test Condition Tolerances for Cyclic
Heating Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor entering dry-bulb temperature,\2\ 2.0 0.5
[deg]F.................................
Indoor entering wet-bulb temperature,\2\ 1.0 ..............
[deg]F.................................
Outdoor entering dry-bulb 2.0 0.5
temperature,\2\ [deg]F.................
Outdoor entering wet-bulb 2.0 1.0
temperature,\2\ [deg]F.................
External resistance to air-flow,\2\ 0.05 ..............
inches of water........................
Airflow nozzle pressure difference or 2.0 \3\ 2.0
velocity pressure,\2\% of reading......
Electrical voltage,\4\% of reading...... 2.0 1.5
------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
\2\ Applies during the interval that air flows through the indoor
(outdoor) coil except for the first 30 seconds after flow initiation.
For units having a variable-speed indoor blower that ramps, the
tolerances listed for the external resistance to airflow shall apply
from 30 seconds after achieving full speed until ramp down begins.
\3\ The test condition must be the average nozzle pressure difference or
velocity pressure measured during the steady-state test conducted at
the same test conditions.
\4\ Applies during the interval that at least one of the following--the
compressor, the outdoor fan, or, if applicable, the indoor blower--are
operating, except for the first 30 seconds after compressor start-up.
3.9 Test Procedures for Frost Accumulation Heating Mode Tests (the
H2, H22, H2V, and H21 Tests).
a. Confirm that the defrost controls of the heat pump are set as
specified in section 2.2.1 of this appendix. Operate the test room
reconditioning apparatus and the heat pump for at least 30 minutes
at the specified section 3.6 test conditions before starting the
``preliminary'' test period. The preliminary test period must
immediately precede the ``official'' test period, which is the
heating and defrost interval over which data are collected for
evaluating average space heating capacity and average electrical
power consumption.
b. For heat pumps containing defrost controls which are likely
to cause defrosts at intervals less than one hour, the preliminary
test period starts at the termination of an automatic defrost cycle
and ends at the termination of the next occurring automatic defrost
cycle. For heat pumps containing defrost controls which are likely
to cause defrosts at intervals exceeding one hour, the preliminary
test period must consist of a heating interval lasting at least one
hour followed by a defrost cycle that is either manually or
automatically initiated. In all cases, the heat pump's own controls
must govern when a defrost cycle terminates.
c. The official test period begins when the preliminary test
period ends, at defrost termination. The official test period ends
at the termination of the next occurring automatic defrost cycle.
When testing a heat pump that uses a time-adaptive defrost control
system (see section 1.2 of this appendix, Definitions), however,
manually initiate the defrost cycle that ends the official test
period at the instant indicated by instructions provided by the
manufacturer. If the heat pump has not undergone a defrost after 6
hours, immediately conclude the test and use the results from the
full 6-hour period to calculate the average space heating capacity
and average electrical power consumption.
For heat pumps that turn the indoor blower off during the
defrost cycle, take steps to cease forced airflow through the indoor
coil and block the outlet duct whenever the heat pump's controls
cycle off the indoor blower. If it is installed, use the outlet
damper box described in section 2.5.4.1 of this appendix to affect
the blocked outlet duct.
d. Defrost termination occurs when the controls of the heat pump
actuate the first change in converting from defrost operation to
normal heating operation. Defrost initiation occurs when the
controls of the heat pump first alter its normal heating operation
in order to eliminate possible accumulations of frost on the outdoor
coil.
e. To constitute a valid frost accumulation test, satisfy the
test tolerances specified in Table 18 during both the preliminary
and official test periods. As noted in Table 18, test operating
tolerances are specified for two sub-intervals:
(1) When heating, except for the first 10 minutes after the
termination of a defrost cycle (sub-interval H, as described in
Table 18) and
(2) When defrosting, plus these same first 10 minutes after
defrost termination (sub-interval D, as described in Table 18).
Evaluate compliance with Table 18 test condition tolerances and the
majority of the test operating tolerances using the averages from
measurements recorded only during sub-interval H. Continuously
record the dry bulb temperature of the air entering the indoor coil,
and the dry bulb temperature and water vapor content of the air
entering the outdoor coil. Sample the remaining parameters listed in
Table 18 at equal intervals that span 5 minutes or less.
f. For the official test period, collect and use the following
data to calculate average space heating capacity and electrical
power. During heating and defrosting intervals when the controls of
the heat pump have the indoor blower on, continuously record the
dry-bulb temperature of the air entering (as noted above) and
leaving the indoor coil. If using a thermopile, continuously record
the difference between the leaving and entering dry-bulb
temperatures during the interval(s) that air flows through the
indoor coil. For coil-only system heat pumps, determine the
corresponding cumulative time (in hours) of indoor coil airflow,
[Delta][tau]a. Sample measurements used in calculating
the air volume rate (refer to sections 7.7.2.1 and 7.7.2.2 of ANSI/
ASHRAE 37-2009) at equal intervals that span 10 minutes or less.
(Note: In the first printing of ANSI/ASHRAE 37-2009, the second IP
equation for Qmi should read:) Record the electrical
energy consumed, expressed in watt-hours, from defrost termination
to defrost termination, eDEF\k\(35), as well as the
corresponding elapsed time in hours, [Delta][tau]FR.
Table 18--Test Operating and Test Condition Tolerances for Frost Accumulation Heating Mode Tests
----------------------------------------------------------------------------------------------------------------
Test operating tolerance \1\ Test condition
-------------------------------- tolerance \1\
Sub-interval H Sub-interval D Sub-interval H
\2\ \3\ \2\
----------------------------------------------------------------------------------------------------------------
Indoor entering dry-bulb temperature, [deg]F.................... 2.0 \4\ 4.0 0.5
Indoor entering wet-bulb temperature, [deg]F.................... 1.0 .............. ..............
Outdoor entering dry-bulb temperature, [deg]F................... 2.0 10.0 1.0
Outdoor entering wet-bulb temperature, [deg]F................... 1.5 .............. 0.5
External resistance to airflow, inches of water................. 0.05 .............. \5\ 0.02
Electrical voltage, % of reading................................ 2.0 .............. 1.5
----------------------------------------------------------------------------------------------------------------
\1\ See section 1.2 of this appendix, Definitions.
[[Page 1566]]
\2\ Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a
defrost cycle.
\3\ Applies during a defrost cycle and during the first 10 minutes after the termination of a defrost cycle when
the heat pump is operating in the heating mode.
\4\ For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies
during the 10 minute interval that follows defrost termination.
\5\ Only applies when testing non-ducted heat pumps.
3.9.1 Average Space Heating Capacity and Electrical Power Calculations
a. Evaluate average space heating capacity, Qh\k\(35), when
expressed in units of Btu per hour, using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.190
where,
Vi = the average indoor air volume rate measured during sub-interval
H, cfm.
Cp,a = 0.24 + 0.444 [middot] Wn, the constant
pressure specific heat of the air-water vapor mixture that flows
through the indoor coil and is expressed on a dry air basis, Btu/
lbmda [middot] [deg]F.
vn' = specific volume of the air-water vapor mixture at
the nozzle, ft\3\/lbmmx.
Wn = humidity ratio of the air-water vapor mixture at the
nozzle, lbm of water vapor per lbm of dry air.
[Delta][tau]FR = [tau]2 - [tau]1,
the elapsed time from defrost termination to defrost termination,
hr.
[GRAPHIC] [TIFF OMITTED] TR05JA17.191
Tal([tau]) = dry bulb temperature of the air entering the
indoor coil at elapsed time [tau], [deg]F; only recorded when indoor
coil airflow occurs; assigned the value of zero during periods (if
any) where the indoor blower cycles off.
Ta2([tau]) = dry bulb temperature of the air leaving the
indoor coil at elapsed time [tau], [deg]F; only recorded when indoor
coil airflow occurs; assigned the value of zero during periods (if
any) where the indoor blower cycles off.
[tau]1 = the elapsed time when the defrost termination
occurs that begins the official test period, hr.
[tau]2 = the elapsed time when the next automatically
occurring defrost termination occurs, thus ending the official test
period, hr.
vn = specific volume of the dry air portion of the
mixture evaluated at the dry-bulb temperature, vapor content, and
barometric pressure existing at the nozzle, ft\3\ per lbm of dry
air.
To account for the effect of duct losses between the outlet of
the indoor unit and the section 2.5.4 dry-bulb temperature grid,
adjust Qh\k\(35) in accordance with section 7.3.4.3 of ANSI/ASHRAE
37-2009 (incorporated by reference, see Sec. 430.3).
b. Evaluate average electrical power, Eh\k\(35), when expressed
in units of watts, using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.192
For mobile home and space-constrained coil-only system heat pumps,
increase Qh\k\(35) by
[GRAPHIC] [TIFF OMITTED] TR05JA17.193
where Vis is the average measured indoor air volume
rate expressed in units of cubic feet per minute of standard air
(scfm).
For non-mobile home, non-space-constrained coil-only system heat
pumps, increase Qh\k\(35) by
[GRAPHIC] [TIFF OMITTED] TR05JA17.194
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
c. For heat pumps having a constant-air-volume-rate indoor
blower, the five additional steps listed below are required if the
average of the external static pressures measured during sub-
interval H exceeds the applicable section 3.1.4.4, 3.1.4.5, or
3.1.4.6 minimum (or targeted) external static pressure
([Delta]Pmin) by 0.03 inches of water or more:
(1) Measure the average power consumption of the indoor blower
motor (Efan,1) and record the corresponding external
static pressure ([Delta]P1) during or immediately
following the frost accumulation heating mode test. Make the
measurement at a time when the heat pump is heating, except for the
first 10 minutes after the termination of a defrost cycle.
(2) After the frost accumulation heating mode test is completed
and while maintaining the same test conditions, adjust the exhaust
fan of the airflow measuring apparatus until the external static
pressure increases to approximately [Delta]P1 +
([Delta]P1 - [Delta]Pmin).
(3) After re-establishing steady readings for the fan motor
power and external static pressure, determine average values for the
indoor blower power (Efan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
(4) Approximate the average power consumption of the indoor
blower motor had the frost accumulation heating mode test been
conducted at [Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TR05JA17.195
[[Page 1567]]
(5) Decrease the total heating capacity, Qh\k\(35), by the
quantity [(Efan,1 - Efan,min)[middot]
([Delta][tau] a/[Delta][tau] FR], when
expressed on a Btu/h basis. Decrease the total electrical power,
Eh\k\(35), by the same quantity, now expressed in watts.
3.9.2 Demand Defrost Credit
a. Assign the demand defrost credit, Fdef, that is
used in section 4.2 of this appendix to the value of 1 in all cases
except for heat pumps having a demand-defrost control system (see
section 1.2 of this appendix, Definitions). For such qualifying heat
pumps, evaluate Fdef using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.196
where:
[Delta][tau]def = the time between defrost terminations
(in hours) or 1.5, whichever is greater. Assign a value of 6 to
[Delta][tau]def if this limit is reached during a frost
accumulation test and the heat pump has not completed a defrost
cycle.
[Delta][tau]max = maximum time between defrosts as
allowed by the controls (in hours) or 12, whichever is less, as
provided in the certification report.
b. For two-capacity heat pumps and for section 3.6.2 units,
evaluate the above equation using the [Delta][tau]def
that applies based on the frost accumulation test conducted at high
capacity and/or at the heating full-load air volume rate. For
variable-speed heat pumps, evaluate [Delta][tau]def based
on the required frost accumulation test conducted at the
intermediate compressor speed.
3.10 Test Procedures for Steady-State Low Temperature and Very Low
Temperature Heating Mode Tests (the H3, H32,
H31, H33, H4, H42, and
H43 Tests)
Except for the modifications noted in this section, conduct the
low temperature and very low temperature heating mode tests using
the same approach as specified in section 3.7 of this appendix for
the maximum and high temperature tests. After satisfying the section
3.7 requirements for the pretest interval but before beginning to
collect data to determine the capacity and power input, conduct a
defrost cycle. This defrost cycle may be manually or automatically
initiated. Terminate the defrost sequence using the heat pump's
defrost controls. Begin the 30-minute data collection interval
described in section 3.7 of this appendix, from which the capacity
and power input are determined, no sooner than 10 minutes after
defrost termination. Defrosts should be prevented over the 30-minute
data collection interval.
3.11 Additional Requirements for the Secondary Test Methods
3.11.1 If Using the Outdoor Air Enthalpy Method as the Secondary Test
Method.
a. For all cooling mode and heating mode tests, first conduct a
test without the outdoor air-side test apparatus described in
section 2.10.1 of this appendix connected to the outdoor unit
(``free outdoor air'' test).
b. For the first section 3.2 steady-state cooling mode test and
the first section 3.6 steady-state heating mode test, conduct a
second test in which the outdoor-side apparatus is connected
(``ducted outdoor air'' test). No other cooling mode or heating mode
tests require the ducted outdoor air test so long as the unit
operates the outdoor fan during all cooling mode steady-state tests
at the same speed and all heating mode steady-state tests at the
same speed. If using more than one outdoor fan speed for the cooling
mode steady-state tests, however, conduct the ducted outdoor air
test for each cooling mode test where a different fan speed is first
used. This same requirement applies for the heating mode tests.
3.11.1.1 Free Outdoor Air Test
a. For the free outdoor air test, connect the indoor air-side
test apparatus to the indoor coil; do not connect the outdoor air-
side test apparatus. Allow the test room reconditioning apparatus
and the unit being tested to operate for at least one hour. After
attaining equilibrium conditions, measure the following quantities
at equal intervals that span 5 minutes or less:
(1) The section 2.10.1 evaporator and condenser temperatures or
pressures;
(2) Parameters required according to the Indoor Air Enthalpy
Method.
Continue these measurements until a 30-minute period (e.g.,
seven consecutive 5-minute samples) is obtained where the Table 9 or
Table 16, whichever applies, test tolerances are satisfied.
b. For cases where a ducted outdoor air test is not required per
section 3.11.1.b of this appendix, the free outdoor air test
constitutes the ``official'' test for which validity is not based on
comparison with a secondary test.
c. For cases where a ducted outdoor air test is required per
section 3.11.1.b of this appendix, the following conditions must be
met for the free outdoor air test to constitute a valid ``official''
test:
(1) The energy balance specified in section 3.1.1 of this
appendix is achieved for the ducted outdoor air test (i.e., compare
the capacities determined using the indoor air enthalpy method and
the outdoor air enthalpy method).
(2) The capacities determined using the indoor air enthalpy
method from the ducted outdoor air and free outdoor air tests must
agree within 2 percent.
3.11.1.2 Ducted Outdoor Air Test
a. The test conditions and tolerances for the ducted outdoor air
test are the same as specified for the official test, where the
official test is the free outdoor air test described in section
3.11.1.1 of this appendix.
b. After collecting 30 minutes of steady-state data during the
free outdoor air test, connect the outdoor air-side test apparatus
to the unit for the ducted outdoor air test. Adjust the exhaust fan
of the outdoor airflow measuring apparatus until averages for the
evaporator and condenser temperatures, or the saturated temperatures
corresponding to the measured pressures, agree within 0.5[emsp14][deg]F of the averages achieved during the free
outdoor air test. Collect 30 minutes of steady-state data after re-
establishing equilibrium conditions.
c. During the ducted outdoor air test, at intervals of 5 minutes
or less, measure the parameters required according to the indoor air
enthalpy method and the outdoor air enthalpy method for the
prescribed 30 minutes.
d. For cooling mode ducted outdoor air tests, calculate capacity
based on outdoor air-enthalpy measurements as specified in sections
7.3.3.2 and 7.3.3.3 of ANSI/ASHRAE 37-2009 (incorporated by
reference, see Sec. 430.3). For heating mode ducted tests,
calculate heating capacity based on outdoor air-enthalpy
measurements as specified in sections 7.3.4.2 and 7.3.3.4.3 of the
same ANSI/ASHRAE Standard. Adjust the outdoor-side capacity
according to section 7.3.3.4 of ANSI/ASHRAE 37-2009 to account for
line losses when testing split systems. As described in section
8.6.2 of ANSI/ASHRAE 37-2009, use the outdoor air volume rate as
measured during the ducted outdoor air tests to calculate capacity
for checking the agreement with the capacity calculated using the
indoor air enthalpy method.
3.11.2 If Using the Compressor Calibration Method as the Secondary Test
Method
a. Conduct separate calibration tests using a calorimeter to
determine the refrigerant flow rate. Or for cases where the
superheat of the refrigerant leaving the evaporator is less than
5[emsp14][deg]F, use the calorimeter to measure total capacity
rather than refrigerant flow rate. Conduct these calibration tests
at the same test conditions as specified for the tests in this
appendix. Operate the unit for at least one hour or until obtaining
equilibrium conditions before collecting data that will be used in
determining the average refrigerant flow rate or total capacity.
Sample the data at equal intervals that span 5 minutes or less.
Determine average flow rate or average capacity from data sampled
over a 30-minute period where the Table 9 (cooling) or the Table 16
(heating) tolerances are satisfied. Otherwise, conduct the
calibration tests according to sections 5, 6, 7, and 8 of ASHRAE
23.1-2010 (incorporated by reference, see Sec. 430.3); sections 5,
6, 7, 8, 9, and 11 of ASHRAE 41.9-2011 (incorporated by reference,
see Sec. 430.3); and section 7.4 of ANSI/ASHRAE 37-2009
(incorporated by reference, see Sec. 430.3).
b. Calculate space cooling and space heating capacities using
the compressor calibration method measurements as specified in
section 7.4.5 and 7.4.6 respectively, of ANSI/ASHRAE 37-2009.
[[Page 1568]]
3.11.3 If Using the Refrigerant-Enthalpy Method as the Secondary Test
Method
Conduct this secondary method according to section 7.5 of ANSI/
ASHRAE 37-2009. Calculate space cooling and heating capacities using
the refrigerant-enthalpy method measurements as specified in
sections 7.5.4 and 7.5.5, respectively, of the same ANSI/ASHRAE
Standard.
3.12 Rounding of Space Conditioning Capacities for Reporting
Purposes
a. When reporting rated capacities, round them off as specified
in Sec. 430.23 (for a single unit) and in 10 CFR 429.16 (for a
sample).
b. For the capacities used to perform the calculations in
section 4 of this appendix, however, round only to the nearest
integer.
3.13 Laboratory Testing To Determine Off Mode Average Power Ratings
Voltage tolerances: As a percentage of reading, test operating
tolerance must be 2.0 percent and test condition tolerance must be
1.5 percent (see section 1.2 of this appendix for definitions of
these tolerances).
Conduct one of the following tests: If the central air
conditioner or heat pump lacks a compressor crankcase heater,
perform the test in section 3.13.1 of this appendix; if the central
air conditioner or heat pump has a compressor crankcase heater that
lacks controls and is not self-regulating, perform the test in
section 3.13.1 of this appendix; if the central air conditioner or
heat pump has a crankcase heater with a fixed power input controlled
with a thermostat that measures ambient temperature and whose
sensing element temperature is not affected by the heater, perform
the test in section 3.13.1 of this appendix; if the central air
conditioner or heat pump has a compressor crankcase heater equipped
with self-regulating control or with controls for which the sensing
element temperature is affected by the heater, perform the test in
section 3.13.2 of this appendix.
3.13.1 This Test Determines the Off Mode Average Power Rating for
Central Air Conditioners and Heat Pumps That Lack a Compressor
Crankcase Heater, or Have a Compressor Crankcase Heating System That
Can Be Tested Without Control of Ambient Temperature During the Test.
This Test Has No Ambient Condition Requirements
a. Test Sample Set-up and Power Measurement: For coil-only
systems, provide a furnace or modular blower that is compatible with
the system to serve as an interface with the thermostat (if used for
the test) and to provide low-voltage control circuit power. Make all
control circuit connections between the furnace (or modular blower)
and the outdoor unit as specified by the manufacturer's installation
instructions. Measure power supplied to both the furnace (or modular
blower) and power supplied to the outdoor unit. Alternatively,
provide a compatible transformer to supply low-voltage control
circuit power, as described in section 2.2.d of this appendix.
Measure transformer power, either supplied to the primary winding or
supplied by the secondary winding of the transformer, and power
supplied to the outdoor unit. For blower coil and single-package
systems, make all control circuit connections between components as
specified by the manufacturer's installation instructions, and
provide power and measure power supplied to all system components.
b. Configure Controls: Configure the controls of the central air
conditioner or heat pump so that it operates as if connected to a
building thermostat that is set to the OFF position. Use a
compatible building thermostat if necessary to achieve this
configuration. For a thermostat-controlled crankcase heater with a
fixed power input, bypass the crankcase heater thermostat if
necessary to energize the heater.
c. Measure P2x: If the unit has a crankcase heater time delay,
make sure that time-delay function is disabled or wait until delay
time has passed. Determine the average power from non-zero value
data measured over a 5-minute interval of the non-operating central
air conditioner or heat pump and designate the average power as P2x,
the heating season total off mode power.
d. Measure Px for coil-only split systems and for blower coil
split systems for which a furnace or a modular blower is the
designated air mover: Disconnect all low-voltage wiring for the
outdoor components and outdoor controls from the low-voltage
transformer. Determine the average power from non-zero value data
measured over a 5-minute interval of the power supplied to the
(remaining) low-voltage components of the central air conditioner or
heat pump, or low-voltage power, Px. This power measurement does not
include line power supplied to the outdoor unit. It is the line
power supplied to the air mover, or, if a compatible transformer is
used instead of an air mover, it is the line power supplied to the
transformer primary coil. If a compatible transformer is used
instead of an air mover and power output of the low-voltage
secondary circuit is measured, Px is zero.
e. Calculate P2: Set the number of compressors equal to the
unit's number of single-stage compressors plus 1.75 times the unit's
number of compressors that are not single-stage.
For single-package systems and blower coil split systems for
which the designated air mover is not a furnace or modular blower,
divide the heating season total off mode power (P2x) by the number
of compressors to calculate P2, the heating season per-compressor
off mode power. Round P2 to the nearest watt. The expression for
calculating P2 is as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.197
For coil-only split systems and blower coil split systems for
which a furnace or a modular blower is the designated air mover,
subtract the low-voltage power (Px) from the heating season total
off mode power (Px) and divide by the number of compressors to
calculate P2, the heating season per-compressor off mode power.
Round P2 to the nearest watt. The expression for calculating P2 is
as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.198
f. Shoulder-season per-compressor off mode power, P1: If the
system does not have a crankcase heater, has a crankcase heater
without controls that is not self-regulating, or has a value for the
crankcase heater turn-on temperature (as certified to DOE) that is
higher than 71[emsp14][deg]F, P1 is equal to P2.
Otherwise, de-energize the crankcase heater (by removing the
thermostat bypass or otherwise disconnecting only the power supply
to the crankcase heater) and repeat the measurement as described in
section 3.13.1.c of this appendix. Designate the measured average
power as P1x, the shoulder season total off mode power.
Determine the number of compressors as described in section
3.13.1.e of this appendix.
For single-package systems and blower coil systems for which the
designated air mover is not a furnace or modular blower, divide the
shoulder season total off mode power (P1x) by the number of
compressors to calculate P1, the shoulder season per-compressor off
mode power. Round P1 to the nearest watt. The expression for
calculating P1 is as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.199
For coil-only split systems and blower coil split systems for
which a furnace or a modular blower is the designated air mover,
subtract the low-voltage power (Px) from the shoulder season total
off mode power (P1x) and divide by the number of compressors to
calculate P1, the shoulder season per-compressor off mode power.
Round P1 to the nearest watt. The expression for calculating P1 is
as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.200
3.13.2 This Test Determines the Off Mode Average Power Rating for
Central Air Conditioners and Heat Pumps for Which Ambient Temperature
Can Affect the Measurement of Crankcase Heater Power
a. Test Sample Set-up and Power Measurement: set up the test and
measurement as described in section 3.13.1.a of this appendix.
b. Configure Controls: Position a temperature sensor to measure
the outdoor dry-bulb temperature in the air between 2 and 6 inches
from the crankcase heater control temperature sensor or, if no such
temperature sensor exists, position it in the air between 2 and 6
inches from the crankcase heater. Utilize the temperature
measurements from this sensor for this portion of the test
procedure. Configure the controls of the central air conditioner or
heat pump so that it operates as if connected to a building
thermostat that is set to the OFF position. Use a compatible
building thermostat if necessary to achieve this configuration.
Conduct the test after completion of the B, B1, or
B2 test. Alternatively, start the test when the outdoor
dry-bulb temperature is at 82[emsp14][deg]F and the temperature of
the compressor shell (or temperature of each compressor's shell if
there is more than one compressor) is at least 81[emsp14][deg]F.
Then adjust the outdoor
[[Page 1569]]
temperature and achieve an outdoor dry-bulb temperature of
72[emsp14][deg]F. If the unit's compressor has no sound blanket,
wait at least 4 hours after the outdoor temperature reaches
72[emsp14][deg]F. Otherwise, wait at least 8 hours after the outdoor
temperature reaches 72[emsp14][deg]F. Maintain this temperature
within 2[emsp14][deg]F while the compressor temperature
equilibrates and while making the power measurement, as described in
section 3.13.2.c of this appendix.
c. Measure P1x: If the unit has a crankcase heater time delay,
make sure that time-delay function is disabled or wait until delay
time has passed. Determine the average power from non-zero value
data measured over a 5-minute interval of the non-operating central
air conditioner or heat pump and designate the average power as P1x,
the shoulder season total off mode power. For units with crankcase
heaters which operate during this part of the test and whose
controls cycle or vary crankcase heater power over time, the test
period shall consist of three complete crankcase heater cycles or 18
hours, whichever comes first. Designate the average power over the
test period as P1x, the shoulder season total off mode power.
d. Reduce outdoor temperature: Approach the target outdoor dry-
bulb temperature by adjusting the outdoor temperature. This target
temperature is five degrees Fahrenheit less than the temperature
certified by the manufacturer as the temperature at which the
crankcase heater turns on. If the unit's compressor has no sound
blanket, wait at least 4 hours after the outdoor temperature reaches
the target temperature. Otherwise, wait at least 8 hours after the
outdoor temperature reaches the target temperature. Maintain the
target temperature within 2[emsp14][deg]F while the
compressor temperature equilibrates and while making the power
measurement, as described in section 3.13.2.e of this appendix.
e. Measure P2x: If the unit has a crankcase heater time delay,
make sure that time-delay function is disabled or wait until delay
time has passed. Determine the average non-zero power of the non-
operating central air conditioner or heat pump over a 5-minute
interval and designate it as P2x, the heating season total off mode
power. For units with crankcase heaters whose controls cycle or vary
crankcase heater power over time, the test period shall consist of
three complete crankcase heater cycles or 18 hours, whichever comes
first. Designate the average power over the test period as P2x, the
heating season total off mode power.
f. Measure Px for coil-only split systems and for blower coil
split systems for which a furnace or modular blower is the
designated air mover: Disconnect all low-voltage wiring for the
outdoor components and outdoor controls from the low-voltage
transformer. Determine the average power from non-zero value data
measured over a 5-minute interval of the power supplied to the
(remaining) low-voltage components of the central air conditioner or
heat pump, or low-voltage power, Px. This power measurement does not
include line power supplied to the outdoor unit. It is the line
power supplied to the air mover, or, if a compatible
transformer is used instead of an air mover, it is the line power
supplied to the transformer primary coil. If a compatible
transformer is used instead of an air mover and power output of the
low-voltage secondary circuit is measured, Px is zero.
g. Calculate P1:
Set the number of compressors equal to the unit's number of
single-stage compressors plus 1.75 times the unit's number of
compressors that are not single-stage.
For single-package systems and blower coil split systems for
which the air mover is not a furnace or modular blower, divide the
shoulder season total off mode power (P1x) by the number of
compressors to calculate P1, the shoulder season per-compressor off
mode power. Round to the nearest watt. The expression for
calculating P1 is as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.201
For coil-only split systems and blower coil split systems for
which a furnace or a modular blower is the designated air mover,
subtract the low-voltage power (Px) from the shoulder season total
off mode power (P1x) and divide by the number of compressors to
calculate P1, the shoulder season per-compressor off mode power.
Round to the nearest watt. The expression for calculating P1 is as
follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.202
h. Calculate P2:
Determine the number of compressors as described in section
3.13.2.g of this appendix.
For, single-package systems and blower coil split systems for
which the air mover is not a furnace, divide the heating season
total off mode power (P2x) by the number of compressors to calculate
P2, the heating season per-compressor off mode power. Round to the
nearest watt. The expression for calculating P2 is as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.203
For coil-only split systems and blower coil split systems for
which a furnace or a modular blower is the designated air mover,
subtract the low-voltage power (Px) from the heating season total
off mode power (P2x) and divide by the number of compressors to
calculate P2, the heating season per-compressor off mode power.
Round to the nearest watt. The expression for calculating P2 is as
follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.204
4 Calculations of Seasonal Performance Descriptors
4.1 Seasonal Energy Efficiency Ratio (SEER2) Calculations
Calculate SEER2 as follows: For equipment covered under sections
4.1.2, 4.1.3, and 4.1.4 of this appendix, evaluate the seasonal
energy efficiency ratio,
[GRAPHIC] [TIFF OMITTED] TR05JA17.205
where,
[[Page 1570]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.206
Tj = the outdoor bin temperature, [deg]F. Outdoor
temperatures are grouped or ``binned.'' Use bins of 5[emsp14][deg]F
with the 8 cooling season bin temperatures being 67, 72, 77, 82, 87,
92, 97, and 102[emsp14][deg]F.
j = the bin number. For cooling season calculations, j ranges from 1
to 8.
Additionally, for sections 4.1.2, 4.1.3, and 4.1.4 of this
appendix, use a building cooling load, BL(Tj). When
referenced, evaluate BL(Tj) for cooling using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.207
where:
Qck=2(95) = the space cooling capacity determined from
the A2 test and calculated as specified in section 3.3 of
this appendix, Btu/h.
1.1 = sizing factor, dimensionless.
The temperatures 95[emsp14][deg]F and 65[emsp14][deg]F in the
building load equation represent the selected outdoor design
temperature and the zero-load base temperature, respectively.
V is a factor equal to 0.93 for variable-speed heat pumps and
otherwise equal to 1.0.
4.1.1 SEER2 Calculations for a Blower Coil System Having a Single-Speed
Compressor and Either a Fixed-Speed Indoor Blower or a Constant-Air-
Volume-Rate Indoor Blower, or a Single-Speed Coil-Only System Air
Conditioner or Heat Pump
a. Evaluate the seasonal energy efficiency ratio, expressed in
units of Btu/watt-hour, using:
SEER2 = PLF(0.5) * EERB
where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.208
PLF(0.5) = 1 - 0.5 [middot] CD\c\, the part-load
performance factor evaluated at a cooling load factor of 0.5,
dimensionless.
b. Refer to section 3.3 of this appendix regarding the
definition and calculation of Qc(82) and
Ec(82). Evaluate the cooling mode cyclic degradation
factor CD\c\ as specified in section 3.5.3 of this
appendix.
4.1.2 SEER2 Calculations for an Air Conditioner or Heat Pump Having a
Single-Speed Compressor and a Variable-Speed Variable-Air-Volume-Rate
Indoor Blower
4.1.2.1 Units Covered by Section 3.2.2.1 of This Appendix Where Indoor
Blower Capacity Modulation Correlates With the Outdoor Dry Bulb
Temperature
The manufacturer must provide information on how the indoor air
volume rate or the indoor blower speed varies over the outdoor
temperature range of 67[emsp14][deg]F to 102[emsp14][deg]F.
Calculate SEER2 using Equation 4.1-1. Evaluate the quantity
qc(Tj)/N in Equation 4.1-1 using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.209
where:
[[Page 1571]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.210
Qc(Tj) = the space cooling capacity of the
test unit when operating at outdoor temperature, Tj, Btu/
h.
nj/N = fractional bin hours for the cooling season; the
ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless.
a. For the space cooling season, assign nj/N as
specified in Table 19. Use Equation 4.1-2 to calculate the building
load, BL(Tj). Evaluate Qc(Tj)
using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.211
where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.212
the space cooling capacity of the test unit at outdoor temperature
Tj if operated at the cooling minimum air volume rate,
Btu/h.
[GRAPHIC] [TIFF OMITTED] TR05JA17.213
the space cooling capacity of the test unit at outdoor temperature
Tj if operated at the Cooling full-load air volume rate,
Btu/h.
b. For units where indoor blower speed is the primary control
variable, FPck=1 denotes the fan speed used during the
required A1 and B1 tests (see section 3.2.2.1
of this appendix), FPck=2 denotes the fan speed used
during the required A2 and B2 tests, and
FPc(Tj) denotes the fan speed used by the unit
when the outdoor temperature equals Tj. For units where
indoor air volume rate is the primary control variable, the three
FPc's are similarly defined only now being expressed in
terms of air volume rates rather than fan speeds. Refer to sections
3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 of this appendix regarding the
definitions and calculations of Qck=1(82),
Qck=1(95),Qc k=2(82), and
Qck=2(95).
Calculate ec(Tj)/N in Equation 4.1-1
using, Equation 4.1.2-3
[GRAPHIC] [TIFF OMITTED] TR05JA17.214
where:
PLFj = 1 - CD\c\ [middot] [1 -
X(Tj)], the part load factor, dimensionless.
Ec(Tj) = the electrical power consumption of
the test unit when operating at outdoor temperature Tj,
W.
c. The quantities X(Tj) and nj/N are the
same quantities as used in Equation 4.1.2-1. Evaluate the cooling
mode cyclic degradation factor CD\c\ as specified in
section 3.5.3 of this appendix.
d. Evaluate Ec(Tj) using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.215
the electrical power consumption of the test unit at outdoor
temperature Tj if operated at the cooling minimum air
volume rate, W.
[[Page 1572]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.216
e. The parameters FPck=1, and FPck=2, and
FPc(Tj) are the same quantities that are used
when evaluating Equation 4.1.2-2. Refer to sections 3.2.2.1, 3.1.4
to 3.1.4.2, and 3.3 of this appendix regarding the definitions and
calculations of Eck=1(82), Eck=1(95),
Eck=2(82), and Eck=2(95).
4.1.2.2 Units Covered by Section 3.2.2.2 of This Appendix Where Indoor
Blower Capacity Modulation is Used to Adjust the Sensible to Total
Cooling Capacity Ratio
Calculate SEER2 as specified in section 4.1.1 of this appendix.
4.1.3 SEER2 Calculations for an Air Conditioner or Heat Pump Having a
Two-Capacity Compressor
Calculate SEER2 using Equation 4.1-1. Evaluate the space cooling
capacity, Qck=1 (Tj), and electrical power
consumption, Eck=1 (Tj), of the test unit when
operating at low compressor capacity and outdoor temperature
Tj using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.217
[GRAPHIC] [TIFF OMITTED] TR05JA17.218
where Qck=1 (82) and Eck=1 (82) are determined
from the B1 test, Qck=1 (67) and
Eck=1 (67) are determined from the F1 test,
and all four quantities are calculated as specified in section 3.3
of this appendix. Evaluate the space cooling capacity,
Qck=2 (Tj), and electrical power consumption,
Eck=2 (Tj), of the test unit when operating at
high compressor capacity and outdoor temperature Tj
using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.219
[GRAPHIC] [TIFF OMITTED] TR05JA17.220
where Qck=2(95) and Eck=2(95) are determined
from the A2 test, Qck=2(82), and
Eck=2(82), are determined from the B2 test,
and all are calculated as specified in section 3.3 of this appendix.
The calculation of Equation 4.1-1 quantities
qc(Tj)/N and ec(Tj)/N
differs depending on whether the test unit would operate at low
capacity (section 4.1.3.1 of this appendix), cycle between low and
high capacity (section 4.1.3.2 of this appendix), or operate at high
capacity (sections 4.1.3.3 and 4.1.3.4 of this appendix) in
responding to the building load. For units that lock out low
capacity operation at higher outdoor temperatures, the outdoor
temperature at which the unit locks out must be that specified by
the manufacturer in the certification report so that the appropriate
equations are used. Use Equation 4.1-2 to calculate the building
load, BL(Tj), for each temperature bin.
4.1.3.1 Steady-state Space Cooling Capacity at Low Compressor Capacity
Is Greater Than or Equal to the Building Cooling Load at Temperature
Tj, Qck=1(Tj) >=BL(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.221
Where:
Xk=1(Tj) = BL(Tj)/
Qck=1(Tj), the cooling mode low capacity load
factor for temperature bin j, dimensionless.
PLFj = 1 - CD\c\ [middot] [1 -
Xk=1(Tj)], the part load factor, dimensionless.
nj/N = fractional bin hours for the cooling season;
the ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qck=1(Tj) and
Eck=1(Tj). Evaluate the cooling mode cyclic
degradation factor CD\c\ as specified in section 3.5.3 of
this appendix.
Table 19--Distribution of Fractional Hours Within Cooling Season Temperature Bins
----------------------------------------------------------------------------------------------------------------
Fraction of of
Bin Representative total
Bin number, j temperature temperature temperature
range [deg]F for bin [deg]F bin hours, nj/
N
----------------------------------------------------------------------------------------------------------------
1............................................................... 65-69 67 0.214
[[Page 1573]]
2............................................................... 70-74 72 0.231
3............................................................... 75-79 77 0.216
4............................................................... 80-84 82 0.161
5............................................................... 85-89 87 0.104
6............................................................... 90-94 92 0.052
7............................................................... 95-99 97 0.018
8............................................................... 100-104 102 0.004
----------------------------------------------------------------------------------------------------------------
4.1.3.2 Unit Alternates Between High (k=2) and Low (k=1) Compressor
Capacity to Satisfy the Building Cooling Load at Temperature
Tj, Qck=1(Tj) <(BL(Tj)
<(Qck=2(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.222
Where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.223
Xk=2(Tj) = 1 - Xk=1(Tj), the cooling mode,
high capacity load factor for temperature bin j, dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qck=1(Tj) and
Eck=1(Tj). Use Equations 4.1.3-3 and 4.1.3-4,
respectively, to evaluate Qck=2(Tj) and
Eck=2(Tj).
4.1.3.3 Unit Only Operates at High (k=2) Compressor Capacity at
Temperature Tj and Its Capacity Is Greater Than the Building
Cooling Load, BL(Tj) ck=2(Tj). This
section applies to units that lock out low compressor capacity
operation at higher outdoor temperatures.
[GRAPHIC] [TIFF OMITTED] TR05JA17.224
Where,
Xk=2(Tj) = BL(Tj)/
Qck=2(Tj), the cooling mode high capacity load
factor for temperature bin j, dimensionless.
PLFj = 1-CDc(k = 2) * [1-Xk=2(Tj)], the part load factor,
dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. Use Equations 4.1.3-3 and 4.1.3-4,
respectively, to evaluate Qck=2 (Tj) and
Eck=2 (Tj). If the C2 and
D2 tests described in section 3.2.3 and Table 7 of this
appendix are not conducted, set CD\c\ (k=2) equal to the
default value specified in section 3.5.3 of this appendix.
4.1.3.4 Unit Must Operate Continuously at High (k=2) Compressor
Capacity at Temperature Tj, BL(Tj)
>=Qck=2(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.225
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. Use Equations 4.1.3-3 and 4.1.3-4,
respectively, to evaluate Qck=2(Tj) and
Eck=2(Tj).
4.1.4 SEER2 Calculations for an Air Conditioner or Heat Pump Having a
Variable-Speed Compressor
Calculate SEER2 using Equation 4.1-1. Evaluate the space cooling
capacity, Qck=1(Tj), and electrical power
consumption, Eck=1(Tj), of the test unit when
operating at minimum compressor speed and outdoor temperature
Tj. Use,
[[Page 1574]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.226
[GRAPHIC] [TIFF OMITTED] TR05JA17.227
where Qck=1(82) and Eck=1(82) are determined
from the B1 test, Qck=1(67) and
Eck=1(67) are determined from the F1 test, and all four
quantities are calculated as specified in section 3.3 of this
appendix. Evaluate the space cooling capacity,
Qck=2(Tj), and electrical power consumption,
Eck=2(Tj), of the test unit when operating at
full compressor speed and outdoor temperature Tj. Use
Equations 4.1.3-3 and 4.1.3-4, respectively, where
Qck=2(95) and Eck=2(95) are determined from
the A2 test, Qck=2(82) and
Eck=2(82) are determined from the B2 test, and
all four quantities are calculated as specified in section 3.3 of
this appendix. Calculate the space cooling capacity,
Qc\k=v\(Tj), and electrical power consumption,
Ec\k=v\(Tj), of the test unit when operating
at outdoor temperature Tj and the intermediate compressor
speed used during the section 3.2.4 (and Table 8) EV test
of this appendix using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.228
[GRAPHIC] [TIFF OMITTED] TR05JA17.229
where Qc\k=v\(87) and Ec\k=v\(87) are
determined from the EV test and calculated as specified
in section 3.3 of this appendix. Approximate the slopes of the k=v
intermediate speed cooling capacity and electrical power input
curves, MQ and ME, as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.230
[GRAPHIC] [TIFF OMITTED] TR05JA17.231
Use Equations 4.1.4-1 and 4.1.4-2, respectively, to calculate
Qck=1(87) and Eck=1(87).
4.1.4.1 Steady-state space cooling capacity when operating at
minimum compressor speed is greater than or equal to the building
cooling load at temperature Tj,
Qck=1(Tj) >=BL(Tj).
[GRAPHIC] [TIFF OMITTED] TR05JA17.232
Where:
Xk=1(Tj) = BL(Tj)/
Qck=1(Tj), the cooling mode minimum speed load
factor for temperature bin j, dimensionless.
PLFj = 1 - CD\c\ [middot] [1 -
Xk=1(Tj)], the part load factor, dimensionless.
nj/N = fractional bin hours for the cooling season; the
ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qc\k=l\ (Tj) and
Ec\k=l\ (Tj). Evaluate the cooling mode cyclic
degradation factor CD\c\ as specified in section 3.5.3 of
this appendix.
4.1.4.2 Unit operates at an intermediate compressor speed (k=i)
in order to match the building cooling load at temperature
Tj, Qck=1(Tj) j)
ck=2(Tj).
[GRAPHIC] [TIFF OMITTED] TR05JA17.233
Where:
Qc\k=i\(Tj) = BL(Tj), the space
cooling capacity delivered by the unit in matching the building load
at temperature Tj, Btu/h.
[[Page 1575]]
The matching occurs with the unit operating at compressor speed k =
i.
[GRAPHIC] [TIFF OMITTED] TR05JA17.234
EER\k=i\(Tj) = the steady-state energy efficiency ratio
of the test unit when operating at a compressor speed of k = i and
temperature Tj, Btu/h per W.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 19 of this section. For each temperature
bin where the unit operates at an intermediate compressor speed,
determine the energy efficiency ratio EER\k=i\(Tj) using
the following equations,
For each temperature bin where Qck=1(Tj)
j) c\k=v\(Tj),
[GRAPHIC] [TIFF OMITTED] TR05JA17.235
For each temperature bin where Qc\k=v\(Tj)
<=BL(Tj) ck=2(Tj),
[GRAPHIC] [TIFF OMITTED] TR05JA17.236
Where:
EERk=1(Tj) is the steady-state energy efficiency
ratio of the test unit when operating at minimum compressor speed
and temperature Tj, Btu/h per W, calculated using capacity
Qck=1(Tj) calculated using Equation 4.1.4-1
and electrical power consumption Eck=1(Tj)
calculated using Equation 4.1.4-2;
EER\k=v\(Tj) is the steady-state energy efficiency
ratio of the test unit when operating at intermediate compressor
speed and temperature Tj, Btu/h per W, calculated using capacity
Qc\k=v\(Tj) calculated using Equation 4.1.4-3
and electrical power consumption Ec\k=v\(Tj)
calculated using Equation 4.1.4-4;
EER2k=2(Tj) is the steady-state energy efficiency
ratio of the test unit when operating at full compressor speed and
temperature Tj, Btu/h per W, calculated using capacity
Qck=2(Tj) and electrical power consumption
Eck=2(Tj), both calculated as described in
section 4.1.4; and
BL(Tj) is the building cooling load at temperature
Tj, Btu/h.
4.1.4.3 Unit must operate continuously at full (k=2) compressor
speed at temperature Tj, BL(Tj)
>=Qck=2(Tj). Evaluate the Equation 4.1-1
quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.237
as specified in section 4.1.3.4 of this appendix with the
understanding that Qck=2(Tj) and
Eck=2(Tj) correspond to full compressor speed
operation and are derived from the results of the tests specified in
section 3.2.4 of this appendix.
4.1.5 SEER2 Calculations for an Air Conditioner or Heat Pump Having a
Single Indoor Unit With Multiple Indoor Blowers
Calculate SEER2 using Eq. 4.1-1, where qc(Tj)/N and
ec(Tj)/N are evaluated as specified in the applicable
subsection.
4.1.5.1 For Multiple Indoor Blower Systems That Are Connected to a
Single, Single-Speed Outdoor Unit
a. Calculate the space cooling capacity, Qck=1(Tj),
and electrical power consumption, Eck=1(Tj), of the test
unit when operating at the cooling minimum air volume rate and
outdoor temperature Tj using the equations given in
section 4.1.2.1 of this appendix. Calculate the space cooling
capacity, Qck=2(Tj), and electrical power consumption,
Eck=2(Tj), of the test unit when operating at the cooling
full-load air volume rate and outdoor temperature Tj
using the equations given in section 4.1.2.1 of this appendix. In
evaluating the section 4.1.2.1 equations, determine the quantities
Qck=1(82) and Eck=1(82) from the B1 test,
Qck=1(95) and Eck=1(95) from the Al test,
Qck=2(82) and Eck=2(82) from the B2 test, and
Qck=2(95) and Eck=2(95) from the A2
test. Evaluate all eight quantities as specified in section 3.3.
Refer to section 3.2.2.1 and Table 6 for additional information on
the four referenced laboratory tests.
b. Determine the cooling mode cyclic degradation coefficient,
CD\c\, as per sections 3.2.2.1 and 3.5 to 3.5.3 of this
appendix. Assign this same value to CD\c\(K=2).
c. Except for using the above values of Qck=1(Tj),
Eck=1(Tj), Eck=2(Tj), Qck=2(Tj),
CD\c\, and CD\c\ (K=2), calculate the
quantities qc(Tj)/N and
ec(Tj)/N as specified in section 4.1.3.1 of
this appendix for cases where Qck=1(Tj) >=
BL(Tj). For all other outdoor bin temperatures,
Tj, calculate qc(Tj)/N and ec(Tj)/N
as specified in section 4.1.3.3 of this appendix if
Qck=2(Tj) > BL (Tj) or as specified in section
4.1.3.4 of this appendix if Qck=2(Tj) <=
BL(Tj).
4.1.5.2 For Multiple Indoor Blower Systems That Are Connected to Either
a Lone Outdoor Unit Having a Two-Capacity Compressor or Two Separate
But Identical Model Single-Speed Outdoor Units. Calculate the
Quantities qc(Tj)/N and ec(Tj)/N as Specified in
Section 4.1.3 of This Appendix
4.2 Heating Seasonal Performance Factor 2 (HSPF2) Calculations
Unless an approved alternative efficiency determination method
is used, as set forth in 10 CFR 429.70(e). Calculate HSPF2 as
follows: Six generalized climatic regions are depicted in Figure 1
and otherwise defined in Table 20. For each of these regions and for
each applicable standardized design heating requirement, evaluate
the heating seasonal performance factor using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.238
[[Page 1576]]
Where:
eh(Tj)/N = The ratio of the electrical energy consumed by
the heat pump during periods of the heating season when the outdoor
temperature fell within the range represented by bin temperature
Tj to the total number of hours in the heating season
(N), W. For heat pumps having a heat comfort controller, this ratio
may also include electrical energy used by resistive elements to
maintain a minimum air delivery temperature (see 4.2.5).
RH(Tj)/N = The ratio of the electrical energy used for
resistive space heating during periods when the outdoor temperature
fell within the range represented by bin temperature Tj
to the total number of hours in the heating season (N), W. Except as
noted in section 4.2.5 of this appendix, resistive space heating is
modeled as being used to meet that portion of the building load that
the heat pump does not meet because of insufficient capacity or
because the heat pump automatically turns off at the lowest outdoor
temperatures. For heat pumps having a heat comfort controller, all
or part of the electrical energy used by resistive heaters at a
particular bin temperature may be reflected in eh(Tj)/N
(see section 4.2.5 of this appendix).
Tj = the outdoor bin temperature, [deg]F. Outdoor
temperatures are ``binned'' such that calculations are only
performed based one temperature within the bin. Bins of
5[emsp14][deg]F are used.
nj/N = Fractional bin hours for the heating season; the
ratio of the number of hours during the heating season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
heating season, dimensionless. Obtain nj/N values from
Table 20.
j = the bin number, dimensionless.
J = for each generalized climatic region, the total number of
temperature bins, dimensionless. Referring to Table 20, J is the
highest bin number (j) having a nonzero entry for the fractional bin
hours for the generalized climatic region of interest.
Fdef = the demand defrost credit described in section
3.9.2 of this appendix, dimensionless.
BL(Tj) = the building space conditioning load
corresponding to an outdoor temperature of Tj; the
heating season building load also depends on the generalized
climatic region's outdoor design temperature and the design heating
requirement, Btu/h.
Table 20--Generalized Climatic Region Information
----------------------------------------------------------------------------------------------------------------
Region Number I II III IV V * VI
----------------------------------------------------------------------------------------------------------------
Heating Load Hours, HLH........... 493 857 1247 1701 2202 1842
Outdoor Design Temperature, TOD... 37 27 17 5 -10 30
Heating Load Line Equation Slope 1.10 1.06 1.30 1.15 1.16 1.11
Factor, C........................
Variable-speed Slope Factor, CVS.. 1.03 0.99 1.21 1.07 1.08 1.03
Zero-Load Temperature, Tzl........ 58 57 56 55 55 57
-----------------------------------------------------------------------------
j Tj ([deg]F).................... Fractional Bin Hours, nj/N
----------------------------------------------------------------------------------------------------------------
1 62............................. 0 0 0 0 0 0
2 57............................. .239 0 0 0 0 0
3 52............................. .194 .163 .138 .103 .086 .215
4 47............................. .129 .143 .137 .093 .076 .204
5 42............................. .081 .112 .135 .100 .078 .141
6 37............................. .041 .088 .118 .109 .087 .076
7 32............................. .019 .056 .092 .126 .102 .034
8 27............................. .005 .024 .047 .087 .094 .008
9 22............................. .001 .008 .021 .055 .074 .003
10 17............................. 0 .002 .009 .036 .055 0
11 12............................. 0 0 .005 .026 .047 0
12 7.............................. 0 0 .002 .013 .038 0
13 2.............................. 0 0 .001 .006 .029 0
14 -3............................. 0 0 0 .002 .018 0
15 -8............................. 0 0 0 .001 .010 0
16 -13............................ 0 0 0 0 .005 0
17 -18............................ 0 0 0 0 .002 0
18 -23............................ 0 0 0 0 .001 0
----------------------------------------------------------------------------------------------------------------
* Pacific Coast Region.
Evaluate the building heating load using
[GRAPHIC] [TIFF OMITTED] TR05JA17.239
where,
Tj = the outdoor bin temperature, [deg]F
Tzl = the zero-load temperature, [deg]F, which varies by
climate region according to Table 20
C = the slope (adjustment) factor, which varies by climate region
according to Table 20
Qc(95[deg]F) = the cooling capacity at 95 [deg]F
determined from the A or A2 test, Btu/h
For heating-only heat pump units, replace Qc(95[deg]F) in
Equation 4.2-2 with Qh(47[deg]F)
Qh(47[deg]F)= the heating capacity at 47 [deg]F
determined from the H, H12 or H1N test, Btu/h.
a. For all heat pumps, HSPF2 accounts for the heating delivered
and the energy consumed by auxiliary resistive elements when
operating below the balance point. This condition occurs when the
building load exceeds the space heating capacity of the heat pump
condenser. For HSPF2 calculations for all heat pumps, see either
section 4.2.1, 4.2.2, 4.2.3, or 4.2.4 of this appendix, whichever
applies.
b. For heat pumps with heat comfort controllers (see section 1.2
of this appendix, Definitions), HSPF2 also accounts for
[[Page 1577]]
resistive heating contributed when operating above the heat-pump-
plus-comfort-controller balance point as a result of maintaining a
minimum supply temperature. For heat pumps having a heat comfort
controller, see section 4.2.5 of this appendix for the additional
steps required for calculating the HSPF2.
4.2.1 Additional Steps for Calculating the HSPF2 of a Blower Coil
System Heat Pump Having a Single-Speed Compressor and Either a Fixed-
Speed Indoor Blower or a Constant-Air-Volume-Rate Indoor Blower, or a
Single-Speed Coil-Only System Heat Pump
[GRAPHIC] [TIFF OMITTED] TR05JA17.240
[GRAPHIC] [TIFF OMITTED] TR05JA17.241
Where:
[GRAPHIC] [TIFF OMITTED] TR05JA17.242
whichever is less; the heating mode load factor for temperature bin
j, dimensionless.
Qh(Tj) = the space heating capacity of the heat pump when
operating at outdoor temperature Tj, Btu/h.
Eh(Tj) = the electrical power consumption of the heat
pump when operating at outdoor temperature Tj, W.
[delta](Tj) = the heat pump low temperature cut-out
factor, dimensionless.
PLFj = 1 - CDh [middot] [1 -X(Tj)] the part
load factor, dimensionless.
Use Equation 4.2-2 to determine BL(Tj). Obtain
fractional bin hours for the heating season, nj/N, from
Table 20. Evaluate the heating mode cyclic degradation factor CDh as
specified in section 3.8.1 of this appendix.
Determine the low temperature cut-out factor using
[GRAPHIC] [TIFF OMITTED] TR05JA17.243
Where:
Toff = the outdoor temperature when the compressor is
automatically shut off, [deg]F. (If no such temperature exists,
Tj is always greater than Toff and
Ton).
Ton = the outdoor temperature when the compressor is
automatically turned back on, if applicable, following an automatic
shut-off, [deg]F.
If the H4 test is not conducted, calculate Qh(Tj) and
Eh(Tj) using
[GRAPHIC] [TIFF OMITTED] TR05JA17.244
[GRAPHIC] [TIFF OMITTED] TR05JA17.245
where Qh(47) and Eh(47) are determined from the H1 test and
calculated as specified in section 3.7 of this appendix; Qh(35) and
Eh(35) are determined from the H2 test and calculated as specified
in section 3.9.1 of this appendix; and Qh(17) and
[[Page 1578]]
Eh(17) are determined from the H3 test and calculated as specified
in section 3.10 of this appendix.
If the H4 test is conducted, calculate Qh(Tj) and
Eh(Tj) using
[GRAPHIC] [TIFF OMITTED] TR05JA17.246
[GRAPHIC] [TIFF OMITTED] TR05JA17.247
where Qh(47) and Eh(47) are determined from the H1 test and
calculated as specified in section 3.7 of this appendix; Qh(35) and
Eh(35) are determined from the H2 test and calculated as specified
in section 3.9.1 of this appendix; Qh(17) and Eh(17) are determined
from the H3 test and calculated as specified in section 3.10 of this
appendix; Qh(5) and Eh(5) are determined from the H4 test and
calculated as specified in section 3.10 of this appendix.
4.2.2 Additional Steps for Calculating the HSPF2 of a Heat Pump Having
a Single-Speed Compressor and a Variable-Speed, Variable-Air-Volume-
Rate Indoor Blower
The manufacturer must provide information about how the indoor
air volume rate or the indoor blower speed varies over the outdoor
temperature range of 65[emsp14][deg]F to -23[emsp14][deg]F.
Calculate the quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.248
in Equation 4.2-1 as specified in section 4.2.1 of this appendix
with the exception of replacing references to the H1C test and
section 3.6.1 of this appendix with the H1C1 test and
section 3.6.2 of this appendix. In addition, evaluate the space
heating capacity and electrical power consumption of the heat pump
Qh(Tj) and Eh(Tj) using
[GRAPHIC] [TIFF OMITTED] TR05JA17.249
[GRAPHIC] [TIFF OMITTED] TR05JA17.250
where the space heating capacity and electrical power consumption at
low capacity (k=1) at outdoor temperature Tj are determined using
[[Page 1579]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.251
[GRAPHIC] [TIFF OMITTED] TR05JA17.252
If the H42 test is not conducted, calculate the space
heating capacity and electrical power consumption at high capacity
(k=2) at outdoor temperature Tj using Equations 4.2.2-3 and 4.2.2-4
for k=2.
If the H42 test is conducted, calculate the space
heating capacity and electrical power consumption at high capacity
(k=2) at outdoor temperature Tj using Equations 4.2.2-5 and 4.2.2-6.
[GRAPHIC] [TIFF OMITTED] TR05JA17.253
[GRAPHIC] [TIFF OMITTED] TR05JA17.254
For units where indoor blower speed is the primary control
variable, FPhk=1 denotes the fan speed used during the required
H11 and H31 tests (see Table 12), FPhk=2
denotes the fan speed used during the required H12,
H22, and H32 tests, and FPh(Tj)
denotes the fan speed used by the unit when the outdoor temperature
equals Tj. For units where indoor air volume rate is the
primary control variable, the three FPh's are similarly defined only
now being expressed in terms of air volume rates rather than fan
speeds. Determine Qhk=1(47) and Ehk=1(47) from the H11
test, and Qhk=2(47) and Ehk=2(47) from the H12 test.
Calculate all four quantities as specified in section 3.7 of this
appendix. Determine Qhk=1(35) and Ehk=1(35) as specified in section
3.6.2 of this appendix; determine Qhk=2(35) and Ehk=2(35) and from
the H22 test and the calculation specified in section 3.9
of this appendix. Determine Qhk=1(17) and Ehk=1(17 from the
H31 test, and Qhk=2(17) and Ehk=2(17) from the
H32 test. Calculate all four quantities as specified in
section 3.10 of this appendix. Determine Qhk=2(5) and Ehk=2(5) from
the H42 test and the calculation specified in section
3.10 of this appendix.
4.2.3 Additional Steps for Calculating the HSPF2 of a Heat Pump Having
a Two-Capacity Compressor
The calculation of the Equation 4.2-1 quantities differ
depending upon whether the heat pump would operate at low capacity
(section 4.2.3.1 of this appendix), cycle between low and high
capacity (section 4.2.3.2 of this appendix), or operate at high
capacity (sections 4.2.3.3 and 4.2.3.4 of this appendix) in
responding to the building load. For heat pumps that lock out low
capacity operation at low outdoor temperatures, the outdoor
temperature at which the unit locks out must be that specified by
the manufacturer in the certification report so that the appropriate
equations can be selected.
[[Page 1580]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.255
a. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at low compressor
capacity and outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TR05JA17.256
b. If the H42 test is not conducted, evaluate the
space heating capacity and electrical power consumption
(Qhk=2(Tj) and Ehk=2
(Tj)) of the heat pump when operating at high compressor
capacity and outdoor temperature Tj by solving Equations 4.2.2-3 and
4.2.2-4, respectively, for k=2. If the H42 test is
conducted, evaluate the space heating capacity and electrical power
consumption (Qhk=2(Tj) and Ehk=2
(Tj)) of the heat pump when operating at high compressor
capacity and outdoor temperature Tj using Equations 4.2.2-5 and
4.2.2-6, respectively.
Determine Qhk=1(62) and Ehk=1(62) from the
H01 test, Qhk=1(47) and Ehk=1(47)
from the H11 test, and Qhk=2(47) and
Ehk=2(47) from the H12 test. Calculate all six
quantities as specified in section 3.7 of this appendix. Determine
Qhk=2(35) and Ehk=2(35) from the
H22 test and, if required as described in section 3.6.3
of this appendix, determine Qhk=1(35) and
Ehk=1(35) from the H21 test. Calculate the
required 35 [deg]F quantities as specified in section 3.9 in this
appendix. Determine Qhk=2(17) and Ehk=2(17)
from the H32 test and, if required as described in
section 3.6.3 of this appendix, determine Qhk=1(17) and
Ehk=1(17) from the H31 test. Calculate the
required 17 [deg]F quantities as specified in section 3.10 of this
appendix. Determine Qhk=2(5) and Ehk=2(5) from
the H42 test and the calculation specified in section
3.10 of this appendix.
4.2.3.1 Steady-State Space Heating Capacity When Operating at Low
Compressor Capacity Is Greater Than or Equal to the Building Heating
Load at Temperature Tj, Qhk=1(Tj)
>=BL(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.257
[GRAPHIC] [TIFF OMITTED] TR05JA17.258
Where:
Xk=1(Tj) = BL(Tj)/
Qhk=1(Tj), the heating mode low capacity load factor for
temperature bin j, dimensionless.
PLFj = 1 - CDh [middot] [ 1 - Xk=1(Tj) ], the
part load factor, dimensionless.
[delta]'(Tj) = the low temperature cutoff factor,
dimensionless.
Evaluate the heating mode cyclic degradation factor CDh as
specified in section 3.8.1 of this appendix.
Determine the low temperature cut-out factor using
[GRAPHIC] [TIFF OMITTED] TR05JA17.259
where Toff and Ton are defined in section
4.2.1 of this appendix. Use the calculations given in section
4.2.3.3 of this appendix, and not the above, if:
a. The heat pump locks out low capacity operation at low outdoor
temperatures and
b. Tj is below this lockout threshold temperature.
4.2.3.2 Heat Pump Alternates Between High (k=2) and Low (k=1)
Compressor Capacity To Satisfy the Building Heating Load at a
Temperature Tj, Qhk=1(Tj)
BL(Tj) Qhk=2(Tj)
[[Page 1581]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.260
Xk=2(Tj) = 1 - Xk=1(Tj)
the heating mode, high capacity load factor for temperature bin
j, dimensionless.
Determine the low temperature cut-out factor,
[delta]'(Tj), using Equation 4.2.3-3.
4.2.3.3 Heat Pump Only Operates at High (k=2) Compressor Capacity at
Temperature Tj and its Capacity Is Greater Than the Building
Heating Load, BL(Tj) < Qhk=2(Tj). This
Section Applies to Units That Lock Out Low Compressor Capacity
Operation at Low Outdoor Temperatures
[GRAPHIC] [TIFF OMITTED] TR05JA17.261
where:
Xk=2(Tj)= BL(Tj)/
Qhk=2(Tj). PLFj = 1 -
ChD(k = 2) * [1 - Xk=2(Tj)]
If the H1C2 test described in section 3.6.3 and Table
13 of this appendix is not conducted, set CDh (k=2) equal to the
default value specified in section 3.8.1 of this appendix.
Determine the low temperature cut-out factor,
[delta](Tj), using Equation 4.2.3-3.
4.2.3.4 Heat Pump Must Operate Continuously at High (k=2) Compressor
Capacity at Temperature Tj, BL(Tj)
>=Qhk=2(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.262
4.2.4 Additional Steps for Calculating the HSPF2 of a Heat Pump Having
a Variable-Speed Compressor. Calculate HSPF2 Using Equation 4.2-1
[[Page 1582]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.263
a. Minimum Compressor Speed. Evaluate the space heating
capacity, Qhk=1(Tj), and electrical power consumption,
Ehk=1(Tj), of the heat pump when operating at minimum
compressor speed and outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TR05JA17.264
[GRAPHIC] [TIFF OMITTED] TR05JA17.265
where Qhk=1(62) and Ehk=1(62) are determined from the H01
test, Qhk=1(47) and Ehk=1(47) are determined from the H11
test, and all four quantities are calculated as specified in section
3.7 of this appendix.
b. Minimum Compressor Speed for Minimum-speed-limiting Variable-
speed Heat Pumps: Evaluate the space heating capacity,
Qhk=1(Tj), and electrical power consumption,
Ehk=1(Tj), of the heat pump when operating at minimum
compressor speed and outdoor temperature Tj using
Equation 4.2.4-3
[GRAPHIC] [TIFF OMITTED] TR05JA17.266
[GRAPHIC] [TIFF OMITTED] TR05JA17.267
where Qhk=1(62) and Ehk=1(62) are determined from the H01
test, Qhk=1(47) and Ehk=1(47) are determined from the H11
test, and all four quantities are calculated as specified in section
3.7 of this appendix; Qh\k=v\(35) and Eh\k=v\(35) are determined
from the H2v test and are calculated as specified in
section 3.9 of this appendix; and Qh\k=v\(Tj) and
Eh\k=v\(Tj) are calculated using equations 4.2.4-5 and
4.2.4-6, respectively.
c. Full Compressor Speed for Heat Pumps for which the
H42 test is not Conducted. Evaluate the space heating
capacity, Qhk=2(Tj), and electrical power consumption,
Ehk=2(Tj), of the heat pump when operating at full
compressor speed and outdoor temperature Tj by solving
Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2, using
Qhcalck=2(47) to represent Qhk=2(47) and
Ehcalck=2(47) to represent Ehk=2(47) (see section 3.6.4.b
of this appendix regarding determination of the capacity and power
input used in the HSPF2 calculations to represent the H12
Test). Determine Qhk=2(35) and Ehk=2(35) from the H22
test and the calculations specified in section 3.9 or, if the
H22 test is not conducted, by conducting the calculations
specified in section 3.6.4. Determine Qhk=2(17) and Ehk=2(17) from
the H32 test and the methods specified in section 3.10 of
this appendix.
d. Full Compressor Speed for Heat Pumps for which the
H42 test is Conducted. For Tj above 17 [deg]F,
evaluate the space heating capacity, Qhk=2(Tj), and
electrical power consumption, Ehk=2(Tj), of the heat pump
when operating at full compressor speed as described above for heat
pumps for which the H42 is not conducted. For
Tj between 5 [deg]F and 17 [deg]F, evaluate the space
heating capacity, Qhk=2(Tj), and electrical power
consumption, Ehk=2(Tj), of the heat pump
[[Page 1583]]
when operating at full compressor speed using the following
equations:
[GRAPHIC] [TIFF OMITTED] TR05JA17.268
Determine Qhk=2(17) and Ehk=2(17) from the H32 test, and
Qhk=2(5) and Ehk=2(5) from the H42 test, using the
methods specified in section 3.10 of this appendix for all four
values. For Tj below 5 [deg]F, evaluate the space heating
capacity, Qhk=2(Tj), and electrical power consumption,
Ehk=2(Tj), of the heat pump when operating at full
compressor speed using the following equations:
[GRAPHIC] [TIFF OMITTED] TR05JA17.269
Determine Qhcalck=2(47) and Ehcalck=2(47) as
described in section 3.6.4.b of this appendix. Determine Qhk=2(17)
and Ehk=2(17) from the H32 test, using the methods
specified in section 3.10 of this appendix.
e. Intermediate Compressor Speed. Calculate the space heating
capacity, Qh\k=v\(Tj), and electrical power consumption,
Eh\k=v\(Tj), of the heat pump when operating at outdoor
temperature Tj and the intermediate compressor speed used
during the section 3.6.4 H2V test using
[GRAPHIC] [TIFF OMITTED] TR05JA17.270
[GRAPHIC] [TIFF OMITTED] TR05JA17.271
where Qh\k=v\(35) and Eh\k=v\(35) are determined from the
H2V test and calculated as specified in section 3.9 of
this appendix. Approximate the slopes of the k=v intermediate speed
heating capacity and electrical power input curves, MQ
and ME, as follows:
[GRAPHIC] [TIFF OMITTED] TR05JA17.272
Use Equations 4.2.4-1 and 4.2.4-2, respectively, to calculate
Qhk=1(35) and Ehk=1(35), whether or not the heat pump is a minimum-
speed-limiting variable-speed heat pump.
4.2.4.1 Steady-State Space Heating Capacity When Operating at Minimum
Compressor Speed Is Greater Than or Equal to the Building Heating Load
at Temperature Tj, Qhk=1(Tj >=BL(Tj)
Evaluate the Equation 4.2-1 quantities
[[Page 1584]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.273
as specified in section 4.2.3.1 of this appendix. Except now use
Equations 4.2.4-1 and 4.2.4-2 (for heat pumps that are not minimum-
speed-limiting) or Equations 4.3.4-3 and 4.2.4-4 (for minimum-speed-
limiting variable-speed heat pumps) to evaluate Qhk=1(Tj)
and Ehk=1(Tj), respectively, and replace section 4.2.3.1
references to ``low capacity'' and section 3.6.3 of this appendix
with ``minimum speed'' and section 3.6.4 of this appendix. Also, the
last sentence of section 4.2.3.1 of this appendix does not apply.
4.2.4.2 Heat Pump Operates at an Intermediate Compressor Speed (k=i) in
Order To Match the Building Heating Load at a Temperature
Tj, Qhk=1(Tj) j)
j)
Calculate
[GRAPHIC] [TIFF OMITTED] TR05JA17.274
and [delta](Tj) is evaluated using Equation 4.2.3-3
while, Qh\k=i\(Tj) = BL(Tj), the space heating
capacity delivered by the unit in matching the building load at
temperature (Tj), Btu/h. The matching occurs with the
heat pump operating at compressor speed k=i. COP\k=i\(Tj)
= the steady-state coefficient of performance of the heat pump when
operating at compressor speed k=i and temperature Tj,
dimensionless.
For each temperature bin where the heat pump operates at an
intermediate compressor speed, determine COP\k=i\(Tj)
using the following equations,
For each temperature bin where Qhk=1(Tj)
j) j),
[GRAPHIC] [TIFF OMITTED] TR05JA17.275
For each temperature bin where Qh\k=v\(Tj)
<=BL(Tj) j),
[GRAPHIC] [TIFF OMITTED] TR05JA17.276
Where:
COPhk=1(Tj) is the steady-state coefficient of
performance of the heat pump when operating at minimum compressor
speed and temperature Tj, dimensionless, calculated using capacity
Qhk=1(Tj) calculated using Equation 4.2.4-1 or 4.2.4-3
and electrical power consumption Ehk=1(Tj) calculated
using Equation 4.2.4-2 or 4.2.4-4;
COPh\k=v\(Tj) is the steady-state coefficient of
performance of the heat pump when operating at intermediate
compressor speed and temperature Tj, dimensionless, calculated using
capacity Qh\k=v\(Tj) calculated using Equation 4.2.4-5
and electrical power consumption Eh\k=v\(Tj) calculated
using Equation 4.2.4-6;
COPhk=2(Tj) is the steady-state coefficient of
performance of the heat pump when operating at full compressor speed
and temperature Tj, dimensionless, calculated using capacity
Qhk=2(Tj) and electrical power consumption
Ehk=2(Tj), both calculated as described in section 4.2.4;
and
BL(Tj) is the building heating load at temperature
Tj, Btu/h.
4.2.4.3 Heat Pump Must Operate Continuously at Full (k=2) Compressor
Speed at Temperature Tj, BL(Tj)
>=Qhk=2(Tj). Evaluate the Equation 4.2-1 Quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.277
as specified in section 4.2.3.4 of this appendix with the
understanding that Qhk=2(Tj) and Ehk=2(Tj)
correspond to full compressor speed operation and are derived from
the results of the specified section 3.6.4 tests of this appendix.
4.2.5 Heat Pumps Having a Heat Comfort Controller
Heat pumps having heat comfort controllers, when set to maintain
a typical minimum air delivery temperature, will cause the heat pump
condenser to operate less because of a greater contribution from the
resistive elements. With a conventional heat pump, resistive heating
is only initiated if the heat pump condenser cannot meet the
building load (i.e., is delayed until a second stage call from the
indoor thermostat). With a heat comfort controller, resistive
heating can occur even though the heat pump condenser has adequate
capacity to meet the building load (i.e., both on during a first
stage call from the indoor thermostat). As a result, the outdoor
temperature where the heat pump compressor no longer cycles (i.e.,
starts to run continuously), will be lower than if
[[Page 1585]]
the heat pump did not have the heat comfort controller.
4.2.5.1 Blower Coil System Heat Pump Having a Heat Comfort Controller:
Additional Steps for Calculating the HSPF2 of a Heat Pump Having a
Single-Speed Compressor and Either a Fixed-Speed Indoor Blower or a
Constant-Air-Volume-Rate Indoor Blower Installed, or a Single-Speed
Coil-Only System Heat Pump
Calculate the space heating capacity and electrical power of the
heat pump without the heat comfort controller being active as
specified in section 4.2.1 of this appendix (Equations 4.2.1-4 and
4.2.1-5) for each outdoor bin temperature, Tj, that is
listed in Table 20. Denote these capacities and electrical powers by
using the subscript ``hp'' instead of ``h.'' Calculate the mass flow
rate (expressed in pounds-mass of dry air per hour) and the specific
heat of the indoor air (expressed in Btu/lbmda [middot]
[deg]F) from the results of the H1 test using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.278
where VIs, VImx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 20, calculate
the nominal temperature of the air leaving the heat pump condenser
coil using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.279
Evaluate eh(Tj/N), RH(Tj)/N,
X(Tj), PLFj, and [delta](Tj) as
specified in section 4.2.1 of this appendix. For each bin
calculation, use the space heating capacity and electrical power
from Case 1 or Case 2, whichever applies.
Case 1. For outdoor bin temperatures where
To(Tj) is equal to or greater than
TCC (the maximum supply temperature determined according
to section 3.1.9 of this appendix), determine Qh(Tj) and
Eh(Tj) as specified in section 4.2.1 of this appendix
(i.e., Qh(Tj) = Qhp(Tj) and
Ehp(Tj) = Ehp(Tj)).
Note: Even though To(Tj) >=Tcc,
resistive heating may be required; evaluate Equation 4.2.1-2 for all
bins.
Case 2. For outdoor bin temperatures where
To(Tj) >Tcc, determine
Qh(Tj) and Eh(Tj) using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.280
Note: Even though To(Tj) cc,
additional resistive heating may be required; evaluate Equation
4.2.1-2 for all bins.
4.2.5.2 Heat Pump Having a Heat Comfort Controller: Additional Steps
for Calculating the HSPF2 of a Heat Pump Having a Single-Speed
Compressor and a Variable-Speed, Variable-Air-Volume-Rate Indoor Blower
Calculate the space heating capacity and electrical power of the
heat pump without the heat comfort controller being active as
specified in section 4.2.2 of this appendix (Equations 4.2.2-1 and
4.2.2-2) for each outdoor bin temperature, Tj, that is
listed in Table 20. Denote these capacities and electrical powers by
using the subscript ``hp'' instead of ``h.'' Calculate the mass flow
rate (expressed in pounds-mass of dry air per hour) and the specific
heat of the indoor air (expressed in Btu/lbmda [middot]
[deg]F) from the results of the H12 test using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.281
where VIS, VImx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 20, calculate
the nominal temperature of the air leaving the heat pump condenser
coil using,
[[Page 1586]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.282
Evaluate eh(Tj)/N, RH(Tj)/N,
X(Tj), PLFj, and [delta](Tj) as
specified in section 4.2.1 of this appendix with the exception of
replacing references to the H1C test and section 3.6.1 of this
appendix with the H1C1 test and section 3.6.2 of this
appendix. For each bin calculation, use the space heating capacity
and electrical power from Case 1 or Case 2, whichever applies.
Case 1. For outdoor bin temperatures where
To(Tj) is equal to or greater than
TCC (the maximum supply temperature determined according
to section 3.1.9 of this appendix), determine Qh(Tj) and
Eh(Tj) as specified in section 4.2.2 of this appendix
(i.e. Qh(Tj) = Qhp(Tj) and
Eh(Tj) = Ehp(Tj)). Note: Even
though To(Tj) >=TCC, resistive
heating may be required; evaluate Equation 4.2.1-2 for all bins.
Case 2. For outdoor bin temperatures where
To(Tj) CC, determine
Qh(Tj) and Eh(Tj) using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.283
Note: Even though To(Tj) cc,
additional resistive heating may be required; evaluate Equation
4.2.1-2 for all bins.
4.2.5.3 Heat Pumps Having a Heat Comfort Controller: Additional Steps
for Calculating the HSPF2 of a Heat Pump Having a Two-Capacity
Compressor
Calculate the space heating capacity and electrical power of the
heat pump without the heat comfort controller being active as
specified in section 4.2.3 of this appendix for both high and low
capacity and at each outdoor bin temperature, Tj, that is
listed in Table 20. Denote these capacities and electrical powers by
using the subscript ``hp'' instead of ``h.'' For the low capacity
case, calculate the mass flow rate (expressed in pounds-mass of dry
air per hour) and the specific heat of the indoor air (expressed in
Btu/lbmda [middot] [deg]F) from the results of the
H11 test using:
[GRAPHIC] [TIFF OMITTED] TR05JA17.284
where Vis, Vimx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 20, calculate
the nominal temperature of the air leaving the heat pump condenser
coil when operating at low capacity using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.285
Repeat the above calculations to determine the mass flow rate
(mdak=2) and the specific heat of the indoor
air (Cp,dak=2) when operating at high capacity
by using the results of the H12 test. For each outdoor
bin temperature listed in Table 20, calculate the nominal
temperature of the air leaving the heat pump condenser coil when
operating at high capacity using,
[GRAPHIC] [TIFF OMITTED] TR05JA17.286
Evaluate eh(Tj)/N, RH(Tj)/N,
Xk=1(Tj), and/or
Xk=2(Tj), PLFj, and
[delta]'(Tj) or [delta]''(Tj) as specified in
section 4.2.3.1. 4.2.3.2, 4.2.3.3, or 4.2.3.4 of this appendix,
whichever applies, for each temperature bin. To evaluate these
quantities, use the low-capacity space heating capacity and the low-
capacity electrical power from Case 1 or Case 2, whichever applies;
use the high-capacity space heating capacity and the high-capacity
electrical power from Case 3 or Case 4, whichever applies.
Case 1. For outdoor bin temperatures where
Tok=1(Tj) is equal to or greater
than TCC (the maximum supply temperature determined
according to section 3.1.9 of this appendix), determine
Qhk=1(Tj) and Ehk=1(Tj)
as specified in section 4.2.3 of this appendix (i.e.,
Qhk=1(Tj) =
Qhpk=1(Tj) and
Ehk=1(Tj) =
Ehpk=1(Tj).
Note: Even though Tok=1(Tj)
>=TCC, resistive heating may be required; evaluate
RH(Tj)/N for all bins.
[[Page 1587]]
Case 2. For outdoor bin temperatures where
Tok=1(Tj) TCC, determine
Qhk=1(Tj) and Ehk=1(Tj)
using,
Qhk=\1\(Tj) = Qhpk=\1\(Tj) + QCCk=\1\(Tj) Ehk=\1\(Tj) = Ehpk=\1\(Tj)
+ ECCk=\1\(Tj)
where,
[GRAPHIC] [TIFF OMITTED] TR05JA17.287
Note: Even though Tok=1(Tj)
>=Tcc, additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
Case 3. For outdoor bin temperatures where
Tok=2(Tj) is equal to or greater
than TCC, determine Qhk=2(Tj) and
Ehk=2(Tj) as specified in section 4.2.3 of
this appendix (i.e., Qhk=2(Tj) =
Qhpk=2(Tj) and
Ehk=2(Tj) =
Ehpk=2(Tj)).
Note: Even though Tok=2(Tj)
CC, resistive heating may be required; evaluate
RH(Tj)/N for all bins.
Case 4. For outdoor bin temperatures where
Tok=2(Tj) CC,
determine Qhk=2(Tj) and
Ehk=2(Tj) using,
Qhk=\2\(Tj) = Qhpk=\2\(Tj) + QCCk=\2\(Tj) Ehk=\2\(Tj) = Ehpk=\2\(Tj)
+ ECCk=\2\(Tj)
where,
[GRAPHIC] [TIFF OMITTED] TR05JA17.288
Note: Even though Tok=2(Tj)
Tcc, additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
4.2.5.4 Heat Pumps Having a Heat Comfort Controller: Additional Steps
for Calculating the HSPF2 of a Heat Pump Having a Variable-Speed
Compressor [Reserved]
4.2.6 Additional Steps for Calculating the HSPF2 of a Heat Pump Having
a Triple-Capacity Compressor
The only triple-capacity heat pumps covered are triple-capacity,
northern heat pumps. For such heat pumps, the calculation of the Eq.
4.2-1 quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.289
differ depending on whether the heat pump would cycle on and off at
low capacity (section 4.2.6.1 of this appendix), cycle on and off at
high capacity (section 4.2.6.2 of this appendix), cycle on and off
at booster capacity (section 4.2.6.3 of this appendix), cycle
between low and high capacity (section 4.2.6.4 of this appendix),
cycle between high and booster capacity (section 4.2.6.5 of this
appendix), operate continuously at low capacity (section 4.2.6.6 of
this appendix), operate continuously at high capacity (section
4.2.6.7 of this appendix), operate continuously at booster capacity
(section 4.2.6.8 of this appendix), or heat solely using resistive
heating (also section 4.2.6.8 of this appendix) in responding to the
building load. As applicable, the manufacturer must supply
information regarding the outdoor temperature range at which each
stage of compressor capacity is active. As an informative example,
data may be submitted in this manner: At the low (k=1) compressor
capacity, the outdoor temperature range of operation is 40 [deg]F <=
T <= 65 [deg]F; At the high (k=2) compressor capacity, the outdoor
temperature range of operation is 20 [deg]F <= T <= 50 [deg]F; At
the booster (k=3) compressor capacity, the outdoor temperature range
of operation is -20 [deg]F <= T <= 30 [deg]F.
a. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at low compressor
capacity and outdoor temperature Tj using the equations
given in section 4.2.3 of this appendix for
Qhk=1(Tj) and Ehk=1
(Tj)) In evaluating the section 4.2.3 equations,
Determine Qhk=1(62) and Ehk=1(62) from the
H01 test, Qhk=1(47) and Ehk=1(47)
from the H11 test, and Qhk=2(47) and
Ehk=2(47) from the H12 test. Calculate all
four quantities as specified in section 3.7 of this appendix. If, in
accordance with section 3.6.6 of this appendix, the H31
test is conducted, calculate Qhk=1(17) and
Ehk=1(17) as specified in section 3.10 of this appendix
and determine Qhk=1(35) and Ehk=1(35) as
specified in section 3.6.6 of this appendix.
b. Evaluate the space heating capacity and electrical power
consumption (Qhk=2(Tj) and Ehk=2
(Tj)) of the heat pump when operating at high compressor
capacity and outdoor temperature Tj by solving Equations 4.2.2-3 and
4.2.2-4, respectively, for k=2. Determine Qhk=1(62) and
Ehk=1(62) from the H01 test,
Qhk=1(47) and Ehk=1(47) from the
H11 test, and Qhk=2(47) and
Ehk=2(47) from the H12 test, evaluated as
specified in section 3.7 of this appendix. Determine the equation
input for Qhk=2(35) and Ehk=2(35) from the
H22,test evaluated as specified in section 3.9.1 of this
appendix. Also, determine Qhk=2(17) and
Ehk=2(17) from the H32 test, evaluated as
specified in section 3.10 of this appendix.
c. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at booster compressor
capacity and outdoor temperature Tj using
[[Page 1588]]
[GRAPHIC] [TIFF OMITTED] TR05JA17.290
Determine Qhk=3(17) and Ehk=3(17) from the
H33 test and determine Qhk=2(5) and
Ehk=3(5) from the H43 test. Calculate all four
quantities as specified in section 3.10 of this appendix. Determine
the equation input for Qhk=3(35) and Ehk=3(35)
as specified in section 3.6.6 of this appendix.
4.2.6.1 Steady-State Space Heating Capacity When Operating at Low
Compressor Capacity Is Greater Than or Equal to the Building Heating
Load at Temperature Tj, Qhk=1(Tj)
>=BL(Tj)., and the Heat Pump Permits Low Compressor Capacity
at Tj. Evaluate the Quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.291
using Eqs. 4.2.3-1 and 4.2.3-2, respectively. Determine the equation
inputs Xk=1(Tj), PLFj, and
[delta]'(Tj) as specified in section 4.2.3.1. In
calculating the part load factor, PLFj, use the low-
capacity cyclic-degradation coefficient CDh, [or equivalently,
CDh(k=1)] determined in accordance with section 3.6.6 of this
appendix.
4.2.6.2 Heat Pump Only Operates at High (k=2) Compressor Capacity at
Temperature Tj and Its Capacity Is Greater Than or Equal to
the Building Heating Load, BL(Tj)
k=2(Tj)
Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.292
as specified in section 4.2.3.3 of this appendix. Determine the
equation inputs Xk=2(Tj), PLFj, and
[delta]'(Tj) as specified in section 4.2.3.3 of this
appendix. In calculating the part load factor, PLFj, use
the high-capacity cyclic-degradation coefficient, CDh(k=2)
determined in accordance with section 3.6.6 of this appendix.
4.2.6.3 Heat Pump Only Operates at High (k=3) Compressor Capacity at
Temperature Tj and its Capacity Is Greater Than or Equal to
the Building Heating Load, BL(Tj)
<=Qhk=3(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.293
Determine the low temperature cut-out factor,
[delta]'(Tj), using Eq. 4.2.3-3. Use the booster-capacity
cyclic-degradation coefficient, CDh(k=3) determined in accordance
with section 3.6.6 of this appendix.
4.2.6.4 Heat Pump Alternates Between High (k=2) and Low (k=1)
Compressor Capacity To Satisfy the Building Heating Load at a
Temperature Tj, Qhk=1(Tj)
j) k=2(Tj)
Evaluate the quantities
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[GRAPHIC] [TIFF OMITTED] TR05JA17.294
as specified in section 4.2.3.2 of this appendix. Determine the
equation inputs Xk=1(Tj),
Xk=2(Tj), and [delta]'(Tj) as
specified in section 4.2.3.2 of this appendix.
4.2.6.5 Heat Pump Alternates Between High (k=2) and Booster (k=3)
Compressor Capacity To Satisfy the Building Heating Load at a
Temperature Tj, Qhk=2(Tj)
j) k=3(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.295
and Xk=3(Tj) = Xk=2(Tj)
= the heating mode, booster capacity load factor for temperature bin
j, dimensionless. Determine the low temperature cut-out factor,
[delta]'(Tj), using Eq. 4.2.3-3.
4.2.6.6 Heat Pump Only Operates at Low (k=1) Capacity at Temperature
Tj and Its Capacity Is Less Than the Building Heating Load,
BL(Tj) > Qhk=1(Tj)
[GRAPHIC] [TIFF OMITTED] TR05JA17.296
where the low temperature cut-out factor, [delta]'(Tj),
is calculated using Eq. 4.2.3-3.
4.2.6.7 Heat Pump Only Operates at High (k=2) Capacity at Temperature
Tj and Its Capacity Is Less Than the Building Heating Load,
BL(Tj) > Qhk=2(Tj)
Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TR05JA17.297
as specified in section 4.2.3.4 of this appendix. Calculate
[delta]''(Tj) using the equation given in section 4.2.3.4
of this appendix.
4.2.6.8 Heat Pump Only Operates at Booster (k=3) Capacity at
Temperature Tj and Its Capacity Is Less Than the Building
Heating Load, BL(Tj) > Qhk=3(Tj) or
the System Converts To Using Only Resistive Heating
[GRAPHIC] [TIFF OMITTED] TR05JA17.298
where [delta]''(Tj) is calculated as specified in section
4.2.3.4 of this appendix if the heat pump is operating at its
booster compressor capacity. If the heat pump system converts to
using only resistive heating at outdoor temperature Tj,
set [delta]'(Tj) equal to zero.
4.2.7 Additional Steps for Calculating the HSPF2 of a Heat Pump Having
a Single Indoor Unit With Multiple Indoor Blowers. The Calculation of
the Eq. 4.2-1 Quantities eh(Tj)/N and RH(Tj)/N
Are Evaluated as Specified in the Applicable Subsection
4.2.7.1 For Multiple Indoor Blower Heat Pumps That Are Connected to a
Singular, Single-Speed Outdoor Unit
a. Calculate the space heating capacity, Qhk=1 (Tj),
and electrical power consumption, Ehk=1 (Tj), of the heat
pump when operating at the heating minimum air volume rate and
outdoor temperature Tj using Eqs. 4.2.2-3 and 4.2.2-4,
respectively. Use these same equations to calculate the space
heating capacity, Qhk=2 (Tj) and electrical power
consumption, Ehk=2 (Tj), of the test unit when operating
at the heating full-load air volume rate and outdoor temperature
Tj. In evaluating Eqs. 4.2.2-3 and 4.2.2- 4, determine
the quantities Qhk=1(47) and Ehk=1(47) from
the H11 test; determine
[[Page 1590]]
Qhk=2(47) and Ehk=2(47) from the H12 test.
Evaluate all four quantities according to section 3.7 of this
appendix. Determine the quantities Qhk=1(35) and
Ehk=1(35) as specified in section 3.6.2 of this appendix.
Determine Qhk=2(35) and Ehk=2(35) from the H22
frost accumulation test as calculated according to section 3.9.1 of
this appendix. Determine the quantities Qhk=1(17) and Ehk=1(17) from
the H31 test, and Qhk=2(17) and Ehk=2(17) from the
H32 test. Evaluate all four quantities according to
section 3.10 of this appendix. Refer to section 3.6.2 and Table 12
of this appendix for additional information on the referenced
laboratory tests.
b. Determine the heating mode cyclic degradation coefficient,
CDh, as per sections 3.6.2 and 3.8 to 3.8.1 of this appendix. Assign
this same value to CDh(k = 2).
c. Except for using the above values of Qhk=1(Tj), Ehk=1(Tj),
Qhk=2(Tj), Ehk=2(Tj), CDh, and CDh(k = 2), calculate the
quantities eh(Tj)/N as specified in section 4.2.3.1 of
this appendix for cases where Qhk=1(Tj) >=
BL(Tj). For all other outdoor bin temperatures,
Tj, calculate eh(Tj)/N and RHh(Tj)/N as specified in
section 4.2.3.3 of this appendix if Qhk=2(Tj) > BL(Tj) or
as specified in section 4.2.3.4 of this appendix if Qhk=2(Tj) <=
BL(Tj).
4.2.7.2 For Multiple Indoor Blower Heat Pumps Connected to Either a
Single Outdoor Unit With a Two-Capacity Compressor or to Two Separate
but Identical Model Single-Speed Outdoor Units. Calculate the
Quantities eh(Tj)/N and RH(Tj)/N as
Specified in Section 4.2.3 of This Appendix
4.3 Calculations of Off-Mode Power Consumption
For central air conditioners and heat pumps with a cooling
capacity of: Less than 36,000 Btu/h, determine the off mode
represented value, PW,OFF, with the following equation:
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greater than or equal to 36,000 Btu/h, calculate the capacity
scaling factor according to:
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where, QC(95) is the total cooling capacity at the A or
A2 test condition, and determine the off mode represented
value, PW,OFF, with the following equation:
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4.4 Rounding of SEER2 and HSPF2 for Reporting Purposes
After calculating SEER2 according to section 4.1 of this
appendix and HSPF2 according to section 4.2 of this appendix round
the values off as specified per Sec. 430.23(m) of title 10 of the
Code of Federal Regulations.
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Table 21--Representative Cooling and Heating Load Hours for Each
Generalized Climatic Region
------------------------------------------------------------------------
Cooling Heating
Climatic region load hours load hours
CLHR HLHR
------------------------------------------------------------------------
I............................................. 2,400 493
II............................................ 1,800 857
III........................................... 1,200 1,247
IV............................................ 800 1,701
Rating Values................................. 1,000 1,572
V............................................. 400 2,202
VI............................................ 200 1,842
------------------------------------------------------------------------
4.5 Calculations of the SHR, Which Should Be Computed for Different
Equipment Configurations and Test Conditions Specified in Table 22.
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Table 22--Applicable Test Conditions for Calculation of the Sensible Heat Ratio
----------------------------------------------------------------------------------------------------------------
Reference
Equipment configuration table number SHR computation with Computed values
of Appendix M results from
----------------------------------------------------------------------------------------------------------------
Units Having a Single-Speed 4 B Test............... SHR(B).
Compressor and a Fixed-Speed
Indoor Blower, a Constant Air
Volume Rate Indoor Blower, or
Single-Speed Coil-Only.
Units Having a Single-Speed 5 B2 and B1 Tests...... SHR(B1), SHR(B2).
Compressor That Meet the section
3.2.2.1 Indoor Unit Requirements.
Units Having a Two-Capacity 6 B2 and B1 Tests...... SHR(B1), SHR(B2).
Compressor.
Units Having a Variable-Speed 7 B2 and B1 Tests...... SHR(B1), SHR(B2).
Compressor.
----------------------------------------------------------------------------------------------------------------
The SHR is defined and calculated as follows:
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Where both the total and sensible cooling capacities are
determined from the same cooling mode test and calculated from data
collected over the same 30-minute data collection interval.
4.6 Calculations of the Energy Efficiency Ratio (EER)
Calculate the energy efficiency ratio using,
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where Qck(T) and Eck(T) are the space cooling capacity and
electrical power consumption determined from the 30-minute data
collection interval of the same steady-state wet coil cooling mode
test and calculated as specified in section 3.3 of this appendix.
Add the letter identification for each steady-state test as a
subscript (e.g., EERA2) to differentiate among the resulting EER
values. The represented value of EER is determined from the A or
A2 test, whichever is applicable. The represented value
of EER determined in accordance with this appendix is called EER2.
[FR Doc. 2016-30004 Filed 1-4-17; 8:45 am]
BILLING CODE 6450-01-P