[Federal Register Volume 70, Number 195 (Tuesday, October 11, 2005)]
[Rules and Regulations]
[Pages 59122-59180]
From the Federal Register Online via the Government Publishing Office [www.gpo.gov]
[FR Doc No: 05-15601]



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Part II





Department of Energy





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Office of Energy Efficiency and Renewable Energy



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10 CFR Part 430



Energy Conservation Program for Consumer Products: Test Procedure for 
Residential Central Air Conditioners and Heat Pumps; Final Rule

  Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / 
Rules and Regulations  

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DEPARTMENT OF ENERGY

Office of Energy Efficiency and Renewable Energy

10 CFR Part 430

[Docket No. EE-RM/TP-97-440]
RIN 1904-AA46


Energy Conservation Program for Consumer Products: Test Procedure 
for Residential 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: The Department of Energy (DOE, or the Department) amends its 
test procedures for residential central air conditioners and heat 
pumps. This final rule adds new sections and revises several sections 
of the test procedure to bring it up-to-date by eliminating the need 
for several test procedure waivers and making it more complete. The 
Department also re-organized the test procedure to be more 
chronological in its progression. The revisions to the test procedure 
do not alter the minimum energy conservation standards currently in 
effect for central air conditioners and heat pumps.

DATES: This rule is effective April 10, 2006. The incorporation by 
reference of certain publications listed in this rule is approved by 
the Director of the Federal Register as of April 10, 2006.

ADDRESSES: You may review copies of all materials related to this 
rulemaking at the U.S. Department of Energy, Forrestal Building, Room 
1J-018 (Resource Room of the Building Technologies Program), 1000 
Independence Avenue, SW., Washington, DC, (202) 586-9127, between 9 
a.m. and 4 p.m., Monday through Friday, except Federal holidays. Please 
call Ms. Brenda Edwards-Jones at the above telephone number for 
additional information regarding visiting the Resource Room. Please 
note: The Department's Freedom of Information Reading Room (formerly 
Room 1E-190 at the Forrestal Building) is no longer housing rulemaking 
materials.

FOR FURTHER INFORMATION CONTACT: Michael G. Raymond, U.S. Department of 
Energy, Office of Energy Efficiency and Renewable Energy, EE-2J, 1000 
Independence Avenue, SW., Washington, DC 20585-0121, (202) 586-9611, e-
mail: [email protected]; or Thomas B. DePriest, Esq., U.S. 
Department of Energy, Office of General Counsel, GC-72, 1000 
Independence Avenue, SW., Washington, DC 20585-0121, (202) 586-9507, e-
mail: [email protected].

SUPPLEMENTARY INFORMATION: The final rule incorporates, by reference, 
into Subpart B of Part 430 seven test-method standards published by the 
American Society of Heating, Refrigerating, and Air-Conditioning 
Engineers, Inc. (ASHRAE), as follows:
     Standard 23-1993, ``Methods of Testing for Rating Positive 
Displacement Refrigerant Compressors and Condensing Units;''
     Standard 37-1988, ``Methods of Testing for Rating Unitary 
Air-Conditioning and Heat Pump Equipment;''
     Standard 41.1-1986 (Reaffirmed 2001), ``Standard Method 
for Temperature Measurement;''
     Standard 41.2-1987 (Reaffirmed 1992), ``Standard Methods 
for Laboratory Airflow Measurement;''
     Standard 41.6-1994 (Reaffirmed 2001), ``Standard Method 
for Measurement of Moist Air Properties;''
     Standard 41.9-2000, ``Calorimeter Test Methods for Mass 
Flow Measurements of Volatile Refrigerants;'' and
     Standard 116-1995, ``Methods of Testing for Rating for 
Seasonal Efficiency of Unitary Air Conditioners and Heat Pumps.''

    The following joint test-method standard of ASHRAE and the Air 
Movement and Control Association International, Inc. (ASHRAE/AMCA) is 
incorporated by reference into subpart B of Part 430:
     Standard 51-1999/210-1999, ``Laboratory Methods of Testing 
Fans for Aerodynamic Performance Rating.''

    The following test-and-rating standard of the Air-Conditioning and 
Refrigeration Institute (ARI) is incorporated by reference into Subpart 
B of Part 430:
     Standard 210/240-2003, ``Unitary Air-Conditioning and Air-
Source Heat Pump Equipment.''
    Copies of these standards are available for public review at the 
Department of Energy's Building Technologies Program Resource Room 
described above. Copies of the ASHRAE, ASHRAE/AMCA and ARI Standards 
are available from the American Society of Heating, Refrigerating, and 
Air-Conditioning Engineers, Inc., 1971 Tullie Circle, NE., Atlanta, GA 
30329, http://www.ashrae.org; the Air Movement and Control Association 
International, Inc., 30 West University Drive, Arlington Heights, IL 
60004-1893, http://www.amca.org; and the Air-Conditioning and 
Refrigeration Institute, 4100 North Fairfax Drive, Suite 200, 
Arlington, VA 22203-1629, http://www.ari.org.

I. Introduction
    A. Authority
    B. Background
II. Discussion of Comments
    A. General Discussion
    1. Adopting References Updated Since Public Hearing
    2. Small-Duct, High-Velocity (SDHV) Systems
    3. Non-Defrost Heat Pumps
    4. Two-Capacity, Northern Heat Pumps
    5. Heat Pumps Having a Heat Comfort Controller
    B. Definitions
    C. Testing Conditions
    1. Section 2.2.4 Wet-Bulb Temperature Requirements for Air 
Entering the Indoor and Outdoor Coils
    2. Section 2.2.5 Additional Refrigerant Charging Requirements
    D. Testing Procedures
    1. Section 3.1.4 Airflow Through the Indoor Coil: Systems Having 
a Variable-Speed, Constant Airflow Blower
    2. Sections 3.1.4.2, 3.1.4.5, 3.3, 3.5.1, 3.7, and 3.9.1. 
Testing a Two-Capacity Compressor System: Coil-Only Units Tested at 
Low Capacity and Differences in High/Low Cycling
III. Summary of Other Additions and Changes to the DOE Residential 
Central Air Conditioner and Heat Pump Test Procedure
    A. Update and Add References for ASHRAE and ARI Standards
    B. Air Volume Rates
    C. Cyclic Testing
    D. Fanless (Coil-Only) Units
    E. Frost Accumulation Test
    F. Test Tolerance Tables
    G. Pretest Intervals
    1. Wet Coil Tests
    2. Dry Coil Steady-State Test
    3. Dry Coil Cyclic Test
    4. Maximum and High Temperature Heating Mode Tests
    5. Heating Mode Cyclic Test
    6. Frost Accumulation Test
    7. Low Temperature Test
    H. Multi-Capacity Systems
    1. Two-Capacity Heat Pumps That Lock Out Low Capacity at Higher 
Outdoor Temperatures
    2. Systems Having a Single-Speed Compressor and a Variable-Speed 
Indoor Fan Where Fan Speed or Air Volume Rate Depends on Outdoor 
Temperature
    I. Triple-Split Systems
    J. Time-Adaptive Defrost Control Systems
    K. Test Unit Installation
    L. Test Apparatus and Measurement/Sampling Frequency
    1. Inlet Plenum for Blower Coils
    2. Manifolded Static Pressure Taps
    3. Temperature Measurement Intervals
    4. Temperature Measurement Accuracies
    5. Grid of Individual Temperature Sensors Within the Indoor-Side 
Outlet Plenum

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    6. Duct Loss Correction
    7. Water Vapor Measurements Using a Dew-Point Hygrometer, a 
Relative Humidity Meter, or Any Other Alternative Instrument
    8. Voltmeter Accuracy
    9. Electrical Power Measurement
    M. Different Compressor Speeds and Indoor Fan Capacities Between 
Cooling and Heating
    N. Secondary Test Requirements
    O. Calculations
    P. Effect of Test Procedure Revisions on SEER and HSPF
IV. Procedural Requirements
    A. Review Under Executive Order 12866
    B. Review Under the Regulatory Flexibility Act
    C. Review Under the Paperwork Reduction Act
    D. Review Under the National Environmental Policy Act
    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 of 1999
    I. Review Under Executive Order 12630
    J. Review Under the Treasury and General Government 
Appropriations Act of 2001
    K. Review Under Executive Order 13211
    L. Review Under Section 32 of the Federal Energy Administration 
Act of 1974
    M. Congressional Notification
    N. Approval of the Office of the Secretary

I. Introduction

A. Authority

    Part B of Title III of the Energy Policy and Conservation Act (EPCA 
or Act) (42 U.S.C. 6291 et seq.), established the Energy Conservation 
Program for Consumer Products Other Than Automobiles (Program). The 
products currently subject to this Program (``covered products'') 
include central air conditioners and heat pumps, the subject of today's 
final rule.
    Under the Act, the Program consists of three parts: Testing, 
labeling, and the Federal energy conservation standards. The 
Department, in consultation with the National Institute of Standards 
and Technology (NIST), is authorized to establish or amend test 
procedures as appropriate for each of the covered products. (42 U.S.C. 
6293) The purpose of the test procedures is to measure energy 
efficiency, energy use, or estimated annual operating cost of a covered 
product during a representative, average use cycle or period of use. 
The test procedure must not be unduly burdensome to conduct. (42 U.S.C. 
6293(b)(3))
    If a test procedure is amended, DOE is required to determine to 
what extent, if any, the proposed new 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)) If DOE determines 
that an amended test procedure would alter the measured energy 
efficiency of a covered product, DOE is required to amend the 
applicable energy conservation standard with respect to such test 
procedure. In determining any such amended energy conservation 
standard, DOE is required to measure the energy efficiency or energy 
use of a representative sample of covered products that minimally 
comply with the existing standard. The average efficiency or energy use 
of these representative samples, tested using the amended test 
procedure, constitutes the amended standard. (42 U.S.C. 6293(e)(2)) The 
Department has determined that today's amended test procedure does not 
alter the measured efficiency or measured energy use of central air 
conditioners and heat pumps.
    Beginning 180 days after a test procedure for a covered product is 
prescribed, no manufacturer, distributor, retailer, or private labeler 
may make representations with respect to the energy use, efficiency, or 
cost of energy consumed by such product, except as reflected in tests 
conducted according to the DOE procedure. (42 U.S.C. 6293(c)(2))

B. Background

    On January 22, 2001, the Department published a Notice of Proposed 
Rulemaking (hereafter referred to as the January 22, 2001, proposed 
rule) that proposed a revised test procedure for central air 
conditioners and heat pumps. (66 FR 6768) As summarized in the January 
22, 2001, proposed rule, the Department initiated several interactions, 
including a DOE workshop, phone conferences, and the release of 
multiple drafts for review and comment between DOE and stakeholders 
prior to preparing the revised test procedure.
    Most of the existing test procedure dates back to its original 
publication in the Federal Register on December 27, 1979. (44 FR 76700) 
The Department modified the test procedure on March 14, 1988, to cover 
variable-speed air conditioners and heat pumps, to address testing of 
split-type non-ducted units, and to change the method used for 
crediting heat pumps that provide a demand defrost capability. (53 FR 
8304)
    The January 22, 2001, proposed rule specified dates for holding a 
public hearing and for submitting written comments. At the request of 
ARI, the Department changed these specified dates. (66 FR 15203, March 
16, 2001) Prior to the public hearing and at the invitation of ARI, a 
NIST representative attended a meeting of the ARI Unitary Small 
Equipment Engineering Committee on February 27, 2001, at ARI 
headquarters. The public hearing was held on March 29, 2001, at DOE 
headquarters.\1\ At the public hearing, the participants spent the 
majority of the time discussing the list of items from the proposed 
rulemaking for which the Department solicited stakeholder comment. One 
manufacturer, the Carrier Corporation, presented a prepared oral 
statement. On May 1, 2001, DOE and NIST personnel met with 
representatives of the Carrier Corporation at DOE headquarters.
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    \1\ The Department held a public workshop on issues that would 
not be considered for the current revision to the test procedure 
(i.e., alternative rating method for untested combinations, 
promoting devices that compensate for installation problems, 
metrification of the DOE test procedure) on the day immediately 
following the close of the public hearing.
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    During the comment period, stakeholders, DOE, and NIST held several 
phone and e-mail discussions about issues associated with the proposed 
test procedure (a revision of 10 CFR part 430, Subpart B, Appendix M) 
and about rating untested split-system combinations (a separate test 
procedure issue not covered in Appendix M, but in 10 CFR 430.24(m)). 
The issue of rating untested split-system combinations is not part of 
this rulemaking and will be the subject of a future rulemaking.

II. Discussion of Comments

A. General Discussion

    Nine different stakeholders submitted a total of fourteen comments 
on the January 22, 2001, proposed rule. Concurrent with this 
rulemaking, the Department also conducted a rulemaking to issue new 
energy conservation standards for central air conditioners and heat 
pumps. Both rulemakings covered, among other consumer products, small-
duct, high-velocity (SDHV) systems. In the standards rulemaking (66 FR 
7197), DOE stated that concerns for SDHV systems had been addressed by 
modifying the test procedure for SDHV products. This test procedure 
modification would have given SDHV systems a higher tested value of the 
Seasonal Energy Efficiency Ratio (SEER). (DOE later rejected this test 
procedure modification for reasons discussed in section II.A.2 of this 
preamble). As a result, the Department considered comments received on 
October 18, 2001, from SDHV manufacturers SpacePak and Unico, Inc. 
(Unico) as part of the energy conservation standards rulemaking in 
today's final rule on the test procedure.

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(SpacePak, No. 21, Unico, No. 22) \2\ The Department also considered 
during this rulemaking amended comments from ARI, dated October 30, 
2001, that addressed the SDHV issue. (ARI, No. 20) A discussion of the 
comments and the actions taken in response to them follows.
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    \2\ These comments were received in the course of the standards 
rulemaking, Docket Number EE-RM-98-440, but are relevant to this 
test procedure rulemaking. SpacePak's comments are item 267 in that 
docket; Unico's comments are item 251.
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1. Adopting References Updated Since Public Hearing
    The January 22, 2001, proposed rule referenced seven ASHRAE 
standards, as well as ASHRAE Standard 51-99/AMCA Standard 210-99, and 
ARI standard 210/240. Since the publication of the proposed rule, 
however, two of these standards have been reaffirmed and two have been 
revised. The two reaffirmed standards are ASHRAE Standard 41.1-1986 
(Reaffirmed 2001) and ASHRAE Standard 41.6-1994 (Reaffirmed 2001). When 
a standard is reaffirmed within ASHRAE, no substantive changes are 
permitted to the document. In the ASHRAE Project Committee Manual of 
Procedures, substantive change is defined as

a change that involves an important (has value, weight or 
consequences), fundamental (is the foundation, without which it would 
collapse), or essential (belongs to the very nature of a thing) part or 
changes the meaning of the material or that directly and materially 
affects the use of the standard. Following are example changes that may 
be found substantive when examined in context;

     ``shall'' to ``should'' or ``should'' to ``shall;'
     addition, deletion or revision of mandatory requirements, 
regardless of the number of changes;
     or addition of mandatory compliance with referenced 
standards.

Thus, today's final rule references ASHRAE Standards 41.1-1986 
(Reaffirmed 2001) and 41.6-1994 (Reaffirmed 2001), whereas the January 
22, 2001, proposed rule had referenced ASHRAE Standards 41.1-1986 
(Reaffirmed 1991) and 41.6-1994. These changes have no effect on the 
test procedure itself nor on the reported energy efficiency ratings of 
the tested equipment.
    The two revised standards are ASHRAE Standard 41.9-2000 and ARI 
Standard 210/240-2003. A revision of ASHRAE Standard 41.9, 
``Calorimeter Test Methods for Mass Flow Measurements of Volatile 
Refrigerants,'' was published in 2000. The previous version, Standard 
41.9-1988, was referenced in the proposed rulemaking. This particular 
standard is only referenced in section 3.11.2 of the test procedure. 
Section 3.11.2 pertains to one of three allowed secondary test methods, 
the Compressor Calibration Method. These secondary test methods do not 
affect the reported performance ratings. Instead, these secondary test 
methods are used to provide a check of the primary method, i.e., the 
Indoor Air Enthalpy Method. Specifically, the cooling or heating 
capacity determined using the approved primary method and the user 
selected secondary test method must agree within six percent to 
constitute a valid test set-up. The revised version of ASHRAE Standard 
41.9 is referenced in today's test procedure both because it does not 
affect the reported ratings and because it provides the most current 
methods for making refrigerant calorimeter measurements.
    The other revised standard is ARI Standard 210/240-2003. The main 
impetus behind the 2003 revision of ARI Standard 210/240 was a desire 
to narrow the scope of the equipment covered by the standard. Whereas 
the 1994 version of Standard 210/240 covered equipment up to 135,000 
Btu/h, the 2003 version is limited to equipment having rated capacities 
less than 65,000 Btu/h. With regard to the DOE test procedure, the 
January 22, 2001, proposed rule referenced four sections within ARI 
Standard 210/240-1994. In the 2003 version of the standard, no 
substantive changes were made to these four sections. The numbering/
lettering of the sections, however, did change slightly. For example, 
section 5.1.3.5 in the 1994 document became section 6.1.3.5 in the 2003 
document. Today's test procedure maintains the approach taken in the 
proposed rule of only referencing the four particular sections of 210/
240. Because of this consistency, the DOE test procedure is unaffected 
by referencing ARI Standard 210/240-2003 rather than Standard 210/240-
1994. The reported energy efficiency ratings of the tested equipment 
are unaffected as well.
2. Small-Duct, High-Velocity (SDHV) Systems
    As discussed in the January 22, 2001, proposed rule, Unico, a 
manufacturer of SDHV systems, argued for creating a separate SDHV 
product class that was subject to a lower future energy conservation 
standard than the level established for conventional units. (66 FR 
6768) However, in the energy standards rulemaking, a majority of 
industry members opposed the separate-product-class option. DOE did not 
include a separate SDHV class in the January 22, 2001, proposed rule. 
Instead, DOE proposed testing SDHV systems as coil-only units. Testing 
as coil-only units would give SDHV units an immediate SEER and Heating 
Seasonal Performance Factor (HSPF) boost, as long as the default fan 
power was less than the actual blower wattage. The SEER and HSPF boost 
eliminated the need for a separate product class. Both Unico and ARI at 
first endorsed this approach. (Unico, No. 10; ARI, No. 19 at p. 3) But 
SpacePak, Trane, and ultimately ARI, disagreed with the coil-only 
testing approach. (SpacePak, No. 15; Trane, No. 12 at p. 1, ARI, No. 
20) These comments noted that SDHV systems would be tested in a manner 
that would never occur in real applications and, as a result, give 
energy efficiency and cost-of-operation results that are not 
representative of the unit's true energy performance. Furthermore, SDHV 
manufacturers would have no incentive to use high-efficiency blowers if 
systems were tested without the indoor blower. Finally, there is no 
technical basis for setting the default fan-power level. For these 
reasons, DOE has determined that its proposal to test SDHV systems as 
coil-only units is unacceptable. As a result, today's final rule does 
not amend the test procedures to test SDHV systems as coil-only units.
    DOE considered another alternative for SDHV systems which it also 
ultimately rejected. This alternative was to make no changes at all. In 
other words, test SDHV systems as they are currently tested and require 
them to meet the same future energy conservation standards as 
conventional units. The Department rejected this option because it 
risked the continued existence of SDHV systems. The Department 
explained its position at the public hearing on March 29, 2001: The 
Department cannot set standards in a way that removes from the market a 
product which offers special utility. (Public Hearing Tr., p. 44)
    Because today's final rule does not amend the test procedures for 
SDHV units, DOE recognizes, as it did in the January 22, 2001, energy 
standards final rule, that SDHV units will have difficulty in meeting 
the 13 SEER standard. In the May 23, 2002, final rule on central air 
conditioner and heat pump standards, DOE further discussed how the 
special characteristics of SDHV systems would make it unlikely such 
systems could even meet the 12 SEER/7.4 HSPF standard established for 
space constrained products. (67 FR 36396) However, because of the 
ruling by the

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U.S. Court of Appeals for the Second Circuit in January, 2004, 355 F.3d 
179 (2d Cir. 2004), that bars DOE from adopting a standard of less than 
13 SEER for SDHV systems, the 13 SEER standard applies to SDHV systems, 
despite DOE's later conclusion that it is unlikely such systems can 
meet that standard or even the lower 12 SEER standard for space 
constrained systems. (69 FR 50997) Nonetheless, the inability of SDHV 
systems to meet the applicable energy efficiency standards is not a new 
problem created by the amendments to the test procedure in today's 
rulemaking. Instead, these products were unable to meet the standard 
under the old test procedures. As a result, DOE need not amend the 
applicable test procedure or standard to mitigate this noncompliance. 
DOE has advised the two manufacturers of these systems of the procedure 
available to affected persons under section 504 of the Department of 
Energy Organization Act (42 U.S.C. 7194), which allows them to request 
relief from hardship or inequity caused by a regulation issued under 
EPCA.
3. Non-Defrost Heat Pumps
    The January 22, 2001, proposed rule included steps for calculating 
the HSPF of a non-defrost heat pump. This proposal addressed the test 
procedure waiver granted to Enviromaster International (EMI). In 1992, 
the Department granted EMI a waiver for its line of non-defrost, multi-
split heat pumps. Under the waiver, the Department did not require EMI 
to report an HSPF and instead required EMI to include in its printed 
materials for the product the following sentence, ``No HSPF value has 
been measured since the heat pump cannot be operated at temperatures 
below 35[deg]F.'' EMI finally applied to the Department's Office of 
Hearing and Appeals (OHA) on January 23, 2003, for exception relief 
from the HSPF efficiency standards. OHA granted the exception relief on 
April 1, 2003. Thus, EMI has never calculated HSPF because of its 
waiver, and will not do so in the future because of OHA exception 
relief.
    Since there are no manufacturers of products on the market which 
would actually use the proposed procedure for calculating the HSPF of a 
non-defrost heat pump, the Department has removed from the test 
procedure all references to non-defrost heat pumps and the special 
caveats for calculating an HSPF for such units.
4. Two-Capacity, Northern Heat Pumps
    The January 22, 2001, proposed rule applied to a two-capacity heat 
pump configured to use only low capacity when cooling, while using both 
low and high capacities when heating. (66 FR 6768) The proposed test 
procedure identified such units as ``two-capacity heat pumps that lock 
out high capacity when cooling.'' At the March 29, 2001, public 
hearing, York expressed concern regarding the use of the term 
``lockout.'' (Public Hearing Tr., p. 54) York felt the term was too 
restrictive, since it could be interpreted to mean that the lockout 
feature must be hard-wired, whereas DOE intended the meaning to include 
factory or field-selectable lockout.
    At the March 29, 2001, public hearing, ARI commented that such 
units would typically have two different indoor coil identifiers and, 
as a result, two different sets of ratings. (Public Hearing Tr., p. 53) 
The ARI comment was supported by many of the other participants at the 
public hearing. ARI and York submitted written comments that supported 
the consensus reached at the public hearing. (ARI, No. 19 at p. 2; 
York, No. 9 at p. 2) The Department chose to adopt the public comment 
consensus and now defines these types of systems as ``two-capacity, 
northern heat pumps.'' The Department included a requirement in the 
definition of ``two-capacity, northern heat pump'' that the 
manufacturer must clearly state that the feature is factory or field-
selectable and that manufacturers must publish two sets of ratings. 
Finally, the definition indicates that the lockout feature is to remain 
enabled for all tests. The northern heat pump is allowed to operate at 
high capacity during its defrost cycle, an issue that arose at the 
public hearing. (Public Hearing Tr., p. 55)
5. Heat Pumps Having a Heat Comfort Controller
    The January 22, 2001, proposed rule included an algorithm for 
calculating the HSPF for most single-speed heat pumps having a heat 
comfort controller. (66 FR 6768) At the March 29, 2001, public hearing, 
Trane commented that the wording in the test procedure on the 
calculation of the energy consumed for resistive heating by a heat 
comfort controller needed clarification. Trane suggested that one use 
the higher of: (1) The resistive heating based on meeting the heat 
comfort controller's temperature setting; or (2) the resistive heating 
based on meeting the building load deficit (when operating below the 
balance point). (Public Hearing Tr., p. 30) Later, Trane submitted 
written comments that the algorithm, as interpreted, would overstate 
the HSPF at heat-comfort-controller set points beginning around 
90[deg]F and get progressively worse as the set point was reduced. 
(Trane, No. 12)
    Battelle offered three general recommendations. The first 
recommendation was to emphasize that comfort controllers operate both 
above and below the normal balance point temperature. The second 
recommendation was to account for the fact that conventional heat pumps 
and, to a lesser extent, heat pumps with comfort controllers, will 
cycle below the system balance point. The third recommendation was that 
DOE perform a parametric calculation to determine ``HSPF deficits'' due 
to the operation of a comfort controller. (Battelle, No. 11) The end 
product could potentially be a table listing the reduction in HSPF that 
results from operating the comfort controller at different temperature 
settings.
    The American Gas Association (AGA) comments paralleled those from 
Battelle. Both AGA and Battelle recommended that the definition of HSPF 
specify that for heat pumps with heat comfort controllers, HSPF 
accounts for resistive heating contributed when operating either above 
or below the balance point as a result of maintaining a minimum supply 
temperature. Both also recommended that the equation for the heating 
load factor in section 4.2.1 be changed to the following:
[GRAPHIC] [TIFF OMITTED] TR11OC05.000

where,

X(Tj) = the heating mode load factor for temperature bin j, 
dimensionless
BL(Tj) = the building space conditioning load corresponding 
to an outdoor temperature of Tj
Qh(Tj) = the space heating capacity of the heat 
pump when operating at outdoor temperature Tj, Btu/h
RHb = the size of each resistance heat bank
n = the number of banks needed to exceed the building load at each bin 
temperature.
    Finally, in a slight variation from Battelle, AGA recommended that 
``DOE provide direction in the test procedure for evaluating 
performance of heat pumps retrofitted with heat comfort controllers in 
the field, including a parametric table of HSPF by DOE region for 
various delivered air temperatures.'' (AGA, No. 18, Battelle, No. 11)
    Given the general support for covering those heat pumps having heat 
comfort controllers, today's test procedure covers all heat pumps 
having heat comfort controllers, except when a heat comfort controller 
is used with a heat

[[Page 59126]]

pump having a variable-speed compressor. Test procedure section 4.2.5.4 
is reserved for a variable-speed heat pump having a heat comfort 
controller.
    The algorithm for calculating the HSPF of a heat pump having a heat 
comfort controller is covered in sections 4.2.5.1 to 4.2.5.3 of today's 
final rule. The algorithm captures the fact that the balance point 
temperature (i.e., where the compressor first runs continuously) for a 
heat pump with a heat comfort controller will be less than, or equal 
to, the balance point temperature of that same heat pump without the 
heat comfort controller. In response to Trane's comments (Public 
Hearing Tr., p. 30; Trane, No. 12), today's test procedure includes 
editorial additions that alert the user to evaluate Equation 4.2.1-2 
for all temperature bins. The test procedure then accounts for the 
resistive heating needed to satisfy the minimum air delivery 
temperature of the heat comfort controller and the (additional) 
resistive heating needed to give an overall heating capacity that 
matches the building load.\3\
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    \3\ When calculating the HSPF for a conventional heat pump, the 
section 4.2 variable Eh(Tj) and 
Qh(Tj) represent the electrical power and 
heating capacity provided exclusively by the heat pump, while the 
variable RH(Tj) applies exclusively to any resistive 
heating contribution. When calculating the HSPF of a heat pump 
having a heat comfort controller, by comparison, the variables 
Eh(Tj) and Qh(Tj) 
represent the electrical power and heating capacity provided by the 
heat pump and any supplemental resistive heating needed to provide 
the comfort-controller-set-point air delivery temperature. The 
variable RH(Tj), in this case, reflects any additional 
resistive heating if the combined capacity of heat pump and the 
resistive heating associated with achieving the set-point air 
delivery temperature is nonetheless insufficient to meet the 
building load. Electrical resistive heating for a heat pump having a 
heat comfort controller is thus allocated among two variables 
(Eh(Tj) and RH(Tj)) rather than one 
(RH(Tj)). This redefining allows the calculation 
procedure to capture the reduced heat pump contribution, the shift 
to a lower balance point, and the negative impact on HSPF.
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    In considering AGA and Battelle's recommended definition change, 
the key point is to emphasize the downward shift in the balance point 
and the associated lower contribution by the heat pump. The Department 
doesn't believe that a single sentence referenced to heat comfort 
controllers within the HSPF definition, even when modified as 
recommended, is sufficient. Therefore, the definition of ``Heat pumps 
having a heat comfort controller,'' emphasizes the downward shift in 
the balance point and the associated lower contribution by the heat 
pump.
    The Department is amending the definition of HSPF by moving the 
following language from the definition text in the proposed rule to the 
main text of the test procedure, specifically, to the end of Section 
4.2, ``Heating Seasonal Performance Factor (HSPF) Calculations.''

    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 heat pumps with heat comfort controllers (see Definition 1.26), 
in addition, HSPF also accounts for resistive heating contributed 
when operating above the balance point as a result of maintaining a 
minimum supply temperature.

    This moved text includes the one sentence from the HSPF definition 
in the proposed rule that specifically addressed heat comfort 
controllers. This sentence is the same one that both AGA and Battelle 
recommended changing. Coupled with the additional paragraph in Section 
4.2.5, ``Heat pumps having a heat comfort controller,'' the Department 
believes the revisions more accurately convey the operating changes 
caused by adding a heat comfort controller.
    The Department did not adopt AGA and Battelle's recommendation for 
changing the calculation of the heating-mode-load factor. (AGA, No. 18, 
Battelle, No. 11) The Department agrees with AGA and Battelle that 
resistive heating initiated as the result of a second stage call of the 
indoor thermostat can, under the right conditions, cause a conventional 
heat pump to cycle below its balance point. Even though a conventional 
heat pump terminates resistive heating once the second stage setpoint 
is met, the concentrated burst of resistive heating coupled with the 
capacity of the continuously operating heat pump may cause the first 
stage of the thermostat to be met shortly after the second stage is 
met. An overshoot occurs and the heat pump cycles off. The overshoot is 
more likely to occur near the balance point where only a small amount 
of resistive heating is needed.
    The existing test procedure makes the implicit assumption that an 
overshoot never occurs. AGA and Battelle's proposed change assumes that 
an overshoot always occurs. The frequency of this overshoot is unknown. 
Until data become available showing that overshoot occurs more often 
than the case where the heat pump runs continuously and the resistive 
elements cycle on and off at the second stage, the Department will 
leave the heating-load-factor calculation unchanged. The AGA and 
Battelle recommendation would be more appropriate if resistive heating, 
once initiated as the result of a second-stage call, stayed on until 
the first stage setpoint was met. The Department is not aware of 
conventional heat pumps that use this strategy, so it did not change 
the calculation of the heating-mode-load factor.
    Heat pumps with heat comfort controllers operate differently from 
conventional heat pumps following a second-stage-thermostat call for 
resistive heating. When the second-stage setpoint is satisfied, heat 
comfort controllers reduce the resistive heating rather than cycling it 
off. In this manner, the heat comfort controller attempts to modulate 
the resistive heating so that additional second-stage calls are reduced 
while also avoiding satisfying the first-stage setpoint. The goal is 
for the heat pump to operate continuously below the balance point while 
having the resistive heating regulated to provide a more uniform 
delivery temperature than that provided by a conventional heat pump. 
The heat comfort controller's operation when responding to a second-
stage-thermostat call is believed to provide a more comfortable 
environment for the homeowner, while not causing an energy penalty. The 
one field study cited by both AGA and Battelle \4\ supports this 
assertion. Therefore, as was decided for conventional heat pumps, the 
Department did not adopt the AGA and Battelle recommended heating-load-
factor equation within the section 4.2.5 calculations that only apply 
to heat pumps having a heat comfort controller.
---------------------------------------------------------------------------

    \4\ ``Improving Occupant Comfort Without an Energy Penalty in 
Homes Heated by Electric Heat Pumps,'' Yuill, G.K., and Musser, A., 
ASHRAE Paper 4162, ASHRAE Transactions 1998 V. 104, Pt. 1.
---------------------------------------------------------------------------

    Finally, with regard to the Battelle and AGA recommendations that 
the test procedure contain information on the impact of heat comfort 
controllers for different temperature setpoints and/or quantify the 
impact from an after-market retro-fit installation of a heat comfort 
controller, the Department agrees that such information is probably 
warranted but judges it inappropriate for inclusion in the test 
procedure. The scope of the test procedure is to test and rate new, 
factory-supplied equipment. Addressing the impact of after-market 
products on the performance of covered products is not within the 
purview of EPCA. However, as pointed out at the March 29, 2001, pubic 
hearing, the test procedure may provide a framework for building code 
officials' consideration when deciding how to handle the after-market 
sale of heat comfort controllers. (Public Hearing Tr., p. 32)

[[Page 59127]]

B. Definitions

    In addition to the amendments to the definitions discussed above in 
section II.A.1 of this preamble, today's final rule modifies 
definitions and references as described below.
    An editorial correction was made to the citation for ASHRAE 
Standard 51-99/AMCA Standard 210-99. In the proposed rule the words 
``AMCA Standard'' were wrongly omitted.
    The definitions of ``heating seasonal performance factor (HSPF),'' 
and ``seasonal energy efficiency ratio (SEER)'' have been modified to 
move some text to later sections of the test procedure. The moved text 
provided complementary information that was better placed in the main 
text of the test procedure rather than in a definition. Sentences from 
the definition of HSPF were moved to Section 4.2, ``Heating Seasonal 
Performance Factor (HSPF) Calculations.'' Similarly, one sentence from 
the definition of SEER became the first sentence in Section 4.1, 
``Seasonal Energy Efficiency Ratio (SEER) Calculations.''

C. Testing Conditions

1. Section 2.2.4 Wet-Bulb Temperature Requirements for Air Entering the 
Indoor and Outdoor Coils
    The January 22, 2001, proposed rule included a requirement that 
applied to wet-coil cooling tests of single-packaged units where all or 
part of the indoor section is located in the outdoor test room. The 
requirement was that the average dew point temperature of the air 
entering the outdoor coil must be within 3.0[deg]F of the 
average dew point temperature of the air entering the indoor coil. This 
requirement was added to address concerns about equipment leakage 
affecting capacity measurements. The water vapor content of the outdoor 
air could affect the repeatability of the measurements. Similarly, 
leakage could present a problem when using the Outdoor Air Enthalpy 
test method for testing a single-packaged heat pump where all or part 
of its outdoor section is located in the indoor test room.
    In comments made at the March 29, 2001, public hearing and in 
written comments received thereafter, York and ARI agreed with the 
proposed requirements. ( Public Hearing Tr., p. 79; York, No. 9 at p. 
4; ARI, No. 19 at p. 2) The Department has adopted the proposed test 
requirement in today's final rule without alteration.
2. Section 2.2.5 Additional Refrigerant Charging Requirements
    Existing testing procedures require that the unit be installed in 
accordance with the manufacturer's installation instructions. The ARI, 
as part of its certification program, occasionally makes decisions on 
what is and is not within the spirit of the requirement. Thus, a policy 
has evolved wherein ARI certification testing allows procedures such as 
break-in times for compressors and washing the oil residue from the 
coils prior to testing. ARI does not allow disconnecting an electrical 
component, such as a crankcase heater. For the most part, the 
Department chose to defer to ARI to maintain consistency in the test 
set-ups. However, the Department proposed additional limits on the 
specific issue of the refrigerant-charging procedure. In the section 
2.2.5 of the January 22, 2001, proposed rule, the Department proposed 
two additional requirements. First, the Department sought to avoid a 
gray area of defining when an independent test laboratory should 
consult with the manufacturer on how to charge a unit. The proposed 
section included the sentence: ``For third party testing, for example, 
do not consult the manufacturer about how to charge the unit.'' This 
requirement was thought to place extra responsibility on the 
manufacturer to publish accurate and clear charging instructions.
    The second requirement was to promote the ideal of testing the unit 
in a manner that is similar to its actual installation in the field. 
The Department proposed amendments to section 2.2.5 to include the 
following sentence: ``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.''
    At the March 29, 2001, public hearing, ARI, ITS, and ACEEE spoke in 
favor of allowing the independent test laboratory to contact the 
manufacturer if it had any charging questions. (Public Hearing Tr., 
pages 101 to 112) This discussion noted the value of feedback in 
assisting the manufacturer to identify mistakes or incompleteness in 
its published instructions. Such feedback, if acted upon by the 
manufacturer, could benefit the eventual field installer. At the public 
hearing, attendees also came to the realization that the attempt to 
prevent special lab-only charging criteria could likely be circumvented 
by having a single criteria that listed wide ranges for such charging 
parameters as the targeted superheat or subcooling level(s).
    The Department considered deleting the proposed section 2.2.5. 
However, today's final rule contains a revised version of the January 
22, 2001, proposed rule language. (66 FR 6792) In the proposed rule, 
for third-party testing, the test laboratory was not to consult with 
the manufacturer about how to charge a unit. Based on the public 
hearing comments discussed above, today's final rule has modified this 
requirement. The test laboratory may consult with the manufacturer 
about the refrigerant-charging procedure and make changes that do not 
contradict the published installation instructions. The manufacturer 
may specify an alternative charging criteria to the third-party 
laboratory if the manufacturer then revises the published installation 
instructions accordingly. DOE decided to keep the section in an effort 
to convey the side benefit of the allowed feedback mechanism and to 
emphasize that the goal is a lab set-up as consistent as possible with 
a field installation.

D. Testing Procedures

1. Section 3.1.4 Airflow Through the Indoor Coil: Systems Having a 
Variable-Speed, Constant Airflow Blower
    The January 22, 2001, proposed rule included additions to the test 
procedure for systems having a variable-speed, constant airflow (often 
called constant CFM (cubic foot per minute)) blower. These additions 
included:

    (1) Controlling the exhaust fan of the airflow measuring 
apparatus to obtain a specified external static pressure. DOE 
received no comments on this addition.
    (2) Specifying an additional test and algorithm to correct the 
fan power in cases where the specified external static pressure 
cannot be achieved during testing due to blower instabilities. ITS 
and York commented in favor of this addition. (Public Hearing Tr., 
ITS, p. 72-73, York, p. 73)
    (3) Making use of the fan laws if a unit must be tested at an 
air volume rate other than the (cooling or heating) Certified Air 
Volume Rate. DOE received no comments on this addition.
    (4) Allowing cyclic tests to be conducted with or without the 
indoor fan enabled and using a step profile for the air volume rate 
during cyclic tests. DOE received no comments on this addition.
    (5) Imposing an 8-percent tolerance for the difference between 
the lab-measured and manufacturer-Certified Air Volume Rates.

    At the March 29, 2001, public hearing, ARI, Trane, and York spoke 
in favor of making a change to eliminate the eight percent tolerance. 
(Public Hearing Tr., ARI, p. 69, Trane, p. 70, and York, p. 70) ARI and 
York submitted written comments to the same effect. (ARI, No. 19 at p. 
2; York, No. 9 at p. 2) Opposition to the eight

[[Page 59128]]

percent tolerance was based on the industry's not wanting another 
certified parameter. ARI recommended that DOE limit its focus to rated 
capacity and seasonal performance, SEER and HSPF, and not include 
parameters that affect those values. (ARI, No. 19 at p. 2)
    DOE proposed the tolerance to provide manufacturers with assurance 
that any third-party testing would employ a representative air volume 
rate. However, these blowers have a level of variability which may 
occasionally exceed the proposed eight percent tolerance. The eight-
percent tolerance could cause several unnecessary stoppages in testing 
where the impact on rated capacity and seasonal performance would be 
negligible. Given the foreseeable unfavorable trade-off from imposing 
the tolerance, the Department has eliminated the eight-percent 
tolerance in today's final rule.
2. Sections 3.1.4.2, 3.1.4.5, 3.3, 3.5.1, 3.7, and 3.9.1. Testing a 
Two-Capacity Compressor System: Coil-Only Units Tested at Low Capacity 
and Differences in High/Low Cycling
    The proposed test procedure sections 3.1.4.2 and 3.1.4.5 specified 
that the air volume rate used when testing two-capacity, coil-only 
units at low capacity (i.e., at the Minimum Air Volume Rate) is the 
higher of:
    (1) The rate specified by the manufacturer, or
    (2) 75 percent of the air volume rate used for the high capacity 
tests.
    At both the public hearing and in its written comments, York 
opposed the proposed 75-percent limit. (Public Hearing Tr., pp. 81-86; 
York, No. 9 at p. 3) York argued that the limit was ``arbitrarily 
derived, is unnecessary, and restrictive towards applying existing and 
future technologies in motor speed controls. * * *'' (York, No. 9 at p. 
3) Conversely, at both the public hearing and in their written 
comments, both Copeland Corporation and ARI supported the defining of a 
lower limit. Their written comments specifically endorsed assigning the 
limit at 75 percent. (Public Hearing Tr., pp 86-90; Copeland 
Corporation, No. 13 at p. 2; ARI, No. 19 at p. 2)
    This 75-percent value is based on the assumption that the two-
capacity coil-only unit would most often be used with an existing 
multi-tap furnace blower. The low range offered from typical multi-tap 
motors can vary considerably. Nonetheless, the limited data collected 
by NIST and by industry supports the proposed 75-percent value, and DOE 
has included it in today's final rule.
    The proposed test procedure sections 3.3, 3.5.1, 3.7 and 3.9.1 did 
not differentiate between the default fan power values for high 
capacity and low capacity. The value of 365 watts per 1000 standard 
cubic feet per minute (SCFM) was used in all cases. Only York commented 
on this issue, and York's comment supported the proposed test 
procedure. (Public Hearing Tr., p. 94, York, No. 9 at p. 3) York 
commented that the proposed low capacity default causes a conservative 
prediction of fan power, with a resulting error too insignificant to 
warrant a change. (York, No. 9 at p. 3) Today's final rule maintains 
the changes on this subject incorporated into the proposed test 
procedure.
    The final two-capacity, compressor-system issue was whether there 
is a significant performance difference between compressors (systems) 
that can switch between low and high stages over a very short time 
interval versus those having to turn off for a short period and take 
longer overall to make the transition. (This issue is included because 
DOE received comments about it. It does not appear in the proposed 
rule, nor in today's final rule.) Copeland Corporation noted that it 
has experience manufacturing both types of compressors and that it has 
``observed that shutting a system down for greater than one minute has 
nearly the same cyclic loss impact as a typical on/off CD 
penalty, since the evaporator warms up almost completely.'' Copeland 
encouraged the Department to study the issue further and stated that an 
appropriate action may be to conduct a test program at Intertek Testing 
Services (ITS). (Copeland Corporation, No. 13 at p. 1) York, on the 
other hand, expressed its opinion that the difference in technology was 
not significant enough to warrant a change in the test procedure. 
(York, No. 9 at p. 3) The Department has been unable to identify test 
procedure changes that could capture a performance difference, assuming 
that its overall impact significantly alters the SEER and HSPF ratings. 
The Department would have to make assumptions about the frequency of 
high/low transitions as a function of the magnitudes of the low and 
high stage capacities relative to each temperature bin building load. 
Also, data are needed to determine whether the cooling and heating mode 
on/off degradation coefficients could act as substitutes for the high/
low transition degradation or whether a separate optional test and/or 
separate transition default values are warranted. In general, the 
Department is willing to consider future changes to the test procedure 
but asks that interested industry members take the lead in quantifying 
the impact on SEER and HSPF before making specific recommendations on 
how to alter the test procedure calculations.

III. Summary of Other Additions and Changes to the DOE Residential 
Central Air Conditioner and Heat Pump Test Procedure

    Today's final rule contains numerous changes that were proposed in 
the January 22, 2001, proposed rule, for which the Department received 
no adverse comments.

A. Update and Add References for ASHRAE and ARI Standards

    The current test procedure references ASHRAE Standard 37-78 and 
ASHRAE Standard 41.1 (no year), ARI Standard 210-79, ARI Standard 240-
77, and ARI Standard 320-76. Today's final rule also includes 
references to ARI Standard 210/240-03, ASHRAE Standard 23-93, ASHRAE 
Standard 37-88, ASHRAE Standard 41.1-86 (RA 01), ASHRAE Standard 41.2-
87 (RA 92), ASHRAE Standard 41.6-94 (RA 01), ASHRAE Standard 41.9-00, 
ASHRAE Standard 51-99/AMCA Standard 210-99, and ASHRAE Standard 116-95. 
The additional commercial standards are necessary to more completely 
inform manufacturers and testers about the multiple test options, 
especially for the secondary test method, and to address as many of the 
small details of lab testing as possible. The additional commercial 
standards were all included in the January 22, 2001, proposed rule. (66 
FR 6768) Some of the commercial standards have been updated since the 
publication of the proposed rule as discussed in section II.A.1 of this 
preamble.

B. Air Volume Rates

    The current test procedure references ARI Standard 240-77. Now, 
rather than referencing ARI Standard 210/240-03, which replaced ARI 
Standard 240-77, the Department has added its own sections to the test 
procedure. The main reason for no longer referencing ARI Standard 210/
240 is that it does not cover variable-speed and constant CFM blowers. 
In addition, ARI Standard 210/240 does not directly address two-
capacity and variable-speed systems. The Department believes it is 
preferable to have the overall issue of air volume rates covered in one 
place rather than in two.
    The test procedure set forth in this final rule no longer 
references ASHRAE Standard 37-78 (or ASHRAE Standard 37-88, its 
replacement) for the equation

[[Page 59129]]

used to calculate the air volume rate of standard air, because the 
referenced equation is incorrect. The factor ``1 +Wn'' is 
missing from the denominator of the pertinent equation in both versions 
of ASHRAE Standard 37. Today's test procedure includes what DOE 
believes to be the correct version of the equation.
    Today's test procedure also adopts the approach used in the ISO 
Standard 5151 of conducting each test at zero external static pressure 
when testing a non-ducted unit.
    All of these ``air volume rate'' substantive changes were 
originally published in the proposed rulemaking (66 FR 6778) and are 
included in today's final rule.

C. Cyclic Testing

    The Department is today adopting standard industry practice and the 
method described in ASHRAE Standard 116. Sections 4.1.1.2, 4.1.2, 
4.2.2.2, and 5.1 of the current (1988) test procedure require 
measurement of the air volume rate during cyclic tests and use of this 
measurement in determining the total cooling (heating) delivered. 
Standard laboratory practice, by comparison, is to achieve and maintain 
the same velocity pressure or nozzle static pressure drop that was 
obtained during the comparable steady-state test. The total cooling 
(heating) delivered during a cyclic test, in addition, is calculated 
using the air volume rate measured during the comparable steady-state 
test. Changes to adopt this industry practice and become consistent 
with ASHRAE Standard 116 were introduced in the proposed rulemaking and 
are included in today's final rule in section 3.1.
    When testing split-type non-ducted (ductless) systems, section 
4.1.1.5 of the current test procedure provides, ``The integration time 
for capacity and power shall be from compressor cut-on time to indoor 
fan cutoff time.'' The indoor fan is operated for three minutes prior 
to compressor cut-on and for three minutes after compressor cutoff 
during the final OFF/ON interval. In sections 3.5 and 3.5.2, today's 
final rule adopts industry practice and integrates power from 
compressor OFF to compressor OFF and subtracts the electrical energy 
associated with operating the indoor fan during the initial three-
minute fan-only period. Space cooling capacity is integrated from 
compressor ON to indoor fan OFF. As with the current test procedure, 
fan energy for the three minutes after compressor cutoff is added to 
the integrated cooling capacity.
    The current test procedure does not contain specific information 
regarding the air dampers: where to install them, how well they should 
seal, and how quickly they should respond. Appendix D of ARI Standard 
210/240-03 contains much of this information. Today's final rule 
incorporates the required information in sections 2.5.4.1 and 2.5.7 
rather than make specific references to each pertinent section of 
Appendix D of the ARI Standard.
    For dry coil tests, today's test procedure final rule adopts, in 
section 3.4, the language in ARI Standard 210/240-03 Appendix D with 
regard to the requirements that the drain pan be plugged and completely 
dry.
    Today's final rule clarifies in section 2.8 that the requirement of 
making electrical energy measurements using an instrument having an 
accuracy of 0.5 percent of reading applies during both the 
ON and OFF intervals of cyclic tests.
    Today's final rule deletes the current section 4.1.3.1, ``The 
indoor and outdoor average dry-bulb temperature for the cyclic dry coil 
test D shall both be within 1.0 [deg]F of the indoor and outdoor 
average dry bulb temperature for the steady-state dry coil test C, 
respectively.'' This requirement is automatically met given the 0.5 
[deg]F test condition tolerance associated with each test. (Today's 
amended test procedure is substantially re-organized; the section 
4.1.3.1 in today's final rule has no relation to the deleted section 
4.1.3.1.)
    For units having a variable-speed indoor fan, the manufacturer will 
have the option of conducting the cyclic tests with the indoor fan 
either enabled or disabled, the latter being the default option if an 
attempt at testing with the fan enabled is unsuccessful. See section 
3.5 of today's final rule. Specifically, if the test is performed with 
the indoor fan operating, and the fan automatically reverses, shuts 
down, or operates at an uncharacteristically high external static 
pressure, then the test must be repeated using a pull-thru method, with 
the fan disabled.
    Although a unit having a variable-speed indoor fan may be designed 
to ramp its fan speed when cycling on and/or off, a step response in 
air volume rate is nonetheless required during cyclic tests. See 
section 3.5 of today's final rule. The work associated with moving the 
additional air during the ramp periods is performed by the exhaust fan 
of the air flow measuring apparatus. The step response begins at the 
initiation of ramp up and ends at the termination of ramp down. The 
rationale for imposing the step change is mainly due to the difficulty 
in obtaining the ramp response and then making an accurate measurement 
of the space conditioning delivered. Systems having indoor fans that 
ramp are expected to have low cyclic degradation coefficients 
(CD) regardless of whether the ramp feature is used, thus 
the absolute improvement in CD is expected to be minor.

D. Fanless (Coil-Only) Units

    Section 4.1 of the current test procedure calls for corrections to 
capacity and power based on air flow measured in cubic feet per minute 
(CFM). Section 4.2 of the current test procedure calls for corrections 
to capacity and power based on air flow measured in cubic feet per 
minute under standard conditions (SCFM). To avoid confusion, the test 
procedure should base corrections on either CFM or SCFM, but not both. 
ITS, which tests for both the industry and ARI, uses SCFM in all cases. 
Therefore, in consideration of the above, today's test procedure 
adopts, in sections 3.3, 3.5.1, and 3.7, the practice of specifying all 
corrections in terms of SCFM.
    The test procedure also adopts in section 2.2 the requirement in 
ARI Standard 210/240-03, Appendix D, that an enclosure be constructed 
using one-inch ductboard for testing a coil-only unit that does not 
employ an enclosure.

E. Frost Accumulation Test

    Today's final rule adopts the convention in ASHRAE Standard 116-95 
and ARI 210/240-03 of specifying the outdoor wet bulb temperature (33 
[deg]F) in place of the presently specified dew point temperature (30 
[deg]F). Sections 3.6.1, 3.6.2, 3.6.3, and 3.6.4.

F. Test Tolerance Tables

    The current test procedure contains tables covering all tests 
except steady-state cooling-mode tests, for which Table III in ASHRAE 
Standard 37-78 is referenced. Since the test procedure includes all 
other tables, the Department chose to add the needed parts of Table III 
(Table 7 of this document).
    The test condition tolerance for external resistance to air flow 
now applies only when testing non-ducted units. (See Table 7). Also, 
DOE has added in Table 7 a test condition tolerance for electrical 
supply voltage (previously, only a test operating tolerance was 
specified). The existing test procedure lacked a clarification that the 
test condition tolerance for the indoor inlet wet bulb temperature in 
Table III of ASHRAE Standard 37-78 does not apply for dry coil tests. 
Therefore, today's final rule includes a footnote to Table 7 that makes 
this clarification. In a similar attempt to clarify when particular 
tolerances apply, today's final rule also includes a

[[Page 59130]]

footnote to tables stating that the test tolerances given for the 
outdoor outlet dry and wet bulb temperatures only apply when using the 
Outdoor Air Enthalpy Method to provide the secondary capacity 
measurement.
    For the Frost Accumulation Test, DOE modified slightly the 
intervals considered to be heating versus defrosting. Specifically, in 
the current test procedure in section 4.2.3.3, the first five minutes 
after a defrost termination was included in the defrost interval. In 
today's final rule, the time interval has been increased to ten minutes 
in section 3.7. This is a better approximation of the time needed for 
temperatures to reach equilibrium after defrost termination. Also, in 
making the test condition conversion of 30 [deg]F dew point to 33 
[deg]F wet bulb, the test operating tolerance and test condition 
tolerance convert to wet bulb temperature tolerances of 0.6 [deg]F and 
0.3 [deg]F, respectively. This 0.6 [deg]F test operating tolerance on 
outdoor wet bulb temperature is more stringent than the value allowed 
for the steady-state tests. The 0.3 [deg]F test condition tolerance is 
the same as required for steady-state tests. Because these tolerances 
should be less stringent that those required of a steady-state test, 
the test procedure adopts in Table 15 the values given in ASHRAE 
Standard 37: 1.5 [deg]F and 0.5 [deg]F.

G. Pretest Intervals

1. Wet Coil Tests
    The following change makes the test conditions more specific than 
they are in the current test procedure:
    Current: ``The test room reconditioning apparatus and the equipment 
under test shall be operated until equilibrium conditions are 
attained.'' (Section 4.1.1.1)
    Today's final rule: ``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.'' (Section 3.3)
2. Dry Coil Steady-State Test
    The following change also makes the test conditions more specific 
than they are in the current test procedure. The industry realized the 
merits of this improved wording several years ago. The added text is 
taken from a prescriptive methodology that appears within an appendix 
of ARI Standard 210/240-2003.
    Current: ``The test room reconditioning apparatus and the equipment 
under test shall be operated until equilibrium conditions are attained, 
but not for less than one hour before data for test C are recorded.'' 
(Section 4.1.1.2)
    Today's final rule: Same as proposed for section 3.3 wet coil tests 
with the additional requirement to ``operate the unit at least one hour 
after achieving dry coil conditions.'' (Section 3.4)
3. Dry Coil Cyclic Test
    The following change makes the test conditions more specific than 
they are in the current test procedure. The existing language is weaker 
because the phrase ``until steadily repeating ambient conditions are 
again achieved'' is comparatively subjective.
    Current: ``[T]est unit shall be manually cycled `off' and `on'* * * 
until steadily repeating ambient conditions are again achieved in both 
the indoor and outdoor test chambers, but for not less than two 
complete `off/on' cycles.'' (Section 4.1.1.2)
    Today's final rule: ``After completing a minimum of two complete 
compressor OFF/ON cycles, determine the overall cooling delivered and 
total electrical energy consumption during any subsequent data 
collection interval where the test tolerances given in Table 8 are 
satisfied.'' (Section 3.5)
4. Maximum and High Temperature Heating Mode Tests
    The requirement for the test apparatus and the test unit to operate 
for at least one hour was dropped based on industry comments that it 
had no bearing on the outcome of the testing--the key is to have steady 
operation at the specified test conditions for an interval (30 minutes) 
prior to starting the test.
    Current: ``The test room apparatus and test units must be operated 
for at least one hour with at least one-half hour at equilibrium and at 
the specified test conditions prior to starting the test.'' (Section 
4.2.1.1)
    Today's final rule: ``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.'' (Section 3.7)
5. Heating Mode Cyclic Test
    The new language is more definitive and easier for a test 
laboratory to understand and implement. The existing language is weaker 
because the phrase ``until steadily repeating ambient conditions are 
again achieved'' is comparatively subjective.
    Current: ``[A]nd be cycled `on' and `off' as specified in 3.2.1.2 
until steadily repeating ambient conditions are achieved for both the 
indoor and outdoor test chambers, but for not less than two complete 
`off'/`on' cycles.'' (Section 4.2.1.2)
    Today's final rule: ``After completing a minimum of two complete 
compressor OFF/ON cycles, determine the overall cooling delivered and 
total electrical energy consumption during any subsequent data 
collection interval where the test tolerances given in Table 8 are 
satisfied.'' (Section 3.5)
6. Frost Accumulation Test
    The new wording is clearer about the goal of getting the test room 
to achieve and maintain the specified test conditions. It clarifies the 
30-minute requirement as a period that starts after the test conditions 
are first achieved.
    Current: ``The test room reconditioning equipment and the unit 
under test shall be operated for at least one-half hour prior to the 
start of a `preliminary' test period.'' (Section 4.2.1.3)
    Today's final rule: ``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.'' (Section 3.9)
7. Low Temperature Test
    The existing language can be interpreted to mean that one only 
needs to achieve the test conditions immediately prior to starting the 
test as opposed to maintaining the test conditions for at least 30 
minutes prior to starting the test. The new wording is clearer. The new 
wording also clarifies the sequential process for having the heat pump 
conduct a defrost.
    Current: ``The test room reconditioning equipment shall first be 
operated in a steady-state manner for at least one-half hour at 
equilibrium and at the specified test conditions. The unit shall then 
undergo a defrost, either automatic or manually induced.'' (Section 
4.2.1.4)
    Today's final rule: ``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.'' (Section 3.7) ``After satisfying the 
section 3.7 requirements for the pretest interval, but before beginning 
to collect data to determine Qhk(17) and 
Ehk(17), conduct a defrost cycle. This defrost 
cycle may be manually or automatically initiated.'' (Section 3.10)

[[Page 59131]]

H. Multi-Capacity Systems

1. Two-Capacity Heat Pumps That Lock Out Low Capacity at Higher Outdoor 
Temperatures
    The current test procedure in section 2.2.2 covers two-capacity 
units that operate exclusively at high capacity when the building load 
exceeds the unit's low capacity. The Department is unaware of any two-
capacity units that implement such a control strategy, and so DOE is 
not including coverage of them in today's final rule. However, the 
Department is adding coverage in section 3.2.3 to address units that 
lock out low capacity operation at low (heating) or high (cooling) 
outdoor temperatures. Today's test procedure uses the CD 
determined based on cycling at low capacity (or the appropriate 
default) in all cases.
2. Systems Having a Single-Speed Compressor and a Variable-Speed Indoor 
Fan Where Fan Speed or Air Volume Rate Depends on Outdoor Temperature
    Today's final rule requires two additional steady-state tests for 
the cooling mode (see section 3.2.2.1 and Table 4) and two additional 
steady-state tests for the heating mode (see section 3.6.2 and Table 
10). The additional tests, at a different air volume rate, are required 
to calculate the effect of the variable-speed indoor fan. An additional 
frost accumulation test is optional.

I. Triple-Split Systems

    The current DOE test procedure, in sections 4.1 and 4.2.1, refers 
to ASHRAE Standard 37-78 on the issue of laboratory set up procedures. 
Section 3.1.3 of ASHRAE Standard 37-78 requires using the calorimeter 
air-enthalpy method arrangement when testing units where the compressor 
is in the indoor section and separately ventilated. For this 
arrangement, an enclosure must be built around the equipment within the 
indoor chamber. The present requirement is burdensome, and DOE has 
learned no one uses it when testing triple-splits. Furthermore, the 
heat loss from the indoor compressor section should be reflected, if at 
all, in an adjusted output capacity and not by a raised entering-air 
temperature because the lost heat is transferred to the surrounding 
ambient, not dissipated within the return air duct. The surrounding 
ambient, in this case, may or may not be part of the conditioned space.
    The amount of heat dissipated to the ambient by the indoor 
compressor section of such units is usually minimized as a result of 
the insulated enclosure of the third section (mainly in an effort to 
reduce the operating noise). Based on the limited information currently 
available, DOE believes that the amount of heat lost from the indoor 
compressor section is on the order of two percent or less of the unit's 
space conditioning capacity.
    Today's final rule reflects the assumption that the heat loss from 
the indoor compressor section contributes nothing to the unit's overall 
delivered capacity if the compressor section is located in an 
unconditioned space. If the compressor section is located in the 
conditioned space, it still contributes only a negligible amount. 
Today's final rule specifies that triple-split systems are not to be 
tested using the calorimeter air-enthalpy method arrangement (see note 
in section 2.6 of the test procedure in today's final rule). The final 
rule does not provide for any adjustment to capacity, or any algorithm 
or method for assigning/determining the heat loss from the indoor 
compressor section. If triple-split systems become more popular and if 
information becomes available indicating the heat loss from the indoor 
compressor section exceeds two percent of the air-side capacity, then 
DOE will revisit the option of having a capacity adjustment.

J. Time-Adaptive Defrost Control Systems

    When conducting a frost accumulation test on a heat pump having a 
time-adaptive defrost control system, repeatable frosting and 
defrosting intervals typically require (if obtainable at all) an 
excessive number of cycles. The tester must manually initiate defrosts 
during the ``preliminary'' test and the ``official'' test. Under 
today's final rule, the manufacturer must provide information as to how 
long the unit would optimally frost before it initiates a defrost, and 
on how to initiate a defrost cycle at the appropriate elapsed time. See 
section 2.2.1. However, the controls of the unit will still control the 
duration of the defrost cycle after its initiation.

K. Test Unit Installation

    For the most part, equipment installation requirements under 
today's final rule will continue according to the manufacturer's field 
installation instructions. However, today's final rule adopts the lab 
and field practice of insulating the low pressure line(s) of a split 
system. See section 2.2.

L. Test Apparatus and Measurement/Sampling Frequency

1. Inlet Plenum for Blower Coils
    The current DOE test procedure does not require an inlet plenum 
when testing blower coil units. (Lab ceiling height on vertical 
installation is a limitation.) In today's final rule, the manufacturer 
has the option to test with or without an inlet plenum installed when 
testing a ducted unit having an indoor fan. Space limitations within 
the test room may dictate that the manufacturer choose the latter 
option. (Section 2.4.2)
2. Manifolded Static Pressure Taps
    The current (1988) test procedure does not discuss methods of 
manifolding static pressure taps. Today's final rule allows three 
configurations: The triple-T configuration; the complete ring, four-to-
one manifold configuration; and the broken-ring, four-to-one manifold 
configuration. (Section 2.4.1) A 1976 study found the triple-T 
configuration to be the preferred method for manifolding static 
pressure taps.\5\ The broken-ring, four-to-one manifold configuration 
is generally considered to be the least accurate of the three methods.
---------------------------------------------------------------------------

    \5\ ``The Design of Piezometer Rings'' by K. A. Blake, Journal 
of Fluid Mechanics, Vol. 78, 1976, part 2, pp. 415-428.
---------------------------------------------------------------------------

3. Temperature Measurement Intervals
    Today's final rule (Definition 1.15) specifies dry-bulb temperature 
measurements at the intervals specified in ASHRAE Standard 41.1-86 
(RA01). The tester must measure wet bulb temperature, dew point 
temperature, or relative humidity at the minimum sampling interval 
specified in the definition of the term ``Continuously recorded.''
4. Temperature Measurement Accuracies
    Today's final rule (sections 2.5.5, 2.5.6, 2.11) incorporates the 
accuracy and precision requirements of temperature measurement from 
ASHRAE Standard 41.1-86 (RA 01).
5. Grid of Individual Temperature Sensors Within the Indoor-Side Outlet 
Plenum
    Today's final rule adopts the requirements in ARI Standard 210/240-
03, Appendix D, that a temperature spread of 1.5 [deg]F or less be 
obtained, and that a minimum of 9 sensors compose the outlet 
temperature grid. (Section 2.5.5.) The January 22, 2001, proposed rule 
contained these DOE recommendations (66 FR 6796):

[[Page 59132]]

    DOE recommends using 16 temperature sensors within each temperature 
grid. DOE recommends installing redundant inlet and outlet dry bulb 
temperature sensors and particularly a thermopile. If using 
thermocouples, DOE recommends the following:
    (1) Use 24 gauge wire;
    (2) Remove approximately 1 inch of insulation from each lead when 
preparing to make a junction; and
    (3) Use no more than two bonded turns per junction.

The Department believes these recommendations to be sound, but today's 
final rule omits them because recommendations are not appropriate in a 
regulatory test procedure.
6. Duct Loss Correction
    Today's final rule includes a correction for the heat transfer 
between the test room and an outlet duct sandwiched between the coil 
and the outlet temperature grid. (Section 3.11) This correction is 
already an industry practice.
7. Water Vapor Measurements Using a Dew-Point Hygrometer, a Relative 
Humidity Meter, or Any Other Alternative Instrument
    Today's final rule explicitly permits alternatives to using wet 
bulb temperature sensors. To ease instrumentation selection, the rule 
specifies required instrument accuracies for dew point hygrometers and 
relative humidity meters. (Section 2.5.6)
8. Voltmeter Accuracy
    The required accuracy of voltage measurements has been changed from 
2 percent to 1 percent. (Section 2.7)
9. Electrical Power Measurement
    Adjustable-speed-driven motors, as used in a variable-speed 
compressor, distort the input current and, to a lesser degree, voltage 
waveforms. For reasons that were outlined in the preamble of the 
January 22, 2001, proposed rule (66 FR 6779), today's final rule 
(Section 2.8) eschews the use of induction type meters for measuring 
such non-sinusoidal power. The January 22, 2001, proposed rule included 
a recommendation to use a meter capable of sampling up to the 50th 
harmonic. Sampling up to the 50th harmonic reduces the chances for 
measurement errors, but the extra expense for such a piece of equipment 
may not be justified, so today's final rule does not require its use.

M. Different Compressor Speeds and Indoor Fan Capacities Between 
Cooling and Heating

    The existing test procedure covers variable-speed systems that 
operate at higher speeds when heating than when cooling. Today's final 
rule extrapolates this allowance to coverage of two-capacity, northern 
heat pumps (see section 4.2). Today's rule covers any case where the 
heat pump uses different fan speeds or air volume rates for cooling 
versus when heating. (Section 3.1.4.4.2)

N. Secondary Test Requirements

    When using the Outdoor Air Enthalpy test method, the tester must 
conduct a preliminary test to compensate, if necessary, for any 
performance impact resulting from the outdoor air-side test apparatus. 
(Section 3.11.1) In the existing test procedure, a preliminary test is 
conducted prior to all steady-state tests (i.e., those tests that 
require a secondary measurement of capacity). Today's final rule 
relaxes this requirement. Section 3.11.1 indicates that the number of 
preliminary tests can be reduced in most cases to one (for air 
conditioners or heating-only heat pumps) or two (for heat pumps): One 
for the first cooling mode steady-state test and one for the first 
heating mode steady-state test. The above ``test apparatus and 
measurement/sampling frequency'' substantive changes were introduced in 
the proposed rulemaking and are maintained in today's final rule. 
(Section 3.11.1)

O. HSPF Calculations

    Today's final rule does not include the final paragraph of sections 
5.2.1 and 5.2.2 of the current test procedure. The paragraph in 
question reads ``Once the maximum and minimum HSPF and operating cost 
values have been obtained for each region, the HSPF and operating cost 
shall be determined for each standardized design heating requirement 
(see section 6.2.6) between the maximum and minimum design heating 
requirements by means of interpolation.'' The number of required HSPF 
calculations is covered in 10 CFR Subpart B, 430.23(m)(3)(ii). In 
today's final rule, this section of the CFR is noted in the Definition 
(1.27) for HSPF. Because of the relative ease of automating the 
calculation process, and the nonlinearity of the HSPF-versus-design-
heating-requirement relationship, today's final rule makes no reference 
to obtaining HSPF or operating cost via interpolation.

P. Effect of Test Procedure Revisions on SEER and HSPF

    The most significant revisions to the test procedure in this final 
rule adopt industry practices and clear up gray areas with more precise 
instructions. No existing requirements are changed, but new 
requirements are added. Based on its development, review and analysis 
of the test procedure revisions being published today, the Department 
believes that these test procedure revisions will have no material 
impact on the measured values of SEER and HSPF, and thus it has 
satisfied the requirement of 42 U.S.C. 6293(e)(1): ``In the case of any 
amended test procedure which is prescribed pursuant to this section, 
the Secretary shall determine, in the rulemaking carried out with 
respect to prescribing such procedure, to what extent, if any, the 
proposed test procedure would alter the measured energy efficiency, 
measured energy use, or measured water use of any covered product as 
determined under the existing test procedure.'' In the January 22, 
2001, proposed rule, the Department asked for comments on this issue 
(66 FR 6782), and received no comments contending that these revisions 
would impact measured values of SEER and HSPF.

IV. Procedural Requirements

A. Review Under Executive Order 12866

    It has been determined that today's regulatory action is not a 
``significant regulatory action'' under Executive Order 12866, 
``Regulatory Planning and Review,'' 58 FR 51735 (October 4, 1993). 
Accordingly, this action was not subject to review under the Executive 
Order by the Office of Information and Regulatory Affairs (OIRA) of the 
Office of Management and Budget (OMB) .

B. Review Under the Regulatory Flexibility Act

    The Regulatory Flexibility Act (5 U.S.C. 601 et seq.) requires 
preparation of an initial regulatory flexibility analysis for any rule 
that by law must be proposed for public comment, unless the agency 
certifies that the rule, if promulgated, will not have a significant 
economic impact on a substantial number of small entities. As 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 rulemaking process. (68 FR 7990) DOE has made its 
procedures and policies

[[Page 59133]]

available on the Office of General Counsel's Web site: http:// 
www.gc.doe.gov.
    DOE reviewed today's rule under the provisions of the Regulatory 
Flexibility Act and the procedures and policies published on February 
19, 2003. DOE certified in the January 22, 2001, proposed rule that the 
proposed rule would not impose a significant economic impact on a 
substantial number of small entities. (66 FR 6780) DOE received no 
comments on this issue, and after considering the potential small 
entity impact of this final rule, DOE affirms the certification that 
this rule will not have a significant economic impact on a substantial 
number of small entities.

C. Review Under the Paperwork Reduction Act

    This rulemaking imposes no new information or record keeping 
requirements under the Paperwork Reduction Act. (44 U.S.C. 3501 et 
seq.)

D. Review Under the National Environmental Policy Act

    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 the 
Department's implementing regulations at 10 CFR part 1021. This rule 
amends an existing rule without changing its environmental effect, and, 
therefore, is covered by the Categorical Exclusion in paragraph A5 to 
subpart D, 10 CFR part 1021. Accordingly, neither an environmental 
assessment nor an environmental impact statement is required.

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 today's rule and has 
determined that it does not preempt State law and does 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. No further 
action is required by Executive Order 13132.

F. Review Under Executive Order 12988

    With respect to the review of existing regulations and the 
promulgation of new regulations, section 3(a) of Executive Order 12988, 
``Civil Justice Reform'' (61 FR 4729, February 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; and (3) provide a clear legal 
standard for affected conduct rather than a general standard and 
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 section 3(a) and section 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 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 (Pub. L. 104-
4) (UMRA) requires each Federal agency to assess the effects of Federal 
regulatory actions on State, local, and Tribal governments and the 
private sector. For a proposed regulatory action that may result in the 
expenditure by State, local and Tribal governments, in the aggregate, 
or by the private sector of $100 million or more (adjusted annually for 
inflation), section 202 of UMRA requires a Federal agency to publish 
estimates of the resulting costs, benefits, and other effects on the 
national economy. (2 U.S.C. 1532(a), (b)) 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:// www.gc.doe.gov). The rule published today contains neither 
an intergovernmental mandate, nor a mandate that may result in an 
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 
of 1999

    Section 654 of the Treasury and General Government Appropriations 
Act, 1999 (Pub. L. 105-277) requires Federal agencies to issue a Family 
Policymaking Assessment for any rule that may affect family well-being. 
This rule would 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 would not 
result in any takings which might require compensation under the Fifth 
Amendment to the United States Constitution.

J. Review Under the Treasury and General Government Appropriations Act 
of 2001

    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 (February 22, 2002), and DOE's guidelines 
were published at 67 FR 62446 (October 7, 2002). DOE has reviewed 
today's notice under the OMB and DOE guidelines and has concluded

[[Page 59134]]

that it is 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 OIRA, 
a Statement of Energy Effects for any proposed 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 proposed 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. Today's regulatory 
action would not have a significant adverse effect on the supply, 
distribution, or use of energy and, therefore, is not a significant 
energy action. 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), the Department of Energy must comply with section 32 
of the Federal Energy Administration Act of 1974 (FEAA), as amended by 
the Federal Energy Administration Authorization Act of 1977. (15 U.S.C. 
788) Section 32 provides in essence that, where a proposed rule 
contains or involves use of commercial standards, the notice of 
proposed rulemaking must inform the public of the use and background of 
such standards. This final rule incorporates nine commercial standards 
as discussed in section II.A.1 of this preamble.
    The Department has evaluated these standards and is unable to 
conclude whether they fully comply with the requirements of section 
32(b) of the FEAA, i.e., that they were developed in a manner which 
fully provides for public participation, comment and review. As 
required by Section 32(c) of the FEAA, the Department has consulted 
with the Attorney General and the Chairman of the Federal Trade 
Commission concerning the impact of these two standards on competition, 
and neither recommended against incorporation of these standards.

M. Congressional Notification

    As required by 5 U.S.C. 801, DOE will report to Congress on the 
promulgation of today's rule prior to 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).

N. Approval of the Office of the Secretary

    The Secretary of Energy has approved publication of today's rule.

List of Subjects in 10 CFR Part 430

    Administrative practice and procedure, Energy conservation, 
Household appliances, Incorporation by reference.

    Issued in Washington, DC, on July 21, 2005.
Douglas L. Faulkner,
Acting Assistant Secretary, Energy Efficiency and Renewable Energy.

0
For the reasons set forth in the preamble, Part 430 of Chapter II of 
Title 10, Code of Federal Regulations is amended as set forth below.

PART 430--ENERGY CONSERVATION PROGRAM FOR CONSUMER PRODUCTS

0
1. 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
2. Section 430.22 is amended:
0
a. In paragraph (b)(1) by adding paragraph (b)(1)8.
0
b. In paragraph (b)(5) by removing paragraph (b)(5)2., and adding new 
paragraphs (b)(5)2. through (b)(5)9.
0
c. By adding paragraph (b)(8).
    The additions specified above read as follows:


Sec.  430.22  Reference Sources.

* * * * *
    (b) * * *
    (1) * * *

    8. ANSI Standard Z21.56-1994, ``Gas-Fired Pool Heaters,'' 
section 2.9.
* * * * *
    (5) * * *

    2. American Society of Heating, Refrigerating, and Air-
Conditioning Engineers Standard 23-1993, ``Methods of Testing for 
Rating Positive Displacement Refrigerant Compressors and Condensing 
Units.''
    3. American Society of Heating, Refrigerating, and Air-
Conditioning Engineers Standard 37-1988, ``Methods of Testing for 
Rating Unitary Air-Conditioning and Heat Pump Equipment.''
    4. American Society of Heating, Refrigerating, and Air-
Conditioning Engineers Standard 41.1-1986 (Reaffirmed 2001), 
``Standard Method for Temperature Measurement.''
    5. American Society of Heating, Refrigerating, and Air-
Conditioning Engineers Standard 41.2-1987 (Reaffirmed 1992), 
``Standard Methods for Laboratory Airflow Measurement.''
    6. American Society of Heating, Refrigerating, and Air-
Conditioning Engineers Standard 41.6-1994 (Reaffirmed 2001), 
``Standard Method for Measurement of Moist Air Properties.''
    7. American Society of Heating, Refrigerating, and Air-
Conditioning Engineers Standard 41.9-2000, ``Calorimeter Test 
Methods for Mass Flow Measurements of Volatile Refrigerants.''
    8. American Society of Heating, Refrigerating, and Air-
Conditioning Engineers Standard 116-1995, ``Methods of Testing for 
Rating for Seasonal Efficiency of Unitary Air Conditioners and Heat 
Pumps.''
    9. American Society of Heating, Refrigerating, and Air-
Conditioning Engineers/Air Movement and Control Association 
International, Inc. Standard 51-1999/210-1999, ``Laboratory Methods 
of Testing Fans for Aerodynamic Performance Rating.''
* * * * *
    (8) Air-Conditioning and Refrigeration Institute (ARI), 4100 North 
Fairfax Drive, Suite 200, Arlington, Virginia 22203-1629, (703) 524-
8800, ARI Standard 210/240-2003, ``Unitary Air-Conditioning and Air-
Source Heat Pump Equipment.''
* * * * *

0
3. Section 430.23 of subpart B is amended by revising the section 
heading, paragraph (m) introductory heading and paragraph (m)(1), (2), 
and (3) to read as follows:


Sec.  430.23  Test procedure for measures of energy consumption.

* * * * *
    (m) Central air conditioners and heat pumps. (1) The estimated 
annual operating cost for cooling-only units and air-source heat pumps 
shall be one of the following:
    (i) For cooling-only units or the cooling portion of the estimated 
annual operating cost for air-source heat pumps which provide both 
heating and cooling, the product of:
    (A) The quotient of the cooling capacity, in Btu's per hour, 
determined from the steady-state wet-coil test (A or A2 
Test), as described in section 3.2 of appendix M to this subpart, 
divided by the seasonal energy efficiency ratio (SEER), in Btu's per 
watt-hour, determined from section 4.1 of appendix M to this subpart;
    (B) The representative average use cycle for cooling of 1,000 hours 
per year;

[[Page 59135]]

    (C) A conversion factor of 0.001 kilowatt per watt; and
    (D) The representative average unit cost of electricity in dollars 
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act, 
the resulting product then being rounded off to the nearest dollar per 
year.
    (ii) For air-source heat pumps which provide only heating or the 
heating portion of the estimated annual operating cost for air-source 
heat pumps which provide both heating and cooling, the product of:
    (A) The quotient of the standardized design heating requirement, in 
Btu's per hour, nearest to the heating Region IV minimum design heating 
requirement, determined in section 4.2 of appendix M to this subpart, 
divided by the heating seasonal performance factor (HSPF), in Btu's per 
watt-hour, calculated for heating Region IV corresponding to the above-
mentioned standardized design heating requirement and determined in 
section 4.2 of appendix M to this subpart;
    (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, 
the resulting product then being rounded off to the nearest dollar per 
year.
    (iii) For air-source heat pumps which provide both heating and 
cooling, the estimated annual operating cost is the sum of the quantity 
determined in paragraph (m)(1)(i) of this section added to the quantity 
determined in paragraph (m)(1)(ii) of this section.
    (2) The estimated regional annual operating cost for cooling-only 
units and for air-source heat pumps shall be one of the following:
    (i) For cooling-only units or the cooling portion of the estimated 
regional annual operating cost for air-source heat pumps which provide 
both heating and cooling, the product of:
    (A) The quotient of the cooling capacity, in Btu's per hour, 
determined from the steady-state wet-coil test (A or A2 
Test), as described in section 3.2 of appendix M to this subpart, 
divided by the seasonal energy efficiency ratio (SEER), in Btu's per 
watt-hour, determined from section 4.1 of appendix M to this subpart;
    (B) The estimated number of regional cooling load hours per year 
determined from Figure 3 in section 4.3 of appendix M to this subpart;
    (C) A conversion factor of 0.001 kilowatts per watt; and
    (D) The representative average unit cost of electricity in dollars 
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act, 
the resulting product then being rounded off to the nearest dollar per 
year.
    (ii) For air-source heat pumps which provide only heating or the 
heating portion of the estimated regional annual operating cost for 
air-source heat pumps which provide both heating and cooling, the 
product of:
    (A) The estimated number of regional heating load hours per year 
determined from Figure 2 in section 4.3 of appendix M to this subpart;
    (B) The quotient of the standardized design heating requirement, 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 in section 4.2 of appendix M to this subpart, 
divided by the heating seasonal performance factor (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 while being determined in section 4.2 of 
appendix M to this subpart;
    (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, 
the resulting product then being rounded off to the nearest dollar per 
year.
    (iii) For air-source heat pumps which provide both heating and 
cooling, the estimated regional annual operating cost is the sum of the 
quantity determined in paragraph (m)(3)(i) of this section added to the 
quantity determined in paragraph (m)(3)(ii) of this section.
    (3) The measure(s) of efficiency of performance for cooling-only 
units and air-source heat pumps shall be one or more of the following:
    (i) The cooling mode efficiency measure for cooling-only units and 
air-source heat pumps which provide cooling shall be the seasonal 
energy efficiency ratio (SEER), in Btu's per watt-hour, determined 
according to section 4.1 of appendix M to this subpart, rounded off to 
the nearest 0.05.
    (ii) The heating mode efficiency measure for air-source heat pumps 
shall be the heating seasonal performance factors (HSPF), in Btu's per 
watt-hour, determined according to section 4.2 of appendix M to this 
subpart for each applicable standardized design heating requirement 
within each climatic region, rounded off to the nearest 0.05.
    (iii) The annual efficiency measure for air-source heat pumps which 
provide heating and cooling, shall be the annual performance factors 
(APF), in Btu's per watt-hour, determined according to section 4.3 of 
appendix M to this subpart for each standardized design heating 
requirement within each climatic region, rounded off to the nearest 
0.05.
* * * * *

0
4. Section 430.24 of subpart B is amended by revising the introductory 
text for paragraph (m)(1) to read as follows:


Sec.  430.24  Units to be tested.

* * * * *
    (m)(1) For central air conditioners and heat pumps, each condensing 
unit (outdoor unit) shall have a condenser-evaporator (outdoor coil-
indoor coil) combination selected and a sample of sufficient size 
tested in accordance with applicable provisions of this subpart such 
that
* * * * *

0
5. Appendix M to Subpart B 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

1. DEFINITIONS

2. TESTING CONDITIONS

    2.1 Test room requirements.
    2.2 Test unit installation requirements.
    2.2.1 Defrost control settings.
    2.2.2 Special requirements for units having a multiple-speed 
outdoor fan.
    2.2.3 Special requirements for multi-split air conditioners and 
heat pumps, and systems composed of multiple mini-split units 
(outdoor units located side-by-side) that would normally operate 
using two or more indoor thermostats.
    2.2.4 Wet-bulb temperature requirements for the air entering the 
indoor and outdoor coils.
    2.2.4.1 Cooling mode tests.
    2.2.4.2 Heating mode tests.
    2.2.5 Additional refrigerant charging requirements.
    2.3 Indoor air volume rates.
    2.3.1 Cooling tests.
    2.3.2 Heating tests.
    2.4 Indoor coil inlet and outlet duct connections.

[[Page 59136]]

    2.4.1 Outlet plenum for the indoor unit.
    2.4.2 Inlet plenum for the indoor unit.
    2.5 Indoor coil air property measurements and air damper box 
applications.
    2.5.1 Test set-up on the inlet side of the indoor coil: For 
cases where the inlet damper box is installed.
    2.5.1.1 If the section 2.4.2 inlet plenum is installed.
    2.5.1.2 If the section 2.4.2 inlet plenum is not installed.
    2.5.2 Test set-up on the inlet side of the indoor unit: For 
cases where no inlet damper box is installed.
    2.5.3 Indoor coil static pressure difference measurement.
    2.5.4 Test set-up on the outlet side of the indoor coil.
    2.5.4.1 Outlet air damper box placement and requirements.
    2.5.4.2 Procedures to minimize temperature maldistribution.
    2.5.5 Dry bulb temperature measurement.
    2.5.6 Water vapor content measurement.
    2.5.7 Air damper box performance requirements.
    2.6 Airflow measuring apparatus.
    2.7 Electrical voltage supply.
    2.8 Electrical power and energy measurements.
    2.9 Time measurements.
    2.10 Test apparatus for the secondary space conditioning 
capacity measurement.
    2.10.1 Outdoor Air Enthalpy Method.
    2.10.2 Compressor Calibration Method.
    2.10.3 Refrigerant Enthalpy Method.
    2.11 Measurement of test room ambient conditions.
    2.12 Measurement of indoor fan speed.
    2.13 Measurement of barometric pressure.

3. TESTING PROCEDURES

    3.1 General Requirements.
    3.1.1 Primary and secondary test methods.
    3.1.2 Manufacturer-provided equipment overrides.
    3.1.3 Airflow through the outdoor coil.
    3.1.4 Airflow through the indoor coil.
    3.1.4.1 Cooling Certified Air Volume Rate.
    3.1.4.1.1 Cooling Certified Air Volume Rate for Ducted Units.
    3.1.4.1.2 Cooling Certified Air Volume Rate for Non-ducted 
Units.
    3.1.4.2 Cooling Minimum Air Volume Rate.
    3.1.4.3 Cooling Intermediate Air Volume Rate.
    3.1.4.4 Heating Certified Air Volume Rate.
    3.1.4.4.1 Ducted heat pumps where the Heating and Cooling 
Certified Air Volume Rates are the same.
    3.1.4.4.2 Ducted heat pumps where the Heating and Cooling 
Certified Air Volume Rates are different due to indoor fan 
operation.
    3.1.4.4.3 Ducted heating-only heat pumps.
    3.1.4.4.4 Non-ducted heat pumps, including non-ducted heating-
only heat pumps.
    3.1.4.5 Heating Minimum Air Volume Rate.
    3.1.4.6 Heating Intermediate Air Volume Rate.
    3.1.4.7 Heating Nominal Air Volume Rate.
    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.
    3.1.6 Air volume rate calculations.
    3.1.7 Test sequence.
    3.1.8 Requirement for the air temperature distribution leaving 
the indoor coil.
    3.1.9 Control of auxiliary resistive heating elements.
    3.2 Cooling mode tests for different types of air conditioners 
and heat pumps.
    3.2.1 Tests for a unit having a single-speed compressor that is 
tested with a fixed-speed indoor fan installed, with a constant-air-
volume-rate indoor fan installed, or with no indoor fan installed.
    3.2.2 Tests for a unit having a single-speed compressor and a 
variable-speed variable-air-volume-rate indoor fan installed.
    3.2.2.1 Indoor fan capacity modulation that correlates with the 
outdoor dry bulb temperature.
    3.2.2.2 Indoor fan capacity modulation based on adjusting the 
sensible to total (S/T) cooling capacity ratio.
    3.2.3 Tests for a unit having a two-capacity compressor.
    3.2.4 Tests for a unit having a variable-speed compressor.
    3.3 Test procedures for steady-state wet coil cooling mode tests 
(the A, A2, A1, B, B2, 
B1, EV, and F1 Tests).
    3.4 Test procedures for the optional steady-state dry coil 
cooling mode tests (the C, C1, and G1 Tests).
    3.5 Test procedures for the optional cyclic dry coil cooling 
mode tests (the D, D1, and I1 Tests).
    3.5.1 Procedures when testing ducted systems.
    3.5.2 Procedures when testing non-ducted systems.
    3.5.3 Cooling mode cyclic degradation coefficient calculation.
    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 
that is tested with a fixed speed indoor fan installed, with a 
constant-air-volume-rate indoor fan installed, or with no indoor fan 
installed.
    3.6.2 Tests for a heat pump having a single-speed compressor and 
a variable-speed, variable-air-volume-rate indoor fan: capacity 
modulation correlates with outdoor dry bulb temperature.
    3.6.3 Tests for a heat pump having a two-capacity compressor 
(see Definition 1.45), including two-capacity, northern heat pumps 
(see Definition 1.46).
    3.6.4 Tests for a heat pump having a variable-speed compressor.
    3.6.5 Additional test for a heat pump having a heat comfort 
controller.
    3.7 Test procedures for steady-state Maximum Temperature and 
High Temperature heating mode tests (the H01, H1, 
H12, H11, and H1N Tests).
    3.8 Test procedures for the optional cyclic heating mode tests 
(the H0C1, H1C, and H1C1 Tests).
    3.8.1 Heating mode cyclic degradation coefficient calculation.
    3.9 Test procedures for Frost Accumulation heating mode tests 
(the H2, H22, H2V, and 
H21 Tests).
    3.9.1 Average space heating capacity and electrical power 
calculations.
    3.9.2 Demand defrost credit.
    3.10 Test procedures for steady-state Low Temperature heating 
mode tests (the H3, H32, and H31 
Tests).
    3.11 Additional requirements for the secondary test methods.
    3.11.1 If using the Outdoor Air Enthalpy Method as the secondary 
test method.
    3.11.1.1 If a preliminary test precedes the official test
    3.11.1.2 If a preliminary test does not precede the official 
test.
    3.11.1.3 Official test.
    3.11.2 If using the Compressor Calibration Method as the 
secondary test method.
    3.11.3 If using the Refrigerant Enthalpy Method as the secondary 
test method.
    3.12 Rounding of space conditioning capacities for reporting 
purposes.

4. CALCULATIONS OF SEASONAL PERFORMANCE DESCRIPTORS

    4.1 Seasonal Energy Efficiency Ratio (SEER) Calculations.
    4.1.1 SEER calculations for an air conditioner or heat pump 
having a single-speed compressor that was tested with a fixed-speed 
indoor fan installed, a constant-air-volume-rate indoor fan 
installed, or with no indoor fan installed.
    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 fan.
    4.1.2.1 Units covered by section 3.2.2.1 where indoor fan 
capacity modulation correlates with the outdoor dry bulb 
temperature.
    4.1.2.2 Units covered by section 3.2.2.2 where indoor fan 
capacity modulation is used to adjust the sensible to total cooling 
capacity ratio.
    4.1.3 SEER calculations for an air conditioner or heat pump 
having a two-capacity compressor.
    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).
    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).
    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).
    4.1.3.4 Unit must operate continuously at high (k=2) compressor 
capacity at temperature Tj, BL(Tj) >= 
Qck=2(Tj).
    4.1.4 SEER calculations for an air conditioner or heat pump 
having a variable-speed compressor.
    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).

[[Page 59137]]

    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) < 
BL(Tj) < Qck=2(Tj).
    4.1.4.3 Unit must operate continuously at maximum (k=2) 
compressor speed at temperature Tj, BL(Tj) >= 
Qck=2(Tj).
    4.2 Heating Seasonal Performance Factor (HSPF) Calculations.
    4.2.1 Additional steps for calculating the HSPF of a heat pump 
having a single-speed compressor that was tested with a fixed-speed 
indoor fan installed, a constant-air-volume-rate indoor fan 
installed, or with no indoor fan installed.
    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 fan.
    4.2.3 Additional steps for calculating the HSPF of a heat pump 
having a two-capacity compressor.
    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).
    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).
    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).
    4.2.3.4 Heat pump must operate continuously at high (k=2) 
compressor capacity at temperature Tj, BL(Tj) 
>= Qhk=2(Tj).
    4.2.4 Additional steps for calculating the HSPF of a heat pump 
having a variable-speed compressor.
    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).
    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) < 
BL(Tj) < Qhk=2(Tj).
    4.2.4.3 Heat pump must operate continuously at maximum (k=2) 
compressor speed at temperature Tj, BL(Tj) >= 
Qhk=2(Tj).
    4.2.5 Heat pumps having a heat comfort controller.
    4.2.5.1 Heat pump having a heat comfort controller: Additional 
steps for calculating the HSPF of a heat pump having a single-speed 
compressor that was tested with a fixed-speed indoor fan installed, 
a constant-air-volume-rate indoor fan installed, or with no indoor 
fan installed.
    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 
fan.
    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.
    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]
    4.3 Calculations of the Actual and Representative Regional 
Annual Performance Factors for Heat Pumps.
    4.3.1 Calculation of actual regional annual performance factors 
(APFA) for a particular location and for each 
standardized design heating requirement.
    4.3.2 Calculation of representative regional annual performance 
factors (APFR) for each generalized climatic region and 
for each standardized design heating requirement.
    4.4 Rounding of SEER, HSPF, and APF for reporting purposes.

1. Definitions

    1.1 Annual performance factor means the total heating and 
cooling done by a heat pump in a particular region in one year 
divided by the total electric energy used in one year. Paragraph 
(m)(3)(iii) of Sec.  430.23 of the Code of Federal Regulations 
states the calculation requirements for this rating descriptor.
    1.2 ARI means Air-Conditioning and Refrigeration Institute.
    1.3 ARI Standard 210/240-2003 means the test standard ``Unitary 
Air-Conditioning and Air-Source Heat Pump Equipment'' published in 
2003 by ARI.
    1.4 ASHRAE means the American Society of Heating, Refrigerating 
and Air-Conditioning Engineers, Inc.
    1.5 ASHRAE Standard 23-93 means the test standard ``Methods of 
Testing for Rating Positive Displacement Refrigerant Compressors and 
Condensing Units'' published in 1993 by ASHRAE.
    1.6 ASHRAE Standard 37-88 means the test standard ``Methods of 
Testing for Rating Unitary Air-Conditioning and Heat Pump 
Equipment'' published in 1988 by ASHRAE.
    1.7 ASHRAE Standard 41.1-86 (RA 01) means the test standard 
``Standard Method for Temperature Measurement'' published in 1986 
and reaffirmed in 2001 by ASHRAE.
    1.8 ASHRAE Standard 41.2-87 (RA 92) means the test standard 
``Standard Methods for Laboratory Airflow Measurement'' published in 
1987 and reaffirmed in 1992 by ASHRAE.
    1.9 ASHRAE Standard 41.6-94 (RA 01) means the test standard 
``Method for Measurement of Moist Air Properties'' published in 1994 
and reaffirmed in 2001 by ASHRAE.
    1.10 ASHRAE Standard 41.9-00 means the test standard 
``Calorimeter Test Methods for Mass Flow Measurements of Volatile 
Refrigerants'' published in 2000 by ASHRAE.
    1.11 ASHRAE Standard 51-99/AMCA Standard 210-1999 means the test 
standard ``Laboratory Methods of Testing Fans for Aerodynamic 
Performance Rating'' published in 1999 by ASHRAE and the Air 
Movement and Control Association International, Inc.
    1.12 ASHRAE Standard 116-95 means the test standard ``Methods of 
Testing for Rating for Seasonal Efficiency of Unitary Air 
Conditioners and Heat Pumps'' published in 1995 by ASHRAE.
    1.13 CFR means Code of Federal Regulations.
    1.14 Constant-air-volume-rate indoor fan means a fan that varies 
its operating speed to provide a fixed air-volume-rate from a ducted 
system.
    1.15 Continuously recorded, when referring to a dry bulb 
measurement, means that the specified temperature must be sampled at 
regular intervals that are equal to or less than the maximum 
intervals specified in section 4.3 part ``a'' of ASHRAE Standard 
41.1-86 (RA 01). If such dry bulb temperatures are used only for 
test room control, it means that one samples at regular intervals 
equal to or less than the maximum intervals specified in section 4.3 
part ``b'' of the same ASHRAE Standard. Regarding wet bulb 
temperature, dew point temperature, or relative humidity 
measurements, continuously recorded means that the measurements must 
be made at regular intervals that are equal to or less than 1 
minute.
    1.16 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. The 
denominator is 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.
    1.17 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 tied to a single set of operating conditions. 
COP is a dimensionless quantity. When determined for a ducted unit 
tested without an indoor fan installed, COP must include the section 
3.7, 3.8, and 3.9.1 default values for the heat output and power 
input of a fan motor.
    1.18 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.
    1.19 Damper box means a short section of duct having an air 
damper that meets the performance requirements of section 2.5.7.
    1.20 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\.
    1.21 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 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, etc.) at least once for every ten minutes 
of compressor ON-time when space heating. One acceptable alternative 
to the criterion given in the prior sentence is a feedback system 
that measures the length of the defrost period and adjusts defrost 
frequency accordingly.\1\ In all cases, when the frost parameter(s) 
reaches a predetermined value,

[[Page 59138]]

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.
---------------------------------------------------------------------------

    \1\ 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.
    1.22 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.
    1.23 Dry-coil tests are cooling mode tests where the wet-bulb 
temperature of the air supplied to the indoor coil is maintained low 
enough that no condensate forms on this coil.
    1.24 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-
packaged unit.
    1.25 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. 
These rate quantities must be determined from a single test or, if 
derived via interpolation, must be tied to a single set of operating 
conditions. EER is expressed in units of
[GRAPHIC] [TIFF OMITTED] TR11OC05.001

When determined for a ducted unit tested without an indoor fan 
installed, EER must include the section 3.3 and 3.5.1 default values 
for the heat output and power input of a fan motor.
    1.26 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. The 
denominator is the total heating that would be delivered, given the 
same ambient conditions, if the unit operated continuously at its 
steady-state space heating capacity for the same total time (ON plus 
OFF) interval.
    1.27 Heating seasonal performance factor (HSPF) means the total 
space heating required during the space heating season, expressed in 
Btu's, 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 the Energy Conservation 
Standards (see 10 CFR 430.32(c), Subpart C) is based on Region IV, 
the minimum standardized design heating requirement, and the 
sampling plan stated in 10 CFR 430.24(m), Subpart B.
    1.28 Heat pump having a heat comfort controller means equipment 
that regulates the operation of the electric resistance elements to 
assure that the air temperature leaving the indoor section does not 
fall below a specified temperature. This specified temperature is 
usually field adjustable. 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.
    1.29 Mini-split air conditioners and heat pumps means systems 
that have a single outdoor section and one or more indoor sections. 
The indoor sections cycle on and off in unison in response to a 
single indoor thermostat.
    1.30 Multiple-split air conditioners and heat pumps means 
systems that have two or more indoor sections. The indoor sections 
operate independently and can be used to condition multiple zones in 
response to multiple indoor thermostats.
    1.31 Non-ducted system means an air conditioner or heat pump 
that is designed to be permanently installed equipment and directly 
heats or cools air within the conditioned space using one or more 
indoor coils that are mounted on room walls and/or ceilings. The 
unit may be of a modular design that allows for combining multiple 
outdoor coils and compressors to create one overall system. Non-
ducted systems covered by this test procedure are all split systems.
    1.32 Part-load factor (PLF) means the ratio of the cyclic energy 
efficiency ratio (coefficient of performance) to the steady-state 
energy efficiency ratio (coefficient of performance). Evaluate both 
energy efficiency ratios (coefficients of performance) based on 
operation at the same ambient conditions.
    1.33 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 air conditioner or heat pump during the same season, 
expressed in watt-hours. The SEER calculation in section 4.1 of this 
Appendix and the sampling plan stated in 10 CFR Subpart B, 430.24(m) 
are used to evaluate compliance with the Energy Conservation 
Standards. (See 10 CFR 430.32(c), Subpart C.)
    1.34 Single-packaged unit means any central air conditioner or 
heat pump that has all major assemblies enclosed in one cabinet.
    1.35 Small-duct, high-velocity system means a system that 
contains a blower and indoor coil combination that is designed for, 
and produces, at least 1.2 inches (of water) of external static 
pressure when operated at the certified air volume rate of 220-350 
cfm per rated ton of cooling. When applied in the field, small-duct 
products use high-velocity room outlets (i.e., generally greater 
than 1000 fpm) having less than 6.0 square inches of free area.
    1.36 Split system means any air conditioner or heat pump that 
has one or more of the major assemblies separated from the others.
    1.37 Standard Air means dry air at 70 [deg]F and 14.696 psia. 
Under these conditions, dry air has a mass density of 0.075 lb/
ft3.
    1.38 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.
    1.39 Temperature bin means the 5 [deg]F increments that are used 
to partition the outdoor dry-bulb temperature ranges of the cooling 
(>= 65 [deg]F) and heating (< 65 [deg]F) seasons.
    1.40 Test condition tolerance means the maximum permissible 
difference between the average value of the measured test parameter 
and the specified test condition.
    1.41 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.
    1.42 Time adaptive defrost control system is a demand-defrost 
control system (see definition 1.21) that measures the length of the 
prior defrost period(s) and uses that information to automatically 
determine when to initiate the next defrost cycle.
    1.43 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 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 1.21).
    1.44 Triple-split system means an air conditioner or heat pump 
that is composed of three separate components: An outdoor fan coil 
section, an indoor fan coil section, and an indoor compressor 
section.
    1.45 Two-capacity (or two-stage) compressor means an air 
conditioner or heat pump that has one of the following:
    (1) A two-speed compressor,
    (2) Two compressors where only one compressor ever operates at a 
time,
    (3) Two compressors where one compressor (Compressor 1) 
operates at low loads and both compressors (Compressors 1 
and 2) operate at high loads but Compressor 2 
never operates alone, or
    (4) A compressor that is capable of cylinder or scroll 
unloading.
    For such systems, low capacity means:
    (1) Operating at low compressor speed,
    (2) Operating the lower capacity compressor,
    (3) Operating Compressor 1, or
    (4) Operating with the compressor unloaded (e.g., operating one 
piston of a two-piston reciprocating compressor, using a

[[Page 59139]]

fixed fractional volume of the full scroll, etc.).
    For such systems, high capacity means:
    (1) Operating at high compressor speed,
    (2) Operating the higher capacity compressor,
    (3) Operating Compressors 1 and 2, or
    (4) Operating with the compressor loaded (e.g., operating both 
pistons of a two-piston reciprocating compressor, using the full 
volume of the scroll).
    1.46 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 indoor coil 
model number should 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.
    1.47 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 Conditions

    This test procedure covers split-type and single-packaged ducted 
units and split-type non-ducted units. Except for units having a 
variable-speed compressor, ducted units tested without an indoor fan 
installed are covered.
    a. Only a subset of the sections listed in this test procedure 
apply when testing and rating a particular unit. Tables 1-A through 
1-C show which sections of the test procedure apply to each type of 
equipment. In each table, look at all four of the Roman numeral 
categories to see what test sections apply to the equipment being 
tested.
    1. The first category, Rows I-1 through I-4 of the Tables, 
pertains to the compressor and indoor fan features of the equipment. 
After identifying the correct ``I'' row, find the table cells in the 
same row that list the type of equipment being tested: Air 
conditioner (AC), heat pump (HP), or heating-only heat pump (HH). 
Use the test section(s) listed above each noted table cell for 
testing and rating the unit.
    2. The second category, Rows II-1 and II-2, pertains to the 
presence or absence of ducts. Row II-1 shows the test procedure 
sections that apply to ducted systems, and Row II-2 shows those that 
apply to non-ducted systems.
    3. The third category is for special features that may be 
present in the equipment. When testing units that have one or more 
of the three (special) equipment features described by the Table 
legend for Category III, use Row III to find test sections that 
apply.
    4. The fourth category is for the secondary test method to be 
used. If the secondary method for determining the unit's cooling 
and/or heating capacity is known, use Row IV to find the appropriate 
test sections. Otherwise, include all of the test sections 
referenced by Row IV cell entries--i.e., sections 2.10 to 2.10.3 and 
3.11 to 3.11.3--among those sections consulted for testing and 
rating information.
    b. Obtain a complete listing of all pertinent test sections by 
recording those sections identified from the four categories above.
    c. The user should note that, for many sections, only part of a 
section applies to the unit being tested. In a few cases, the entire 
section may not apply. For example, sections 3.4 to 3.5.3 (which 
describe optional dry coil tests), are not relevant if the allowed 
default value for the cooling mode cyclic degradation coefficient is 
used rather than determining it by testing.

Example for Using Tables 1-A to 1-C

    Equipment Description: A ducted air conditioner having a single-
speed compressor, a fixed-speed indoor fan, and a multi-speed 
outdoor fan.
    Secondary Test Method: Refrigerant Enthalpy Method
    Step 1. Determine which of four listed Row ``I'' options applies 
==> Row I-2
    Table 1-A: ``AC'' in Row I-2 is found in the columns for 
sections 1.1 to 1.47, 2.1 to 2.2, 2.2.4 to 2.2.4.1, 2.2.5, 2.3 to 
2.3.1, 2.4 to 2.4.1, 2.5, 2.5.2 to 2.10, and 2.11 to 2.13.
    Table 1-B: ``AC'' is listed in Row I-2 for sections 3 to 3.1.4, 
3.1.5 to 3.1.8, 3.2.1, 3.3 to 3.5, 3.5.3, 3.11 and 3.12.
    Table 1-C: ``AC'' is listed in Row I-2 for sections 4.1.1 and 
4.4.
    Step 2. Equipment is ducted ==> Row II-1
    Table 1-A: ``AC'' is listed in Row II-1 for sections 2.4.2 and 
2.5.1 to 2.5.1.2.
    Table 1-B: ``AC'' is listed in Row II-1 for sections 3.1.4.1 to 
3.1.4.1.1 and 3.5.1.
    Table 1-C: no ``AC'' listings in Row II-1.
    Step 3. Equipment Special Features include multi-speed outdoor 
fan ==> Row III, M
    Table 1-A: ``M'' is listed in Row III for section 2.2.2
    Tables 1-B and 1-C: no ``M'' listings in Row III.
    Step 4. Secondary Test Method is Refrigerant Enthalpy Method ==> 
Row IV, R
    Table 1-A: ``R'' is listed in Row IV for section 2.10.3
    Table 1-B: ``R'' is listed in Row IV for section 3.11.3
    Table 1-C: no ``R'' listings in Row IV.
    Step 5. Cumulative listing of applicable test procedure sections 
1.1 to 1.47, 2.1 to 2.2, 2.2.2, 2.2.4 to 2.4.1, 2.2.5, 2.3 to 2.3.1, 
2.4 to 2.4.1, 2.4.2, 2.5, 2.5.1 to 2.5.1.2, 2.5.2 to 2.10, 2.10.3, 
2.11 to 2.13, 3. to 3.1.4, 3.1.4.1 to 3.1.4.1.1, 3.1.5 to 3.1.8, 
3.2.1, 3.3 to 3.5, 3.5.1, 3.5.3, 3.11, 3.11.3, 3.12, 4.1.1, and 4.4.
BILLING CODE 6450-01-U

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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. These rooms 
must comply with the requirements specified in sections 8.1.2 and 
8.1.3 of ASHRAE Standard 37-88 (incorporated by reference, see Sec.  
430.22).
    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. When 
applied, 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 8.6 of ASHRAE Standard 37-88 (incorporated by 
reference, see Sec.  430.22). With respect to interconnecting tubing 
used when testing split systems, however, follow the requirements 
given in section 6.1.3.5 of ARI Standard 210/240-2003 (incorporated 
by reference, see Sec.  430.22). When testing triple-split systems 
(see Definition 1.44), use the tubing length specified in section 
6.1.3.5 of ARI Standard 210/240-2003 (incorporated by reference, see 
Sec.  430.22) 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. When testing 
non-ducted systems having multiple indoor coils, connect each indoor 
fan-coil to the outdoor unit using: a. 25 feet of tubing, or b. 
tubing furnished by the manufacturer, whichever is longer. If they 
are needed to make a secondary measurement of capacity, install 
refrigerant pressure measuring instruments as described in section 
8.6.5 of ASHRAE Standard 37-88 (incorporated by reference, see Sec.  
430.22). Refer to section 2.10 of this Appendix to learn which 
secondary methods require refrigerant pressure measurements. At a 
minimum, insulate the low pressure line(s) of a split system with 
foam insulation having an inside diameter that matches the 
refrigerant tubing and a nominal thickness of \1/2\ inch.
    b. For units designed for both horizontal and vertical 
installation or for both up-flow and down-flow vertical 
installations, the manufacturer must specify the orientation used 
for testing. 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 
Definition 1.28).
    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 2, note 3 (see 
section 3.1.4). Except as noted in section 3.1.9, prevent the indoor 
air supplementary heating coils from operating during all tests. For 
coil-only indoor units that are supplied without an enclosure, 
create an enclosure using 1 inch fiberglass ductboard having a 
nominal density of 6 pounds per cubic foot. Or alternatively, use 
some other insulating material having a thermal resistance (``R'' 
value) between 4 and 6 hr[middot]ft2[middot][deg]F/Btu. 
For units where the coil is housed within an enclosure or cabinet, 
no extra insulating or sealing is allowed.
    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 2 and Table 17 of 
section 4.2 for information on region IV.) For heat pumps that use a 
time-adaptive defrost control system (see Definition 1.42), the 
manufacturer must specify the frosting interval to be used during 
Frost Accumulation tests and provide the procedure for manually 
initiating the defrost at the specified time. To ease testing of any 
unit, the manufacturer should provide information and any necessary 
hardware to manually initiate a defrost cycle.
    2.2.2 Special requirements for units having a multiple-speed 
outdoor fan. Configure the multiple-speed outdoor fan according to 
the manufacturer's specifications, 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 systems composed of multiple mini-split units 
(outdoor units located side-by-side) that would normally operate 
using two or more indoor thermostats. During the steady-state tests, 
shunt all thermostats to make all indoor fan-coil units operate 
simultaneously. To ease the testing burden of cyclic tests, consider 
creating a single control circuit that allows simultaneous cycling 
of all compressor systems. For these systems, the test procedure 
references to a single indoor fan, outdoor fan, and compressor means 
all indoor fans, all outdoor fans, and all compressor systems.
    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 
to the applicable wet-bulb temperature listed in Tables 3 to 6. 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 3-6 list the applicable wet-bulb temperatures.
    (2) Single-packaged 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. For dry coil 
tests on such units, it may be necessary to limit the moisture 
content of the air entering the outdoor side of the unit to meet the 
requirements of section 3.4.
    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 9 to 12. 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 is used while testing a single-packaged 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. Charging 
according to the ``manufacturer's instructions,'' as stated in 
section 8.6 of ASHRAE Standard 37-88 (incorporated by reference, see 
Sec.  430.22), means the manufacturer's installation instructions 
that come packaged with the unit. If a unit requires charging but 
the installation instructions do not specify a charging procedure, 
then evacuate the unit and add the nameplate refrigerant charge. 
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. For third-
party testing, the test laboratory may consult with the manufacturer 
about the refrigerant charging procedure and make any needed 
corrections so long as they do not contradict the published 
installation instructions. The manufacturer may specify an 
alternative charging criteria to the third-party laboratory so long 
as the manufacturer thereafter revises the published installation 
instructions accordingly.
    2.3 Indoor air volume rates. If a unit's controls allow for 
overspeeding the indoor fan (usually on a temporary basis), take the 
necessary steps to prevent overspeeding during all tests.
    2.3.1 Cooling tests. a. Set indoor fan control options (e.g., 
fan motor pin settings, fan motor speed) according to the published 
installation instructions that are provided with the equipment while 
meeting the airflow requirements that are specified in sections 
3.1.4.1 to 3.1.4.3.
    b. Express the Cooling Certified 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. If needed, set the indoor fan control 
options (e.g., fan motor pin settings, fan motor speed) according to 
the published installation instructions that are provided with the 
equipment. Do this set-up while meeting all applicable airflow 
requirements specified in sections 3.1.4.4 to 3.1.4.7.

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    b. Express the Heating Certified 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 described in section 2.4.1 and, if 
installed, the inlet plenum described in section 2.4.2 with thermal 
insulation having a nominal overall sistance (R-value) of at least 
19 hr[middot]ft\2\[middot][deg]F/Btu.
    2.4.1 Outlet plenum for the indoor unit. 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.) For non-ducted 
systems having multiple indoor coils, attach a plenum to each indoor 
coil outlet. 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 1 
shows two of the three options allowed for the manifold 
configuration; the third option is the broken-ring, four-to-one 
manifold configuration that is shown in Figure 7 of ASHRAE Standard 
37-88 (incorporated by reference, see Sec.  430.22). See Figures 7 
and 8 of ASHRAE Standard 37-88 (incorporated by reference, see Sec.  
430.22) for the cross-sectional dimensions and minimum length of the 
(each) plenum and the locations for adding the static pressure taps 
for units tested with and without an indoor fan installed. For a 
non-ducted system having multiple indoor coils, have all outlet 
plenums discharge air into a single common duct. At the plane where 
each plenum enters the common duct, install an adjustable airflow 
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    2.4.2 Inlet plenum for the indoor unit. Install an inlet plenum 
when testing a coil-only indoor unit or a packaged system where the 
indoor coil is located in the outdoor test room. Add static pressure 
taps at the center of each face of this plenum, if rectangular, or 
at four evenly distributed locations along the circumference of an 
oval or round plenum. Make a manifold that connects the four static 
pressure taps using one of the three configurations specified in 
section 2.4.1. See Figure 8 of ASHRAE Standard 37-88 (incorporated 
by reference, see Sec.  430.22) for cross-sectional dimensions, the 
minimum length of the inlet plenum, and the locations of the static 
pressure taps. When testing a ducted unit having an indoor fan (and 
the indoor coil is in the indoor test room), the manufacturer has 
the option to test with or without an inlet plenum installed. Space 
limitations within the test room may dictate that the manufacturer 
choose the latter option. If used, construct the inlet plenum and 
add the four static pressure taps as shown in Figure 8 of ASHRAE 
Standard 37-88 (incorporated by reference, see Sec.  430.22). 
Manifold the four static pressure taps using one of the three 
configurations specified in section 2.4.1. Never use an inlet plenum 
when testing a non-ducted system.
    2.5 Indoor coil air property measurements and air damper box 
applications. 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 Figure 2 of ASHRAE 
Standard 41.1-86 (RA 01) (incorporated by reference, see Sec.  
430.22) for guidance on constructing an air sampling device. The 
sampling device may also divert air to a remotely located sensor(s) 
that measures dry bulb temperature. 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 leaving air dry bulb temperature 
sensor(s) may be used for all tests except:
    (1) Cyclic tests; and
    (2) Frost accumulation tests.
    b. An acceptable alternative in all cases, including the two 
special cases noted above, is to install a grid of dry bulb 
temperature sensors within the outlet and inlet ducts. Use a 
temperature grid to get the average dry bulb temperature at one 
location, leaving or entering, or when two grids are applied as a 
thermopile, to directly obtain the temperature difference. A grid of 
temperature sensors (which may also be used for determining average 
leaving air dry bulb temperature) is required to measure the 
temperature distribution within a cross-section of the leaving 
airstream.
    c. Use an inlet and outlet air damper box when testing ducted 
systems if conducting one or both of the cyclic tests listed in 
sections 3.2 and 3.6. Otherwise, install an outlet air damper box 
when testing heat pumps, both ducted and non-ducted, that cycle off 
the indoor fan during defrost cycles if no other means is available 
for preventing natural or forced convection through the indoor unit 
when the indoor fan is off. Never use an inlet damper box when 
testing a non-ducted system.
    2.5.1 Test set-up on the inlet side of the indoor coil: for 
cases where the inlet damper box is installed. a. Install the inlet 
side damper box as specified in section 2.5.1.1 or 2.5.1.2, 
whichever applies. Insulate or construct the ductwork between the 
point where the air damper is installed and where the connection is 
made to either the inlet plenum (section 2.5.1.1 units) or the 
indoor unit (section 2.5.1.2 units) with thermal insulation that has 
a nominal overall resistance (R-value) of at least 19 
hr[middot]ft\2\[middot][deg]F/Btu.
    b. Locate the grid of entering air dry-bulb temperature sensors, 
if used, at the inlet of the damper box. Locate 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.
    2.5.1.1 If the section 2.4.2 inlet plenum is installed. Install 
the inlet damper box upstream of the inlet plenum. The cross-
sectional flow area of the damper box must be equal to or greater 
than the flow area of the inlet plenum. If needed, use an adaptor 
plate or a transition duct section to connect the damper box with 
the inlet plenum.
    2.5.1.2 If the section 2.4.2 inlet plenum is not installed. 
Install the damper box immediately upstream of the air inlet of the 
indoor unit. The cross-sectional dimensions of the damper box must 
be equal to or greater than the dimensions of the indoor unit inlet. 
If needed, use an adaptor plate or a short transition duct section 
to connect the damper box with the unit's air inlet. Add static 
pressure taps at the center of each face of the damper box, if 
rectangular, or at four evenly distributed locations along the 
circumference, if oval or round. Locate the pressure taps between 
the inlet damper and the inlet of the indoor unit. Make a manifold 
that connects the four static pressure taps.
    2.5.2 Test set-up on the inlet side of the indoor unit: for 
cases where no inlet damper box 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, preferably at the entrance plane of the 
inlet plenum. If the section 2.4.2 inlet plenum is not used, but a 
grid of dry bulb temperature sensors is used, locate the grid 
approximately 6 inches upstream from the inlet of the indoor coil. 
Or, in the case of non-ducted units having multiple indoor coils, 
locate a grid approximately 6 inches upstream from the inlet of each 
indoor coil. 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. 
Section 6.4.4.1 of ASHRAE Standard 37-88 (incorporated by reference, 
see Sec.  430.22) describes the method for fabricating static 
pressure taps. Also refer to Figure 2A of ASHRAE Standard 51-99/AMCA 
Standard 210-99 (incorporated by reference, see Sec.  430.22). 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 air damper box. If an inlet 
plenum or inlet damper box are not used, leave the inlet side of the 
differential pressure instrument open to the surrounding atmosphere. 
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 and the airflow measuring apparatus described below 
in section 2.6. 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). Air that circulates through an air sampling device and past a 
remote water-vapor-content sensor(s) must be returned to the 
interconnecting duct at a point:
    (1) Downstream of the air sampling device;
    (2) Upstream of the outlet air damper box, if installed; 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), install it within 
the interconnecting duct at a location downstream of the location 
where air from the sampling device is reintroduced or downstream of 
the in-duct sensor that measures water vapor content of the outlet 
air. 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

[[Page 59148]]

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. Mixing devices are described in sections 6.3--6.5 of 
ASHRAE Standard 41.1-86 (RA 01) (incorporated by reference, see 
Sec.  430.22) and section 5.2.2 of ASHRAE Standard 41.2-87 (RA 92) 
(incorporated by reference, see Sec.  430.22).
    2.5.5 Dry bulb temperature measurement. a. Measure dry bulb 
temperatures as specified in sections 4, 5, 6.1-6.10, 9, 10, and 11 
of ASHRAE Standard 41.1-86 (RA 01) (incorporated by reference, see 
Sec.  430.22). The transient testing requirements cited in section 
4.3 of ASHRAE Standard 41.1-86 (RA 01) (incorporated by reference, 
see Sec.  430.22) apply if conducting a cyclic or frost accumulation 
test.
    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, 9, 10, and 11 of ASHRAE Standard 41.1-86 (RA 
01) (incorporated by reference, see Sec.  430.22). As specified in 
ASHRAE 41.1-86 (RA 01) (incorporated by reference, see Sec.  
430.22), the temperature sensor (wick removed) must be accurate to 
within 0.2 [deg]F. If used, apply dew point hygrometers 
as specified in sections 5 and 8 of ASHRAE Standard 41.6-94 (RA 01) 
(incorporated by reference, see Sec.  430.22). The dew point 
hygrometers must be accurate to within 0.4 [deg]F when 
operated at conditions that result in the evaluation of dew points 
above 35 [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), 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 Air 
Flow Measuring Apparatus as specified in section 6.6 of ASHRAE 
Standard 116-95 (incorporated by reference, see Sec.  430.22). Refer 
to Figure 12 of ASHRAE Standard 51-99/AMCA Standard 210-99 
(incorporated by reference, see Sec.  430.22) or Figure 14 of ASHRAE 
Standard 41.2-87 (RA 92) (incorporated by reference, see Sec.  
430.22) for guidance on placing the static pressure taps and 
positioning the diffusion baffle (settling means) relative to the 
chamber inlet.
    b. Connect the airflow measuring apparatus to the 
interconnecting duct section described in section 2.5.4. See 
sections 6.1.1, 6.1.2, and 6.1.4, and Figures 1, 2, and 4 of ASHRAE 
Standard 37-88 (incorporated by reference, see Sec.  430.22), and 
Figures D1, D2, and D4 of ARI Standard 210/240-2003 (incorporated by 
reference, see Sec.  430.22) 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 ASHRAE Standard 37-88 (incorporated by reference, see Sec.  
430.22) when testing triple-split units.)
    2.7 Electrical voltage supply. Perform all tests at the voltage 
specified in section 6.1.3.2 of ARI Standard 210/240-2003 
(incorporated by reference, see Sec.  430.22) for ``Standard Rating 
Tests.'' 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 active within 15 seconds prior to 
beginning an ON cycle. For ducted units tested with a fan installed, 
the ON cycle lasts from compressor ON to indoor fan OFF. For ducted 
units tested without an indoor fan installed, the ON cycle lasts 
from compressor ON to compressor OFF. For non-ducted units, the ON 
cycle lasts from indoor fan ON to indoor fan 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 fan motor to within 
1.0 percent. If required according to sections 3.3, 3.4, 
3.7, 3.9.1, and/or 3.10, this same instrumentation requirement 
applies when testing air conditioners and heat pumps having a 
variable-speed constant-air-volume-rate indoor fan or a variable-
speed, variable-air-volume-rate indoor fan.
    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. In addition, for all 
steady-state tests, conduct a second, independent measurement of 
capacity as described in section 3.1.1. For split systems, use one 
of the following secondary measurement methods: Outdoor Air Enthalpy 
Method, Compressor Calibration Method, or Refrigerant Enthalpy 
Method. For single packaged 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) An outlet plenum containing static pressure taps (sections 
2.4, 2.4.1, and 2.5.3),
    (2) An airflow measuring apparatus (section 2.6),
    (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), and
    (4) On the inlet side, a sampling device and optional 
temperature grid (sections 2.5 and 2.5.2).
    c. During the preliminary tests described in sections 3.11.1 and 
3.11.1.1, 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, connect pressure gages to the access valves or 
to ports created from tapping into the suction and discharge lines. 
Use this alternative approach when testing a unit charged with a 
zeotropic refrigerant having a temperature glide in excess of 1 
[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 [deg]F, total 
capacity from separate calibration tests conducted under identical 
operating conditions. When using this method, install 
instrumentation, measure refrigerant properties, and adjust the

[[Page 59149]]

refrigerant charge according to section 7.4.2 of ASHRAE Standard 37-
88 (incorporated by reference, see Sec.  430.22). Use refrigerant 
temperature and pressure measuring instruments that meet the 
specifications given in sections 5.1.1 and 5.2 of ASHRAE Standard 
37-88 (incorporated by reference, see Sec.  430.22).
    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 7.6.2 of ASHRAE Standard 37-88 (incorporated 
by reference, see Sec.  430.22) 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 ASHRAE Standard 37-88 (incorporated by reference, see Sec.  
430.22).
    2.11 Measurement of test room ambient conditions. 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 ASHRAE Standard 37-88 (incorporated by 
reference, see Sec.  430.22)), add instrumentation to permit 
measurement of the indoor test room dry-bulb temperature.
    b. If the Outdoor Air Enthalpy Method is not used, add 
instrumentation to measure the dry-bulb temperature and the water 
vapor content of the air entering the outdoor coil. If an air 
sampling device is used, construct and apply the device as per 
section 6 of ASHRAE Standard 41.1-86 (RA 01) (incorporated by 
reference, see Sec.  430.22). Take steps (e.g., add or re-position a 
lab circulating fan), as needed, to minimize the magnitude of the 
temperature distribution non-uniformity. Position any fan in the 
outdoor test room while trying to keep air velocities in the 
vicinity of the test unit below 500 feet per minute.
    c. Measure dry bulb temperatures as specified in sections 4, 5, 
6.1-6.10, 9, 10, and 11 of ASHRAE Standard 41.1-86 (RA 01) 
(incorporated by reference, see Sec.  430.22). Measure water vapor 
content as stated above in section 2.5.6.
    2.12 Measurement of indoor fan 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 ASHRAE Standard 37-88 
(incorporated by reference, see Sec.  430.22).

3. Testing Procedures

    3.1 General Requirements. If, during the testing process, an 
equipment set-up adjustment is made that would alter the performance 
of the unit when conducting an 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.
    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 all steady-state 
tests (i.e., the A, A2, A1, B, B2, 
B1, C, C1, EV, F1, G1, 
H01, H1, H12, H11, 
HIN, H3, H32, and H31 
Tests), in addition, use one of the acceptable secondary methods 
specified in section 2.10 to determine indoor space conditioning 
capacity. Calculate this secondary check of capacity according to 
section 3.11. 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 ASHRAE Standard 37-88 (incorporated by reference, see 
Sec.  430.22) (and do not make the after-test fan heat adjustments 
described in sections 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.
    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 fan 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 ARI Standard 210/240-2003 
(incorporated by reference, see Sec.  430.22) when obtaining the 
airflow through the outdoor coil.
    3.1.4 Airflow through the indoor coil.
    3.1.4.1 Cooling Certified Air Volume Rate.
    3.1.4.1.1 Cooling Certified Air Volume Rate for Ducted Units. 
The manufacturer must specify the Cooling Certified Air Volume Rate. 
Use this value as long as the following two requirements are 
satisfied. First, when conducting the A or A2 Test 
(exclusively), the measured air volume rate, when divided by the 
measured indoor air-side total cooling capacity, must not exceed 
37.5 cubic feet per minute of standard air (scfm) per 1000 Btu/h. If 
this ratio is exceeded, reduce the air volume rate until this ratio 
is equaled. Use this reduced air volume rate for all tests that call 
for using the Cooling Certified Air Volume Rate. The second 
requirement is as follows:
    a. For ducted units that are tested with a fixed-speed, multi-
speed, or variable-speed variable-air-volume-rate indoor fan 
installed. For the A or A2 Test (exclusively), the 
measured external static pressure must be equal to or greater than 
the applicable minimum external static pressure cited in Table 2. If 
the Table 2 minimum is not equaled or exceeded, incrementally change 
the set-up of the indoor fan (e.g., fan motor pin settings, fan 
motor speed) until the Table 2 requirement is met while maintaining 
the same air volume rate. If the indoor fan set-up changes cannot 
provide the minimum external static, then reduce the air volume rate 
until the correct Table 2 minimum is equaled. For the last scenario, 
use the reduced air volume rate for all tests that require the 
Cooling Certified Air Volume Rate.
    b. For ducted units that are tested with a constant-air-volume-
rate indoor fan installed. For all tests that specify the Cooling 
Certified Air Volume Rate, obtain an external static pressure as 
close to (but not less than) the applicable Table 2 value that does 
not cause instability or an automatic shutdown of the indoor blower.
    c. For ducted units that are tested without an indoor fan 
installed. 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 Certified Air Volume Rate.

  Table 2.--Minimum External Static Pressure for Ducted Systems Tested
                      With an Indoor Fan Installed
------------------------------------------------------------------------
   Rated Cooling \1\ or Heating \2\      Minimum External Resistance \3\
           Capacity (Btu/h)                     (Inches of Water)
------------------------------------------------------------------------
Up Thru 28,800........................  0.10
29,000 to 42,500......................  0.15
43,000 and Above......................  0.20
------------------------------------------------------------------------
\1\ For air conditioners and heat pumps, the value cited by the
  manufacturer in published literature for the unit's capacity when
  operated at the A or A2 Test conditions.
\2\ For heating-only heat pumps, the value the manufacturer cites in
  published literature for the unit's 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.


[[Page 59150]]

    3.1.4.1.2 Cooling Certified Air Volume Rate for Non-ducted 
Units. For non-ducted units, the Cooling Certified 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. a. For ducted units 
that regulate the speed (as opposed to the cfm) of the indoor fan,
[GRAPHIC] [TIFF OMITTED] TR11OC05.002

where ``Cooling Minimum Fan Speed'' corresponds to the fan speed 
used when operating at low compressor capacity (two-capacity 
system), the fan speed used when operating at the minimum compressor 
speed (variable-speed system), or the lowest fan speed used when 
cooling (single-speed compressor and a variable-speed variable-air-
volume-rate indoor fan). For such systems, obtain the Cooling 
Minimum Air Volume Rate regardless of the external static pressure.
    b. For ducted units that regulate the air volume rate provided 
by the indoor fan, the manufacturer must specify the Cooling Minimum 
Air Volume Rate. For such systems, 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 
instability or an automatic shutdown of the indoor blower while 
being as close to, but not less than,
[GRAPHIC] [TIFF OMITTED] TR11OC05.003

where [Delta]Pst,A2 is the applicable Table 2 minimum 
external static pressure that was targeted during the A2 
(and B2) Test.
    c. For ducted two-capacity units that are tested without an 
indoor fan installed, the Cooling Minimum Air Volume Rate is the 
higher of (1) the rate specified by the manufacturer or (2) 75 
percent of the Cooling Certified Air Volume Rate. During the 
laboratory tests on a coil-only (fanless) unit, 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 fan 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 fan, use the lowest fan 
setting allowed for cooling.
    3.1.4.3 Cooling Intermediate Air Volume Rate. a. For ducted 
units that regulate the speed of the indoor fan,
[GRAPHIC] [TIFF OMITTED] TR11OC05.004

For such units, obtain the Cooling Intermediate Air Volume Rate 
regardless of the external static pressure.
    b. For ducted units that regulate the air volume rate provided 
by the indoor fan, the manufacturer must specify the Cooling 
Intermediate Air Volume Rate. For such systems, conduct the 
EV Test at an external static pressure that does not 
cause instability or an automatic shutdown of the indoor blower 
while being as close to, but not less than,
[GRAPHIC] [TIFF OMITTED] TR11OC05.005

where [Delta]Pst,A2 is the applicable Table 2 minimum 
external static pressure that was targeted during the A2 
(and B2) Test.
    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 Certified Air Volume Rate.
    3.1.4.4.1 Ducted heat pumps where the Heating and Cooling 
Certified Air Volume Rates are the same. a. Use the Cooling 
Certified Air Volume Rate as the Heating Certified Air Volume Rate 
for:
    1. Ducted heat pumps that operate at the same indoor fan speed 
during both the A (or A2) and the H1 (or H12) 
Tests;
    2. Ducted heat pumps that regulate fan speed to deliver the same 
constant air volume rate during both the A (or A2) and 
the H1 (or H12) Tests; and
    3. Ducted heat pumps that are tested without an indoor fan 
installed (except two-capacity northern heat pumps that are tested 
only at low capacity cooling--see 3.1.4.4.2).

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. For heat pumps that meet the above 
criterion ``2,'' test at an external static pressure that does not 
cause instability or an automatic shutdown of the indoor blower 
while being as close to, but not less than, the same Table 2 minimum 
external static pressure as was specified for the A (or 
A2) cooling mode test.
    3.1.4.4.2 Ducted heat pumps where the Heating and Cooling 
Certified Air Volume Rates are different due to indoor fan 
operation. a. For ducted heat pumps that regulate the speed (as 
opposed to the cfm) of the indoor fan,
[GRAPHIC] [TIFF OMITTED] TR11OC05.006


[[Page 59151]]


For such heat pumps, obtain the Heating Certified Air Volume Rate 
without regard to the external static pressure.
    b. For ducted heat pumps that regulate the air volume rate 
delivered by the indoor fan, the manufacturer must specify the 
Heating Certified Air Volume Rate. For such heat pumps, conduct all 
tests that specify the Heating Certified Air Volume Rate at an 
external static pressure that does not cause instability or an 
automatic shutdown of the indoor blower while being as close to, but 
not less than,
[GRAPHIC] [TIFF OMITTED] TR11OC05.007

where the Cooling Certified [Delta]Pst is the applicable 
Table 2 minimum external static pressure that was specified for the 
A or A2 Test.
    c. When testing ducted, two-capacity northern heat pumps (see 
Definition 1.46), use the appropriate approach of the above two 
cases for units that are tested with an indoor fan installed. For 
coil-only (fanless) northern heat pumps, the Heating Certified Air 
Volume Rate is the lesser of the rate specified by the manufacturer 
or 133 percent of the Cooling Certified Air Volume Rate. For this 
latter case, obtain the Heating Certified Air Volume Rate regardless 
of the pressure drop across the indoor coil assembly.
    3.1.4.4.3 Ducted heating-only heat pumps. The manufacturer must 
specify the Heating Certified Air Volume Rate. Use this value when 
the following two requirements are satisfied. First, when conducting 
the H1 or H12 Test (exclusively), the measured air volume 
rate, when divided by the measured indoor air-side total heating 
capacity, must not exceed 37.5 cubic feet per minute of standard air 
(scfm) per 1000 Btu/h. If this ratio is exceeded, reduce the air 
volume rate until this ratio is equaled. Use this reduced air volume 
rate for all tests of heating-only heat pumps that call for the 
Heating Certified Air Volume Rate. The second requirement is as 
follows:
    a. For heating-only heat pumps that are tested with a fixed-
speed, multi-speed, or variable-speed variable-air-volume-rate 
indoor fan installed. For the H1 or H12 Test 
(exclusively), the measured external static pressure must be equal 
to or greater than the Table 2 minimum external static pressure that 
applies given the heating-only heat pump's rated heating capacity. 
If the Table 2 minimum is not equaled or exceeded, incrementally 
change the set-up of the indoor fan until the Table 2 requirement is 
met while maintaining the same air volume rate. If the indoor fan 
set-up changes cannot provide the necessary external static 
pressure, then reduce the air volume rate until the correct Table 2 
minimum is equaled. For the last scenario, use the reduced air 
volume rate for all tests that require the Heating Certified Air 
Volume Rate.
    b. For ducted heating-only heat pumps having a constant-air-
volume-rate indoor fan. For all tests that specify the Heating 
Certified Air Volume Rate, obtain an external static pressure that 
does not cause instability or an automatic shutdown of the indoor 
blower while being as close to, but not less than, the applicable 
Table 2 minimum.
    c. For ducted heating-only heat pumps that are tested without an 
indoor fan installed. For 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 Certified 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 Certified 
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. a. For ducted heat 
pumps that regulate the speed (as opposed to the cfm) of the indoor 
fan,
[GRAPHIC] [TIFF OMITTED] TR11OC05.008

where ``Heating Minimum Fan Speed'' corresponds to the fan speed 
used when operating at low compressor capacity (two-capacity 
system), the lowest fan speed used at any time when operating at the 
minimum compressor speed (variable-speed system), or the lowest fan 
speed used when heating (single-speed compressor and a variable-
speed variable-air-volume-rate indoor fan). For such heat pumps, 
obtain the Heating Minimum Air Volume Rate without regard to the 
external static pressure.
    b. For ducted heat pumps that regulate the air volume rate 
delivered by the indoor fan, the manufacturer must specify the 
Heating Minimum Air Volume Rate. For such heat pumps, 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 
instability or an automatic shutdown of the indoor blower while 
being as close to, but not less than,
[GRAPHIC] [TIFF OMITTED] TR11OC05.009

[GRAPHIC] [TIFF OMITTED] TR11OC05.161

is the minimum external static pressure that was targeted during the 
H12 Test.
    c. For ducted two-capacity northern heat pumps that are tested 
with an indoor fan installed, use the appropriate approach of the 
above two cases.
    d. For ducted two-capacity heat pumps that are tested without an 
indoor fan installed, use the Cooling Minimum Air Volume Rate as the 
Heating Minimum Air Volume Rate. For ducted two-capacity northern 
heat pumps that are tested without an indoor fan installed, use the 
Cooling Certified Air Volume Rate as the Heating Minimum Air Volume 
Rate. For ducted two-capacity heating-only heat pumps that are 
tested without an indoor fan installed, the Heating Minimum Air 
Volume Rate is the higher of the rate specified by the manufacturer 
or 75 percent of the Heating Certified Air Volume Rate. During the 
laboratory tests on a coil-only (fanless) unit, 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 fan 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

[[Page 59152]]

indoor fan, use the lowest fan setting allowed for heating.
    3.1.4.6 Heating Intermediate Air Volume Rate. a. For ducted heat 
pumps that regulate the speed of the indoor fan,
[GRAPHIC] [TIFF OMITTED] TR11OC05.010

    For such heat pumps, obtain the Heating Intermediate Air Volume 
Rate without regard to the external static pressure.
    b. For ducted heat pumps that regulate the air volume rate 
delivered by the indoor fan, the manufacturer must specify the 
Heating Intermediate Air Volume Rate. For such heat pumps, conduct 
the H2V Test at an external static pressure that does not 
cause instability or an automatic shutdown of the indoor blower 
while being as close to, but not less than,
[GRAPHIC] [TIFF OMITTED] TR11OC05.011

[GRAPHIC] [TIFF OMITTED] TR11OC05.162

is the minimum external static pressure that was specified for the 
H12 Test.
    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. Except for the noted 
changes, determine the Heating Nominal Air Volume Rate using the 
approach described in section 3.1.4.6. Required changes include 
substituting ``H1N Test'' for H2V Test'' 
within the first section 3.1.4.6 equation, substituting 
``H1N Test [Delta]Pst'' for ``H2V 
Test [Delta]Pst'' in the second section 3.1.4.6 equation, 
substituting ``H1N Test'' for each ``H2V 
Test'', and substituting ``Heating Nominal Air Volume Rate'' for 
each ``Heating Intermediate Air Volume Rate.''
[GRAPHIC] [TIFF OMITTED] TR11OC05.012

    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 ASHRAE 
Standard 37-88) (incorporated by reference, see Sec.  430.22), 
maintain the dry bulb temperature within the test room within 5.0 [deg]F of the applicable sections 3.2 and 3.6 dry bulb 
temperature test condition for the air entering the indoor unit.
    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 7.8.3.1 and 7.8.3.2 of ASHRAE 
Standard 37-88 (incorporated by reference, see Sec.  430.22). When 
using the Outdoor Air Enthalpy Method, follow sections 7.8.3.1 and 
7.8.3.2 to calculate the air volume rate through the outdoor coil. 
To express air volume rates in terms of standard air, use:
[GRAPHIC] [TIFF OMITTED] TR11OC05.013

where,

Vs = air volume rate of standard (dry) air, 
(ft3/min)da
Vmx = air volume rate of the air-water vapor mixture, 
(ft3/min)mx
vn' = specific volume of air-water vapor mixture at the 
nozzle, ft3 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/
ft3)
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, ft3 per lbm 
of dry air.

    3.1.7 Test sequence. When testing a ducted unit (except if a 
heating-only heat pump), conduct the A or A2 Test first 
to establish the Cooling Certified Air Volume Rate. For ducted heat 
pumps where the Heating and Cooling Certified Air Volume Rates are 
different, make the first heating mode test one that requires the 
Heating Certified Air Volume Rate. For ducted heating-only heat 
pumps, conduct the H1 or H12 Test first to establish the 
Heating Certified Air Volume Rate. When conducting an optional 
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 if one expects to adjust the 
indoor fan control options when preparing for the first Minimum Air 
Volume Rate test. Under the same circumstances, the first test using 
the Heating Minimum Air Volume Rate should 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. For the 30-minute data 
collection interval used to determine capacity, the maximum spread 
among the

[[Page 59153]]

outlet dry bulb temperatures from any data sampling must not exceed 
1.5 [deg]F. Install the mixing devices described in section 2.5.4.2 
to minimize the temperature spread.
    3.1.9 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, 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, 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 Certified 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 unit having a single-speed compressor that is 
tested with a fixed-speed indoor fan installed, with a constant-air-
volume-rate indoor fan installed, or with no indoor fan installed. 
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, CDc. If the two optional tests 
are not conducted, assign CDc the default 
value of 0.25. Table 3 specifies test conditions for these four 
tests.

 Table 3.--Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Fan, a Constant Air Volume Rate Indoor Fan,
                                                                    or No Indoor Fan
--------------------------------------------------------------------------------------------------------------------------------------------------------
                                                 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 certified \2\
B Test--required (steady, wet coil)...........            80            67            82        \1\ 65  Cooling certified \2\
C Test--optional (steady, dry coil)...........            80         (\3\)            82  ............  Cooling certified \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.
\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 and a 
variable-speed variable-air-volume-rate indoor fan installed.
    3.2.2.1 Indoor fan capacity modulation that correlates with the 
outdoor dry bulb temperature. 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, 
CDc. If the two optional tests are not 
conducted, assign CDc the default value of 
0.25. Table 4 specifies test conditions for these six tests.
    3.2.2.2 Indoor fan 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 and Table 3. 
Use a Cooling Certified Air Volume Rate that represents a normal 
residential 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 4.--Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Variable Air Volume Rate Indoor Fan That correlates With the
                                                       Outdoor Dry Bulb Temperature (Sec. 3.2.2.1)
--------------------------------------------------------------------------------------------------------------------------------------------------------
                                                 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 certified \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 certified \2\
B1 Test--required (steady, wet coil)..........            80            67            82        \1\ 65  Cooling minimum \3\
C1 Test \4\--optional (steady, dry coil)......            80         (\4\)            82  ............  Cooling minimum \3\
D1 Test \4\--optional (cyclic, dry coil)......            80         (\4\)            82  ............  (\5\)
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ Defined in section 3.1.4.2.
\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 [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 
Definition 1.45.) a. 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, 
CDc. If the two optional tests are not 
conducted, assign CDc the default value of 
0.25. Table 5 specifies test conditions for these six tests.
    b. For units having a variable speed indoor fan that is 
modulated to adjust the sensible to total (S/T) cooling capacity 
ratio, use Cooling Certified and Cooling Minimum Air Volume Rates 
that represent a normal residential installation. Additionally, if 
conducting the optional dry-coil tests,

[[Page 59154]]

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 Definition 1.46) 
in the same way as a single speed heat pump with the unit operating 
exclusively at low compressor capacity (see section 3.2.1 and Table 
3).
    d. If a two-capacity air conditioner or heat pump locks out low 
capacity operation at outdoor temperatures that are less than 95 
[deg]F, conduct the A1 Test using the outdoor temperature 
conditions listed for the F1 Test in Table 6 rather than 
using the outdoor temperature conditions listed in Table 5 for the 
A1 Test.

                Table 5.--Cooling Mode Test Conditions for Units Having a Two-Capacity Compressor
----------------------------------------------------------------------------------------------------------------
                                 Air entering        Air entering
                                  indoor unit        outdoor unit
                                  temperature         temperature     Compressor
      Test description             ([deg]F)            ([deg]F)         capacity      Cooling air volume rate
                             ----------------------------------------
                              Dry bulb  Wet bulb  Dry bulb  Wet bulb
----------------------------------------------------------------------------------------------------------------
A2 Test--required (steady,          80        67        95      1 75        High  Cooling Certified 2
 wet coil).
A1 Test--required (steady,          80        67        95      1 75         Low  Cooling Minimum 3
 wet coil).
B2 Test--required (steady,          80        67        82      1 65        High  Cooling Certified 2
 wet coil).
B1 Test--required (steady,          80        67        82      1 65         Low  Cooling Minimum 3
 wet coil).
C1 Test 4--optional (steady,        80       (4)        82  ........         Low  Cooling Minimum 3
 dry coil).
D1 Test 4--optional (cyclic,        80       (4)        82  ........         Low  (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.
3 Defined in section 3.1.4.2.
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 [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.

    3.2.4 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,CDc. If the two optional tests are 
not conducted, assign CDc the default value of 
0.25. Table 6 specifies test conditions for these seven tests. 
Determine the intermediate compressor speed cited in Table 6 using:
[GRAPHIC] [TIFF OMITTED] TR11OC05.014

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 fan speed to adjust the 
sensible to total (S/T) cooling capacity ratio, use Cooling 
Certified, Cooling Intermediate, and Cooling Minimum Air Volume 
Rates that represent a normal residential installation. 
Additionally, if conducting the optional dry-coil tests, operate the 
unit in the same S/T capacity control mode as used for the 
F1 Test.

                                   Table 6.--Cooling Mode Test Conditions for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
                                                  Air entering        Air entering
                                                   indoor unit        outdoor unit
                                                   Temperature         Temperature
               Test description                     ([deg]F)            ([deg]F)       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           Maximum  Cooling Certified \2\
B2 Test--required (steady, wet coil).........        80        67        82    \1\ 65           Maximum  Cooling Certified 2
EV Test--required (steady, wet coil).........        80        67        87    \1\ 69      Intermediate  Cooling Intermediate 3
B1 Test--required (steady, wet coil).........        80        67        82    \1\ 65           Minimum  Cooling Minimum 4
F1 Test--required (steady, wet coil).........        80        67        67  \1\ 53.5           Minimum  Cooling Minimum 4
G1 Test 5--optional (steady, dry coil).......        80       (5)        67  ........           Minimum  Cooling Minimum 4
I1 Test 5--optional (cyclic, dry coil).......        80       (5)        67  ........           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.
3 Defined in section 3.1.4.3.
4 Defined in section 3.1.4.2.
5 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.)
6 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 G1 Test.

    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 fan of the test unit to obtain and then 
maintain the indoor air volume rate and/or external static pressure 
specified for

[[Page 59155]]

the particular test. Continuously record (see Definition 1.15):
    (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 cases where its control is required, 
the water vapor content of the air entering the outdoor coil.
    Refer to section 3.11 for additional requirements that depend on 
the selected secondary test method.
    b. After satisfying the pretest equilibrium requirements, make 
the measurements specified in Table 5 of ASHRAE Standard 37-88 
(incorporated by reference, see Sec.  430.22) for the Indoor Air 
Enthalpy method and the user-selected secondary method. Except for 
external static pressure, make the Table 5 measurements at equal 
intervals that span 10 minutes or less. Measure external static 
pressure every 5 minutes or less. Continue data sampling until 
reaching a 30-minute period (e.g., four consecutive 10-minute 
samples) where the test tolerances specified in Table 7 are 
satisfied. For those continuously recorded parameters, use the 
entire data set from the 30-minute interval to evaluate Table 7 
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 as specified in 
section 7.3.3.1 of ASHRAE Standard 37-88 (incorporated by reference, 
see Sec.  430.22). 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. Assign the 
average total space cooling capacity and electrical power 
consumption over the 30-minute data collection interval to the 
variables Qck(T) and 
Eck(T), respectively. For these two 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 maximum speed, k=1 to denote 
low capacity or minimum speed, and k=v to denote the intermediate 
speed.
    d. For units tested without an indoor fan installed, decrease 
Qck(T) by
[GRAPHIC] [TIFF OMITTED] TR11OC05.015

and increase Eck(T) by,
[GRAPHIC] [TIFF OMITTED] TR11OC05.016

where Vs is the average measured indoor air volume rate 
expressed in units of cubic feet per minute of standard air (scfm).

 Table 7.--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 tolerance   Test condition tolerance
                                                                        1                          2
----------------------------------------------------------------------------------------------------------------
Indoor dry-bulb, [deg]F
    Entering temperature..................................                       2.0                        0.5
    Leaving temperature...................................                       2.0
Indoor wet-bulb, [deg]F
    Entering temperature..................................                       1.0                    \3\ 0.3
    Leaving temperature...................................                   \3\ 1.0
Outdoor dry-bulb, [deg]F
    Entering temperature..................................                       2.0                        0.5
    Leaving temperature...................................                   \4\ 2.0
Outdoor wet-bulb, [deg]F
    Entering temperature..................................                       1.0                    \5\ 0.3
    Leaving temperature...................................                   \4\ 1.0
External resistance to airflow, inches of water...........                       0.05                   \6\ 0.02
Electrical voltage, % of rdg..............................                       2.0                        1.5
Nozzle pressure drop, % of rdg............................                       2.0
----------------------------------------------------------------------------------------------------------------
1 See Definition 1.41.
2 See Definition 1.40.
3 Only applies during wet coil tests; does not apply during steady-state, dry coil cooling mode tests.
4 Only applies when using the Outdoor Air Enthalpy Method.
5 Only applies during wet coil cooling mode tests where the unit rejects condensate to the outdoor coil.
6 Only applies when testing non-ducted units.

    d. For air conditioners and heat pumps having a constant-air-
volume-rate indoor fan, 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 fan 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 fan 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 fan 
motor at [Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TR11OC05.017

    5. Increase the total space cooling capacity, 
Qck(T), by the quantity (Efan,1 - 
Efan,min), when expressed on a Btu/h basis. Decrease the 
total electrical power, Eck(T), by the same 
fan power difference, now expressed in watts.
    3.4 Test procedures for the optional steady-state dry coil 
cooling mode tests (the C, C1, 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 
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.

[[Page 59156]]

    b. Denote the resulting total space cooling capacity and 
electrical power derived from the test as Qss,dry and 
Ess,dry(T). In preparing for the section 3.5 cyclic test, 
record the average indoor-side air volume rate, V, 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 fan (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 fan turned off (see section 3.5), 
include the electrical power used by the indoor fan motor among the 
recorded parameters from the 30-minute test.
    3.5 Test procedures for the optional cyclic dry coil cooling 
mode tests (the D, D1, and I1 Tests). a. 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 fan, 
the manufacturer has the option of electing at the outset whether to 
conduct the cyclic test with the indoor fan enabled or disabled. 
Always revert to testing with the indoor fan disabled if cyclic 
testing with the fan enabled is unsuccessful.
    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.
    c. Sections 3.5.1 and 3.5.2 specify airflow requirements through 
the indoor coil of ducted and non-ducted systems, respectively. In 
all cases, use the exhaust fan of the airflow measuring apparatus 
(covered under section 2.6) along with the indoor fan 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 fan 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 fan, 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 fan 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 blower, 
temporarily remove the blower.
    e. After completing a minimum of two complete compressor OFF/ON 
cycles, determine the overall cooling delivered and total electrical 
energy consumption during any subsequent data collection interval 
where the test tolerances given in Table 8 are satisfied. If 
available, use electric resistance heaters (see section 2.1) to 
minimize the variation in the inlet air temperature.
    f. With regard to the Table 8 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 fan (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 units tested with an 
indoor fan installed and operating, integrate electrical power from 
indoor fan OFF to indoor fan 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 8.--Test Operating and Test Condition Tolerances for Cyclic Dry
                         Coil Cooling Mode Tests
------------------------------------------------------------------------
                                                  Test          Test
                                                Operating     Condition
                                                Tolerance     Tolerance
                                                   \1\           \2\
------------------------------------------------------------------------
Indoor entering dry-bulb temperature \3\,             2.0            0.5
 [deg]F.....................................
Indoor entering wet-bulb temperature, [deg]F  ............       (\4\)
Outdoor entering dry-bulb temperature \3\,            2.0            0.5
 [deg]F.....................................
External resistance to airflow \3\, inches            0.05  ............
 of water...................................
Airflow nozzle pressure difference or                 2.0        \5\ 2.0
 velocity pressure \3\, % of reading........
Electrical voltage \6\, % of rdg............          2.0            1.5 
------------------------------------------------------------------------
\1\ See Definition 1.41.
\2\ See Definition 1.40.
\3\ 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 fan that ramps, the
  tolerances listed for the external resistance to airflow apply from 30
  seconds after achieving full speed until ramp down begins.
\4\ Shall at no time exceed a wet-bulb temperature that results in
  condensate forming on the indoor coil.
\5\ The test condition shall be the average nozzle pressure difference
  or velocity pressure measured during the steady-state dry coil test.
\6\ Applies during the interval when at least one of the following--the
  compressor, the outdoor fan, or, if applicable, the indoor fan--are
  operating except for the first 30 seconds after compressor start-up.

    i. If the Table 8 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] TR11OC05.018

where V, Cp,a, vn' (or vn), and 
Wn are the values recorded during the section 3.4 dry 
coil steady-state test and,

[[Page 59157]]

[GRAPHIC] [TIFF OMITTED] TR11OC05.019

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.

    3.5.1 Procedures when testing ducted systems. The automatic 
controls that are normally installed with 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, if installed, 
the indoor fan of the test unit). For example, for ducted units 
tested without an indoor fan installed but rated based on using a 
fan time delay relay, control the indoor coil airflow according to 
the rated ON and/or OFF delays provided by the relay. For ducted 
units having a variable-speed indoor fan 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 units 
tested without an indoor fan installed, cycle the indoor coil 
airflow in unison with the cycling of the compressor. Close air 
dampers on the inlet (section 2.5.1) and outlet side (sections 2.5 
and 2.5.4) 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 fan. For ducted units 
tested without an indoor fan installed (excluding the special case 
where a variable-speed fan is temporarily removed), increase 
ecyc,dry by the quantity,
[GRAPHIC] [TIFF OMITTED] TR11OC05.020

and decrease qcyc,dry by,
[GRAPHIC] [TIFF OMITTED] TR11OC05.021

where Vs 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 fan 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 
fan power measured during or following the dry coil steady-state 
test; or,
    b. The following algorithm if the indoor fan ramps its speed 
when cycling.
    1. Measure the electrical power consumed by the variable-speed 
indoor fan 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 
fan 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 a manufacturer-supplied ramp interval exceeds 45 
seconds, use a 45-second ramp interval nonetheless when estimating 
the fan energy.
    The manufacturer is allowed to choose option a, and forego the 
extra testing burden of option b, even if the unit ramps indoor fan 
speed when cycling.
    3.5.2 Procedures when testing non-ducted systems. Do not use air 
dampers when conducting cyclic tests on non-ducted 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 fan 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 fan during the 3 minutes prior to compressor cut-on from the 
integrated electrical energy, ecyc,dry. Add the 
electrical energy used by the indoor fan during the 3 minutes after 
compressor cutoff to the integrated cooling capacity, 
qcyc,dry. For the case where the non-ducted unit uses a 
variable-speed indoor fan which is disabled during the cyclic test, 
correct ecyc,dry and qcyc,dry using the same 
approach as prescribed in section 3.5.1 for ducted units having a 
disabled variable-speed indoor fan.
    3.5.3 Cooling mode cyclic degradation coefficient calculation. 
Use two optional dry-coil tests to determine the cooling mode cyclic 
degradation coefficient, CDc. If the two 
optional tests are not conducted, assign CDc 
the default value of 0.25. Evaluate CDc using 
the above results and those from the section 3.4 dry coil steady-
state test.
[GRAPHIC] [TIFF OMITTED] TR11OC05.022

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.023

the average energy efficiency ratio during the cyclic dry coil 
cooling mode
test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TR11OC05.024

the average energy efficiency ratio during the steady-state dry coil 
cooling mode test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TR11OC05.025

the cooling load factor dimensionless.
Round the calculated value for CDc to the 
nearest 0.01. If CDc 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 
that is tested with a fixed speed indoor fan installed, with a 
constant-air-volume-rate indoor fan installed, or with no indoor fan 
installed. Conduct three tests: The High Temperature (H1) Test, the 
Frost Accumulation (H2) Test, and the Low Temperature (H3) Test. 
Conduct the optional High Temperature Cyclic (H1C) Test to determine 
the heating mode cyclic degradation coefficient, 
CDh. If this optional test is not conducted, 
assign CDh the default value of 0.25. Test 
conditions for these four tests are specified in Table 9.

 Table 9.--Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Fan, a Constant Air Volume Rate Indoor Fan,
                                                                    or No Indoor Fan
--------------------------------------------------------------------------------------------------------------------------------------------------------
                                                  Air entering indoor unit    Air entering outdoor
                                                     Temperature ([deg]F)       unit  Temperature
                Test description                 --------------------------         ([deg]F)                        Heating air volume rate
                                                                           --------------------------
                                                    Dry bulb     Wet bulb     Dry bulb     Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H1 Test (required, steady)......................           70      60(max)           47           43  Heating Certified \1\
H1C Test (optional, cyclic).....................           70      60(max)           47           43  (\2\)
H2 Test (required)..............................           70      60(max)           35           33  Heating Certified \1\
H3 Test (required, steady)......................           70      60(max)           17           15  Heating Certified \1\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4.
\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.


[[Page 59158]]

    3.6.2 Tests for a heat pump having a single-speed compressor and 
a variable-speed, variable-air-volume-rate indoor fan: capacity 
modulation correlates with outdoor dry bulb temperature. 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, CDh. If this optional 
test is not conducted, assign CDh the default 
value of 0.25. Table 10 specifies test conditions for these seven 
tests. If the optional H21 Test is not done, use the 
following equations to approximate the capacity and electrical power 
of the heat pump at the H21 test conditions:
[GRAPHIC] [TIFF OMITTED] TR11OC05.026

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.027

The quantities Qhk=2(47), 
Ehk=2(47), Qhk=1(47), 
and Ehk=1(47) are determined from the 
H12 and H11 Tests and evaluated as specified 
in section 3.7; the quantities Qhk=2(35) and 
Ehk=2(35) are determined from the 
H22 Test and evaluated as specified in section 3.9; and 
the quantities Qhk=2(17), 
Ehk=2(17), Qhk=1(17), 
and Ehk=1(17), are determined from the 
H32 and H31 Tests and evaluated as specified 
in section 3.10.

              Table 10.--Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Variable Air Volume Rate Indoor Fan
--------------------------------------------------------------------------------------------------------------------------------------------------------
                                            Air entering indoor unit  temperature    Air entering outdoor
                                                          ([deg]F)                     unit  temperature
             Test description             ----------------------------------------         ([deg]F)                    Heating air volume rate
                                                                                  --------------------------
                                             Dry bulb            Wet bulb            Dry bulb     Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H12 Test (required, steady)..............           70  60(max)..................           47           43  Heating Certified.\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 Certified.\1\
H21 Test (optional)......................           70  60(max)..................           35           33  Heating Minimum.\2\
H32 Test (required, steady)..............           70  60(max)..................           17           15  Heating Certified.\1\
H31 Test (required, steady)..............           70  60(max)..................           17           15  Heating Minimum.\2\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4.
\2\ Defined in section 3.1.4.5.
\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 Definition 1.45), including two-capacity, northern heat pumps 
(see Definition 1.46). 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). 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 seasonal performance 
calculations, and
    2. The heat pump's controls allow low capacity operation at 
outdoor temperatures of 37[deg]F and less.
    b. Conduct the optional Maximum Temperature Cyclic Test 
(H0C1) to determine the heating mode cyclic degradation 
coefficient, CDh. If this optional test is not 
conducted, assign CDh the default value of 
0.25. Table 11 specifies test conditions for these eight tests.

                                   Table 11.--Heating Mode Test Conditions for Units Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
                                      Air entering indoor unit    Air entering outdoor
                                         Temperature ([deg]F)       unit Temperature
          Test description           --------------------------         ([deg]F)           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
H0C1 Test (optional, cyclic)........           70      60(max)           62         56.5  Low..................  (2)
H12 Test (required, steady).........           70      60(max)           47           43  High.................  Heating Certified 3

[[Page 59159]]

 
H11 Test (required, steady).........           70      60(max)           47           43  Low..................  Heating Minimum 1
H22 Test (required).................           70      60(max)           35           33  High.................  Heating Certified 3
H21 Test 4 (required)...............           70      60(max)           35           33  Low..................  Heating Minimum 1
H32 Test (required, steady).........           70      60(max)           17           15  High.................  Heating Certified 3
H31 Test 4 (required, steady).......           70      60(max)           17           15  Low..................  Heating Minimum 1
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5.
\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 H01 Test.
\3\ Defined in section 3.1.4.4.
\4\ 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.

    3.6.4 Tests for a heat pump having a variable-speed compressor. 
a. Conduct one Maximum Temperature Test (H01), two High 
Temperature Tests (H12 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 (H1N ) and 
an additional Frost Accumulation Test (H22). Conduct the 
optional Maximum Temperature Cyclic (H0C1) Test to 
determine the heating mode cyclic degradation coefficient, 
CDh. If this optional test is not conducted, 
assign CDh the default value of 0.25. Table 12 
specifies test conditions for these eight tests. Determine the 
intermediate compressor speed cited in Table 12 using the heating 
mode maximum and minimum compressors speeds and:
[GRAPHIC] [TIFF OMITTED] TR11OC05.028

where a tolerance of plus 5 percent or the next higher inverter 
frequency step from that calculated is allowed. 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] TR11OC05.029

    b. Determine the quantities Qhk=2(47) and 
from Ehk=2(47) from the H12 Test 
and evaluate them according to section 3.7. Determine the quantities 
Qhk=2(17) and Ehk=2(17) 
from the H32 Test and evaluate them according to section 
3.10. For heat pumps where the heating mode maximum compressor speed 
exceeds its cooling mode maximum compressor speed, conduct the 
H1N Test if the manufacturer requests it. If the 
H1N Test is done, operate the heat pump's compressor at 
the same speed as the speed used for the cooling mode A2 
Test. Refer to the last sentence of section 4.2 to see how the 
results of the H1N Test may be used in calculating the 
heating seasonal performance factor.

                                  Table 12.--Heating Mode Test Conditions for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
                                     Air entering indoor unit       Air entering outdoor
                                       temperature ([deg]F)           unit  temperature
        Test description         --------------------------------         ([deg]F)                 Compressor speed           Heating air volume rate
                                                                 --------------------------
                                    Dry bulb        Wet bulb        Dry bulb     Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).....           70  60\(max)\........           62         56.5  Minimum......................  Heating Minimum.\1\
H0C1 Test (optional, cyclic)....           70  60\(max)\........           62         56.5  Minimum......................   (\2\)
H12 Test (required, steady).....           70  60\(max)\........           47           43  Maximum......................  Heating Certified.\3\
H11 Test (required, steady).....           70  60\(max)\........           47           43  Minimum......................  Heating Minimum.\1\
H1N Test (optional, steady).....           70  60\(max)\........           47           43  Cooling Mode Maximum.........  Heating Nominal.\4\
H22 Test (optional).............           70  60\(max)\........           35           33  Maximum......................  Heating Certified.\3\
H2V Test (required).............           70  60\(max)\........           35           33  Intermediate.................  Heating Intermediate.\5\
H32 Test (required, steady).....           70  60\(max)\........           17           15  Maximum......................  Heating Certified.\3\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5.
\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 H01 Test.
\3\ Defined in section 3.1.4.4.
\4\ Defined in section 3.1.4.7.
\5\ Defined in section 3.1.4.6.


[[Page 59160]]

    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 Definition 1.28) 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 
3.1.9 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.)
    3.7 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 fan 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 for additional requirements that 
depend on the selected secondary test method. After satisfying the 
pretest equilibrium requirements, make the measurements specified in 
Table 5 of ASHRAE Standard 37-88 (incorporated by reference, see 
Sec.  430.22) for the Indoor Air Enthalpy method and the user-
selected secondary method. Except for external static pressure, make 
the Table 5 measurements at equal intervals that span 10 minutes or 
less. Measure external static pressure every 5 minutes or less. 
Continue data sampling until a 30-minute period (e.g., four 
consecutive 10-minute samples) is reached where the test tolerances 
specified in Table 13 are satisfied. For those continuously recorded 
parameters, use the entire data set for the 30-minute interval when 
evaluating Table 13 compliance. Determine the average electrical 
power consumption of the heat pump over the same 30-minute interval.

 Table 13.--Test Operating and Test Condition Tolerances for Section 3.7
            and Section 3.10 Steady-State Heating Mode Tests
------------------------------------------------------------------------
                                                       Test       Test
                                                    operating  condition
                                                    tolerance  tolerance
                                                        1          2
------------------------------------------------------------------------
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...........................     3 1.0   .........
External resistance to airflow, inches of water...       0.05     4 0.02
Electrical voltage, % of rdg......................       2.0        1.5
Nozzle pressure drop, % of rdg....................       2.0
------------------------------------------------------------------------
1 See Definition 1.41.
2 See Definition 1.40.
3 Only applies when the Outdoor Air Enthalpy Method is used.
4 Only applies when testing non-ducted units.

    b. Calculate indoor-side total heating capacity as specified in 
section 7.3.4.1 of ASHRAE Standard 37-88 (incorporated by reference, 
see Sec.  430.22). 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 
Qhk and Ehk(T) 
respectively. The ``T'' and superscripted ``k'' are the same as 
described in section 3.3. Additionally, for the heating mode, use 
the superscript to denote results from the optional H1N 
Test, if conducted.
    c. For heat pumps tested without an indoor fan installed, 
increase Qhk(T) by
[GRAPHIC] [TIFF OMITTED] TR11OC05.030

and increase Ehk(T) by,
[GRAPHIC] [TIFF OMITTED] TR11OC05.031

where Vs 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 [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 13 test tolerances are satisfied. In 
this case, use only the results from the second 30-minute data 
collection interval to evaluate Qhk(47) and 
Ehk(47).
    d. If conducting the optional cyclic heating mode test, which is 
described in section 3.8, record the average indoor-side air volume 
rate, V, 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 fan motor (Efan,1):
    1. The section 3.8 cyclic test will be conducted and the heat 
pump has a variable-speed indoor fan that is expected to be disabled 
during the cyclic test; or
    2. The heat pump has a (variable-speed) constant-air volume-rate 
indoor fan 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

[[Page 59161]]

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 fan 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 fan 
motor if the 30-minute test had been conducted at 
[Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TR11OC05.032

    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.
    3.8 Test procedures for the optional cyclic heating mode tests 
(the H0C1, H1C, and H1C1 Tests). a. Except as 
noted below, conduct the cyclic heating mode test as specified in 
section 3.5. 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 14 
rather than Table 8. Record the outdoor coil entering wet-bulb 
temperature according to the requirements given in section 3.5 for 
the outdoor coil entering dry-bulb temperature. Drop the subscript 
``dry'' used in variables cited in section 3.5 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 except for making the 
following changes:
    (1) When evaluating Equation 3.5-1, use the values of V, 
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] TR11OC05.033
    
    b. For ducted heat pumps tested without an indoor fan installed 
(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 
(Vs) 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 fan 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 fan 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 optional 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. If the optional test is not conducted, 
assign CDh the default value of 0.25.
[GRAPHIC] [TIFF OMITTED] TR11OC05.034

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.035

the average coefficient of performance during the cyclic heating 
mode test, dimensionless.
[GRAPHIC] [TIFF OMITTED] TR11OC05.036

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] TR11OC05.037

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 CDh to the 
nearest 0.01. If CDh is negative, then set it 
equal to zero.

   Table 14.--Test operating and test condition tolerances for cyclic
                           heating mode tests.
------------------------------------------------------------------------
                                                       Test       Test
                                                    operating  condition
                                                    tolerance  tolerance
                                                       \1\        \2\
------------------------------------------------------------------------
Indoor entering dry-bulb temperature,\3\ [deg]F...        2.0        0.5
Indoor entering wet-bulb temperature,\3\ [deg]F...        1.0
Outdoor entering dry-bulb temperature,\3\ [deg]F..        2.0        0.5
Outdoor entering wet-bulb temperature,\3\ [deg]F..        2.0        1.0
External resistance to air-flow,\3\ inches of            0.05
 water............................................
Airflow nozzle pressure difference or velocity            2.0    \4\ 2.0
 pressure,\3\ % of reading........................
Electrical voltage,\5\ % of rdg...................        2.0       1.5
------------------------------------------------------------------------
\1\ See Definition 1.41.
\2\ See Definition 1.40.
\3\ 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 fan that ramps, the
  tolerances listed for the external resistance to airflow shall apply
  from 30 seconds after achieving full speed until ramp down begins.
\4\ 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.
\5\ Applies during the interval that at least one of the following--the
  compressor, the outdoor fan, or, if applicable, the indoor fan--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. 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

[[Page 59162]]

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 Definition 1.42), 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 12 hours, immediately conclude the test 
and use the results from the full 12-hour period to calculate the 
average space heating capacity and average electrical power 
consumption. For heat pumps that turn the indoor fan 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 fan. If it is installed, use the outlet damper 
box described in section 2.5.4.1 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 15 during both the preliminary 
and official test periods. As noted in Table 15, 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 15) and (2) when 
defrosting, plus these same first 10 minutes after defrost 
termination (Sub-interval D, as described in Table 15). Evaluate 
compliance with Table 15 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 15 at equal intervals that span 10 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 fan 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 
heat pumps tested without an indoor fan installed, 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 7.8.3.1 and 7.8.3.2 of ASHRAE 
Standard 37-88 (incorporated by reference, see Sec.  430.22)) at 
equal intervals that span 10 minutes or less. Record the electrical 
energy consumed, expressed in watt-hours, from defrost termination 
to defrost termination, eDEFk(35), 
as well as the corresponding elapsed time in hours, 
[Delta][tau]FR.

    Table 15.--Test Operating and Test Condition Tolerances for Frost
                    Accumulation Heating Mode Tests.
------------------------------------------------------------------------
                                   Test operating tolerance      Test
                                              \1\             condition
                                  --------------------------  tolerance
                                       Sub-         Sub-      \2\  Sub-
                                    interval H   interval D   interval H
                                       \3\          \4\           3
------------------------------------------------------------------------
Indoor entering dry-bulb                   2.0      \5\ 4.0          0.5
 temperature, [deg]F.............
Indoor entering wet-bulb                   1.0  ...........  ...........
 temperature, [deg]F.............
Outdoor entering dry-bulb                  2.0         10.0          1.0
 temperature, [deg]F.............
Outdoor entering wet-bulb                  1.5  ...........          0.5
 temperature, [deg]F.............
External resistance to airflow,           0.05  ...........     0.02 \6\
 inches of water.................
Electrical voltage, % of rdg.....          2.0  ...........         1.5
------------------------------------------------------------------------
\1\ See Definition 1.41.
\2\ See Definition 1.40.
\3\ Applies when the heat pump is in the heating mode, except for the
  first 10 minutes after termination of a defrost cycle.
\4\ 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.
\5\ For heat pumps that turn off the indoor fan during the defrost
  cycle, the noted tolerance only applies during the 10 minute interval
  that follows defrost termination.
\6\ 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, 
Qhk(35), when expressed in units of Btu per 
hour, using:
[GRAPHIC] [TIFF OMITTED] TR11OC05.038

where,

V = 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] TR11OC05.039

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 fan 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 fan 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.

[[Page 59163]]

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.
    b. Evaluate average electrical power, 
Ehk(35), when expressed in units of watts, 
using:
[GRAPHIC] [TIFF OMITTED] TR11OC05.040

    For heat pumps tested without an indoor fan installed, increase 
Qhk(35) by,
[GRAPHIC] [TIFF OMITTED] TR11OC05.041

and increase Ehk(35) by,
[GRAPHIC] [TIFF OMITTED] TR11OC05.042

where Vs 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 fan, 
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 fan 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 fan 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 fan 
motor had the Frost Accumulation heating mode test been conducted at 
[Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TR11OC05.043

    5. Decrease the total heating capacity, 
Qhk(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, Ehk(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 to the value of 
1 in all cases except for heat pumps having a demand-defrost control 
system (Definition 1.21). For such qualifying heat pumps, evaluate 
Fdef using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.044

where,
[Delta][tau]def = the time between defrost terminations 
(in hours) or 1.5, whichever is greater.
[Delta][tau]max = maximum time between defrosts as 
allowed by the controls (in hours) or 12, whichever is less.
    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 Certified 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 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 
Qhk(17) and Ehk(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, from which 
Qhk(17) and Ehk(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 methods. 
Prior to evaluating if the energy balance specified in section 3.1.1 
is obtained, make an adjustment to account for the energy loss 
within the air duct that connects the indoor coil and the location 
where the outlet dry-bulb temperature is measured. If using the 
Outdoor Air Enthalpy Method, make an adjustment to account for the 
energy loss within the air duct that connects the outdoor coil and 
the location where the outlet temperature is measured. In all cases, 
apply the correction to the indoor space conditioning capacity that 
is determined using the secondary test method.
    3.11.1 If using the Outdoor Air Enthalpy Method as the secondary 
test method. During the ``official'' test, the outdoor air-side test 
apparatus described in section 2.10.1 is connected to the outdoor 
unit. To help compensate for any effect that the addition of this 
test apparatus may have on the unit's performance, conduct a 
``preliminary'' test where the outdoor air-side test apparatus is 
disconnected. Conduct a preliminary test prior to the first section 
3.2 steady-state cooling mode test and prior to the first section 
3.6 steady-state heating mode test. No other preliminary tests are 
required 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 a preliminary test prior to 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 If a preliminary test precedes the official test. a. 
The test conditions for the preliminary test are the same as 
specified for the official test. Connect the indoor air-side test 
apparatus to the indoor coil; disconnect 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 10 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., four 
consecutive 10-minute samples) is obtained where the Table 7 or 
Table 13, whichever applies, test tolerances are satisfied.
    b. After collecting 30 minutes of steady-state data, reconnect 
the outdoor air-side test apparatus to the unit. 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 when the outdoor 
air-side test apparatus was disconnected. Calculate the averages for 
the reconnected case using five or more consecutive readings taken 
at one minute intervals. Make these consecutive readings after re-
establishing equilibrium conditions and before initiating the 
official test.
    3.11.1.2 If a preliminary test does not precede the official 
test. Connect the outdoor-side test apparatus to the unit. Adjust 
the exhaust fan of the outdoor airflow measuring apparatus to 
achieve the same external static pressure as measured during the 
prior preliminary test conducted with the unit operating in the same 
cooling or heating mode at the same outdoor fan speed.
    3.11.1.3 Official test. a. Continue (preliminary test was 
conducted) or begin (no preliminary test) the official test by 
making measurements for both the Indoor and Outdoor Air Enthalpy 
Methods at equal intervals that span 10 minutes or less.

[[Page 59164]]

Discontinue these measurement only after obtaining a 30-minute 
period where the specified test condition and test operating 
tolerances are satisfied. To constitute a valid official test:
    (1) Achieve the energy balance specified in section 3.1.1; and,
    (2) For cases where a preliminary test is conducted, the 
capacities determined using the Indoor Air Enthalpy Method from the 
official and preliminary test periods must agree within 2.0 percent.
    b. For space cooling tests, calculate capacity from the outdoor 
air enthalpy measurements as specified in section 7.3.3.2 of ASHRAE 
Standard 37-88 (incorporated by reference, see Sec.  430.22). 
Calculate heating capacity based on outdoor air enthalpy 
measurements as specified in section 7.3.4.2 of the same ASHRAE 
Standard. Adjust outdoor side capacities according to section 
7.3.3.3 of ASHRAE Standard 37-88 (incorporated by reference, see 
Sec.  430.22) to account for line losses when testing split systems. 
Do not correct the average electrical power measurement as described 
in section 8.5.3 of ASHRAE Standard 37-88 (incorporated by 
reference, see Sec.  430.22).
    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 
[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 10 minutes or less. Determine average 
flow rate or average capacity from data sampled over a 30-minute 
period where the Table 7 (cooling) or the Table 13 (heating) 
tolerances are satisfied. Otherwise, conduct the calibration tests 
according to ASHRAE Standard 23-93 (incorporated by reference, see 
Sec.  430.22), ASHRAE Standard 41.9-00 (incorporated by reference, 
see Sec.  430.22), and section 7.5 of ASHRAE Standard 37-88 
(incorporated by reference, see Sec.  430.22).
    b. Calculate space cooling and space heating capacities using 
the compressor calibration method measurements as specified in 
sections 7.5.7 and 7.5.8, respectively, of ASHRAE Standard 37-88 
(incorporated by reference, see Sec.  430.22).
    3.11.3 If using the Refrigerant Enthalpy Method as the secondary 
test method. Conduct this secondary method according to section 7.6 
of ASHRAE Standard 37-88 (incorporated by reference, see Sec.  
430.22). Calculate space cooling and space heating capacities using 
the refrigerant enthalpy method measurements as specified in 
sections 7.6.4 and 7.6.5, 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 follows:
    1. For capacities less than 20,000 Btu/h, round to the nearest 
100 Btu/h.
    2. For capacities between 20,000 and 37,999 Btu/h, round to the 
nearest 200 Btu/h.
    3. For capacities between 38,000 and 64,999 Btu/h, round to the 
nearest 500 Btu/h.
    b. For the capacities used to perform the section 4 
calculations, however, round only to the nearest integer.
    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, evaluate the seasonal energy efficiency 
ratio,
[GRAPHIC] [TIFF OMITTED] TR11OC05.045

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.046

the ratio of the total space cooling provided during periods of the 
space 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 (N), Btu/h.
[GRAPHIC] [TIFF OMITTED] TR11OC05.047

the electrical energy consumed by the test unit during periods of 
the space 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 (N), W.
    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, use a 
building cooling load, BL(Tj). When referenced, evaluate 
BL(Tj) for cooling using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.049

where,
Qck=2(95) = the space cooling capacity 
determined from the A2 Test and calculated as specified 
in section 3.3, 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 an air conditioner or heat pump 
having a single-speed compressor that was tested with a fixed-speed 
indoor fan installed, a constant-air-volume-rate indoor fan 
installed, or with no indoor fan installed. a. Evaluate the seasonal 
energy efficiency ratio, expressed in units of Btu/watt-hour, using:

SEER = PLF(0.5) [middot] EERB
where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.050

the energy efficiency ratio determined from the B Test described in 
sections 3.2.1, 3.1.4.1, and 3.3, Btu/h per watt.
    PLF(0.5) = 1 - 0.5 [middot] CDc, the part-
load performance factor evaluated at a cooling load factor of 0.5, 
dimensionless.
    b. Refer to section 3.3 regarding the definition and calculation 
of Qc(82) and Ec(82). If the optional tests 
described in section 3.2.1 are not conducted, set the cooling mode 
cyclic degradation coefficient, CDc, to the 
default value specified in section

[[Page 59165]]

3.5.3. If these optional tests are conducted, set 
CDc to the lower of:
    1. The value calculated as per section 3.5.3; or
    2. The section 3.5.3 default value of 0.25.
    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 fan.
    4.1.2.1 Units covered by section 3.2.2.1 where indoor fan 
capacity modulation correlates with the outdoor dry bulb 
temperature. The manufacturer must provide information on how the 
indoor air volume rate or the indoor fan speed varies over the 
outdoor temperature range of 67 [deg]F to 102 [deg]F. Calculate SEER 
using Equation 4.1-1. Evaluate the quantity 
qc(Tj)/N in Equation 4.1-1 using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.052

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.053

whichever is less; the cooling mode load factor for temperature bin 
j, dimensionless.
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 16. Use Equation 4.1-2 to calculate the building 
load, BL(Tj). Evaluate Qc(Tj) 
using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.056

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.057

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] TR11OC05.058

the space cooling capacity of the test unit at outdoor temperature 
Tj if operated at the Cooling Certified Air Volume Rate, 
Btu/h.
    b. For units where indoor fan 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), 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 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,
[GRAPHIC] [TIFF OMITTED] TR11OC05.059

where,

PLFj = 1 - CDc [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. If the optional tests 
described in section 3.2.2.1 and Table 4 are not conducted, set the 
cooling mode cyclic degradation coefficient, 
CDc, to the default value specified in section 
3.5.3. If these optional tests are conducted, set 
CDc to the lower of:
    1. The value calculated as per section 3.5.3; or
    2.The section 3.5.3 default value of 0.25.
    d. Evaluate Ec(Tj) using,
    [GRAPHIC] [TIFF OMITTED] TR11OC05.060
    

[[Page 59166]]


where
[GRAPHIC] [TIFF OMITTED] TR11OC05.061

the electrical power consumption of the test unit at outdoor 
temperature Tj if operated at the Cooling Minimum Air 
Volume Rate, W.
[GRAPHIC] [TIFF OMITTED] TR11OC05.062

the electrical power consumption of the test unit at outdoor 
temperature Tj if operated at the Cooling Certified Air 
Volume Rate, W.
    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 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 where indoor fan 
capacity modulation is used to adjust the sensible to total cooling 
capacity ratio. Calculate SEER as specified in section 4.1.1.
    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, 
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] TR11OC05.063

[GRAPHIC] [TIFF OMITTED] TR11OC05.064

where Qck=1(95) and 
Eck=1(95) are determined from the 
A1 Test, Qck=1(82) and 
Eck=1(82) are determined from the 
B1 Test, and all are calculated as specified in section 
3.3. For two-capacity units that lock out low capacity operation at 
outdoor temperatures less than 95 [deg]F (but greater than 82 
[deg]F), use Equations 4.1.4-1 and 4.1.4-2 rather than Equations 
4.1.3-1 and 4.1.3-2 for estimating performance at low compressor 
capacity. 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] TR11OC05.065

[GRAPHIC] [TIFF OMITTED] TR11OC05.066

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.
    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), cycle between low and high capacity 
(section 4.1.3.2), or operate at high capacity (sections 4.1.3.3 and 
4.1.3.4) in responding to the building load. For units that lock out 
low capacity operation at higher outdoor temperatures, the 
manufacturer must supply information regarding this temperature 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] TR11OC05.067

where,
Xk=1(Tj) = BL(Tj)/
Qck=1(Tj), the cooling mode low 
capacity load factor for temperature bin j, dimensionless.
PLFj = 1 - CDc [middot] [1 - 
Xk=1(Tj)], the part load factor, 
dimensionless.
[GRAPHIC] [TIFF OMITTED] TR11OC05.068

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 16. Use Equations 4.1.3-1 and 4.1.3-2, 
respectively, to evaluate Qck=1(Tj) 
and Eck=1(Tj). If the optional 
tests described in section 3.2.3 and Table 5 are not conducted, set 
the cooling mode cyclic degradation coefficient, 
CDc, to the default value specified in section 
3.5.3. If these optional tests are conducted, set 
CDc to the lower of:

[[Page 59167]]

    a. The value calculated according to section 3.5.3; or
    b. The section 3.5.3 default value of 0.25.

               Table 16.--Distribution of Fractional Hours Within Cooling Season Temperature Bins
----------------------------------------------------------------------------------------------------------------
                                                                   Representative
                Bin number, j                  Bin temperature    temperature for       Fraction of of total
                                                 range [deg]F        bin [deg]F      temperature 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, 
Qck=1(Tj) < BL(Tj) < 
Qck=2(Tj).
[GRAPHIC] [TIFF OMITTED] TR11OC05.069

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.070

the cooling mode, low capacity load factor for temperature bin j, 
dimensionless.

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 16. 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) < 
Qck=2(Tj). This section applies to 
units that lock out low compressor capacity operation at higher 
outdoor temperatures.
[GRAPHIC] [TIFF OMITTED] TR11OC05.072

where,
Xk=2(Tj) = BL(Tj)/
Qck=2(Tj), the cooling mode high 
capacity load factor for temperature bin j, dimensionless.
PLFj = 1 - CDc [middot] [1 - 
Xk=2(Tj)], the part load factor, 
dimensionless.

    Obtain the fractional bin hours for the cooling season, 
nj/N, from Table 16. Use Equations 4.1.3-3 and 4.1.3-4, 
respectively, to evaluate Qck=2(Tj) 
and Eck=2(Tj). When evaluating the 
above equation for part load factor at high capacity, use the same 
value of CDc as used in the section 4.1.3.1 
calculations.
    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] TR11OC05.074

    Obtain the fractional bin hours for the cooling season, 
nj/N, from Table 16. 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, 
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,
[GRAPHIC] [TIFF OMITTED] TR11OC05.076

[GRAPHIC] [TIFF OMITTED] TR11OC05.077

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. 
Evaluate the space cooling capacity, 
Qck=2(Tj), and electrical power 
consumption, Eck=2(Tj), of the test 
unit when operating at maximum 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. Calculate the space cooling capacity, 
Qck=v(Tj), and electrical power 
consumption, Eck=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 6) EV Test using,

[[Page 59168]]

[GRAPHIC] [TIFF OMITTED] TR11OC05.078

[GRAPHIC] [TIFF OMITTED] TR11OC05.079

where Qck=v(87) and 
Eck=v(87) are determined from the 
EV Test and calculated as specified in section 3.3. 
Approximate the slopes of the k = v intermediate speed cooling 
capacity and electrical power input curves, MQ and 
ME, as follows:
[GRAPHIC] [TIFF OMITTED] TR11OC05.080

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.081

    Calculating Equation 4.1-1 quantities
    [GRAPHIC] [TIFF OMITTED] TR11OC05.082
    
differs depending upon whether the test unit would operate at 
minimum speed (section 4.1.4.1), operate at an intermediate speed 
(section 4.1.4.2), or operate at maximum speed (section 4.1.4.3) in 
responding to the building load. Use Equation 4.1-2 to calculate the 
building load, BL(Tj), for each temperature bin.
    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] TR11OC05.083

where,

Xk=1(Tj) = BL(Tj) / 
Qck=1(Tj), the cooling mode minimum 
speed load factor for temperature bin j, dimensionless.
PLFj = 1 - CDc [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 16. Use Equations 4.1.4-1 and 4.1.4-2, 
respectively, to evaluate Qck=1(Tj) 
and Eck=1(Tj). If the optional 
tests described in section 3.2.4 and Table 6 are not conducted, set 
the cooling mode cyclic degradation coefficient, 
CDc, to the default value specified in section 
3.5.3. If these optional tests are conducted, set 
CDc to the lower of:
    a. The value calculated according to section 3.5.3; or
    b. The section 3.5.3 default value of 0.25.
    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) < 
BL(Tj) < Qck=2(Tj).
[GRAPHIC] [TIFF OMITTED] TR11OC05.085

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] TR11OC05.086

the electrical power input required by the test unit when operating 
at a compressor speed of k = i and temperature Tj, W.

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 16. 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] Tj2.

    For each unit, determine the coefficients A, B, and C by 
conducting the following calculations once:
[GRAPHIC] [TIFF OMITTED] TR11OC05.088

where,

Tl = the outdoor temperature at which the unit, when 
operating at minimum compressor speed, provides a space cooling 
capacity that is equal to the

[[Page 59169]]

building load (Qck=1(T1) = 
BL(T1)), [deg]F. Determine T1 by equating 
Equations 4.1.4-1 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, provides a space cooling capacity 
that is equal to the building load (Q ck=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 maximum 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] TR11OC05.089

    4.1.4.3 Unit must operate continuously at maximum (k=2) 
compressor speed at temperature Tj, BL(Tj) >= 
Qck=2(Tj). Evaluate the Equation 
4.1-1 quantities
[GRAPHIC] [TIFF OMITTED] TR11OC05.090

as specified in section 4.1.3.4 with the understanding that 
Qck=2(Tj) and 
Eck=2(Tj) correspond to maximum 
compressor speed operation and are derived from the results of the 
tests specified in section 3.2.4.
    4.2 Heating Seasonal Performance Factor (HSPF) Calculations. 
Unless an approved alternative rating method is used, as set forth 
in 10 CFR 430.24(m), Subpart B, HSPF must be calculated as follows: 
Six generalized climatic regions are depicted in Figure 2 and 
otherwise defined in Table 17. For each of these regions and for 
each applicable standardized design heating requirement, evaluate 
the heating seasonal performance factor using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.091

where,

eh(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, 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 
4.2.5).

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 17.

j = the bin number, dimensionless.
J = for each generalized climatic region, the total number of 
temperature bins, dimensionless. Referring to Table 17, 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, 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 17.--Generalized Climatic Region Information
----------------------------------------------------------------------------------------------------------------
 
----------------------------------------------------------------------------------------------------------------
Region Number.................................      I          II        III         IV         V          VI
Heating Load Hours, HLH.......................        750       1250       1750       2250       2750      *2750
Outdoor Design Temperature, TOD...............         37         27         17          5        -10         30
                                               ------------
 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

[[Page 59170]]

 
 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] TR11OC05.096
    
where,

TOD = the outdoor design temperature, [deg]F. An outdoor 
design temperature is specified for each generalized climatic region 
in Table 17.
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 Definition 1.22), Btu/h.

    Calculate the minimum and maximum design heating requirements 
for each generalized climatic region as follows:
[GRAPHIC] [TIFF OMITTED] TR11OC05.097

and
[GRAPHIC] [TIFF OMITTED] TR11OC05.098

where Qhk(47) is expressed in units of Btu/h 
and otherwise defined as follows:

    1. For a single-speed heat pump tested as per section 3.6.1, 
Qhk(47) = Qh(47), the space heating 
capacity determined from the H1 Test.
    2. For a variable-speed heat pump, a section 3.6.2 single-speed 
heat pump, or a two-capacity heat pump not covered by item 3, 
Qnk(47) = Qnk=2(47), the 
space heating capacity determined from the H12 Test.
    3. For two-capacity, northern heat pumps (see Definition 1.46), 
Qkh(47) = Qk=1h(47), the 
space heating capacity determined from the H11 Test.
    If the optional H1N Test is conducted on a variable-
speed heat pump, the manufacturer has the option of defining 
Qkh(47) as specified above in item 2 or as 
Qkh(47)=Qk=Nh(47), the 
space heating capacity determined from the H1N 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 for all heat pumps, see either section 4.2.1, 
4.2.2, 4.2.3, or 4.2.4, whichever applies.
    For heat pumps with heat comfort controllers (see Definition 
1.28), 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 for the 
additional steps required for calculating the HSPF.

[[Page 59171]]



       Table 18.--Standardized Design Heating Requirements (Btu/h)
------------------------------------------------------------------------
 
------------------------------------------------------------------------
5,000..................................     25,000     50,000     90,000
10,000.................................     30,000     60,000    100,000
15,000.................................     35,000     70,000    110,000
20,000.................................     40,000     80,000    130,000
------------------------------------------------------------------------

    4.2.1 Additional steps for calculating the HSPF of a heat pump 
having a single-speed compressor that was tested with a fixed-speed 
indoor fan installed, a constant-air-volume-rate indoor fan 
installed, or with no indoor fan installed.
[GRAPHIC] [TIFF OMITTED] TR11OC05.099

[GRAPHIC] [TIFF OMITTED] TR11OC05.100

where,

[GRAPHIC] [TIFF OMITTED] TR11OC05.101

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 17. If the optional H1C Test described in section 3.6.1 is not 
conducted, set the heating mode cyclic degradation coefficient, 
CDh, to the default value specified in section 
3.8.1. If this optional test is conducted, set 
CDh to the lower of:
    a. The value calculated according to section 3.8.1 or
    b. The section 3.8.1 default value of 0.25.
    Determine the low temperature cut-out factor using
    [GRAPHIC] [TIFF OMITTED] TR11OC05.102
    
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] TR11OC05.103

[GRAPHIC] [TIFF OMITTED] TR11OC05.104


[[Page 59172]]


where Qh(47) and Eh(47) are determined from 
the H1 Test and calculated as specified in section 3.7; 
Qh(35) and Eh(35) are determined from the H2 
Test and calculated as specified in section 3.9.1; and 
Qh(17) and Eh(17) are determined from the H3 
Test and calculated as specified in section 3.10.
    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 fan. The manufacturer must provide information 
about how the indoor air volume rate or the indoor fan speed varies 
over the outdoor temperature range of 65 [deg]F to -23 [deg]F. 
Calculate the quantities

[GRAPHIC] [TIFF OMITTED] TR11OC05.105

in Equation 4.2-1 as specified in section 4.2.1 with the exception 
of replacing references to the H1C Test and section 3.6.1 with the 
H1C1 Test and section 3.6.2. In addition, evaluate the 
space heating capacity and electrical power consumption of the heat 
pump Qh(Tj) and Eh(Tj) 
using
[GRAPHIC] [TIFF OMITTED] TR11OC05.106

[GRAPHIC] [TIFF OMITTED] TR11OC05.107

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] TR11OC05.108

[GRAPHIC] [TIFF OMITTED] TR11OC05.109

For units where indoor fan speed is the primary control variable, 
FPhk=1 denotes the fan speed used during the 
required H11 and H31 Tests (see Table 10), 
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. Determine Qhk=1(35) 
and Ehk=1(35) as specified in section 3.6.2; 
determine Qhk=2(35) and 
Ehk=2(35) and from the H22 Test and 
the calculation specified in section 3.9. 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.
    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
[GRAPHIC] [TIFF OMITTED] TR11OC05.110

differs depending upon whether the heat pump would operate at low 
capacity (section 4.2.3.1), cycle between low and high capacity 
(Section 4.2.3.2), or operate at high capacity (sections 4.2.3.3 and 
4.2.3.4) in responding to the building load. For heat pumps that 
lock out low capacity operation at low outdoor temperatures, the 
manufacturer must supply information regarding the cutoff 
temperature(s) so that the appropriate equations can be selected.
    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

[[Page 59173]]

[GRAPHIC] [TIFF OMITTED] TR11OC05.111

[GRAPHIC] [TIFF OMITTED] TR11OC05.112

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. Determine 
Qhk=2(35) and Ehk=2(35) 
from the H22 Test and, if required as described in 
section 3.6.3, 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. Determine Qhk=2(17) and 
Ehk=2(17) from the H32 Test and, if 
required as described in section 3.6.3, 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.
    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) [gteqt] 
BL(Tj).
[GRAPHIC] [TIFF OMITTED] TR11OC05.113

[GRAPHIC] [TIFF OMITTED] TR11OC05.114

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.

    If the optional H0C1 Test described in section 3.6.3 
is not conducted, set the heating mode cyclic degradation 
coefficient, CDh, to the default value 
specified in section 3.8.1. If this optional test is conducted, set 
CDh to the lower of:
    a. The value calculated according to section 3.8.1; or
    b. The section 3.8.1 default value of 0.25.
    Determine the low temperature cut-out factor using
    [GRAPHIC] [TIFF OMITTED] TR11OC05.115
    
where Toff and Ton are defined in section 
4.2.1. Use the calculations given in section 4.2.3.3, 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

[[Page 59174]]

at a temperature Tj, 
Qhk=1(Tj) < BL(Tj) < 
Qhk=2(Tj).
Calculate
[GRAPHIC] [TIFF OMITTED] TR11OC05.116

using Equation 4.2.3-2. Evaluate
[GRAPHIC] [TIFF OMITTED] TR11OC05.117

using
[GRAPHIC] [TIFF OMITTED] TR11OC05.118

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.119

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. Calculate
[GRAPHIC] [TIFF OMITTED] TR11OC05.120

using Equation 4.2.3-2. Evaluate
[GRAPHIC] [TIFF OMITTED] TR11OC05.121

using
[GRAPHIC] [TIFF OMITTED] TR11OC05.122

where,

Xk=2(Tj)= BL(Tj)/
Qhk=2(Tj).
PLFj = 1 - CDh  [ 1 - 
Xk=2(Tj) ].

    When evaluating the above equation for part load factor at high 
capacity, use the same value of CDh as used in 
the section 4.2.3.1 calculations. 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] TR11OC05.123

Where
[GRAPHIC] [TIFF OMITTED] TR11OC05.124

    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] TR11OC05.125

[GRAPHIC] [TIFF OMITTED] TR11OC05.126

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. Evaluate the space heating capacity, 
Qhk=2(Tj), and electrical power 
consumption, Ehk=2(Tj), of the heat 
pump when operating at maximum compressor speed and outdoor 
temperature Tj by solving Equations 4.2.2-3 and 4.2.2-4, 
respectively, for k=2. Determine the Equation 4.2.2-3 and 4.2.2-4 
quantities Qhk=2(47) and 
Ehk=2(47) from the H12 Test and the 
calculations specified in section 3.7. 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 calculations specified in 
section 3.10. Calculate the space heating capacity, 
Qhk=v(Tj), and electrical power 
consumption, Ehk=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

[[Page 59175]]

[GRAPHIC] [TIFF OMITTED] TR11OC05.127

[GRAPHIC] [TIFF OMITTED] TR11OC05.128

where Qhk=v(35) and 
Ehk=v(35) are determined from the 
H2V Test and calculated as specified in section 3.9. 
Approximate the slopes of the k=v intermediate speed heating 
capacity and electrical power input curves, MQ and 
ME, as follows:
[GRAPHIC] [TIFF OMITTED] TR11OC05.129

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.130

[GRAPHIC] [TIFF OMITTED] TR11OC05.131

    Use Equations 4.2.4-1 and 4.2.4-2, respectively, to calculate 
Qhk=1(35) and Ehk=1(35).
    The calculation of Equation 4.2-1 quantities
    [GRAPHIC] [TIFF OMITTED] TR11OC05.132
    
differs depending upon whether the heat pump would operate at 
minimum speed (section 4.2.4.1), operate at an intermediate speed 
(section 4.2.4.2), or operate at maximum speed (section 4.2.4.3) in 
responding to the building load.
    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] TR11OC05.133

as specified in section 4.2.3.1. 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 with ``minimum speed'' and section 3.6.4. Also, the last 
sentence of section 4.2.3.1 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) < 
BL(Tj) < Qhk=2(Tj). 
Calculate
[GRAPHIC] [TIFF OMITTED] TR11OC05.134

using Equation 4.2.3-2 while evaluating
[GRAPHIC] [TIFF OMITTED] TR11OC05.135

using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.136

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.137

and [delta](Tj) is evaluated using Equation 4.2.3-3 
while,

Qhk=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.
COPk=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 
COPk=i(Tj) using,

COPk=i(Tj) = A + B . Tj + C . 
Tj2.

    For each heat pump, determine the coefficients A, B, and C by 
conducting the following calculations once:
[GRAPHIC] [TIFF OMITTED] TR11OC05.138

where,

T3 = the outdoor temperature at which the heat pump, when 
operating at minimum compressor speed, provides a space heating 
capacity that is equal to the building load 
(Qhk=1(T3) = BL(T3)), 
[deg]F. Determine T3 by equating Equations 4.2.4-1 and 
4.2-2 and solving for:

[[Page 59176]]

[GRAPHIC] [TIFF OMITTED] TR11OC05.139

outdoor temperature.

Tvh = the outdoor temperature at which the heat pump, 
when operating at the intermediate compressor speed used during the 
section 3.6.4 H2V Test, provides a space heating capacity 
that is equal to the building load 
(Qhk=v(Tvh) = BL(Tvh)), 
[deg]F. Determine Tvh by equating Equations 4.2.4-3 and 
4.2-2 and solving for outdoor temperature.
T4 = the outdoor temperature at which the heat pump, when 
operating at maximum compressor speed, provides a space heating 
capacity that is equal to the building load 
(Qhk=2(T4) = BL(T4)), 
[deg]F. Determine T4 by equating Equations 4.2.2-3 (k=2) 
and 4.2-2 and solving for outdoor temperature.
[GRAPHIC] [TIFF OMITTED] TR11OC05.140

[GRAPHIC] [TIFF OMITTED] TR11OC05.141

    4.2.4.3 Heat pump must operate continuously at maximum (k=2) 
compressor speed at temperature Tj, BL(Tj) >= 
Qhk=2(Tj). Evaluate the Equation 
4.2-1 quantities
[GRAPHIC] [TIFF OMITTED] TR11OC05.142

as specified in section 4.2.3.4 with the understanding that 
Qhk=2(Tj) and 
Ehk=2(Tj) correspond to maximum 
compressor speed operation and are derived from the results of the 
specified section 3.6.4 tests.
    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.
    4.2.5.1 Heat pump having a heat comfort controller: additional 
steps for calculating the HSPF of a heat pump having a single-speed 
compressor that was tested with a fixed-speed indoor fan installed, 
a constant-air-volume-rate indoor fan installed, or with no indoor 
fan installed. 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 (Equations 4.2.1-4 and 4.2.1-5) 
for each outdoor bin temperature, Tj, that is listed in 
Table 17. 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] TR11OC05.143

where Vs, Vmx, v'n (or 
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 17, calculate 
the nominal temperature of the air leaving the heat pump condenser 
coil using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.144

    Evaluate eh(Tj/N), RH(Tj)/N, 
X(Tj), PLFj, and [delta](Tj) as 
specified in section 4.2.1. 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), determine Qh(Tj) and 
Eh(Tj) as specified in section 4.2.1 (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] TR11OC05.145

where,


[[Page 59177]]


[GRAPHIC] [TIFF OMITTED] TR11OC05.146

[GRAPHIC] [TIFF OMITTED] TR11OC05.147


    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 
fan. 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 (Equations 4.2.2-1 and 4.2.2-2) for each 
outdoor bin temperature, Tj, that is listed in Table 17. 
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] TR11OC05.148

where VS, Vmx, v'n (or 
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 17, calculate 
the nominal temperature of the air leaving the heat pump condenser 
coil using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.149

    Evaluate eh(Tj)/N , RH(Tj)/N, 
X(Tj), PLFj, and [delta](Tj) as 
specified in section 4.2.1 with the exception of replacing 
references to the H1C Test and section 3.6.1 with the 
H1C1 Test and section 3.6.2. 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), determine Qh(Tj) and 
Eh(Tj) as specified in section 4.2.2 (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,

Qh(Tj) = Qhp(Tj) + 
QCC(Tj)

Eh(Tj) = Ehp(Tj) + 
ECC(Tj)

where,

QCC(Tj) = mda [middot] 
Cp,da [middot] [TCC - 
To(Tj)]
[GRAPHIC] [TIFF OMITTED] TR11OC05.150


    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 for both high and low capacity 
and at each outdoor bin temperature, Tj, that is listed 
in Table 17. 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] TR11OC05.151

where Vs, Vmx, v'n (or 
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 17, calculate 
the nominal temperature of the air leaving the heat pump condenser 
coil when operating at low capacity using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.152

    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 17, calculate the nominal 
temperature of the air leaving the heat pump condenser coil when 
operating at high capacity using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.153

    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, 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), determine 
Qhk=1(Tj) and 
Ehk=1(Tj) as specified in section 
4.2.3 (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,

Qhk=1(Tj) = 
Qhpk=1(Tj) + 
QCCk=1(Tj)

Ehk=1(Tj) = 
Ehpk=1(Tj) + 
ECCk=1(Tj)

where,

[[Page 59178]]

[GRAPHIC] [TIFF OMITTED] TR11OC05.154


    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 (i.e., Qhk=2(Tj) = 
Qhpk=2(Tj) and 
Ehk=2(Tj) = 
Ehpk=2(Tj)). Note: Even though 
Tok=2(Tj) < TCC, 
resistive heating may be required; evaluate RH(Tj)/N for 
all bins.
    Case 4. For outdoor bin temperatures where 
Tok=2(Tj) < TCC, 
determine Qhk=2(Tj) and 
Ehk=2(Tj) using,
[GRAPHIC] [TIFF OMITTED] TR11OC05.155

where,
[GRAPHIC] [TIFF OMITTED] TR11OC05.156


    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 HSPF of a heat pump having a variable-
speed compressor. [Reserved]
    4.3 Calculations of the Actual and Representative Regional 
Annual Performance Factors for Heat Pumps.
    4.3.1 Calculation of actual regional annual performance factors 
(APFA) for a particular location and for each 
standardized design heating requirement.
[GRAPHIC] [TIFF OMITTED] TR11OC05.157

where,

CLHA = the actual cooling hours for a particular location 
as determined using the map given in Figure 3, hr.
Qck(95) = the space cooling capacity of the 
unit as determined from the A or A2 Test, whichever 
applies, Btu/h.
HLHA = the actual heating hours for a particular location 
as determined using the map given in Figure 2, hr.
DHR = the design heating requirement used in determining the HSPF; 
refer to section 4.2 and Definition 1.22, Btu/h.
C = defined in section 4.2 following Equation 4.2-2, dimensionless.
SEER = the seasonal energy efficiency ratio calculated as specified 
in section 4.1, Btu/W[middot]h.
HSPF = the heating seasonal performance factor calculated as 
specified in section 4.2 for the generalized climatic region that 
includes the particular location of interest (see Figure 2), Btu/
W[middot]h. The HSPF should correspond to the actual design heating 
requirement (DHR), if known. If it does not, it may correspond to 
one of the standardized design heating requirements referenced in 
section 4.2.

    4.3.2 Calculation of representative regional annual performance 
factors (APFR) for each generalized climatic region and 
for each standardized design heating requirement.
[GRAPHIC] [TIFF OMITTED] TR11OC05.158

where,

CLHR = the representative cooling hours for each 
generalized climatic region, Table 19, hr.
HLHR = the representative heating hours for each 
generalized climatic region, Table 19, hr.
HSPF = the heating seasonal performance factor calculated as 
specified in section 4.2 for the each generalized climatic region 
and for each standardized design heating requirement within each 
region, Btu/W.h.

    The SEER, Qck(95), DHR, and C are the same 
quantities as defined in section 4.3.1. Figure 2 shows the 
generalized climatic regions. Table 18 lists standardized design 
heating requirements.

[[Page 59179]]



    Table 19.--Representative Cooling and Heating Load Hours for Each
                       Generalized Climatic Region
------------------------------------------------------------------------
                      Region                           CLHR       HLHR
------------------------------------------------------------------------
I.................................................       2400        750
II................................................       1800       1250
III...............................................       1200       1750
IV................................................        800       2250
V.................................................        400       2750
VI................................................        200       2750
------------------------------------------------------------------------

    4.4. Rounding of SEER, HSPF, and APF for reporting purposes. 
After calculating SEER according to section 4.1, round it off as 
specified in subpart B 430.23(m)(3)(i) of Title 10 of the Code of 
Federal Regulations. Round section 4.2 HSPF values and section 4.3 
APF values as per Sec.  430.23(m)(3)(ii) and (iii) of Title 10 of 
the Code of Federal Regulations.
[GRAPHIC] [TIFF OMITTED] TR11OC05.172


[[Page 59180]]


[GRAPHIC] [TIFF OMITTED] TR11OC05.173


0
6. Section 430.32 of subpart C is amended by revising the section 
heading and adding introductory text to paragraph (c) to read as 
follows:


Sec.  430.32  Energy conservation standards and effective dates.

* * * * *
    (c) Central air conditioners and heat pumps. The energy 
conservation standards defined in terms of the heating seasonal 
performance factor are based on Region IV, the minimum standardized 
design heating requirement, and the sampling plan stated in Sec.  
430.24(m).
* * * * *
[FR Doc. 05-15601 Filed 10-7-05; 8:45 am]
BILLING CODE 6450-01-U