[Federal Register Volume 81, Number 199 (Friday, October 14, 2016)]
[Rules and Regulations]
[Pages 70923-70925]
From the Federal Register Online via the Government Publishing Office [www.gpo.gov]
[FR Doc No: 2016-24869]



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  Federal Register / Vol. 81, No. 199 / Friday, October 14, 2016 / 
Rules and Regulations  

[[Page 70923]]



DEPARTMENT OF ENERGY

10 CFR Part 430

[Docket Number EERE-2014-BT-TP-0014]
RIN 1904-AD22


Energy Conservation Program: Test Procedures for Portable Air 
Conditioners; Correction

AGENCY: Office of Energy Efficiency and Renewable Energy, Department of 
Energy.

ACTION: Correcting amendments.

-----------------------------------------------------------------------

SUMMARY: The U.S. Department of Energy (DOE) published a final rule in 
the Federal Register on June 1, 2016, establishing test procedures for 
portable air conditioners. This correction addresses typographical 
errors in that final rule that were included in Title 10 of the Code of 
Federal Regulations (CFR) part 430, subpart B, appendix CC. Neither the 
errors nor the corrections in this document affect the substance of the 
rulemaking or any of the conclusions reached in support of the final 
rule.

DATES: This correction is effective October 14, 2016.

FOR FURTHER INFORMATION CONTACT: Mr. Bryan Berringer, U.S. Department 
of Energy, Office of Energy Efficiency and Renewable Energy, Building 
Technologies Office, EE-5B, 1000 Independence Avenue SW., Washington, 
DC 20585-0121. Telephone: (202) 586-0371. Email: 
[email protected].
    Ms. Sarah Butler, U.S. Department of Energy, Office of the General 
Counsel, Mailstop GC-33, 1000 Independence Ave. SW., Washington, DC 
20585-0121. Telephone: (202) 586-1777. Email: [email protected].

SUPPLEMENTARY INFORMATION: On June 1, 2016, DOE published a final rule 
(the ``June 2016 final rule'') to establish test procedures for 
portable air conditioners. 81 FR 35241. DOE has since found that the 
June 2016 final rule contained minor typographical errors in Title 10 
of the Code of Federal Regulations (CFR) part 430, subpart B, appendix 
CC. This final rule correction revises appendix CC to subpart B of 10 
CFR part 430, to correct these typographical errors. Specifically, in 
section 4.1.1, DOE is correcting the following errors: An incorrect 
subscript for the variable Tduct_SD_j in the 
Qduct_SD equation and missing subscripts ``j'' on the 
Tduct variables in the equations for Qduct_95 and 
Qduct_83. In section 4.1.2, DOE is correcting the following 
errors: A missing equals sign and parenthesis; incorrect subscripts for 
the variable Cp_da and the infiltration air variables in the 
Qs_95 equation; incorrect subscripts in the infiltration air 
variables in the Qs_83 equation; missing equals signs in the 
Ql_95 and Ql_83 equations; and missing ``Q'' 
variables and incorrect subscripts for the Ql_95 and 
Ql_83 variables in the Qinfiltration_95 and 
Qinfiltration_83 equations.
    DOE also found that the summation symbols in the two dual-duct 
Qduct equations in section 4.1.1 were not properly 
represented in the Electronic Code of Federal Regulations (eCFR).
    Neither the errors nor the corrections in this document affect the 
substance of the rulemaking or any of the conclusions reached in 
support of the final rule. Accordingly, DOE finds that there is good 
cause under 5 U.S.C. 553(b)(B) to not issue a separate notice to 
solicit public comment on the corrections contained in this final rule 
as doing so would be impractical, unnecessary, and contrary to the 
public interest. For the same reasons and pursuant to 5 U.S.C. 553(d), 
DOE finds good cause to waive the 30-day delay in effective date.

Procedural Issues and Regulatory Review

    DOE has concluded that the determinations made pursuant to the 
various procedural requirements to the June 2016 final rule that 
originally codified DOE's test procedures for portable air conditioners 
remain unchanged for this final rule technical correction. 81 FR 35241. 
The amendments from that final rule became effective July 1, 2016. Id.

List of Subjects in 10 CFR Part 430

    Administrative practice and procedure, Confidential business 
information, Energy conservation, Household appliances, Imports, 
Intergovernmental relations, Reporting and recordkeeping requirements, 
and Small businesses.

    Issued in Washington, DC, on October 7, 2016.
Kathleen Hogan,
Deputy Assistant Secretary for Energy Efficiency, Energy Efficiency and 
Renewable Energy.

    For the reasons set forth in the preamble, DOE amends part 430 of 
title 10, Code of Federal Regulations by making the following 
correcting amendments:

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. Appendix CC to subpart B of part 430 is amended by revising sections 
4.1.1 and 4.1.2 to read as follows:

Appendix CC to Subpart B of Part 430- Uniform Test Method for Measuring 
the Energy Consumption of Portable Air Conditioners

* * * * *
    4. * * *
    4.1.1. Duct Heat Transfer. Measure the surface temperature of 
the condenser exhaust duct and condenser inlet duct, where 
applicable, throughout the cooling mode test. Calculate the average 
temperature at each individual location, and then calculate the 
average surface temperature of each duct by averaging the four 
average temperature measurements taken on that duct. Calculate the 
surface area (Aduct_j) of each duct according to:

Aduct_j = [pi] x dj x Lj

Where:

dj = the outer diameter of duct ``j'', including any 
manufacturer-supplied insulation.
Lj = the extended length of duct ``j'' while under test.
j represents the condenser exhaust duct and, for dual-duct units, 
the condenser exhaust duct and the condenser inlet duct.

    Calculate the total heat transferred from the surface of the 
duct(s) to the indoor conditioned space while operating in cooling mode 
for the outdoor test conditions in Table 1 of this appendix, as 
follows. For single-duct portable air conditioners:

Qduct_SD = h x Aduct_j x (Tduct_SD_j-
Tei)


[[Page 70924]]


For dual-duct portable air conditioners:

Qduct_95 = [sum]j{h x Aduct_j x 
(Tduct_95_j-Tei){time} 
Qduct_83 = [sum]j{h x Aduct_j x 
(Tduct_83_j-Tei){time} 

Where:

Qduct_SD = for single-duct portable air conditioners, the 
total heat transferred from the duct to the indoor conditioned space 
in cooling mode when tested according to the test conditions in 
Table 1 of this appendix, in Btu/h.
Qduct_95 and Qduct_83 = for dual-duct portable 
air conditioners, the total heat transferred from the ducts to the 
indoor conditioned space in cooling mode, in Btu/h, when tested 
according to the 95[emsp14][deg]F dry-bulb and 83 [deg]F dry-bulb 
outdoor test conditions in Table 1 of this appendix, respectively.
h = convection coefficient, 3 Btu/h per square foot per [deg]F.
Aduct_j = surface area of duct ``j'', in square feet.
Tduct_SD_j = average surface temperature for the 
condenser exhaust duct of single-duct portable air conditioners, as 
measured during testing according to the test condition in Table 1 
of this appendix, in [deg]F.
Tduct_95_j and Tduct_83_j = average surface 
temperature for duct ``j'' of dual-duct portable air conditioners, 
as measured during testing according to the two outdoor test 
conditions in Table 1 of this appendix, in [deg]F.
j represents the condenser exhaust duct and, for dual-duct units, 
the condenser exhaust duct and the condenser inlet duct.
Tei = average evaporator inlet air dry-bulb temperature, 
in [deg]F.

    4.1.2 Infiltration Air Heat Transfer. Measure the heat contribution 
from infiltration air for single-duct portable air conditioners and 
dual-duct portable air conditioners that draw at least part of the 
condenser air from the conditioned space. Calculate the heat 
contribution from infiltration air for single-duct and dual-duct 
portable air conditioners for both cooling mode outdoor test 
conditions, as described in this section. Calculate the dry air mass 
flow rate of infiltration air according to the following equations:
[GRAPHIC] [TIFF OMITTED] TR14OC16.001

    For dual-duct portable air conditioners:
    [GRAPHIC] [TIFF OMITTED] TR14OC16.002
    

    Where:

mSD = dry air mass flow rate of infiltration air for 
single-duct portable air conditioners, in pounds per minute (lb/m).
m95 and m83 = dry air mass flow rate of 
infiltration air for dual-duct portable air conditioners, as 
calculated based on testing according to the test conditions in 
Table 1 of this appendix, in lb/m.
Vco_SD, Vco_95, and Vco_83 = 
average volumetric flow rate of the condenser outlet air during 
cooling mode testing for single-duct portable air conditioners; and 
at the 95 [deg]F and 83 [deg]F dry-bulb outdoor conditions for dual-
duct portable air conditioners, respectively, in cubic feet per 
minute (cfm).
Vci_95, and Vci_83 = average volumetric flow 
rate of the condenser inlet air during cooling mode testing at the 
95 [deg]F and 83 [deg]F dry-bulb outdoor conditions for dual-duct 
portable air conditioners, respectively, in cfm.
[rho]co_SD, [rho]co_95, and 
[rho]co_83 = average density of the condenser outlet air 
during cooling mode testing for single-duct portable air 
conditioners, and at the 95[emsp14][deg]F and 83[emsp14][deg]F dry-
bulb outdoor conditions for dual-duct portable air conditioners, 
respectively, in pounds mass per cubic foot (lbm/ft\3\).
[rho]ci_95, and [rho]ci_83 = average density 
of the condenser inlet air during cooling mode testing at the 
95[emsp14][deg]F and 83[emsp14][deg]F dry-bulb outdoor conditions 
for dual-duct portable air conditioners, respectively, in 
lbm/ft\3\.
[omega]co_SD, [omega]co_95, and 
[omega]co_83 = average humidity ratio of condenser outlet 
air during cooling mode testing for single-duct portable air 
conditioners, and at the 95[emsp14][deg]F and 83[emsp14][deg]F dry-
bulb outdoor conditions for dual-duct portable air conditioners, 
respectively, in pounds mass of water vapor per pounds mass of dry 
air (lbw/lbda).
[omega]ci_95, and [omega]ci_83 = average 
humidity ratio of condenser inlet air during cooling mode testing at 
the 95[emsp14][deg]F and 83[emsp14][deg]F dry-bulb outdoor 
conditions for dual-duct portable air conditioners, respectively, in 
lbw/lbda.

    For single-duct and dual-duct portable air conditioners, calculate 
the sensible component of infiltration air heat contribution according 
to:

Qs_95 = m x 60
x [cp\da x (Tia\95 - Tindoor))
+ (cp_wv x ([omega]ia\95 x Tia\95 - [omega]indoor 
x Tindoor))]
Qs\83 = m x 60
x [(cp\da x Tia\83 - Tindoor
+ (cp\wv x ([omega]ia\83 x Tia\83 - [omega]indoor 
x Tindoor))]

Where:

Qs_95 and Qs_83 = sensible heat added to the 
room by infiltration air, calculated at the 95[emsp14][deg]F and 
83[emsp14][deg]F dry-bulb outdoor conditions in Table 1 of this 
appendix, in Btu/h.
m = dry air mass flow rate of infiltration air, mSD or 
m95 when calculating Qs_95 and mSD 
or m83 when calculating Qs_83, in lb/m.
cp_da = specific heat of dry air, 0.24 Btu/lbm 
- [deg]F.
cp_wv = specific heat of water vapor, 0.444 Btu/
lbm - [deg]F.
Tindoor = indoor chamber dry-bulb temperature, 
80[emsp14][deg]F.
Tia_95 and Tia_83 = infiltration air dry-bulb 
temperatures for the two test conditions in Table 1 of this 
appendix, 95[emsp14][deg]F and 83[emsp14][deg]F, respectively.
[omega]ia_95 and [omega]ia_83 = humidity 
ratios of the 95[emsp14][deg]F and 83[emsp14][deg]F dry-bulb 
infiltration air, 0.0141 and 0.01086 lbw/lbda, 
respectively.
[omega]indoor = humidity ratio of the indoor chamber air, 
0.0112 lbw/lbda.
60 = conversion factor from minutes to hours.

    Calculate the latent heat contribution of the infiltration air 
according to:

Ql\95 = m x 60 x Hfg x ([omega]ia\95 - [omega]indoor)
Ql\83 = m x 60 x Hfg x ([omega]ia\83 - 
[omega]indoor)

Where:

Ql_95 and Ql_83 = latent heat added to the 
room by infiltration air, calculated at the 95[deg]F and 83[deg]F 
dry-bulb outdoor conditions in Table 1 of this appendix, in Btu/h.
m = mass flow rate of infiltration air, mSD or 
m95 when calculating Ql_95 and mSD 
or m83 when calculating Ql_83, in lb/m.
Hfg = latent heat of vaporization for water vapor, 1061 
Btu/lbm.
[omega]ia_95 and [omega]ia_83 = humidity 
ratios of the 95 [deg]F and 83 [deg]F dry-bulb infiltration air, 
0.0141 and 0.01086 lbw/lbda, respectively.
[omega]indoor = humidity ratio of the indoor chamber air, 
0.0112 lbw/lbda. 60 = conversion factor from 
minutes to hours.

    The total heat contribution of the infiltration air is the sum of 
the sensible and latent heat:
Qinfiltration\95 = Qs\95 + Ql\95

[[Page 70925]]

Qinfiltration\83 = Qs\83 + Q 83

Where:

Qinfiltration_95 and Qinfiltration_83 = total 
infiltration air heat in cooling mode, calculated at the 95 [deg]F 
and 83 [deg]F dry-bulb outdoor conditions in Table 1 of this 
appendix, in Btu/h.
Qs_95 and Qs_83 = sensible heat added to the 
room by infiltration air, calculated at the 95 [deg]F and 83 [deg]F 
dry-bulb outdoor conditions in Table 1 of this appendix, in Btu/h.
Ql_95 and Ql_83 = latent heat added to the 
room by infiltration air, calculated at the 95 [deg]F and 83 [deg]F 
dry-bulb outdoor conditions in Table 1 of this appendix, in Btu/h.

* * * * *
[FR Doc. 2016-24869 Filed 10-13-16; 8:45 am]
 BILLING CODE 6450-01-P