```

[Federal Register Volume 80, Number 37 (Wednesday, February 25, 2015)]
[Proposed Rules]
[Pages 10211-10248]
From the Federal Register Online via the Government Printing Office [www.gpo.gov]
[FR Doc No: 2015-03589]

[[Page 10211]]

Vol. 80

Wednesday,

No. 37

February 25, 2015

Part II

Department of Energy

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10 CFR Parts 429 and 430

Energy Conservation Program: Test Procedures for Portable Air 
Conditioners; Proposed Rule

Federal Register / Vol. 80 , No. 37 / Wednesday, February 25, 2015 / 
Proposed Rules

[[Page 10212]]

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DEPARTMENT OF ENERGY

10 CFR Parts 429 and 430

[Docket No. EERE-2014-BT-TP-0014]
RIN 1904-AD22

Energy Conservation Program: Test Procedures for Portable Air 
Conditioners

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

ACTION: Notice of proposed rulemaking.

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SUMMARY: The U.S. Department of Energy (DOE) proposes to establish test 
procedures for portable air conditioners (ACs) in accordance with the 
guidance and requirements set forth by the Energy Policy and 
Conservation Act to establish technologically feasible, economically 
justified energy conservation standards for products identified by 
specific criteria to provide national energy savings through improved 
energy efficiency. The proposed test procedures are based upon industry 
methods to determine energy consumption in active modes, off-cycle 
mode, standby modes, and off mode, with certain modifications to ensure 
the test procedures are repeatable and representative. The proposed 
test procedure would create a new appendix CC, which would be used to 
determine capacities and energy efficiency metrics that could be the 
basis for any future energy conservation standards for portable ACs. 
DOE also proposes adding a sampling plan and rounding requirements for 
portable ACs, necessary when certifying capacity and efficiency of a 
basic model.

DATES:  DOE will accept comments, data, and information regarding this 
notice of proposed rulemaking (NOPR) before and after the public 
meeting, but no later than May 11, 2015. See section V, ``Public 
Participation,'' for details.
    DOE will hold a public meeting on Wednesday, March 18, 2015, from 9 
a.m. to 12 p.m., in Washington, DC. The meeting will also be broadcast 
as a webinar. See section V, ``Public Participation,'' for webinar 
registration information, participant instructions, and information 
about the capabilities available to webinar participants.

ADDRESSES: The public meeting will be held at the U.S. Department of 
Energy, Forrestal Building, Room 8E-089, 1000 Independence Avenue SW., 
Washington, DC 20585. To attend, please notify Ms. Brenda Edwards at 
(202) 586-2945. See section V Public Participation for additional 
meeting information.
    Any comments submitted must identify the NOPR for Test Procedures 
for Portable Air Conditioners, and provide docket number EERE-2014-BT-
TP-0014 and/or regulatory information number (RIN) number 1904-AD22. 
Comments may be submitted using any of the following methods:
    1. Federal eRulemaking Portal: www.regulations.gov. Follow the 
instructions for submitting comments.
    2. Email: PortableAC2014TP0014@ee.doe.gov. Include the docket 
number and/or RIN in the subject line of the message.
    3. Mail: Ms. Brenda Edwards, U.S. Department of Energy, Building 
Technologies Program, Mailstop EE-5B, 1000 Independence Avenue SW., 
Washington, DC 20585-0121. If possible, please submit all items on a 
CD. It is not necessary to include printed copies.
    4. Hand Delivery/Courier: Ms. Brenda Edwards, U.S. Department of 
Energy, Building Technologies Program, 950 L'Enfant Plaza, SW., Suite 
600, Washington, DC 20024. Telephone: (202) 586-2945. If possible, 
please submit all items on a CD. It is not necessary to include printed 
copies.
    For detailed instructions on submitting comments and additional 
information on the rulemaking process, see section V of this document 
(Public Participation).
    Docket: The docket, which includes Federal Register notices, public 
meeting attendee lists and transcripts, comments, and other supporting 
documents/materials, is available for review at regulations.gov. All 
documents in the docket are listed in the regulations.gov index. 
However, some documents listed in the index, such as those containing 
information that is exempt from public disclosure, may not be publicly 
available.
    A link to the docket Web page can be found at: http://www.regulations.gov/#!docketDetail;D=EERE-2014-BT-TP-0014. This Web 
page will contain a link to the docket for this notice on the 
regulations.gov site. The regulations.gov Web page will contain simple 
instructions on how to access all documents, including public comments, 
in the docket. See section VII for information on how to submit 
comments through regulations.gov.
    For further information on how to submit a comment, review other 
public comments and the docket, or participate in the public meeting, 
contact Ms. Brenda Edwards at (202) 586-2945 or by email: 
Brenda.Edwards@ee.doe.gov.

FOR FURTHER INFORMATION CONTACT: Mr. Bryan Berringer, U.S. Department 
of Energy, Office of Building Technology Programs, Appliance Standards 
Division, 950 L'Enfant Plaza SW. Room 603, Washington, DC 20585-0121. 
Telephone: 202-586-0371. Email: Bryan.Berringer@ee.doe.gov.
    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: Sarah.Butler@hq.doe.gov.

SUPPLEMENTARY INFORMATION: DOE intends to incorporate by reference the 
following industry standards into 10 CFR part 430: Portable Air 
Conditioners AHAM PAC-1-2014, 2014.
    Copies of AHAM PAC-1-2014 can be obtained from the Association of 
Home Appliance Manufacturers, 1111 19th Street NW., Suite 402, 
Washington, DC 20036, 202-872-5955, or by going to http://www.aham.org/ht/d/ProductDetails/sku/PAC12009/from/714/pid/.

Table of Contents

I. Authority and Background
    A. General Test Procedure Rulemaking Process
    B. Test Procedure for Portable Air Conditioners
II. Summary of the Notice of Proposed Rulemaking
III. Discussion
    A. Products Covered by the Proposed Test Procedure
    B. Determination, Classification, and Testing Provisions for 
Operational Modes
    1. Active Modes
    a. Cooling Mode
    b. Heating Mode
    2. Off-Cycle Mode
    3. Standby Mode and Off Mode
    a. Mode Definitions
    b. Determination of Standby Mode and Off Mode Power Consumption
    4. Combined Energy Efficiency Ratio
    a. CEER Calculations
    b. Mode Annual Operating Hours
    C. Sampling Plan and Rounding Requirements
    D. Compliance With Other Energy Policy and Conservation Act 
Requirements
    1. Test Burden
    2. Potential Incorporation of International Electrotechnical 
Commission Standard 62087
IV. Procedural Issues and Regulatory Review
    A. Review Under Executive Order 12866
    B. Review under the Regulatory Flexibility Act
    C. Review Under the Paperwork Reduction Act of 1995
    D. Review Under the National Environmental Policy Act of 1969
    E. Review Under Executive Order 13132
    F. Review Under Executive Order 12988
    G. Review Under the Unfunded Mandates Reform Act of 1995
    H. Review Under the Treasury and General Government 
Appropriations Act, 1999

[[Page 10213]]

    I. Review Under Executive Order 12630
    J. Review Under Treasury and General Government Appropriations 
Act, 2001
    K. Review Under Executive Order 13211
    L. Review Under Section 32 of the Federal Energy Administration 
Act of 1974
    M. Description of Materials Incorporated by Reference
V. Public Participation
    A. Attendance at Public Meeting
    B. Procedure for Submitting Prepared General Statements for 
Distribution
    C. Conduct of Public Meeting
    D. Submission of Comments
    E. Issues on Which DOE Seeks Comment
VI. Approval of the Office of the Secretary

I. Authority and Background

    Title III of the Energy Policy and Conservation Act (EPCA), as 
amended (42 U.S.C. 6291, et seq.; ``EPCA'' or, ``the Act'') sets forth 
various provisions designed to improve energy efficiency. Part A of 
title III of EPCA (42 U.S.C. 6291-6309) establishes the ``Energy 
Conservation Program for Consumer Products Other Than Automobiles,'' 
which covers consumer products and certain commercial products 
(hereinafter referred to as ``covered products'').\1\ EPCA authorizes 
DOE to establish technologically feasible, economically justified 
energy conservation standards for covered products or equipment that 
would be likely to result in significant national energy savings. (42 
U.S.C. 6295(o)(2)(B)(i)(I)-(VII)) In addition to specifying a list of 
covered consumer and industrial products, EPCA contains provisions that 
enable the Secretary of Energy to classify additional types of consumer 
products as covered products. (42 U.S.C. 6292(a)(20)) For a given 
product to be classified as a covered product, the Secretary must 
determine that:
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    \1\ For editorial reasons, upon codification in the U.S. Code, 
Part B was re-designated Part A.
---------------------------------------------------------------------------

    (1) Classifying the product as a covered product is necessary for 
the purposes of EPCA; and
    (2) The average annual per-household energy use by products of each 
type is likely to exceed 100 kilowatt-hours (kWh) per year. (42 U.S.C. 
6292(b)(1))
    To prescribe an energy conservation standard pursuant to 42 U.S.C. 
6295(o) and (p) for covered products added pursuant to 42 U.S.C. 
6292(b)(1), the Secretary must also determine that:
    (1) The average household energy use of the products has exceeded 
150 kWh per household for a 12-month period;
    (2) The aggregate 12-month energy use of the products has exceeded 
4.2 terawatt-hours (TWh);
    (3) Substantial improvement in energy efficiency is technologically 
feasible; and
    (4) Application of a labeling rule under 42 U.S.C. 6294 is unlikely 
to be sufficient to induce manufacturers to produce, and consumers and 
other persons to purchase, covered products of such type (or class) 
that achieve the maximum energy efficiency that is technologically 
feasible and economically justified. (42 U.S.C. 6295(l)(1))
    Under EPCA, the energy conservation program consists essentially of 
four parts: (1) Testing, (2) labeling, (3) Federal energy conservation 
standards, and (4) certification and enforcement procedures. The 
testing requirements consist of test procedures that manufacturers of 
covered products must use as the basis for: (1) Certifying to DOE that 
their products comply with the applicable energy conservation standards 
adopted under EPCA, and (2) making representations about the efficiency 
of those products. Similarly, DOE must use these test procedures to 
determine whether the products comply with any relevant standards 
promulgated under EPCA.

A. General Test Procedure Rulemaking Process

    Under 42 U.S.C. 6293, EPCA sets forth the criteria and procedures 
DOE must follow when prescribing or amending test procedures for 
covered products. EPCA provides in relevant part that any test 
procedures prescribed or amended under this section shall be reasonably 
designed to produce test results that measure energy efficiency, energy 
use or estimated annual operating cost of a covered product during a 
representative average use cycle or period of use and shall not be 
unduly burdensome to conduct. (42 U.S.C. 6293(b)(3))
    In addition, if DOE determines that a test procedure should be 
prescribed or amended, it must publish proposed test procedures and 
offer the public an opportunity to present oral and written comments on 
them. (42 U.S.C. 6293(b)(2))

B. Test Procedure for Portable Air Conditioners

    There are currently no DOE test procedures or energy conservation 
standards for portable ACs. On July 5, 2013, DOE issued a notice of 
proposed determination (NOPD) of coverage (hereinafter referred to as 
the ``July 2013 NOPD''), in which DOE announced that it tentatively 
determined that portable ACs meet the criteria under 42 U.S.C. 
6292(b)(1) to be classified as a covered product. 78 FR 40403. DOE 
estimated that 973.7 thousand portable AC units were shipped in North 
America in 2012, with a projected growth to 1743.7 thousand units by 
2018, representing nearly 80-percent growth in 6 years.\2\ Id. at 
40404. In addition, DOE estimated the average per-household electricity 
consumption by portable ACs to be approximately 650 kWh per year. Id.
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    \2\ Transparency Media Research, ``Air Conditioning Systems 
Market--Global Scenario, Trends, Industry Analysis, Size, Share and 
Forecast, 2012-2018,'' January 2013.
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    In response to the July 2013 NOPD, DOE received comments from 
interested parties on several topics regarding appropriate test 
procedures for portable ACs that DOE should consider if it issues a 
final determination classifying portable ACs as a covered product.
    On May 9, 2014, DOE published in the Federal Register a notice of 
data availability (NODA) (hereinafter referred to as the ``May 2014 
NODA''), in which it agreed that a DOE test procedure for portable ACs 
would provide consistency and clarity for representations of energy use 
of these products. DOE evaluated available industry test procedures to 
determine whether such methodologies would be suitable for 
incorporation in a future DOE test procedure, should DOE determine to 
classify portable ACs as a covered product. DOE conducted testing on a 
range of portable ACs to determine typical cooling capacities and 
cooling energy efficiencies based on the existing industry test methods 
and other modified approaches for portable ACs. 79 FR 26639, 26640 (May 
9, 2014).
    As discussed above, DOE also recently initiated a separate 
rulemaking to consider establishing energy conservation standards for 
portable ACs. Any new standards would be based on the same efficiency 
metrics derived from the test procedure that DOE would adopt in a final 
rule in this rulemaking.

II. Summary of the Notice of Proposed Rulemaking

    In this NOPR, DOE proposes to establish in Title 10 of the Code of 
Federal Regulations (CFR), section 430.2, the definition of portable AC 
that was initially proposed in the July 2013 NOPD, modified to 
distinguish from room ACs and dehumidifiers.
    DOE also proposes to establish in 10 CFR part 430, subpart B, a 
test procedure for single-duct and dual-duct portable ACs that would 
provide an accurate representation of performance in active modes, 
standby modes, and off mode. Because spot cooler portable ACs do not 
provide net cooling to a conditioned space, DOE is not proposing test 
procedures for these products in this NOPR. The proposed active mode 
testing methodology would utilize the Association of Home

[[Page 10214]]

Appliance Manufacturers (AHAM) portable AC test procedure (AHAM PAC-1) 
to measure cooling capacity and cooling energy efficiency ratio 
(EERcm), with additional provisions to account for heat 
transferred to the indoor conditioned space from the case, ducts, and 
any infiltration air from unconditioned spaces. DOE also proposes to 
clarify for such active mode testing (1) test duct configuration; (2) 
instructions for condensate collection; (3) control settings for 
operating mode, fan speed, temperature set point, and louver 
oscillation; and (4) unit placement within the test chamber. DOE 
proposes to define this operating mode as ``cooling mode'' to 
distinguish it from other active modes, such as ``heating mode.''
    For those single-duct and dual-duct portable ACs that incorporate a 
heating function, DOE proposes additional testing methodology for 
measuring energy use in heating mode similar to the methodology 
proposed for the measurement of cooling capacity and EERcm, 
except that testing conditions would be specified that are 
representative of ambient conditions when portable ACs would be used 
for heating purposes. The proposed test procedure includes a measure of 
heating capacity and heating energy efficiency ratio 
(EERhm).
    The proposed single-duct and dual-duct portable AC test procedure 
also includes a measure of energy use in off-cycle mode, which occurs 
when the ambient dry-bulb temperature reaches the setpoint. This may 
include operation of the fan either continuously or cyclically without 
activating the refrigeration (or heating) system, or periods in standby 
mode when the fan is not operating.
    In this NOPR, DOE identifies and discusses all relevant low-power 
modes, including bucket-full mode, delay-start mode, inactive mode, and 
off mode. DOE also proposes definitions for inactive mode and off mode, 
and proposes test procedures to determine energy consumption 
representative of each of these low-power modes based on the procedures 
outlined in the standard published by the International 
Electrotechnical Commission (IEC), titled ``Household electrical 
appliances--Measurement of standby power,'' Publication 62301, Edition 
2.0 (2011-01) (hereinafter referred to as ``IEC Standard 62301'').
    In addition, DOE proposes a combined energy efficiency ratio (CEER) 
metric to be used in reporting the overall energy efficiency of a 
single-duct and dual-duct portable AC. The CEER metric would represent 
energy use in all available operating modes. DOE also proposes to 
define a separate CEER metric for cooling mode that would also apply to 
units that include heating mode and would be a common metric used for 
comparison among portable ACs. DOE also proposes an EER metric to 
represent performance in cooling and heating modes that could be used 
to compare cooling and heating performance with other similar products.
    Finally, DOE proposes adding a sampling plan and rounding 
requirements for portable ACs to a new section 10 CFR 429.62. These 
instructions are necessary when certifying capacity and efficiency of a 
basic model.

III. Discussion

A. Products Covered by the Proposed Test Procedure

    A portable AC is a self-contained, refrigeration-based product 
that, similar to a room AC, removes latent and sensible heat from the 
ambient air in a single space such as a room. Similar to room ACs, 
portable ACs are standalone appliances designed to operate 
independently of any other air treatment devices, though they may also 
be used in conjunction with other pre-existing air treatment devices. 
However, unlike room ACs, portable ACs are not designed as a unit to be 
mounted in a window or through the wall. Portable ACs are placed in the 
conditioned space and may have flexible ducting, typically connected to 
a window to remove condenser outlet air from the conditioned space.
    DOE is generally aware of 3 categories of portable ACs including 
single-duct models, dual-duct models, and spot coolers. Single-duct 
portable ACs utilize a single condenser exhaust duct to vent heated air 
to the unconditioned space. Other configurations include dual-duct, 
which intakes some or all condenser air from and exhausts to 
unconditioned space, and spot coolers, which have no ducting on the 
condenser side and may utilize small directional ducts on the 
evaporator exhaust. Spot coolers are often used in applications that 
require cooling in one localized zone and can tolerate exhaust heat 
outside of this zone.
    In the July 2013 NOPD, DOE proposed to define ``portable air 
conditioner'' as:
    A consumer product, other than a ``packaged terminal air 
conditioner'' which is powered by a single-phase electric current and 
which is an encased assembly designed as a portable unit that may rest 
on the floor or other elevated surface for the purpose of providing 
delivery of conditioned air to an enclosed space. It includes a prime 
source of refrigeration and may include means for ventilating and 
heating. 78 FR 40403, 40404 (July 5, 2013).
    DOE maintained this proposed definition in the May 2014 NODA. In 
the July 2013 NOPD, DOE also stated that portable ACs are moveable 
units typically designed to provide 8,000 to 14,000 British thermal 
units per hour (Btu/h) of cooling capacity for a single room. Id.
    In response to the proposed definition, Pacific Gas and Electric 
Company, Southern California Gas Company, San Diego Gas and Electric, 
and Southern California Edison (hereinafter referred to as the 
``California Investor-Owned Utilities (IOUs)'') and Edison Electric 
Institute (EEI) stated that the requirement in the definition to be 
powered by a single-phase electric current may exclude some equipment 
designed for commercial applications. The California IOUs encouraged 
DOE to consider a large range of portable ACs, both residential and 
commercial, to ensure that all potential savings are examined and 
analyzed. In particular, the California IOUs recommended that DOE 
consider covering portable ACs with capacities above 14,000 Btu/h 
because there are units currently on the market with cooling capacities 
up to and above 65,000 Btu/h. (California IOUs, NOPD No. 5 at pp. 1-2; 
\3\ EEI, NOPD No. 3 at p. 5) EEI also commented that DOE should 
consider revising the definition of ``portable air conditioner'' to 
ensure that three-phase electrical current units are covered, and to 
better reflect products that currently are on the market with and 
without heating capability. (EEI, NOPD No. 3 at p. 5)
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    \3\ A notation in the form ``California IOUs, NOPD No. 5 at pp. 
1-2'' identifies a written comment: (1) Made by Pacific Gas and 
Electric Company, San Diego Gas and Electric Company, and Southern 
California Edison (``the California IOUs''); (2) recorded in 
document number 5 that is filed in the docket of the rulemaking for 
determination of coverage of portable air conditioners as a covered 
consumer product (Docket No. EERE-2013- BT-STD-0033) and available 
for review at www.regulations.gov; and (3) which appears on pages 1-
2 of document number 5.
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    Oceanaire Inc. (Oceanaire) commented that according to the EPCA 
definition, commercial spot coolers (portable ACs that do not have 
ducting attached to the condenser) are not covered products. According 
to Oceanaire, commercial spot coolers are mainly used in the rental 
market where emergencies create a need for immediate and focused 
cooling systems, with example applications including food and cosmetics 
processing plants,

[[Page 10215]]

outdoor entertainment venues, and steel processing factories. Oceanaire 
noted that the cooling capacity of these rental units range between 1 
and 5 tons (12,000 to 60,000 Btu/h), where actual performance is 
determined by a wide range of operating environments, which may include 
high and low temperatures, high humidity, and corrosive conditions that 
are not experienced in household applications. Further, Oceanaire noted 
that its commercial product construction is robust, comprising mainly 
18 gauge and thicker steel cabinetry and support structures. 
(Oceanaire, No. 2 at pp. 1-2 \4\)
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    \4\ A notation in the form ``Oceanaire, No. 2 at pp. 1-2'' 
identifies a written comment: (1) Made by Oceanaire, Inc. 
(Oceanaire); (2) recorded in document number 2 that is filed in the 
docket of the portable air conditioner test procedure rulemaking 
(Docket No. EERE-2014- BT-TP-0014) and available for review at 
www.regulations.gov; and (3) which appears on pages 1-2 of document 
number 2.
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    Portable ACs, most commonly in single-duct or dual-duct 
configuration, typically range in cooling capacity from 5,000 to 14,000 
Btu/h when measured according to existing industry test methods. 
According to sizing charts provided by vendors, these portable ACs are 
intended to cool rooms of up to approximately 525 square feet in 
area,\5\ are often heavier than 50 pounds, and so are designed with 
wheels to provide mobility from room to room. Spot coolers, a category 
of portable ACs under DOE's proposed definition, are typically intended 
for larger spaces and harsher applications. Most have cooling 
capacities greater than 14,000 Btu/h, when measured according to 
existing industry test methods, and are typically larger than single-
duct and dual-duct portable ACs, often weighing more than 100 pounds. 
Because they are frequently moved from site to site, spot coolers are 
more rugged in construction, although they also have wheels to maintain 
portability. During interviews, manufacturers indicated that spot 
cooler shipments represent no more than approximately 1.5 percent of 
the total portable AC market in the United States, and that only about 
half of those shipments are for spot coolers with single-phase, 120-
volt, and 60-Hertz power supply requirements (the power supply 
appropriate for consumer products). Additionally, manufacturers noted 
that the spot coolers typically incorporate more powerful and louder 
blowers, condensate collection without auto-evaporation, and larger 
case sizes than typical single-duct and dual-duct portable ACs. 
Manufacturer interviews confirmed that spot coolers are often rented on 
a seasonal or emergency basis, unlike other portable ACs, which are 
generally purchased for regular use on a seasonal or occasional basis. 
Based on these considerations, DOE is not considering a test procedure 
for spot coolers at this time even though DOE believes spot coolers 
would meet the proposed definition of portable AC if DOE finalizes the 
coverage determination as proposed.
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    \5\ For example: www.air-n-water.com/portable-ac-size.htm.
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    DOE recognizes that certain portable ACs also include options for 
operating as a dehumidifier and/or heater, with heating means provided 
by either an electric resistance heater or by modifying internal 
refrigerant flow to operate the unit as a heat pump. The 
dehumidification function may be achieved in some units by decreasing 
fan speeds, removing the condenser duct(s), and for some units, 
disabling the self-evaporative feature by draining the condensate 
before it reaches the condenser coils or deactivating the condensate 
slinger fan when the controls are set to dehumidification mode. In all 
of these cases, the air flow pattern and psychrometrics differ 
fundamentally from those of a dehumidifier, resulting in different 
energy efficiencies during dehumidification operation, even though both 
products may use a refrigeration system to remove moisture from the 
air.
    DOE also recognizes that although room ACs and portable ACs share 
many of the same components that operate similarly to provide cooled 
air to a conditioned space, a portable AC, unlike a room AC, may be 
entirely located within the conditioned space so that some or all of 
the condenser air may be drawn from that space, and some heat from the 
refrigeration system and ducting is transferred to the conditioned 
space as well. These differences would lead to differing cooling mode 
energy efficiencies between room ACs and portable ACs, even if the 
products were to incorporate the same components. In addition, 
operation of the portable AC without activation of the refrigeration 
system may be more accurately characterized as ``air circulation'' 
rather than ``ventilation'' because the portable AC may be operated 
without drawing air from outside the conditioned space. Thus, DOE 
proposes to clarify in the definition of ``portable air conditioner'' 
that the primary function of the product is to provide cooled, 
conditioned air to the space in addition to other functions such as air 
circulation or heating, and that it is a product other than a room AC 
or dehumidifier. DOE also proposes to restructure the portable AC 
definition to align with both the room AC and dehumidifier definitions. 
In sum, DOE proposes to add to 10 CFR 430.2 the following definition 
for ``portable air conditioner.''
    An encased assembly, other than a ``packaged terminal air 
conditioner,'' ``room air conditioner,'' or ``dehumidifier,'' designed 
as a portable unit for delivering cooled, conditioned air to an 
enclosed space, that is powered by single-phase electric current, which 
may rest on the floor or other elevated surface. It includes a source 
of refrigeration and may include additional means for air circulation 
and heating.
    Although this proposed definition differs from the definition 
presented in the July 2013 NOPD, DOE maintains its tentative 
determination that portable ACs qualify as a covered product under Part 
A of Title III of EPCA, as amended. A product may be added as a covered 
product, pursuant to 42 U.S.C. 6292(b)(1), if (1) classifying products 
of such type as covered products is necessary and appropriate to carry 
out the purposes of EPCA; and (2) the average per-household energy use 
by products of such type is likely to exceed 100 kWh (or its Btu 
equivalent) per year. As discussed in the July 2013 NOPD, DOE 
determined that portable ACs meet the first requirement because: 
Shipments are projected to increase 80 percent over a 6-year period 
from 2012 to 2017, coverage of portable ACs would allow for 
conservation of energy through labeling programs and the regulation of 
portable AC energy efficiency, and there is significant variation in 
the annual energy consumption of different portable AC models currently 
available on the market. 78 FR 40403, 40404 (July 5, 2013). For the 
second requirement, DOE determined that a typical portable AC uses 
approximately 650 kWh/year, well above the 100 kWh/year threshold. 78 
FR 40403, 40404-40405 (July 5, 2013). The updated portable AC 
definition proposed in this NOPR only includes additional clarification 
to differentiate portable ACs from dehumidifiers and room ACs, it does 
not alter the intended scope of the definition. Accordingly, the 
determinations from the July 2013 NOPD remain valid for the revised 
proposed portable AC definition.
    DOE also proposes to include in the new test procedure at appendix 
CC the following definitions for different portable AC configurations 
to clarify the testing provisions to be used to obtain representative 
results for cooling capacity, heating capacity (where applicable), and 
CEER:
    ``Single-duct portable air conditioner'' means a portable air 
conditioner that

[[Page 10216]]

draws all of the condenser inlet air from the conditioned space without 
the means of a duct, and discharges the condenser outlet air outside 
the conditioned space through a single duct.
    ``Dual-duct portable air conditioner'' means a portable air 
conditioner that draws some or all of the condenser inlet air from 
outside the conditioned space through a duct, and may draw additional 
condenser inlet air from the conditioned space. The condenser outlet 
air is discharged outside the conditioned space by means of a separate 
duct.
    DOE is also proposing a definition for ``spot cooler'' as a 
portable air conditioner that draws condenser inlet air from and 
discharges condenser outlet air to the conditioned space, and draws 
evaporator inlet air from and discharges evaporator outlet air to a 
localized zone within the conditioned space. DOE is proposing such a 
definition in this NOPR to clarify that testing these products would 
not be required at this time, as discussed previously in this section.
    DOE requests comment on these proposed definitions for portable ACs 
and their specific configurations, including the proposal that spot 
coolers not be addressed in this rulemaking.

B. Determination, Classification, and Testing Provisions for 
Operational Modes

1. Active Modes
    Portable ACs are typically purchased by consumers to provide cooled 
air to a conditioned space, although certain models provide additional 
functions such as heating, dehumidification, and air circulation. 
Because room ACs and dehumidifiers share many of the same internal 
components and incorporate some of the same operating modes as portable 
ACs, DOE considered the mode definitions for these products to develop 
applicable mode definitions for portable ACs.
    Appendix F of title 10, part 430, subpart B of the CFR defines 
``active mode'' for room ACs as a mode in which the room AC is 
connected to a mains power source, has been activated and is performing 
the main function of cooling or heating the conditioned space, or 
circulating air through activation of its fan or blower, with or 
without energizing active air-cleaning components or devices such as 
ultraviolet (UV) radiation, electrostatic filters, ozone generators, or 
other air-cleaning devices. Appendix X within that same subpart of the 
CFR defines ``active mode'' for dehumidifiers as a mode in which a 
dehumidifier is connected to a mains power source, has been activated, 
and is performing the main functions of removing moisture from air by 
drawing moist air over a refrigerated coil using a fan, or circulating 
air through activation of the fan without activation of the 
refrigeration system.
    Portable ACs provide the same main functions as room ACs: (1) 
Cooling with activation of the refrigeration system and blower or fan; 
(2) for certain models, heating by means of activation of a blower or 
fan and either the refrigeration system and a reverse-cycle solenoid 
valve or a resistance heater; or (3) air circulation by activating only 
the blower or fan. As with dehumidifiers, a portable AC evaporator may 
also experience frosting and may need to perform a defrost operation. 
DOE, therefore, proposes the following definition for portable AC 
active mode:
    ``Active mode'' means a mode in which the portable air conditioner 
is connected to a mains power source, has been activated, and is 
performing the main functions of cooling or heating the conditioned 
space, circulating air through activation of its fan or blower without 
activation of the refrigeration system, or defrosting the refrigerant 
coil.
    DOE proposes to designate active mode functions performed when the 
temperature setpoint is not yet reached as either ``cooling mode'' or 
``heating mode,'' depending upon the user-selected function.
    Portable ACs may also operate in ``off-cycle mode,'' during which 
the fan or blower may operate without activation of the refrigeration 
system after the temperature setpoint has been reached. Under these 
conditions, the fan may be operated to ensure that air is drawn over 
the thermostat to monitor ambient conditions, or for air circulation in 
the conditioned space. It is also possible that immediately following a 
period of cooling or heating, fan operation may be initiated to remove 
any remaining frost or moisture from the evaporator. Although the 
periods of fan operation would classify those periods of off-cycle mode 
as an active mode, DOE notes that the portable AC may also enter one or 
more periods of a standby mode during off-cycle mode, in which the fan 
or blower does not operate. Therefore, DOE proposes to define off-cycle 
mode to include all periods of fan operation and standby mode that 
occur when the temperature set point has been reached, and further 
proposes to measure the energy consumption during off-cycle mode 
according to methodology discussed in section III.B.2 of this NOPR.
    Portable ACs may also operate in a consumer-selected mode during 
which the blower is operated with all other cooling or heating 
components disabled. The blower may operate cyclically or continuously 
to circulate air in the conditioned space. DOE refers to this consumer-
selected, active mode as ``air-circulation mode.'' DOE does not 
currently have information on the usage of this consumer-initiated air 
circulation feature and, therefore is not proposing to measure energy 
usage during ``air-circulation mode.'' However, DOE seeks information 
on annual hours associated with this mode.
    Some portable ACs also include a dehumidification or ``dry'' 
function. DOE learned through manufacturer interviews that portable AC 
operation in this mode is adjusted to maximize latent rather than 
sensible heat removal, typically by decreasing the evaporator fan or 
blower speed. Though not always specified in the user manual, when 
operating in dry mode, the installation may be modified to direct 
condenser exhaust into the conditioned space. In this case, a drain 
setup is necessary to remove condensate before it passes over the 
condenser to be re-evaporated into the condenser exhaust. Though the 
evaporator and condenser outlet air streams are not fully mixed, the 
net effect is minimal heating or cooling within the conditioned space 
and a reduction in relative humidity. DOE considered addressing 
dehumidification performance as part of this test procedure proposal, 
and determined that it is not technically feasible to combine 
dehumidification performance, in units of liters per kWh, with a 
cooling or heating performance, in units of Btu/Wh. Because 
dehumidification is not the primary mode of operation for portable ACs, 
DOE does not believe that the annual operating hours in 
dehumidification mode would be significant and would therefore not 
substantially impact a metric that considers the combined annual energy 
consumption of each operating mode. DOE's tentative conclusion is 
supported by a recent field study conducted by Burke, et al., 
(hereinafter referred to as the Burke Portable AC Study), in which 
portable ACs were monitored over multiple summer months in 19 locations 
in New York and Pennsylvania.\6\ No users in this study reported 
operating their portable AC in dehumidification mode. DOE also notes

[[Page 10217]]

that including dehumidification mode in a portable AC test procedure 
would significantly and disproportionately increase test burden. 
Therefore, DOE does not propose to include dehumidification mode as an 
operating mode to be addressed in a portable AC test procedure.
---------------------------------------------------------------------------

    \6\ T. Burke, et al., Using Field-Metered Data to Quantify 
Annual Energy Use of Portable Air Conditioners, Lawrence Berkeley 
National Laboratory, Report No. LBNL-6868E (December 2014). 
Available at: www.osti.gov/scitech/servlets/purl/1166989.
---------------------------------------------------------------------------

    In summary, DOE proposes to include the following definitions in 
new appendix CC to clarify the types of portable AC operation within 
active mode:
    ``Cooling mode'' means an active mode in which a portable air 
conditioner has activated the main cooling function according to the 
thermostat or temperature sensor signal, including activating the 
refrigeration system, or the fan or blower without activation of the 
refrigeration system.
    ``Heating mode'' means an active mode in which a portable air 
conditioner has activated the main heating function according to the 
thermostat or temperature sensor signal, including activating a 
resistance heater, the refrigeration system with a reverse refrigerant 
flow valve, or the fan or blower without activation of the resistance 
heater or refrigeration system.
    Further discussion of off-cycle mode, including a proposed 
definition, is included in section III.2 of this NOPR.
a. Cooling Mode
    As discussed in the May 2014 NODA, DOE identified three industry 
test procedures that measure portable AC performance in cooling mode 
and that are applicable to products sold in North America:

    (1) AHAM PAC-1-2009 ``Portable Air Conditioners'' (AHAM PAC-1-
2009) specifies cooling mode testing conducted in accordance with 
American National Standards Institute (ANSI)/American Society of 
Heating, Refrigerating, and Air-Conditioning Engineers (ASHRAE) 
Standard 37-2005 ``Methods of Testing for Rating Electrically Driven 
Unitary Air-Conditioning and Heat Pump Equipment'' (ANSI/ASHRAE 
Standard 37-2005).\7\ The metrics incorporated in AHAM PAC-1-2009 
include capacity and energy efficiency ratio (EER) for the following 
configurations: Single-Duct, Dual-Duct, Spot Cooling, and Water 
Cooled Condenser.
---------------------------------------------------------------------------

    \7\ ANSI/ASHRAE Standard 37 was updated in 2009. DOE reviewed 
the 2005 and 2009 versions and concluded there would be no 
measurable difference in portable air conditioner results obtained 
from each. Therefore, DOE utilized ANSI/ASHRAE Standard 37-2009 when 
testing according to AHAM PAC-1-2009.
---------------------------------------------------------------------------

    (2) Canadian Standards Association (CSA) C370-2013 ``Cooling 
Performance of Portable Air Conditioners'' (CSA C370-2013) is 
harmonized with AHAM PAC-1-2009, and thus also incorporates testing 
provisions from ANSI/ASHRAE Standard 37-2009.
    (3) ANSI/ASHRAE Standard 128-2011 ``Method of Rating Unitary 
Spot Air Conditioners'' (ANSI/ASHRAE Standard 128-2011) is adapted 
from the previous 2009 version of CSA C370. It too references ANSI/
ASHRAE Standard 37-2009. The previous version of ANSI/ASHRAE 
Standard 128, published in 2001, is required by California 
regulations to be used to certify spot cooler performance for such 
products sold in that State. A key difference between ANSI/ASHRAE 
Standard 128-2011 and ANSI/ASHRAE Standard 128-2001 is that the 
older version specifies a higher indoor ambient testing temperature, 
which increases measured cooling capacity and EER. 79 FR 26639, 
26640-26641 (May 9, 2014).

    DOE found no significant differences that would produce varying 
results among the three test procedures. The aforementioned versions of 
the AHAM, CSA, and ASHRAE test procedures each measure cooling capacity 
and EER based on an air enthalpy approach that measures the airflow 
rate, dry-bulb temperature, and water vapor content of air at the inlet 
and outlet of the indoor (evaporator) side. In addition, for air-cooled 
portable ACs with cooling capacity less than 135,000 Btu/h, which 
include the products that are the subject of this NOPR, the indoor air 
enthalpy results must be validated by measuring cooling capacity by 
either an outdoor air enthalpy method or a compressor calibration 
method. As explained in the May 2014 NODA, DOE selected the outdoor air 
enthalpy method for its investigative testing to minimize test burden 
because it only requires additional metering components, similar to 
those used for the indoor air enthalpy method. DOE conducted initial 
testing according to AHAM PAC-1-2009 to establish baseline capacities 
and efficiencies of a preliminary sample of test units according to the 
existing industry test procedures. 79 FR 26639, 26641 (May 9, 2014).
    To investigate the contribution of operational factors on the 
apparent reduction in cooling capacity observed for units in the field, 
DOE compared the results of AHAM PAC-1-2009 testing with the results of 
additional testing with a test room calorimeter approach based on ANSI/
ASHRAE Standard 16-1983 (RA 99), ``Method of Testing for Rating Room 
Air Conditioners and Packaged Terminal Air Conditioners'' (ANSI/ASHRAE 
Standard 16-1983), with certain modifications to allow testing of 
portable ACs. The room calorimeter approach allowed DOE to determine 
the cooling capacity of a portable AC that accounts for any air 
infiltration effects and heat transfer to the conditioned space through 
gaps in the product case and seams in the duct connections, along with 
an associated EER. Values of these performance metrics measured 
accordingly may more accurately reflect real-world portable AC 
operation. In that test series, DOE also investigated cooling capacity 
and EER as a function of the infiltration air temperature for single-
duct and dual-duct units, and the effect of condenser exhaust air 
entrainment at the intake for dual-duct portable ACs. DOE presented the 
results of this preliminary testing in the May 2014 NODA. 79 FR 26639, 
26643-26648 (May 9, 2014).
    Although AHAM PAC-1-2009, CSA C370-2013, and ANSI/ASHRAE Standard 
128-2011, all reference the test setup and methodology from ANSI/ASHRAE 
Standard 37, AHAM PAC-1-2009 did not specify the particular sections in 
ANSI/ASHRAE Standard 37 that are to be used. However, AHAM recently 
published an updated version of its portable AC test procedure, AHAM 
PAC-1-2014, that references specific sections in ANSI/ASHRAE Standard 
37 for equipment setup, cooling capacity determination, power input 
determination, data recording, and results reporting, consistent with 
the approach in CSA C370-2013 and ANSI/ASHRAE Standard 128-2011. These 
clarifications will likely improve testing reproducibility by 
eliminating different possible interpretations of the provisions to 
reference from ANSI/ASHRAE Standard 37. AHAM also slightly revised the 
evaporator inlet and condenser inlet temperatures for its standard 
rating conditions in AHAM PAC-1-2014, in order to harmonize with the 
temperatures specified in CSA C370-2013 and ANSI/ASHRAE Standard 128-
2011. Conditions that had been specified as 80 degrees Fahrenheit 
([deg]F) dry-bulb temperature and 67 [deg]F wet-bulb temperature were 
adjusted to 80.6 [deg]F/66.2 [deg]F, and conditions that had been 
specified as 95 [deg]F/75 [deg]F were adjusted to 95 [deg]F/75.2 
[deg]F. DOE did not identify other substantive changes between the 2009 
and 2014 versions of AHAM PAC-1 that would affect testing results.
    For the May 2014 NODA, DOE conducted an initial round of 
performance testing on a preliminary sample of test units 
representative of products available at that time on the U.S. market. 
The test sample included a total of eight portable ACs (four single-
duct, two dual-duct, and two spot coolers), covering a range of rated 
cooling capacities (8,000-13,500 Btu/h) and EERs (7.0-11.2 Btu per 
watt-hour (Btu/Wh)). Following publication of the May 2014 NODA, DOE 
performed additional testing on a larger set of test units. This second 
test sample included a total of eighteen portable ACs; thirteen

[[Page 10218]]

single-duct and 5 dual-duct \8\ units, expanding the range of rated 
cooling capacities (5,000-14,000 Btu/h) and the maximum rated EER to 
12.1 Btu/Wh. DOE did not include any spot coolers in the second test 
sample because it is not proposing testing provisions for them at this 
time for reasons discussed in section IIII.A of this NOPR.
---------------------------------------------------------------------------

    \8\ One of the dual-duct units was shipped with a conversion kit 
to enable testing in single-duct configuration. DOE performed all 
tests on this ``convertible'' unit in both single-duct and dual-duct 
configurations.
---------------------------------------------------------------------------

    Because DOE does not currently regulate portable ACs, manufacturers 
may advertise or market their products using any available test 
procedure. For those models that are included in the California Energy 
Commission (CEC) product database and that are sold in California, 
however, manufacturers must report cooling capacity and EER according 
to ANSI/ASHRAE Standard 128-2001. DOE notes that the cooling capacities 
and EERs obtained from using ANSI/ASHRAE Standard 128-2001 are higher 
than those obtained using the current ANSI/ASHRAE Standard 128-2011, 
primarily due to higher temperature evaporator inlet air in the 2001 
version of the test procedure.\9\
---------------------------------------------------------------------------

    \9\ ANSI/ASHRAE Standard 128-2011 specifies 80.6 degrees [deg]F 
dry-bulb temperature and 66.2 [deg]F wet-bulb temperature for the 
standard rating conditions for the evaporator inlet of dual-duct 
portable ACs and both the evaporator and condenser inlets of single-
duct units. It also specifies standard rating conditions of 95 
[deg]F dry-bulb temperature and 75.2 [deg]F wet-bulb temperature for 
the condenser inlet side of dual-duct portable ACs and both the 
evaporator and condenser inlets of spot coolers. ANSI/ASHRAE 
Standard 128-2001 specifies 95 [deg]F dry-bulb temperature and 83 
[deg]F wet-bulb temperature for the standard rating conditions for 
both the evaporator and condenser inlets of all portable ACs, 
including spot coolers.
---------------------------------------------------------------------------

    Due to the consistent method of reporting performance required by 
the CEC, DOE selected units for its test sample largely from cooling 
capacities and EERs listed in the CEC product database. However, due to 
the difference in testing temperature, DOE expected that these values 
would differ from the cooling capacities and EERs that would be 
obtained using any of the three current industry test methods. For 
additional products not listed in the CEC product database, DOE 
utilized information from manufacturer literature to inform its 
selection.
    The 24 test units \10\ (comprising the samples from the May 2014 
NODA testing and testing for this proposal) and their key features are 
presented in Table III.1, with cooling capacity expressed in Btu/h and 
EER expressed in Btu/Wh.
---------------------------------------------------------------------------

    \10\ DOE also tested two spot coolers for the May 2014 NODA. 
However, because DOE is not proposing testing provisions for these 
units at this time, the results for those units are not considered 
further in this analysis.

                                      Table III.1--Portable AC Test Sample
----------------------------------------------------------------------------------------------------------------
                                                                                 Rated cooling    Rated EER (Btu/
                  Test unit                              Duct type              capacity (Btu/h)        Wh)
----------------------------------------------------------------------------------------------------------------
SD1 \1\.....................................  Single.........................              8,000             7.0
SD2 \1\.....................................  Single.........................              9,500             9.6
SD3 \1\.....................................  Single.........................             12,000             8.7
SD4 \1\.....................................  Single.........................             13,000             9.7
SD5.........................................  Single.........................              8,000            10.2
SD6.........................................  Single.........................             14,000             8.9
SD7.........................................  Single.........................             12,000             8.1
SD8.........................................  Single.........................              9,000             9.2
SD9.........................................  Single.........................              9,000            10.3
SD10........................................  Single.........................             10,000             9.5
SD11........................................  Single.........................             12,000            12.6
SD12........................................  Single.........................             10,000             8.8
SD13........................................  Single.........................             12,500         \3\ N/A
SD14........................................  Single.........................             12,000            10.0
SD15........................................  Single.........................              5,000             8.6
SD16........................................  Single.........................             11,000             9.2
SD17........................................  Single.........................             12,000         \3\ N/A
DD1 \1\.....................................  Dual...........................              9,500             9.4
DD2 \1\.....................................  Dual...........................             13,000             8.9
DD3.........................................  Dual...........................             11,600             8.8
DD4 \2\.....................................  Dual...........................             14,000         \3\ N/A
DD5.........................................  Dual...........................              9,000             9.2
DD6.........................................  Dual...........................             14,000             9.5
DD7.........................................  Dual...........................             13,500             9.5
----------------------------------------------------------------------------------------------------------------
\1\ These units were tested and discussed in the May 2014 NODA. This table does not include the two spot coolers
  that were tested in support of the May 2014 NODA.
\2\ This test unit shipped with the capabilities of operating in both single-duct and dual-duct configuration.
  Therefore, it was tested according to both configurations.
\3\ No rated value was published in the CEC database or in manufacturer documentation.

Baseline Testing
    DOE first performed testing in accordance with AHAM PAC-1-2009 \11\ 
to determine baseline performance according to industry standards. This 
baseline performance was then compared to performance measured 
according to modified or alternate test approaches to determine an 
optimal approach.
---------------------------------------------------------------------------

    \11\ DOE's testing and analysis was completed prior to the 
publication of AHAM PAC-1-2014. Because, as discussed earlier, DOE 
concludes that the differences between the 2009 and 2014 versions of 
the test standard would not affect testing results substantively, 
DOE proposes a test procedure in this rule that would referenece 
certain provisions of the current versions of the standard (AHAM 
PAC-1-2014).
---------------------------------------------------------------------------

    AHAM PAC-1-2009 requires two-chamber air enthalpy testing for 
single-duct and dual-duct units, and a single-chamber setup for spot 
coolers. For each ducted configuration, the portable AC and any 
associated ducting is located entirely within a chamber held at 
``indoor'' standard rating conditions at the evaporator inlet of 80 
[deg]F dry-bulb temperature and 67 [deg]F wet-bulb temperature, which 
correspond to 51-

[[Page 10219]]

percent relative humidity. For the condenser-side exhaust on single-
duct and dual-duct units, the manufacturer-supplied or manufacturer-
specified flexible ducting connects the unit under test to a separate 
test chamber maintained at ``outdoor'' standard rating conditions. The 
outdoor conditions specify 95 [deg]F dry-bulb temperature and 75 [deg]F 
wet-bulb temperature (40-percent relative humidity) at the condenser 
inlet for dual-duct units. The outdoor conditions for single-duct 
units, however, are not explicitly specified. AHAM PAC-1-2009 only 
requires that the condenser inlet conditions, which would be set by air 
intake from the indoor side chamber, be maintained at 80 [deg]F dry-
bulb temperature and 67 [deg]F wet-bulb temperature. Because the 
single-duct condenser air is discharged to the outdoor side with no 
intake air from that location, DOE does not believe that the results 
obtained using AHAM PAC-1-2009 would be measurably affected by the 
conditions in the outdoor side chamber. Nonetheless, for consistency 
with the testing of dual-duct units, DOE chose to maintain the outdoor 
side conditions, measured near to the condenser exhaust but not close 
enough to be affected by that airflow, at 95 [deg]F dry-bulb 
temperature and 75 [deg]F wet-bulb temperature.
    Section 6.1 of AHAM PAC-1-2009, ``Method of Test,'' instructs that 
the details of testing are as specified in ANSI/ASHRAE Standard 37-
2005, but does not identify particular provisions to be used other than 
noting that references in Section 8.5.1 of ANSI/ASHRAE Standard 37-2005 
refer to the indoor side (the cooling, or evaporator side) and the 
outdoor side (the heat rejection, or condenser, side) of the portable 
AC under test. DOE determined that additional relevant sections to 
incorporate would include those referring to test setup, test conduct, 
cooling capacity and power input determination, data recording, and 
test result reporting. The following paragraphs describe the equivalent 
clauses from ANSI/ASHRAE Standard 37-2009 that DOE decided were 
appropriate for conducting its baseline tests for both the May 2014 
NODA and this proposal.
    The test apparatus (i.e., ducts, air flow-measurement nozzle, and 
additional instrumentation) were adjusted according to Section 8.6, 
``Additional Requirements for the Outdoor Air Enthalpy Method,'' of 
ANSI/ASHRAE Standard 37-2009, which ensures that air flow rate and 
static pressure in the condenser exhaust air stream, and condenser 
inlet air stream for dual-duct units, are representative of actual 
installations. The test room conditioning apparatus and the units under 
test were then operated until steady-state performance was achieved 
according to the specified test tolerances in Section 8.7, ``Test 
Procedure for Cooling Capacity Tests,'' of ANSI/ASHRAE Standard 37-
2009. Airflow rate, dry-bulb temperature, and water vapor content were 
recorded to evaluate cooling capacity at equal intervals that spanned 5 
minutes or less until readings over one-half hour were within the same 
tolerances, as required by that section.
    These collected data were then used to calculate total, sensible, 
and latent indoor cooling capacity based on the equations in Section 
7.3.3, ``Cooling Calculations,'' of ANSI/ASHRAE Standard 37-2009. This 
section provides calculations to determine indoor cooling capacity 
based on both the indoor and outdoor air enthalpy methods. As described 
in Section 7.3.3.3 of ANSI/ASHRAE Standard 37-2009, the indoor air 
enthalpy cooling capacity calculation was adjusted for heat transferred 
from the surface of the duct(s) to the conditioned space. DOE estimated 
a convective heat transfer coefficient of 4 Btu/h per square foot per 
[deg]F, based on a midpoint of values for forced convection and free 
convection as recommended by the test laboratory for this specific test 
and setup. Four thermocouples were placed in a grid on the surface of 
the condenser duct(s). The heat transfer was determined by multiplying 
the estimated heat transfer coefficient by the surface area of each 
component and by the average temperature difference between the duct 
surface and test chamber air.
    Although AHAM PAC-1-2009 specifies in Section 5.1 that the 
evaporator circulating fan heat shall be included in the total cooling 
capacity by means of fan power measurement, DOE selected an alternate 
calculation that it concluded would provide a more accurate measure of 
overall heat transfer to the conditioned space. DOE estimated this heat 
transferred to the conditioned space by monitoring the temperature 
differential between the case surfaces and the indoor room, with 
measurements and calculations similar to those used for the ducts. This 
estimate was made by placing four thermocouples on each surface of the 
case and measuring the surface area to determine the total heat 
transfer through the case. This approach directly estimates the heating 
contribution of all internal components within the case to the cooling 
capacity, while making no assumption regarding whether the heat from 
individual components is transferred to the cooling or heat rejection 
side.
    Based on the provisions discussed above, DOE used the following 
equation when calculating the cooling capacity and EER for portable ACs 
according to AHAM PAC-1-2009:
Cooling Capacity = Qindoor - Qduct - Qcase

Where:

Qindoor is the evaporator air enthalpy cooling capacity, 
in Btu/h, as calculated according to Section 7.3.3.1 of ANSI/ASHRAE 
37-2009.
Qduct is the heat transferred from the condenser exhaust 
duct (and condenser inlet duct for dual-duct units) to the 
conditioned space, in Btu/h, as calculated according to Section 
7.3.3.3 of ANSI/ASHRAE 37-2009.
Qcase is the heat transferred from the portable AC case 
to the conditioned space, in Btu/h, also calculated using the 
methodology in 7.3.3.3 of ANSI/ASHRAE 37-2009, but using temperature 
measurements located on the case surfaces rather than the ducts.

    From the calculated evaporator air enthalpy cooling capacity, DOE 
determined the associated EER consistent with the definitions in 
Sections 3.8 and 3.9 and ratings requirements in Sections 5.3 and 5.4 
of AHAM PAC-1-2009. Table III.2 shows the results of the baseline 
testing for all test units according to AHAM PAC-1-2009, including 
results from testing for the May 2014 NODA and this proposal.

                                       Table III.2--Baseline Test Results
----------------------------------------------------------------------------------------------------------------
                                                                                Cooling capacity
                  Test unit                              Duct type                  (Btu/h)        EER (Btu/Wh)
----------------------------------------------------------------------------------------------------------------
SD1.........................................  Single.........................              5,850             6.8
SD2.........................................  Single.........................              6,600             7.4
SD3.........................................  Single.........................             10,950             7.5
SD4.........................................  Single.........................              9,500             6.6
SD5.........................................  Single.........................              5,600             8.3

[[Page 10220]]

 
SD6.........................................  Single.........................             10,250             8.0
SD7.........................................  Single.........................              8,550             6.4
SD8.........................................  Single.........................              6,750             5.9
SD9.........................................  Single.........................              6,700             6.9
SD10........................................  Single.........................              8,100             8.1
SD11........................................  Single.........................              5,700             5.7
SD12........................................  Single.........................              8,050             7.3
SD13........................................  Single.........................             10,350             8.6
SD14........................................  Single.........................              9,250             8.1
SD15........................................  Single.........................              4,250             8.2
SD16........................................  Single.........................              8,200             7.3
SD17........................................  Single.........................              5,800             6.8
SD18 \1\....................................  Single.........................              7,200             5.4
DD1.........................................  Dual...........................              8,600             7.4
DD2.........................................  Dual...........................              7,200             5.5
DD3.........................................  Dual...........................              5,950             4.8
DD4 \1\.....................................  Dual...........................              5,900             4.1
DD5.........................................  Dual...........................              5,250             5.3
DD6.........................................  Dual...........................              7,450             6.0
DD7.........................................  Dual...........................              7,300             5.7
----------------------------------------------------------------------------------------------------------------
\1\ This test unit shipped with the capabilities of operating in both single-duct and dual-duct configuration.
  Therefore, it was tested according to both configurations.

Calorimeter Method Testing
    For the May 2014 NODA and this proposal, DOE further investigated 
heat transfer effects not currently captured in available portable AC 
test procedures, through additional testing according to the room 
calorimeter approach described in the May 2014 NODA. 79 FR 26639, 26644 
(May 9, 2014). This approach, adapted from ANSI/ASHRAE Standard 16-
1983, used two test chambers, one maintained at the indoor conditions 
and the other adjusted to maintain the outdoor conditions as specified 
below. The portable AC under test was located within the indoor test 
room with the condenser duct(s) interfacing with the outdoor test room 
by means of the manufacturer-supplied or manufacturer-recommended 
mounting fixture, unless otherwise noted. Infiltration air from the 
outdoor chamber at 95 [deg]F dry-bulb and 75 [deg]F wet-bulb (40-
percent relative humidity) was introduced by means of a pressure-
equalizing device to the indoor chamber, which was maintained at 80 
[deg]F dry-bulb and 67 [deg]F wet-bulb (51-percent relative humidity). 
The pressure-equalizing device maintained a static pressure 
differential of less than 0.005 inches of water between the chambers, 
as specified in Section 4.2.3 of ANSI/ASHRAE Standard 16-1983.
    DOE measured all energy consumed by the indoor chamber components 
to maintain the required ambient conditions while the portable AC under 
test operated continuously at its maximum fan speed during a 1-hour 
stable period following a period of no less than 1 hour with stabilized 
conditions. All heating and cooling contributions to the indoor chamber 
were summed, including: Chamber cooling, heat transferred through the 
chamber wall, air-circulation fans, dehumidifiers, humidifiers, and 
scales. The net indoor chamber cooling was recorded as the portable 
AC's cooling capacity. This approach encompasses all cooling and 
heating effects generated by the portable AC, including air 
infiltration effects that are not captured or estimated by the air 
enthalpy approach.
    The test units were installed with the manufacturer-provided 
ducting, duct attachment collar, and mounting fixture. This test 
approach included the impacts of heat transfer from the ducts and air 
leaks in the duct connections and mounting fixture, in addition to heat 
leakage through the case and infiltration air. Table III.3 shows the 
measured net cooling capacities and EER values for all units tested 
according to the calorimeter approach when the infiltration air dry-
bulb temperature was 95 [deg]F. Also included are the results for the 
rated and baseline values. Figure III.1 also presents the comparison of 
baseline and calorimeter testing results.

                              Table III.3--Rated, Baseline, and Calorimeter Results
----------------------------------------------------------------------------------------------------------------
                                           Cooling capacity (Btu/h)                     EER (Btu/Wh)
             Test unit             -----------------------------------------------------------------------------
                                       Rated       Baseline   Calorimeter     Rated       Baseline   Calorimeter
----------------------------------------------------------------------------------------------------------------
SD1...............................        8,000        5,850         -450          7.0          6.8         -0.5
SD2...............................        9,500        6,600         -650          9.6          7.4         -0.7
SD3...............................       12,000       10,950        3,500          8.7          7.5          2.3
SD4...............................       13,000        9,500        1,850          9.7          6.6          1.3
SD5...............................        8,000        5,600          150         10.2          8.3          0.2
SD6...............................       14,000       10,250        3,000          8.9          8.0          2.3
SD7...............................       12,000        8,550        2,850          8.1          6.4          2.1
SD8...............................        9,000        6,750          900          9.2          5.9          0.8
SD9...............................        9,000        6,700        1,050         10.3          6.9          1.1
SD10..............................       10,000        8,100        1,900          9.5          8.1          1.9
SD11..............................       12,000        5,700        1,100         12.6          5.7          1.1
SD12..............................       10,000        8,050        1,600          8.8          7.3          1.5

[[Page 10221]]

 
SD13..............................       12,500       10,350        3,900      \1\ N/A          8.6          3.2
SD14..............................       12,000        9,250        2,300         10.0          8.1          2.0
SD15..............................        5,000        4,250       -2,450          8.6          8.2         -4.7
SD16..............................       11,000        8,200        1,700          9.2          7.3          1.5
SD17..............................       12,000        5,800         -650      \1\ N/A          6.8         -0.7
SD18 \2\..........................       14,000        7,200          850      \1\ N/A          5.4          0.6
DD1...............................        9,500        8,600        3,400          9.4          7.4          2.9
DD2...............................       13,000        7,200        3,450          8.9          5.5          2.6
DD3...............................       11,600        5,950        3,100          8.8          4.8          2.5
DD4 \2\...........................       14,000        5,900        2,400      \1\ N/A          4.1          1.7
DD5...............................        9,000        5,250        2,700          9.2          5.3          2.8
DD6...............................       14,000        7,450        2,800          9.5          6.0          2.2
DD7...............................       13,500        7,300        4,000          9.5          5.7          3.0
----------------------------------------------------------------------------------------------------------------
\1\ No rated value was published in the CEC database or on manufacturer documentation.
\2\ This test unit shipped with the capabilities of operating in both single-duct and dual-duct configuration.
  Therefore, it was tested according to both configurations.

  [GRAPHIC] [TIFF OMITTED] TP25FE15.000
  
    Figure III.1 demonstrates that there is little correlation between 
EER and cooling capacity for the baseline results when the effects of 
air infiltration and heat losses are not accounted for. When such 
effects are included, the values of both EER and cooling capacity are 
reduced for a given test unit, but the data evidence a clear 
relationship between EER and cooling capacity. Figure III.1 also 
demonstrates that the net cooling of portable ACs may be significantly 
lower than an air enthalpy measurement would suggest, due to the 
effects of infiltration air. Thus, DOE determined that the existing 
representations of capacity and EER, which are based on air enthalpy 
methods, are likely to be inconsistent and may not represent true 
portable AC performance. Further, the varying differences between the 
calorimeter and baseline results indicate that varying infiltration air 
flow rates and heat losses would preclude a fixed translation factor 
that could be applied to the results of an air enthalpy measurement to 
account for the impact of these effects. For these reasons, DOE 
determined that a DOE test procedure for portable ACs that includes a 
measure of infiltration air effects and heat losses would provide 
consistency and clarity for representation of capacity and energy use 
for these products. Specific proposals for such a test procedure are 
discussed in the following sections.
i. General Test Approach
    As discussed in the previous section, the results from baseline 
testing according to AHAM PAC-1-2009 and investigative testing 
according to the calorimeter approach suggest that the calorimeter 
approach most accurately represents portable AC performance by 
accounting for the effects of air infiltration and heat losses.
    DOE considered comments received in response to the initial 
baseline and calorimeter approach results presented in the May 2014 
NODA. Appliance Standards Awareness Project, Alliance to Save Energy, 
American Council for an Energy-Efficient Economy, Consumers Union, 
Natural Resources Defense Council, and Northwest Energy Efficiency 
Alliance (hereinafter referred to as the ``Joint Commenters'') and the 
California IOUs observed that the current industry test procedures do 
not capture the effects of infiltration air and duct heat loss and 
leakage, which would lead to an overestimation of portable AC

[[Page 10222]]

performance in real-world settings. In addition, according to the Joint 
Commenters, the current industry test procedures do not provide an 
accurate relative ranking of portable AC units, such that single-duct 
units appear to be more efficient than dual-duct units. Therefore, the 
Joint Commenters and the California IOUs urged DOE to adopt a test 
procedure for portable ACs based on the calorimeter approach, which 
would align with the current test procedures for room ACs and would 
better reflect real-world cooling capacities and EERs of both single-
duct and dual-duct configurations. The California IOUs commented that 
because portable ACs can be used as a substitute for room ACs, they 
support the adoption of a test procedure for portable ACs that would 
allow consumers to make realistic comparisons of capacity and 
efficiency between comparable product types. (California IOUs, No. 5 at 
pp. 2-3; Joint Commenters, No. 6 at pp. 1-2)
    AHAM supports the incorporation by reference of AHAM PAC-1-2014, 
which is harmonized with CSA C370-2013, in a DOE test procedure for 
portable ACs. AHAM indicated that AHAM PAC-1-2014 best measures 
representative performance for each portable AC configuration, in 
comparison to other approaches. AHAM commented that, unlike other air 
conditioning products, portable ACs are intended to be easily relocated 
from one room to another and therefore the compressor and condenser are 
both inside the conditioned room, as opposed to a room AC, where the 
compressor and condenser are outside the room. Because a portable AC 
does not operate in between the conditioned and unconditioned space as 
room ACs do, and instead is located solely in the conditioned space, 
AHAM believes that the calorimeter approach, intended for room ACs, may 
not be as representative as the enthalpy approach for portable ACs. 
AHAM also commented that ANSI/ASHRAE 128-2011 instructs that it is not 
to be used for portable ACs with cooling capacities less than 65,000 
Btu/h, and ANSI/AHAM 128-2001 does not address all portable AC 
configurations. AHAM noted that Canada may promulgate portable AC 
standards using CSA C370-2013, and stated that North American 
harmonization will provide consistency and clarity for regulated 
parties and consumers in both countries. (AHAM, No. 4 at p. 2) AHAM 
acknowledged the differences between rated values and baseline test 
results obtained using AHAM PAC-1-2009, and stated that a conversion 
factor between rated values and results obtained using its recommended 
test procedure, AHAM PAC-1-2014, is not feasible due to the wide range 
of differences between these values. (AHAM, No. 4 at p. 3)
    De' Longhi Appliances s.r.l. (De' Longhi) indicated that the air 
enthalpy method and a calorimeter method with no air infiltration would 
ensure levels of reproducibility and repeatability required for 
regulated products. Further, De' Longhi stated that AHAM PAC-1-2009 and 
CSA C370-2013 are more suitable for representing performance of all the 
categories of portable ACs. (De' Longhi, No. 3 at p. 5)
    AHAM and De' Longhi also stated that the calorimeter approach is 
much more burdensome than the air enthalpy approach, requiring more 
expensive test equipment and longer test times. AHAM believes that 
adoption of the calorimeter method for testing portable ACs would also 
require many laboratories to build new test facilities because portable 
ACs are not currently tested using a calorimeter approach, representing 
a significant burden. AHAM is also concerned that there are few third-
party test laboratories that have the capability to test using a 
calorimeter approach, which would impact choice and availability for 
testing. Therefore, AHAM urged DOE to adopt the test approach of AHAM 
PAC-1-2014 to produce representative test results that are not unduly 
burdensome to conduct. (AHAM, No. 4 at p. 4) De' Longhi stated that the 
test burden associated with a test method should be proportionate to 
the amount of energy consumed by a certain product category. According 
to De' Longhi, because portable ACs are a small fraction of the air 
conditioning market with a unique usage pattern, being operated 
generally for short period of time, the test burden should be 
minimized. De' Longhi commented that the calorimeter method would 
result in an unreasonably large burden for this product category, and 
therefore, the air enthalpy method is preferable due to the higher 
availability of testing apparatus and lower cost of testing. (De' 
Longhi, No. 3 at p. 3)
    The results presented in Table III.3 and displayed in Figure III.1 
demonstrate that the calorimeter method provides a measure of net 
portable AC cooling capacity and EER across different product 
configurations and varying air infiltration rates that is comparable to 
the performance trends obtained according to AHAM PAC-1-2009. However, 
DOE found in its testing that, although equipment setup is simpler for 
the calorimeter approach as based on ANSI/ASHRAE Standard 16 
requirements, maintaining the conditions in a calorimeter chamber can 
be difficult, particularly at higher test unit cooling capacities. In 
those cases, additional climate control components may be necessary, 
all of which must be monitored to measure the heat transfer to and from 
the indoor side test room. These additional components may include air 
circulating fans to ensure conditions are uniform throughout the test 
room, humidifiers and dehumidifiers to maintain the necessary relative 
humidity, and scales to measure the evaporated or condensed moisture 
during testing. Incorporating the heating and cooling effects from each 
of these components proved to be complex, with potential uncertainties 
in the net cooling capacity accumulating with each additional 
component. After considering the burdens and complexity of the 
calorimeter approach, DOE determined the air enthalpy approach provided 
in AHAM PAC-1-2009 and AHAM PAC-1-2014 to be a less burdensome 
approach. Although AHAM PAC-1-2014 requires comprehensive 
instrumentation to monitor air stream enthalpies and specific measures 
to ensure that this instrumentation has no impact on performance, it 
also provides a straight-forward calculation for determining indoor-
side cooling based on a well-defined set of variables. Many of the 
instruments required for the air enthalpy approach, as specified in 
ANSI/ASHRAE Standard 37, are used in testing central ACs and heat 
pumps, and ANSI/ASHRAE Standard 37 is also referenced in the DOE test 
procedure to determine energy consumption of furnace fans. Thus, DOE 
believes that many commercial laboratories have the capability to 
perform the air enthalpy test, while few laboratories in the United 
States have the test chamber and instrumentation required to test 
according to the calorimeter approach. In addition, the air enthalpy 
approach, as specified in ANSI/ASHRAE Standard 37 with additional 
guidance in AHAM PAC-1-2014, is specifically applicable for testing 
portable ACs, while the calorimeter approach requires modifications 
from the room AC test procedure specified in ANSI/ASHRAE 16 to 
accommodate portable ACs.
    Therefore, if DOE determines that portable ACs are covered products 
and establishes a test procedure for them, DOE proposes that AHAM PAC-
1-2014 be the basis of the DOE test procedure to ensure that multiple 
labs are capable of performing the test, to minimize added test burden, 
and to align with current industry practices. However, as described in 
the remaining subsections of section III.1.a, DOE believes that 
additional provisions and clarifications

[[Page 10223]]

would be necessary to incorporate AHAM PAC-1-2014 into a DOE portable 
AC test procedure.
ii. Infiltration Air Effects and Cooling Capacity
    Infiltration from outside the conditioned space in which the 
portable AC is located occurs due to the negative pressure induced as 
condenser air is exhausted to the outdoor space. Although this effect 
is most pronounced for single-duct units, which draw all of their 
condenser air from within the conditioned space, dual-duct units also 
draw a portion of their condenser air from the conditioned space. In 
its testing, DOE estimated the infiltration air flow rate as equal to 
the condenser exhaust flow rate to the outdoor chamber minus any 
condenser intake flow rate from the outdoor chamber because it had 
determined that air leakage from the outdoor chamber to locations other 
than the indoor chamber was negligible.
    For a single-duct unit, the air balance equation results in the 
infiltration air flow rate being equal to the condenser exhaust air 
flow rate. For dual-duct units, the condenser exhaust duct flow rate 
may be higher than the inlet duct flow rate. This is due to some intake 
air being drawn from the indoor chamber via louvers or leakage through 
the case, duct connections, or between the evaporator and condenser 
sections. Table III.4 presents the estimated infiltration air flow 
rates for the full test sample.

                 Table III.4--Infiltration Air Flow Rate
------------------------------------------------------------------------
                                   Condenser    Condenser        Net
                                   outlet air   inlet air   infiltration
            Test unit              flow rate    flow rate     air flow
                                     (CFM)       (CFM) *     rate (CFM)
------------------------------------------------------------------------
SD1.............................       268.03  ...........        268.03
SD2.............................       262.59  ...........        262.59
SD3.............................       285.45  ...........        285.45
SD4.............................       254.30  ...........        254.30
SD5.............................       217.77  ...........        217.77
SD6.............................       228.43  ...........        228.43
SD7.............................       221.83  ...........        221.83
SD8.............................       224.61  ...........        224.61
SD9.............................       229.09  ...........        229.09
SD10............................       220.80  ...........        220.80
SD11............................       175.07  ...........        175.07
SD12............................       237.37  ...........        237.37
SD13............................       247.39  ...........        247.39
SD14............................       262.52  ...........        262.52
SD15............................       278.89  ...........        278.89
SD16............................       250.69  ...........        250.69
SD17............................       249.37  ...........        249.37
SD18............................       246.48  ...........        246.48
                                 ---------------------------------------
    Average of Single-Duct......  ...........  ...........        242.26
                                 ---------------------------------------
DD1.............................       271.85       170.79        101.06
DD2.............................       214.83       128.05         86.78
DD3.............................       234.87       146.29         88.58
DD4.............................       251.67       126.60        125.07
DD5.............................       207.85       113.15         94.71
DD6.............................       272.43        76.61        195.82
DD7.............................       244.47       107.49        136.99
                                 ---------------------------------------
    Average of Dual-Duct........  ...........  ...........        118.43
------------------------------------------------------------------------
* Condenser inlet air flow rate is only applicable for dual-duct units.

    As discussed in the May 2014 NODA, DOE investigated various 
infiltration air temperatures. In its initial calorimeter tests, DOE 
maintained the outdoor test chamber conditions at 95 [deg]F dry-bulb 
temperature and 75 [deg]F wet-bulb temperature, which would be 
representative of outdoor air being drawn directly into the conditioned 
space to replace any condenser inlet air from that same conditioned 
space. However, it is possible that some or all of the replacement air 
is drawn from a location other than the outdoors directly, such as a 
basement, attic, garage, or a space that is conditioned by other 
equipment. Because varying infiltration air temperature would have a 
significant impact on cooling capacity and EER, DOE performed 
additional testing over a range of dry-bulb temperatures for the 
infiltration air that spanned 78 [deg]F to 95 [deg]F, all at the 40-
percent relative humidity specified at the 95 [deg]F condition. 79 FR 
26639, 26646 (May 9, 2014).
    In response to the May 2014 NODA, the Joint Commenters and 
California IOUs stated that the current industry standard outdoor air 
conditions (95 [deg]F dry-bulb temperature and 75 [deg]F wet-bulb 
temperature) are appropriate for infiltration air. (Joint Commenters, 
No. 6 at p. 3; California IOUs, No. 5 at p. 3) The Joint Commenters 
added that although some or all of the infiltration air may be drawn 
from a location other than the outdoors directly, such as a basement, 
attic, garage, or a space that is conditioned by other equipment, all 
infiltration air is ultimately coming from the outdoors and adding heat 
to the home where the portable AC is installed. (Joint Commenters, No. 
6 at p. 3)
    AHAM stated that in the field, there is a mixture of indoor and 
outdoor air, and infiltration air will be at different temperature and 
humidity levels in every home, due to varying home designs. Therefore, 
AHAM does not

[[Page 10224]]

believe there is an ``average'' condition that DOE could select to 
replicate in a test procedure condition and would not support an 
approach that utilizes existing test procedures with numerical 
adjustments for infiltration air. (AHAM, No. 4 at p. 5) De' Longhi 
concurred, stating that the effect of air infiltration would be complex 
to standardize. De' Longhi commented that air infiltration flow 
pathways are determined by the path of minimum air flow resistance, and 
therefore it is not possible to determine the amount of infiltration 
air that originates from adjacent indoor rooms versus from outdoors. 
De' Longhi believes that in most situations, unconditioned outdoor air 
is just a small portion of the total infiltration air. Accordingly, De' 
Longhi stated that the standard outdoor air conditions of 95 [deg]F 
dry-bulb temperature and 75 [deg]F wet-bulb temperature are not 
representative of the infiltration air temperatures. De' Longhi 
suggested that if DOE determines to include portable ACs as a covered 
product, the heat transfer effects of infiltration air should not be 
taken into account in a DOE test procedure. (De' Longhi, No. 3 at p. 4)
    DOE agrees that, as for all covered products, real-world 
installations experience varying ambient conditions. The test procedure 
must thus consider the most representative operation in selecting 
appropriate specifications for those conditions. Recognizing that in 
some cases the infiltration air enters the conditioned space directly 
from outdoors, and that any air infiltrating from other conditioned 
spaces likely also originated from outdoors before being conditioned by 
other cooling equipment, DOE concludes that 95 [deg]F dry-bulb 
temperature and 75 [deg]F wet-bulb temperature is most representative 
for infiltration air conditions, in accordance with the outdoor 
conditions specified in AHAM PAC-1-2014, and proposes to specify these 
conditions in the portable AC test procedure. Such conditions would 
also produce comparable results for single-duct and dual-duct 
configurations.
    DOE also developed methodology for the May 2014 NODA that would 
adjust the results obtained from an air enthalpy method to account for 
the total heat added to the room by the infiltration air. The 
infiltration air mass flow rate of dry air would be calculated as:
[GRAPHIC] [TIFF OMITTED] TP25FE15.001

Where:

mmsd is the dry air mass flow rate of infiltration air 
for a single-duct unit, in pounds per minute (lb/m).
mmdd is the dry air mass flow rate of infiltration air 
for a dual-duct unit, in lb/m.
Vco is the volumetric flow rate of the condenser outlet 
air, in cubic feet per minute (cfm).
Vci is the volumetric flow rate of the condenser inlet 
air, in cfm.
[rho]co is the density of the condenser inlet air, in 
pounds mass per cubic feet (lbm/ft\3\).
[rho]ci is the density of the condenser inlet air, in 
lbm/ft\3\.
[omega]co is the humidity ratio of condenser outlet air, 
in pounds mass of water vapor per pounds mass of dry air 
(lbw/lbda).
[omega]ci is the humidity ratio of condenser inlet air, 
in lbw/lbda.

    The sensible heat contribution of the infiltration air would be 
calculated as follows:
[GRAPHIC] [TIFF OMITTED] TP25FE15.002

Where:

Qs is the sensible heat added to the room by infiltration 
air, in Btu/h;
mm is the dry air mass flow rate of infiltration air for a single-
duct or dual-dual duct unit, in lb/m;
cp_da is the specific heat of dry air, 0.24 Btu/
lbm- [deg]F.
cp_wv is the specific heat of water vapor, 0.444 Btu/
lbm- [deg]F.
[omega]ia is the humidity ratio of the infiltration air, 
0.0141 lbw/lbda.
[omega]ei is the humidity ratio of the evaporator inlet 
air, in lbw/lbda.
60 is the conversion factor from minutes to hours.
Tei is the indoor chamber dry-bulb temperature measured 
at the evaporator inlet, in [deg]F.
Tia is the infiltration air dry-bulb temperature, 95 
[deg]F.

    DOE used the following equation for the latent heat contribution of 
the infiltration air:
[GRAPHIC] [TIFF OMITTED] TP25FE15.003

Where:

Ql is the latent heat added to the room by infiltration 
air, in Btu/h.
mm is the mass flow rate of infiltration air for a single-duct or 
dual-dual duct unit, in lb/m.
[omega]ia is the humidity ratio of the infiltration air, 
0.0141 lbw/lbda.
[omega]ei is the humidity ratio of the evaporator inlet 
air, in lbw/lbda.
Hfg is the latent heat of vaporization for water vapor, 
1061 Btu/lbm.
60 is the conversion factor from minutes to hours.

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

Where:

Qinfiltration is the total infiltration air heat, in Btu/
h.
Qs is the sensible heat added to the room by infiltration 
air, in Btu/h.
Ql is the latent heat added to the room by infiltration 
air, in Btu/h.

    Table III.5 displays the cooling capacity as determined by the 
baseline air enthalpy testing approach of AHAM PAC-1-2009, and the 
modified air enthalpy approach that subtracts the estimated 
infiltration air heat input from the cooling capacity measurement.

                                 Table III.5--Modified Air Enthalpy Performance
----------------------------------------------------------------------------------------------------------------
                                                     Cooling capacity (Btu/h)             EERcm (Btu/Wh)
                    Test unit                    ---------------------------------------------------------------
                                                     Baseline      Modified AHAM     Baseline      Modified AHAM
----------------------------------------------------------------------------------------------------------------
SD1.............................................           5,850            -900             6.8            -1.0
SD2.............................................           6,600             200             7.4             0.2
SD3.............................................          10,950           4,050             7.5             2.8

[[Page 10225]]

 
SD4.............................................           9,500           4,000             6.6             2.8
SD5.............................................           5,600             400             8.3             0.6
SD6.............................................          10,250           4,750             8.0             3.7
SD7.............................................           8,550           3,500             6.4             2.6
SD8.............................................           6,750           1,500             5.9             1.3
SD9.............................................           6,700           1,150             6.9             1.2
SD10............................................           8,100           2,750             8.1             2.7
SD11............................................           5,700           1,350             5.7             1.4
SD12............................................           8,050           2,250             7.3             2.0
SD13............................................          10,350           4,450             8.6             3.7
SD14............................................           9,250           2,800             8.1             2.4
SD15............................................           4,250          -2,900             8.2            -5.6
SD16............................................           8,200           2,200             7.3             2.0
SD17............................................           5,800            -850             6.8            -1.0
SD18............................................           7,200           1,300             5.4             1.0
DD1.............................................           8,600           6,550             7.4             5.6
DD2.............................................           7,200           5,500             5.5             4.2
DD3.............................................           5,950           4,150             4.8             3.4
DD4.............................................           5,900           3,100             4.1             2.2
DD5.............................................           5,250           3,200             5.3             3.2
DD6.............................................           7,450           2,800             6.0             2.2
DD7.............................................           7,300           4,200             5.7             3.3
----------------------------------------------------------------------------------------------------------------

    The data above show the significant reduction in cooling capacity 
and EERcm caused by infiltration air heat input, which is 
greater for single-duct units than for dual-duct units. For three of 
the single-duct units, the impacts of infiltration air were so great 
that they produced net heating in the conditioned space, as indicated 
by the negative cooling capacity values.
    In response to this approach, which was presented in the May 2014 
NODA, the Joint Commenters stated that this modified air enthalpy 
testing approach is not a suitable alternative to the proposed 
calorimeter approach. According to the Joint Commenters, the alternate 
testing approach would provide a significant improvement over the 
current industry test procedures by addressing the impact of 
infiltration air with a numerical adjustment, but the alternate testing 
approach fails to capture additional impacts on portable AC performance 
such as leakage through gaps in the ducts and duct connections and heat 
transfer through the ducts. The Joint Commenters expressed concern that 
DOE found no consistent difference between the calorimeter approach and 
the alternate test approach, and therefore believe the alternate test 
approach would not necessarily provide a good indication of real-world 
portable AC performance. Although the alternate testing approach may 
represent a lower testing burden compared to the calorimeter approach, 
the Joint Commenters reminded DOE that the current room AC test 
procedure is based on a calorimeter approach, and stated that the 
calorimeter approach is also appropriate for portable ACs. (Joint 
Commenters, No. 6 at p. 3)
    DOE recognizes that the modified air enthalpy approach and 
calorimeter approach both greatly reduce the cooling capacity and 
EERcm when compared with the results from AHAM PAC-1-2014 
and other current industry-accepted test procedures that do not address 
infiltration air. Based on the data presented above and comments 
received from interested parties and manufacturer interviews, DOE 
believes that any portable AC test procedure must include the heat 
transfer effects of infiltration air, in addition to the effects of 
duct and case heat transfer, discussed later in this NOPR. DOE also 
recognizes that the results produced by the calorimeter and modified 
air enthalpy approaches do not align. However, as discussed earlier in 
this section, DOE found it difficult to maintain the test chamber 
conditions for the calorimeter approach, particularly for higher-
capacity portable ACs. Due to significant infiltration of air at 
conditions substantially different than the required indoor-side test 
chamber conditions, additional air conditioning equipment is required 
to maintain the indoor-side test chamber conditions, all of which must 
be accounted for in determining the net heating or cooling effect in 
the test chamber. DOE believes the cumulative uncertainty related to 
incorporating the heating and cooling effects from each of these 
components may have been significant enough to have resulted in the 
inconsistency between the calorimeter and modified air enthalpy 
approaches. The modified air enthalpy approach accounts for the major 
heating and cooling effects of the portable AC with direct measurements 
of the product air streams and temperature measurements of the case and 
ducts. Therefore, DOE is confident in the accuracy of the results from 
this test approach.
    Based on the significant heat input from infiltration air seen from 
testing, DOE determined that applying such a numerical adjustment for 
infiltration air to the results of testing with AHAM PAC-1-2014 would 
accurately reflect portable AC performance. Therefore, DOE proposes the 
adjusted cooling capacity be determined as follows:

Adjusted Cooling Capacity = Capacitycm-Qinfiltration-Qmisc

Where:

Capacitycm is the cooling capacity as determined in 
accordance with AHAM PAC-1-2014.
Qinfiltration is the sum of sensible (Qs) and 
latent (Ql) heat transfer from infiltration air, as 
calculated above.
Qmisc is the impact of other heat transfer effects, 
discussed in the following sections.
iii. Test Conditions
    AHAM PAC-1-2014 requires two-chamber air enthalpy testing in which 
the ``indoor'' standard rating conditions are maintained at the 
evaporator inlet of 80.6 [deg]F dry-bulb temperature and 66.2

[[Page 10226]]

[deg]F wet-bulb temperature, which correspond to approximately 46-
percent relative humidity. For single-duct units, the condenser inlet 
conditions are the same as the evaporator inlet. For dual-duct units, 
the outdoor conditions, as monitored at the interface between the 
condenser inlet duct and outdoor test room, must be maintained at 95 
[deg]F dry-bulb temperature and 75.2 [deg]F wet-bulb temperature (40-
percent relative humidity). Because these conditions are close to those 
required by the DOE room air conditioner test procedure (80 [deg]F dry-
bulb temperature and 67 [deg]F wet-bulb temperature on the indoor side, 
and 95 [deg]F dry-bulb temperature and 75 [deg]F wet-bulb temperature 
on the outdoor side), test results obtained for portable ACs under the 
proposed test procedure would be comparable to those for room ACs, 
which would allow consumers to directly compare these product types. 
Therefore, DOE proposes to utilize the following ambient conditions 
presented in
    Table III.6 below, based on those test conditions specified in 
Table 3, ``Standard Rating Conditions,'' of AHAM PAC-1-2014. The test 
configurations in
    Table III.6 refer to the test configurations referenced in Table 2 
of AHAM PAC-1-2014, with Test Configuration 3 applicable to dual-duct 
portable ACs and Test Configuration 5 applicable to single-duct 
portable ACs.

                              Table III.6--Standard Rating Conditions--Cooling Mode
----------------------------------------------------------------------------------------------------------------
                                                   Evaporator inlet air, [deg]F     Condenser inlet air, [deg]F
                                                             ([deg]C)                        ([deg]C)
               Test configuration                ---------------------------------------------------------------
                                                     Dry bulb        Wet bulb        Dry bulb        Wet bulb
----------------------------------------------------------------------------------------------------------------
3...............................................       80.6 (27)       66.2 (19)       95.0 (35)       75.2 (24)
5...............................................       80.6 (27)       66.2 (19)       80.6 (27)       66.2 (19)
----------------------------------------------------------------------------------------------------------------

    For single-duct units, AHAM PAC-1-2014 specifies identical 
evaporator and condenser inlet conditions, with the same allowable 
tolerances on the dry-bulb and wet-bulb temperatures. Depending upon 
the airflow and unit configuration, the evaporator and condenser inlet 
may be directly adjacent to one another or on opposite faces of the 
test unit case. Thus, although both evaporator and condenser inlets 
intake air from the same conditioned space, it is possible that the two 
inlet air conditions may not simultaneously meet the requirements in 
AHAM PAC-1-2014 due to slight non-homogeneity in the test chamber, even 
if one or the other inlet is within tolerance.
    Table 2b in Section 8.7 of ANSI/ASHRAE Standard 37-2009, referenced 
by AHAM PAC-1-2014, specifies that both condenser inlet and evaporator 
inlet dry-bulb temperatures must be maintained within a range of 2.0 
[deg]F and an average within 0.5 [deg]F of the nominal values. However, 
test chambers may experience varying levels of homogeneity in test 
conditions and test laboratories may differently prioritize maintaining 
conditions at either the condenser inlet or evaporator inlet. 
Therefore, to ensure repeatability and reproducibility, DOE proposes in 
this NOPR to specify a more stringent tolerance for the evaporator 
inlet dry-bulb that is consistent with the evaporator inlet wet-bulb 
temperature tolerance, within a range of 1.0 [deg]F with an average 
difference of 0.3 [deg]F. The condenser inlet dry-bulb temperature 
would be maintained within the test tolerance as specified in Table 2b 
of ANSI/ASHRAE Standard 37-2009. This tolerance modification will 
ensure that all test laboratories employ the same approach in testing, 
to first maintain the evaporator inlet test conditions and then ensure 
that condenser inlet conditions satisfy the tolerance requirements.
    As discussed in the May 2014 NODA, portable AC manufacturers 
typically provide a single mounting fixture for dual-duct units that 
houses both the condenser inlet and exhaust ducts to minimize 
installation time and optimize the use of window space. However, this 
approach typically positions the condenser inlet and exhaust directly 
adjacent to one another. During operation when installed in the field, 
short-circuiting may occur between some of the condenser exhaust air 
and the outdoor ambient air. DOE investigated the effects of potential 
condenser inlet and exhaust mixing and results indicated that there was 
minimal mixing between the condenser exhaust and inlet air flows. 79 FR 
26639, 26648 (May 9, 2014).
    In response to the May 2014 NODA, De' Longhi commented that the 
condenser inlet and exhaust mixing only has a minimal influence as 
reported by DOE results. (De' Longhi, No. 3 at p. 4) AHAM agreed with 
DOE's conclusion that condenser exhaust air and inlet air mixing in 
dual-duct units need not be addressed or measured in a portable AC test 
procedure. (AHAM, No. 4 at p. 5)
iv. Duct Heat Transfer and Leakage
    In response to the May 2014 NODA, the California IOUs commented 
that it is unclear if there is a standard test set-up in regards to 
length of ducting and distance from the portable AC to the outdoor 
chamber. They suggested that DOE should address alignment of the 
portable AC and the associated ducting, in relation to the outdoor 
chamber, including distance, duct length, duct insulation, and duct 
configuration (e.g., inclusion of bends). (California IOUs, No. 5 at p. 
3) Section 7.3.7 and Figure 2 of AHAM PAC-1-2014 address the required 
ducting arrangement and specifies the duct height, duct length, and 
spacing of the test unit in relation to the chamber walls. 
Additionally, duct insulation and unit placement are further discussed 
in this section and section III.B.1.a.viii of this NOPR.
    DOE also received comments from AHAM and De' Longhi expressing 
concern about including in a portable AC test procedure the effects of 
heat loss through minimally insulated ducts. They commented that there 
is no standardized method to account for such heat loss and that 
incorporating duct heat loss and leakage would impact test 
reproducibility and repeatability. AHAM stated that the approach DOE 
used in its investigative testing for estimating duct heat transfer is 
overly complicated and unnecessary. Accordingly, AHAM and De' Longhi 
suggested that the DOE test procedure should not address these factors. 
(AHAM, No. 4 at pp. 3-4; De' Longhi, No. 3 at p. 3)
    As discussed in the May 2014 NODA, DOE investigated cooling 
performance impacts of uninsulated ducts and any air leakage at the 
duct connections or mounting fixtures. To quantify the heat transfer to 
the conditioned space through the minimally insulated condenser duct(s) 
and from any leaks at the duct connections or mounting fixture, DOE 
repeated the calorimeter testing with insulation surrounding the 
condenser ducts to benchmark results without this heat transfer for the 
initial

[[Page 10227]]

four single-duct and two dual-duct test units. DOE used insulation 
having a nominal R value of 6 (in units of hours-[deg]F-square feet per 
Btu), with seams around the duct, adapter, and mounting bracket sealed 
with tape to minimize air leakage. To determine duct losses and air 
leakage effects, DOE compared results from these tests to the results 
from the initial calorimeter approach tests with no insulation. DOE 
found that uninsulated ducts and leaks in duct connections contribute 
anywhere from 460 to 1,300 Btu/h, which correlate to percentages of 
uninsulated cooling capacity that range from 18 to 199 percent. 79 FR 
26639, 26645 (May 9, 2014). Therefore, DOE determined that duct heat 
losses and air leakage are non-negligible effects, and that duct 
configurations during the DOE test must be representative of actual 
usage. In addition, DOE notes that Section 7.3.3 of AHAM PAC-1-2014 
states that ``the portable AC shall be tested with clean filters in 
place as supplied by the manufacturer. Other equipment recommended as 
part of the air conditioner shall be in place, as well.'' DOE proposes, 
therefore, that all ducting components (e.g., duct, duct connections, 
and mounting bracket) as supplied by the manufacturer would be used for 
determining performance and would be installed in accordance with the 
manufacturer instructions. No additional sealing or insulation would be 
applied.
    Section 7.3.3.3 of ANSI/ASHRAE Standard 37, as referenced by AHAM 
PAC-1-2014, specifies that the indoor cooling capacity shall be 
adjusted for heat transferred from the surface of ducts to the 
conditioned space. DOE recognizes that additional guidance may be 
necessary to determine such an adjustment, and for this reason proposes 
to account for heat transferred from the duct surface to the 
conditioned space in a portable AC test procedure methodology.
    DOE proposes that four equally spaced thermocouples be adhered to 
the side of the entire length of the condenser exhaust duct for single-
duct units and to each of the condenser inlet and exhaust ducts for 
dual-duct units. To ensure accurate heat transfer estimates, DOE 
proposes that temperature measurements would be required to have an 
accuracy to within 0.5 [deg]F. DOE proposes to average the 
four surface temperatures measurements to obtain Tduct for 
each duct. DOE further proposes that a convection heat transfer 
coefficient of 4 Btu/h per square foot per [deg]F be used, based on an 
average of values for forced convection and free convection. The 
surface area of each duct would be calculated as follows:

Aduct_j = [pi] x dj x Lj

Where:

dj is the outer duct diameter of duct ``j''.
Lj is the extended length of duct ``j'' while under test.
j represents the condenser exhaust duct and, for dual-duct units, 
condenser inlet duct.

    Heat transferred from the surface of the duct(s) to the indoor 
conditioned space while operating in cooling mode shall be calculated 
as follows:

Qduct_cm = [Sigma]j{h x Aduct\j x (Tduct\j - Tei){time} 

Where:

Qduct_cm is the total heat transferred from the duct(s) 
to the indoor conditioned space in cooling mode.
h is the convection coefficient, 4 Btu/h per square foot per [deg]F.
Aduct_j is the surface area of duct ``j'', in square 
feet.
Tduct_j is the average surface temperature for duct 
``j'', in [deg]F.
j represents the condenser exhaust duct and, for dual-duct units, 
condenser inlet duct.
Tei is the average evaporator inlet dry-bulb temperature, 
in [deg]F.
v. Case Heat Transfer
    As discussed previously in section III.B.1.a, DOE baseline testing 
incorporated a case heat transfer calculation, similar to that required 
to determine the heat transfer from the duct to the conditioned space 
in ANSI/AHAM Standard 37-2009, in lieu of the evaporator circulating 
fan heat measurement specified in AHAM PAC-1-2014. To determine case 
heat transfer, DOE placed four thermocouples on each face of the case 
to calculate average surface temperatures throughout the cooling mode 
test period. Table III.7 shows the average surface temperatures during 
the baseline testing for all single-duct and dual-duct test units.

                                                   Table III.7--Cooling Mode Case Surface Temperatures
--------------------------------------------------------------------------------------------------------------------------------------------------------
                                                               Average surface temperature during AHAM test ([deg]F)
                Test unit                ------------------------------------------------------------------------------------------------     Average
                                                Top            Front           Right           Back            Left           Bottom
--------------------------------------------------------------------------------------------------------------------------------------------------------
SD1.....................................            79.4            81.6            81.5            81.3            81.9            84.2            81.7
SD2.....................................            79.6            79.0            80.9            89.2            91.5            88.5            84.8
SD3.....................................            76.6            82.3            80.0            82.3            84.9            83.0            81.5
SD4.....................................            73.0            85.3            92.2            82.9            82.7            84.8            83.5
SD5.....................................            77.9            81.3            82.3            83.6            82.4            89.8            82.9
SD6.....................................            72.8            80.5            78.5            81.7            81.9            86.0            80.2
SD7.....................................            73.2            82.8            82.7            81.4            78.2            87.7            81.0
SD8.....................................            88.6            79.7            84.2            91.2            87.8            77.3            84.8
SD9.....................................            78.2            85.0            77.8            86.0            80.5            93.3            83.5
SD10....................................            76.8            91.4            84.3            84.5            85.0            97.4            86.6
SD11....................................            79.8            87.7            85.4            84.5            87.6            90.6            85.9
SD12....................................            72.7            82.2            80.8            81.8            80.3            81.2            79.8
SD13....................................            72.8            79.7            81.1            81.8            82.2            83.7            80.2
SD14....................................            75.6            78.9            79.2            84.1            81.5            81.8            80.2
SD15....................................            79.9            83.7            81.1            81.4            85.9            80.6            82.1
SD16....................................            75.5            88.1            88.1            80.3            81.7            84.5            83.0
SD17....................................            80.3            80.0            83.4            94.9            91.0            95.1            87.4
SD18....................................            76.4            78.8            79.1            81.4            78.9            87.2            80.3
DD1.....................................            75.1            78.0            80.2            82.7            80.5            81.4            79.7
DD2.....................................            80.8            75.9            80.6            86.7            81.0            87.7            82.1
DD3.....................................            76.7            80.2            80.7            86.4            81.8            81.4            81.2
DD4.....................................            78.2            79.8            80.3            85.2            79.9            89.2            82.1
DD5.....................................            75.7            77.0            82.2            84.6            83.2            85.1            81.3
DD6.....................................            76.7            78.3            81.0            85.1            79.0            78.1            79.7
DD7.....................................            74.4            83.3            79.6            88.0            76.9            80.3            80.4

[[Page 10228]]

 
Average.................................            77.1            81.6            81.9            84.5            82.7            85.6  ..............
--------------------------------------------------------------------------------------------------------------------------------------------------------

    As shown in Table III.7, surface temperature varies significantly 
among different case surfaces of a given test unit during cooling mode, 
and that variation is a function of the particular test unit. For 
example, temperatures on test unit SD1 ranged from a top surface 
temperature of 79.4 [deg]F to a bottom side temperature of 84.2 [deg]F, 
a range of 4.8 [deg]F, while test unit SD10 had a top surface 
temperature of 76.8 [deg]F and a bottom side temperature of 97.4 
[deg]F, a range of 20.7 [deg]F. Because each surface on a given test 
unit has a unique surface area and average surface temperature, DOE 
proposes that the heat transfer from the case to the ambient indoor 
space be calculated individually for each surface.
    In response to the same methodology proposed in the May 2014 NODA, 
AHAM commented that this approach for estimating case heat transfer is 
overly complicated and unnecessary. AHAM believes that the approach in 
AHAM PAC-1-2014, which directly measures the evaporator circulating fan 
heat, is easier and simpler. AHAM also stated that DOE's method would 
introduce unnecessary variation in test results. (AHAM, No. 4 at p. 3)
    DOE acknowledges that the proposed case heat transfer approach 
would require additional instrumentation. However, DOE believes that 
the testing burden imposed by the use of multiple thermocouples to 
measure surface temperatures is likely outweighed by the benefit of 
addressing the heat transfer effects of all internal heating 
components. In contrast, AHAM PAC-1-2014 only considers the evaporator 
fan heat, which is just one of the components that generates heat 
internally. Further, the proposed surface temperature approach would 
provide a direct measure of the overall heat transfer of heat-
contributing components within the case to the room, without assuming 
the proportion of heat transferred to either the cooling or heat 
rejection side.
    Therefore, DOE proposes in this NOPR that cooling mode testing 
include case surface heat transfer measured by means of four evenly 
spaced thermocouples placed on each case surface. The thermocouples 
would be positioned such that the case surface, when divided into 
quadrants, contains at least one thermocouple in each quadrant. If even 
spacing would result in a thermocouple being placed on an air inlet or 
exhaust grille, the thermocouple would be placed adjacent to the inlet 
or exhaust grille, maintaining the even spacing as closely as possible. 
To ensure accurate heat transfer estimates, DOE proposes to specify 
that temperature measurements be accurate to within 0.5 
[deg]F. DOE further proposes to average the four surface temperatures 
measurements on each side to obtain Tcase for that side.
    The surface area of each case side, Acase, would be 
calculated as the product of the two primary surface dimensions, as 
follows:

Acase_k = D1_k x D 2_k

Where:

D1 and D2 are the two primary dimensions of 
the case side ``k'' exposed to ambient air.
k represents the case sides including, front, back, right, left, 
top, and bottom.

    Heat transferred from all case sides to the indoor conditioned 
space would be calculated according to the following:

Qcase_cm = [Sigma]k{h x Acase\k x (Tcase\k - Tei){time} 

Where:

Qcase_cm is the total heat transferred from all case 
sides to the indoor conditioned space in cooling mode.
h is the convection coefficient, 4 Btu/h per square foot per [deg]F.
k represents the case sides including: front, back, right, left, 
top, and bottom.
Acase_k is the surface area of case side ``k'', in square 
feet.
Tcase_k is the average surface temperature of case side 
``k'', in [deg]F.
Tei is the average evaporator inlet air dry-bulb 
temperature, in [deg]F.
vi. Condensate Collection
    Many portable ACs include a feature to re-evaporate the condensate 
and remove it from the indoor space through the condenser exhaust air 
stream. This feature is performed by slinging or directing condensate 
that collects and drips off of the evaporator on to one or multiple 
condenser coil surfaces. All units in DOE's test sample included this 
feature. In the event that the condensate collection rate exceeds the 
removal rate of the auto-evaporation feature and the internal 
condensate collection bucket fills, all of the units provide a drain 
option to remove the collected condensate. Portable ACs typically ship 
with this drain sealed with a temporary plug, although a consumer-
supplied drain line may also be installed. Manufacturer setup 
instructions typically do not specify that a drain line be installed 
during normal operation, relying primarily instead on the auto-
evaporative condensate removal feature.
    In response to the May 2014 NODA, the California IOUs confirmed 
DOE's research and indicated that there are different methods of 
handling condensate. Units may include an internal reservoir with a 
fill sensor to interrupt operation until the reservoir is emptied, a 
heater to re-evaporate the water into the exhaust air stream, or 
slingers that pass the condensate over the condenser to re-evaporate 
condensate and improve heat transfer. The California IOUs recommended 
that DOE address the different means of condensate handling. 
(California IOUs, No. 5 at p. 4) DOE agrees that a portable AC test 
procedure should recognize various methods of condensate removal to 
ensure comparable results among units with different condensate removal 
approaches.
    DOE's investigative testing was conducted with a drain line 
attached to simplify condensate draining if necessary, but the line was 
elevated to simulate testing with the drain plug in place. Nonetheless, 
DOE observed that the auto-evaporation feature was effective for all 
test units under testing conditions so that no unit cycled off due to a 
full condensate bucket. Therefore, DOE proposes that the portable AC 
under test be set up in accordance with manufacturer instructions. If 
an auto-evaporative feature is provided along with a condensate drain, 
and the drain setup is unspecified, the drain plug would remain in 
place as shipped and no means of condensate removal would be installed 
for the duration of cooling mode testing. If the internal bucket fills 
during testing, the test would be invalid and halted, the drain plug 
would be removed, means would be provided to drain the condensate from 
the unit, and the test would be started from the beginning.
    Section 7.1.2 of AHAM PAC-1-2014 contains provisions for portable 
ACs that incorporate condensate pumps that cycle to dispose condensate 
collected by the unit. DOE found through market

[[Page 10229]]

research and by investigating units in its test sample that units that 
include a condensate pump typically include an auto-evaporative 
feature. However, the activation of the condensate pump may differ in 
different operating modes. For example, one unit in DOE's sample 
activated the condensate pump only in heating mode, with condensate 
removed solely via auto-evaporation in cooling mode. DOE did not 
observe any units in its test sample that depended upon only a 
condensate pump for removing condensate during cooling mode.
    Section 6.3.3 of AHAM PAC-1-2014 states that ``. . . equipment 
recommended as part of the air conditioner shall be in place.'' 
Therefore, DOE proposes that portable AC cooling mode testing would be 
performed in accordance with manufacturer installation and setup 
instructions, unless otherwise specified in the DOE test procedure. In 
addition, where available and as instructed by the manufacturer, DOE 
proposes that the auto-evaporation feature would be utilized for 
condensate removal during cooling mode testing. If no auto-evaporative 
feature is available, the gravity drain would be used. If no auto-
evaporative feature or gravity drain is available, or if the 
manufacturer specifies the use of an included condensate pump during 
cooling mode operation, then DOE proposes that the portable AC would be 
tested with the condensate pump enabled. For these units, DOE also 
proposes to require the use of Section 7.1.2 of AHAM PAC-1-2014 if the 
pump cycles on and off.
vii. Control Settings
    Portable ACs typically incorporate electronic controls that allow 
selection of the fan speed during cooling or heating mode. The highest 
fan speed will produce the most rapid rate of cooling or heating, while 
the lower fan speeds may be provided to reduce noise. Section 7.3.1 of 
AHAM PAC-1-2014 states that all adjustable settings, including fan 
speed, shall be set to achieve maximum capacity. Although the fan speed 
setting is clearly specified, it is not clear what setting should be 
selected for the cooling or heating setpoint. Many portable ACs have 
controls that allow consumers to select a target temperature, for 
example by setting the desired temperature or by adjusting a dial to a 
more or less cool setting. When the cooling setpoint temperature is 
lower than the ambient temperature, or higher than the ambient 
temperature in heating mode, the portable AC will operate continuously. 
AHAM PAC-1-2014 requires that the test chamber be maintained at 80.6 
[deg]F throughout the cooling mode test period, during which the unit 
must operate continuously, but does not specify a particular cooling 
setpoint temperature. To ensure that the test unit does not enter off-
cycle mode, the test operator must select a control setting that 
corresponds to a temperature lower than 80.6 [deg]F, particularly 
because no portable ACs in DOE's test sample included a ``continuous 
on'' setting. Because DOE acknowledges the potential for a unit to 
operate differently when cooling controls are set to different target 
temperatures below 80.6 [deg]F, DOE proposes during cooling mode 
testing that the fan be set at the maximum speed if the fan speed is 
user adjustable and the temperature controls be set to the lowest 
available value. Similarly, as discussed in section III.B.1.b.i, DOE 
proposes during heating mode testing that the fan be set at the maximum 
speed if the fan speed is user adjustable and the temperature controls 
be set to the highest available value. These settings would likely best 
represent the settings that a consumer would select to achieve the 
primary function of the portable AC, which is to cool or heat the 
desired space as quickly as possible and then to maintain these 
conditions.
    A number of test units in DOE's test sample included the option to 
oscillate the evaporator exhaust louvers to help circulate air 
throughout the conditioned space. Although AHAM PAC-1-2014 does not 
directly address louver oscillation, Section 7.3.1 of AHAM PAC-1-2014 
states that all adjustable setting such as louvers, fan speed, and 
special functions must be set for maximum capacity. Accordingly, if 
there is a setting that automatically opens and closes the louvers, 
this feature would be disabled for the entirety of the rating test 
period, and the louvers would be opened to allow maximum capacity. If 
there is a manual setting to control louver direction and opening size, 
in accordance with section 7.3.1 of AHAM PAC-1-2014, the louvers shall 
be fully open to provide maximum airflow and capacity, and be 
positioned parallel to the air flow. However, this provision does not 
address an oscillating louver function that maintains constant and 
maximum louver exhaust area while redirecting the evaporator exhaust 
air flow. DOE does note, though, that AHAM PAC-1-2014 requires a 
constant external static pressure that is consistent with typical 
operation. The static pressure is initially affected by the test 
instrumentation that is placed over the evaporator exhaust grille to 
capture and measure the air flow rate, temperature, and humidity, such 
that a variable speed fan is required to adjust the external static 
pressure to ensure it is representative of normal operation. If the 
louvers were oscillating during the test period, the external static 
pressure measured at the evaporator exhaust would vary cyclically and 
thus the test would no longer be compliant with the required 
conditions. Also, oscillating louvers may interfere with the 
temperature and humidity instrumentation and possibly dislodge them, 
which could impact the measured performance and the integrity of the 
test procedure. In addition, DOE lacks information on the percentage of 
time that this feature is selected among those units equipped with 
oscillating louvers. Therefore, to provide comparable testing results 
in cooling mode for products with and without a louver oscillation 
feature, DOE proposes that portable AC cooling mode testing be 
conducted with any louver oscillation feature disabled. If the feature 
is included but there is no option to disable it, testing shall proceed 
with the louver oscillation enabled, without altering the unit 
construction or programming. DOE requests feedback on the proposal to 
disable louver oscillation where available and to maximize louver 
opening, either manually or by disabling an automatic feature.
viii. Test Unit Placement
    Section 8.1.3 of ANSI/ASHRAE Standard 37 states that the outdoor 
condition test room must be of sufficient volume and circulate air in a 
manner that does not change the normal air-circulation patterns of the 
unit under test. Specifically, the dimensions of the room must be 
sufficient to ensure that the distance from any room surface to any 
equipment surface where air is discharged is not less than 6 feet and 
the distance to all other equipment surfaces must be no less than 3 
feet. However, no comparable requirements are specified for the indoor 
test room. When tested according to AHAM PAC-1-2014 and ANSI/ASHRAE 
Standard 37, a portable AC is set up entirely within the indoor 
condition test room with the evaporator exhaust connected to 
instrumentation and ducted away from the test unit, and the condenser 
exhaust ducted with instrumentation to the outdoor test room. In that 
case, the requirements in Section 8.1.3 of ASNI/ASHRAE Standard 37 are 
not applicable, as no part of the case is within the outdoor condition 
test room. Instead, the portable AC is placed in the indoor condition 
test room, where walls and other obstructions may impede air flow

[[Page 10230]]

for the evaporator inlet for all configurations, and the condenser 
inlet for single-duct units. Therefore, to ensure performance is as 
repeatable and representative as possible, DOE concludes that the same 
distance requirements included in Section 8.1.3 of ANSI/ASHARE Standard 
37 would be applicable to the indoor condition test room when testing 
portable ACs. DOE proposes that for all portable AC configurations, 
there must be no less than 6 feet from the evaporator inlet to any 
chamber wall surfaces, and for single-duct units, there must be no less 
than 6 feet from the condenser inlet surface to any other wall surface. 
Additionally, there must be no less than 3 feet between the other 
surfaces of the portable AC with no air inlet or exhaust (other than 
the bottom of the unit) and any wall surfaces.
ix. Electrical Supply
    Section 7.3.2 of AHAM PAC-1-2014 does not require a specific test 
voltage, but rather states that the nameplate voltage shall be used. 
DOE notes that its dehumidifier test procedure requires a test voltage 
of either 115 or 230 volts (V), and these voltages would be comparable 
to those required for portable ACs, which are similar consumer 
products. To maintain repeatability and reproducibility for portable AC 
testing, DOE proposes that for active mode testing, the input standard 
voltage would be maintained at 115 V 1 percent. DOE also 
proposes that the electrical supply be set to the nameplate listed 
rated frequency, maintained within 1 percent.
b. Heating Mode
    In response to the May 2014 NODA, DOE received a comment from the 
California IOUs suggesting that any future DOE test procedure for 
portable ACs include a measure of heating mode energy consumption. They 
stated that about 25 percent of models for sale at a major home 
improvement retailer include a heating function, and all of these 
models were marketed as a portable AC. The California IOUs suggested 
that DOE should ensure that the scope of a proposed test procedure that 
covers any products marketed as a portable AC also include testing the 
product's heating performance. (California IOUs, No. 5 at pp. 3-4)
    DOE is aware that certain portable ACs, including some of the units 
in DOE's test sample, incorporate a heating function in addition to 
cooling and air-circulation modes. During teardowns, DOE found that 
there are two primary approaches to implement a heating function for 
portable ACs. The first, and most common, is a reverse-cycle heat pump, 
which requires a four-way reversing solenoid valve in the refrigerant 
loop that reroutes the refrigerant flow and converts the cooling air 
conditioning system to a heat pump. The second type of heating that DOE 
observed during teardowns was a resistance heater installed adjacent to 
the evaporator and in line with the evaporator exhaust air stream.
    In consideration of the comment received and DOE's market and 
teardown observations, DOE conducted additional research to determine 
whether it could incorporate appropriate test methodology to measure 
heating mode energy consumption in a DOE portable AC test procedure.
i. General Test Approach
    ANSI/ASHRAE Standard 37, the basis for DOE's proposed air enthalpy 
cooling mode test procedure, is intended for heat pump equipment in 
addition to air conditioning equipment. Section 1.1 of ANSI/ASHRAE 
Standard 37 states that the purpose of the standard is, in addition to 
determining cooling capacity of air conditioning equipment, providing 
methods to determine cooling and heating capacities of heat pump 
equipment. DOE reviewed ANSI/ASHRAE Standard 37 and determined that the 
same test chamber and instrumentation requirements and capacity 
calculations would apply to portable AC heating mode testing as for the 
proposed cooling mode testing. Further, as with the cooling mode test, 
the unit configurations included in AHAM PAC-1-2014 would be applicable 
to a heating mode test. Therefore, DOE proposes that the test unit be 
set up for a heating mode energy consumption test in accordance with 
the unit and duct setup requirements of AHAM PAC-1-2014, including 
those in Table 2 and Figure 1 of that standard. DOE also proposes to 
specify the same test requirements as for cooling mode, including 
infiltration air, duct heat transfer, case heat transfer, control 
settings, and test unit placement, discussed in the subsections of 
section III.B.1.a of this NOPR. However, DOE proposes that the 
temperature setpoint for heating mode be at the highest available 
temperature setting to ensure continuous operation.
ii. Ambient Test Conditions
    ANSI/ASHRAE Standard 37 specifies the test setup, instrumentation, 
and test conduct, but does not specify the ambient test conditions for 
testing. For cooling mode, AHAM PAC-1-2014 provides the ambient test 
conditions for testing. To determine appropriate test conditions for a 
heating mode test, DOE reviewed ANSI/Air-Conditioning, Heating, and 
Refrigeration Institute (AHRI) 210/240--2008, ``Performance Rating of 
Unitary Air-Conditioning and Air-Source Heat Pump Equipment'' (ANSI/
AHRI 210/240), which provides test conditions for determining 
performance of ACs and heat pumps. Table 4 of Section 6.1.4.2 of ANSI/
AHRI 210/240 provides three test conditions in heating mode for a heat 
pump with a single-speed compressor and a fixed-speed indoor fan. The 
indoor air temperatures are the same for all three tests, 70 [deg]F 
dry-bulb and 60 [deg]F wet-bulb. For the outdoor air inlet 
temperatures, the high-temperature test, ``H1,'' requires 47 [deg]F 
dry-bulb and 43 [deg]F wet-bulb, while the frost accumulation test, 
``H2,'' requires 35 [deg]F dry-bulb and 33 [deg]F wet-bulb, and the 
low-temperature test, ``H3,'' specifies 17 [deg]F dry-bulb and 15 
[deg]F wet bulb.
    DOE believes that the test conditions for H1 are the most 
representative of typical heating mode use for portable ACs, which are 
likely used as supplemental or low-capacity heaters when a central 
heating system is not necessary or operating. Therefore, DOE proposes 
the following ambient air test conditions as shown in Table III.8 
below, with the test configurations referring to the test 
configurations referenced in Table 2 of AHAM PAC-1-2014. Test 
Configuration 3 is applicable to dual-duct portable ACs, and Test 
Configuration 5 is applicable to single-duct portable ACs. DOE notes 
that the terms ``Evaporator'' and ``Condenser'' refer to the heat 
exchanger configuration in cooling mode, not the reverse-cycle heating 
mode. This terminology maintains consistency with the cooling mode test 
conditions specification and would still be applicable for portable ACs 
that incorporate a resistance heater.

[[Page 10231]]

                              Table III.8--Standard Rating Conditions--Heating Mode
----------------------------------------------------------------------------------------------------------------
                                                   Evaporator inlet air, [deg]F     Condenser inlet air, [deg]F
                                                             ([deg]C)                        ([deg]C)
               Test configuration                ---------------------------------------------------------------
                                                     Dry LBulb       Wet LBulb       Dry bulb        Wet bulb
----------------------------------------------------------------------------------------------------------------
3...............................................     70.0 (21.1)     60.0 (15.6)     47.0 (8.33)     43.0 (6.11)
5...............................................     70.0 (21.1)     60.0 (15.6)     70.0 (21.1)     60.0 (15.6)
----------------------------------------------------------------------------------------------------------------

iii. Adjusted Heating Capacity Calculation
    Under the proposed heating mode testing conditions, DOE expects 
that the calculations provided by AHAM PAC-1-2014 would result in 
negative cooling (i.e., heating) capacity values because the outdoor 
side temperature is lower than the indoor side temperature. Therefore, 
DOE proposes to multiply the resulting capacity by -1 to produce a 
positive value that would represent the amount of heating produced 
rather than cooling. Further, because heat transfer from the ducts and 
the case to the room would decrease the net heating in the conditioned 
space, these negative heating values must be added to the heating 
capacity in the adjusted capacity calculation. For the infiltration air 
heat transfer, the lower temperature of the infiltration air compared 
to the evaporator inlet temperature results in a negative temperature 
differential in the heat transfer calculation, which would result in a 
negative value for the heat contribution to the conditioned space. 
Thus, the infiltration air provides net cooling, and the resulting 
negative value would also be added to the heating capacity to obtain 
the adjusted heating capacity (AHC) in the heating mode, expressed in 
Btu/h, according to the following:

AHC = Capacityhm + Qduct\hm + Qcase\hm + Qinfiltration\hm

Where:

Capacityhm is the heating capacity measured in section 
4.1.2 of this appendix.
Qduct_hm is the duct heat transfer while operating in 
heating mode, measured in section 4.1.2 of this appendix.
Qcase_hm is the case heat transfer while operating in 
heating mode, measured in section 4.1.2 of this appendix.
Qinfiltration_hm is the infiltration air heat transfer 
while operating in heating mode, measured in section 4.1.2 of this 
appendix.
2. Off-Cycle Mode
    Certain portable ACs maintain blower operation without activation 
of the compressor after the temperature setpoint has been reached, 
rather than entering standby mode or off mode, or may operate with a 
combination of periods of blower operation and standby mode after 
reaching the setpoint. The fan-only operation may be intended to draw 
air over the internal thermostat to monitor ambient conditions, or may 
occur immediately following a period of cooling mode to defrost and dry 
the evaporator coil (or the condenser coil when operating in reverse-
cycle heating mode). The blower may operate continuously, or may cycle 
on and off intermittently. In addition, some units allow the consumer 
to select operation of the blower continuously for air circulation 
purposes, without activation of the refrigeration system.
    The existing industry portable AC test procedures do not presently 
contain provisions to measure energy use during this fan-only 
operation. However, DOE recently proposed a method for determining fan-
only mode energy use in DOE's test procedure for dehumidifiers based on 
existing methodologies for measuring power consumption in standby mode 
and off mode (hereinafter referred to as the ``dehumidifier test 
procedure NOPR''). 79 FR 29272 (May 21, 2014). In the dehumidifier test 
procedure NOPR, DOE proposed measuring fan-only mode average power by 
adjusting the setpoint to a relative humidity that is higher than the 
ambient relative humidity to ensure that the refrigeration system does 
not cycle on. To minimize testing burden, DOE proposed that the testing 
may be conducted immediately after the conclusion of dehumidification 
mode testing while maintaining the same ambient conditions, or may be 
conducted separately under the test conditions specified for standby 
mode and off mode testing. Id. at 29291.
    In the dehumidifier test procedure NOPR, DOE observed that the 
period of cyclic fan operation was approximately 10 minutes for 
dehumidifiers with cyclical fan-operation in fan-only mode. In 
addition, DOE's research indicated that some units may cycle on for a 
period of a few minutes per hour. In order to obtain a representative 
average measure of fan-only mode power consumption, DOE proposed that 
the fan power be measured and averaged over a period of 1 hour for fan-
only mode in which the fan operates continuously. For fan-only mode in 
which the fan operates cyclically, the average fan-only mode power 
would be measured over a period of 3 or more full cycles for no less 
than 1 hour. DOE also clarified that units with adjustable fan speed 
settings would be set to the maximum fan speed during fan-only mode 
testing, because the maximum speed is typically recommended to 
consumers as the setting that produces the maximum moisture removal 
rate. Id.
    DOE subsequently published a supplemental notice of proposed 
rulemaking (SNOPR) on February 4, 2015, that modified the proposal in 
the dehumidifier test procedure NOPR based on feedback from interested 
parties and further research (hereinafter referred to as the 
``dehumidifier test procedure SNOPR''). 80 FR 5994. DOE withdrew the 
fan-only mode definition proposed in the dehumidifier test procedure 
NOPR and instead modified the proposed ``off-cycle mode'' definition to 
encompass all operation when dehumidification mode has cycled off after 
the humidity setpoint has been reached. DOE proposed to define off-
cycle mode as a mode in which the dehumidifier:
    (1) Has cycled off its main moisture removal function by 
humidistat, humidity sensor, or control setting;
    (2) May or may not operate its fan or blower; and
    (3) May reactivate the main moisture removal function according to 
the humidistat or humidity sensor signal.
    (Id.)
    During investigative testing for this rulemaking, DOE found that 
all portable ACs in its test sample operate the fan in off-cycle mode, 
similar to dehumidifiers, once cooling mode operation reduces the 
ambient temperature below the set point. DOE investigated the approach 
for measuring this fan operation as a part of off-cycle mode, as was 
proposed in the dehumidifier test procedure SNOPR, and found that it 
was applicable to portable ACs. Table III.9 shows the results from this 
portable AC off-cycle mode investigative testing.

[[Page 10232]]

                                     Table III.9--Power in Off-Cycle Mode *
----------------------------------------------------------------------------------------------------------------
                                   Single-duct                                               Dual-duct
----------------------------------------------------------------------------------------------------------------
                              Unit                                Unit power (W)       Unit       Unit power (W)
----------------------------------------------------------------------------------------------------------------
SD1.............................................................          175.0              DD1            69.3
SD3.............................................................           60.4              DD2            76.9
SD4.............................................................           85.1              DD4           224.9
SD5.............................................................          109.6              DD5            47.6
SD6.............................................................           80.14             DD6            76.3
SD7.............................................................           77.0              DD7            74.8
SD8.............................................................          211.0
SD9.............................................................           91.2
SD10............................................................          108.3
SD11............................................................           87.9
SD12............................................................           49.7
SD13............................................................           50.0
SD14............................................................           55.4
SD15............................................................           38.9
SD16............................................................           95.1
----------------------------------------------------------------------------------------------------------------
* Data for units SD2 and DD3 were not available

    Due to the similarity between dehumidifiers and portable ACs, and 
to maintain harmonization among similar test procedures, DOE proposes 
in this NOPR that off-cycle mode for portable ACs be defined as 
proposed in the dehumidifier test procedure SNOPR, modified for 
portable AC operation in either cooling or heating mode. Specifically, 
DOE proposes to define off-cycle mode as a mode in which the portable 
air conditioner:
    (1) Has cycled off its main heating or cooling function by 
thermostat or temperature sensor;
    (2) May or may not operate its fan or blower; and
    (3) Will reactivate the main cooling or heating function according 
to the thermostat or temperature sensor signal.
    In the dehumidifier test procedure SNOPR, DOE proposed that off-
cycle mode measurement begin immediately following compressor operation 
for the dehumidification mode test to ensure sufficient condensation on 
the evaporator to initiate fan operation for those units that dry the 
evaporator coil. DOE asserted that conducting the off-cycle mode test 
subsequent to the dehumidification mode test would capture all energy 
use of the dehumidifier under conditions that meet the newly proposed 
off-cycle mode definition, including fan operation intended to dry the 
evaporator coil, sample the air, or circulate the air. 80 FR 5994.
    In this NOPR, DOE proposes that portable AC off-cycle mode energy 
use be measured five minutes after the termination of compressor 
operation in cooling mode. Because the evaporator is still cool at the 
end of compressor operation in cooling mode, additional room cooling is 
possible through continued fan operation at relatively low energy 
consumption. Therefore, DOE proposes the 5-minute delay before the 
start of off-cycle mode testing to prevent penalizing manufacturers for 
utilizing the cooling potential of the evaporator following the 
compressor cycle. Continued fan operation once that cooling potential 
is no longer available would be included as off-cycle mode energy 
consumption and factored into the CEER measurement.
    In the dehumidifier test procedure SNOPR, DOE determined, based on 
data from its testing, that 2 hours is a typical off-cycle duration and 
would therefore be a representative test duration for off-cycle mode. 
80 FR 5994. In lieu of field data for portable AC operation in off-
cycle mode, and due to the similarity between typical portable 
dehumidifiers and portable ACs, DOE believes that the analysis 
conducted for dehumidifiers is representative for portable ACs. 
Therefore, DOE proposes that the off-cycle mode test begin 5 minutes 
after the completion of the cooling mode test and end after a period of 
2 hours. DOE further proposes that the electrical supply be the same as 
specified for cooling mode, as discussion section III.B.1.a.ix, and 
that this measurement be made using the same power meter specified for 
standby mode and off mode, as discussed in section III.3.
    DOE further proposes to require that, for units with adjustable fan 
speed settings, the fan be set at the maximum speed during fan-only 
mode testing, because the maximum speed is typically recommended to 
consumers as the setting that produces the maximum rate of cooling or 
heating.
    DOE estimates that off-cycle mode energy consumption is similar for 
periods following both heating mode and cooling mode because the fan 
speed setting is selected by the same controls and all other 
significantly energy consumptive components are disabled. Therefore, to 
minimize testing burden, DOE proposes that off-cycle mode testing be 
conducted only after cooling mode. Annual hours for off-cycle mode 
would be allocated for the total hours in this mode following either 
cooling mode or heating mode.
3. Standby Mode and Off Mode
    Section 310 of the Energy Independence and Security Act of 2007 
(EISA 2007), Public Law 110-140, amended EPCA to require DOE to amend 
the test procedures for covered products to address standby mode and 
off mode energy consumption. Specifically, the amendments require DOE 
to integrate standby mode and off mode energy consumption into the 
overall energy efficiency, energy consumption, or other energy 
descriptor for each covered product unless the current test procedures 
already fully account for such consumption or integration of such test 
procedure is technically infeasible. If integration is technically 
infeasible, DOE must prescribe a separate standby mode and off mode 
energy use test procedure, if technically feasible. (42 U.S.C. 
6295(gg)(2)(A)) Any such amendment must consider the most current 
versions of IEC Standard 62301, ``Household electrical appliances--
Measurement of standby power,'' and IEC Standard 62087, ``Methods of 
measurement for the power consumption of audio, video, and related 
equipment.'' Id.
    In addition, these amendments direct DOE to incorporate standby 
mode and

[[Page 10233]]

off mode energy use into any final rule establishing or revising an 
energy conservation standard for a covered product adopted after July 
1, 2010. If it is not feasible to incorporate standby mode and off mode 
into a single amended or new standard, then the statute requires DOE to 
prescribe a separate standard to address standby mode and off mode 
energy consumption. (42 U.S.C. 6295(gg)(3))
a. Mode Definitions
    Should DOE determine to classify portable ACs as a covered product, 
DOE would be required to promulgate energy conservation standards that 
incorporate energy use in active mode, standby mode, and off mode into 
a single metric, if feasible, in accordance with EISA 2007. (42 U.S.C. 
6295 (gg)(3)) In addition, a DOE test procedure for portable ACs would 
be required to measure and, if feasible, integrate standby mode and off 
mode energy consumption into the overall energy descriptor. (42 U.S.C. 
6295 (gg)(2)) Therefore, DOE is proposing the following definitions and 
methods to measure standby mode and off mode energy consumption for 
portable ACs. Based on the similar components and primary function to 
room ACs and dehumidifiers, DOE proposes standby mode and off mode 
definitions for portable ACs that are similar to those included in the 
room AC and dehumidifier test procedures found in appendix F and 
appendix X, respectively, codified at 10 CFR part 430, subpart B.
    ``Standby mode'' would mean any mode where a portable air 
conditioner is connected to a mains power source and offers one or more 
of the following user-oriented or protective functions which may 
persist for an indefinite time:
    (a) To facilitate the activation of other modes (including 
activation or deactivation of active mode) by remote switch (including 
remote control), internal sensor, or timer; or
    (b) Continuous functions, including information or status displays 
(including clocks) or sensor-based functions. A timer is a continuous 
clock function (which may or may not be associated with a display) that 
provides regular scheduled tasks (e.g., switching) and that operates on 
a continuous basis.
    DOE is aware of two relevant modes that would meet the proposed 
definition of standby mode for portable ACs: (1) Inactive mode and (2) 
bucket-full mode.
    Portable ACs often include a digital control board with switches or 
a remote control device to modify settings and initiate or disable 
cooling, heating, or air circulation. When the unit is plugged in and 
awaiting a signal to initiate one of the active modes, it would be 
considered to be in ``inactive mode.'' That is, inactive mode would be 
defined as a standby mode that facilitates the activation of active 
mode by remote switch (including remote control), internal sensor, or 
timer, or that provides continuous status display.
    Unlike room ACs, portable ACs are installed and operated entirely 
within the conditioned space, and thus do not have a means to discharge 
any liquid condensate directly outdoors. Although many portable ACs 
incorporate a feature to re-evaporate the condensate and exhaust it in 
the condenser outlet air stream, under certain ambient conditions this 
moisture removal rate may not be high enough to exhaust all of the 
condensate. Thus, portable ACs may enter a ``bucket-full mode'' when 
the condensate level in the internal collection container reaches a 
manufacturer-specified threshold or the collection container is 
removed; any cooling, heating, or air-circulation functions are 
disabled; and an indication is provided to the consumer that the 
container is full. The portable AC will reactivate the main cooling, 
heating, or air-circulation function once the collection container is 
drained or emptied and is in place in the unit.
    DOE is also aware of an additional low-power mode for portable ACs 
with power consumption levels comparable to inactive mode and bucket-
full modes. ``Delay-start mode'' facilitates activation of an active 
mode by a timer. Due the similarity in power consumption levels between 
delay-start mode and inactive mode, DOE proposes to consider the power 
consumption in inactive mode as representative of delay-start mode and 
to include the operating hours for delay-start mode in the estimate for 
inactive mode operating hours for the purposes of calculating a 
combined metric. In other words, DOE is not proposing to measure delay-
start mode. DOE believes that this approach will minimize test burden 
and simplify testing and determination of overall performance.
    Although all units in DOE's test sample had electronic controls and 
therefore default to inactive mode when connected to a power source, 
DOE recognizes that some portable ACs may instead utilize 
electromechanical controls, and therefore may employ an ``off mode,'' 
in which a portable AC is connected to a mains power source and is not 
providing any active mode or standby mode function, and where the mode 
may persist for an indefinite time. An indicator that only shows the 
user that the product is in the off position is included within the 
classification of an off mode.
b. Determination of Standby Mode and Off Mode Power Consumption
    In accordance with the requirements of EISA 2007, DOE is proposing 
to specify testing equipment and conditions for measuring standby mode 
and off mode power consumption in the portable AC test procedure based 
on the provisions from IEC Standard 62301. (42 U.S.C. 6295 (gg)(1)(B)) 
The measured wattages would then be used in calculations to determine 
standby mode and off mode energy consumption. DOE has reviewed IEC 
Standard 62301, and tentatively concluded that it is generally 
applicable to portable ACs, with certain clarifications, and notes that 
a similar determination has already been made for the DOE test 
procedures for closely-related covered products, such as dehumidifiers 
and room air conditioners. AHAM PAC-1-2014 also references IEC Standard 
62301 for portable AC standby power measurements.
    In examining portable AC operation, DOE recognizes that there is a 
certain commonality between inactive mode and bucket-full mode, in that 
there are no major energy-consuming components energized and there is 
typically only a display to the consumer that provides information as 
to product status. Therefore, DOE expects that the power consumption 
these two modes is comparable.
    In the interest of reducing testing burden, DOE proposes not to 
require the power consumption in both of these modes be measured 
individually. Rather, DOE proposes that the power consumption in just 
inactive mode would be measured, and the annual hours assigned to that 
power measurement would be the sum of annual hours for inactive mode 
and bucket-full mode. DOE requests comment on this proposed 
simplification of testing, including whether the resulting calculation 
would adequately represent product energy use and whether it would 
instead be appropriate to measure each mode separately.
    DOE proposes that the test room ambient air temperatures for 
standby mode and off mode testing would be specified in accordance with 
Section 4, Paragraph 4.2 of IEC Standard 62301. The IEC standard 
specifies a temperature range of 73.4  9 [deg]F, while the 
proposed DOE test procedure for portable ACs would specify an indoor-
side test room ambient temperature of 80.6  0.5 [deg]F dry-
bulb temperature for the cooling mode test and 70.0  0.5 
[deg]F

[[Page 10234]]

dry-bulb temperature for the heating mode test. This proposed test 
procedure would allow manufacturers of portable ACs to conduct active 
mode efficiency testing and standby mode and off mode power consumption 
testing simultaneously in the same room on multiple portable ACs, as 
long as the temperature and setup requirements (e.g., duct setup, 
instrumentation, unit placement) for both tests are met. Alternatively, 
the proposed temperature specifications taken from IEC Standard 62301 
would allow a manufacturer that opts to conduct standby mode and off 
mode testing separately from active mode testing to use the ambient 
temperature requirements of 73.4  9 [deg]F. DOE requests 
comment on the appropriateness of this proposed test room ambient 
temperature range. DOE further proposes that the portable AC would be 
installed in accordance with the unit installation and preparation 
instructions in Section 5.2 of IEC 62301, while disregarding the 
provisions regarding batteries and the determination, classification, 
and testing of relevant modes. DOE is not aware of any portable ACs 
that incorporate batteries other than in remote controls.
    For the duration of standby-mode and off-mode testing, DOE proposes 
that the electrical supply voltage shall be maintained at 115 V 1 percent and supply frequency would be maintained at the rated 
frequency within 1 percent. DOE notes that these 
requirements are consistent with those proposed for cooling mode, and 
the tolerances are in accordance with Section 4, Paragraph 4.3.1 of IEC 
Standard 62301. The supply voltage waveform and wattmeter would comply 
with the requirements in Section 4, Paragraphs 4.3.2 and 4.4 of IEC 
Standard 62301, respectively.
    DOE is aware that some portable ACs may reduce power consumption 
after a period of user inactivity after entering standby mode or off 
mode. For products whose power consumption in standby mode or off mode 
varies in this manner during testing, DOE proposes that the test for 
inactive mode and off mode be conducted after the power level has 
dropped to its lowest level, as discussed in Note 1 in Section 5.1 of 
IEC Standard 62301. DOE further proposes that the test procedure in 
Section 5, Paragraph 5.3.2 of IEC Standard 62301 then be followed for 
inactive mode, off-cycle mode, and off mode, as available on the test 
unit.
4. Combined Energy Efficiency Ratio
    In accordance with the requirements of EISA 2007, DOE is required 
for covered products to establish a single energy conservation standard 
metric that incorporates standby mode and off mode energy use, if 
feasible, for standards adopted after July 1, 2010. (42 U.S.C. 
6295(gg)(3)(A)) For certain products, including dehumidifiers and room 
ACs, DOE has combined the energy use for active modes, off-cycle mode, 
standby modes, and off mode into a single efficiency metric using a 
weighted average based on annual operating hours in each mode. DOE 
proposes a similar approach for portable ACs based on operating hours 
per mode which may be available on the unit, including cooling mode, 
heating mode, off-cycle mode (with and without fan operation), inactive 
mode (including bucket-full mode), and off mode. As discussed 
previously in section III.B.1 of this NOPR, DOE is not addressing 
dehumidification mode for portable ACs in this proposal because the 
annual operating hours are likely small and it is not technically 
feasible to integrate the efficiency descriptor with an EER metric.
a. CEER Calculations
    DOE proposes the following approach to combine energy use in each 
of the considered modes into a single integrated efficiency metric, 
CEER. Average power in each mode would be measured according to the 
proposals in section III.B.1.a through section III.B.1.2 and section 
III.B.3 of this NOPR, and then individually multiplied by the annual 
operating hours for each respective mode, discussed in section III.4.b 
of this NOPR.

AECm = Pm x tm x k

Where:

AECm is the annual energy consumption in each mode, in 
kWh/year.
Pm is the average power in each mode, in watts (W).
tm is the number of annual operating hours in each mode.
m designates the operating mode (``cm'' cooling, ``hm'' heating, 
``oc'' off-cycle, and ``im'' inactive or ``om'' off mode).
k is 0.001 kWh/Wh conversion factor for watt-hours to kilowatt-
hours.

    Total annual energy consumption in all modes except cooling and 
heating would be calculated as follows.

AECT = [Sigma]mAECm

Where:

AECT is the total annual energy consumption attributed to 
all modes except cooling and heating, in kWh/year.
AECm is the annual energy consumption in each mode, in 
kWh/year.
m represents the operating modes included in AECT (``oc'' 
off-cycle, and ``im'' inactive or ``om'' off mode).

    In this NOPR, DOE proposes in 10 CFR 430.23 that the annual energy 
consumption in cooling mode, AECcm and the total annual 
energy consumption in all modes except cooling and heating, 
AECT, would be utilized in calculating the estimated annual 
operating cost. The sum of the two annual energy consumption metrics 
would then be multiplied by a representative average unit cost of 
electrical energy in dollars per kilowatt-hour as provided by the 
Secretary to obtain the estimated annual operating cost.
    For units with only cooling mode, a combined cooling mode EER 
(CEERcm) can be calculated. For purposes of comparison, DOE 
proposes calculating a CEERcm for units that also include 
heating mode. In this case, the metric would be calculated assuming 
heating mode is not used and therefore, the operating hours that would 
have been attributed to heating mode and other associated operating 
modes during the heating season would be apportioned as for portable 
ACs without a heating mode. DOE believes that the resulting 
CEERcm is a meaningful metric for portable ACs without a 
heating function, a basis for comparing cooling mode efficiency for 
units that include heating function, as well as a metric that could be 
compared to other cooling products, such as room ACs.
[GRAPHIC] [TIFF OMITTED] TP25FE15.004

Where:

CEERcm is the combined energy efficiency ratio in cooling 
mode, in Btu/Wh.
ACC is the adjusted cooling capacity, in Btu/h.
AECcm is the annual energy consumption in cooling mode, 
in kWh/year.
AECT is the total annual energy consumption attributed to 
all modes except cooling and heating, in kWh/year.
t is the number of hours per year, 8,760.
k is 0.001 kWh/Wh conversion factor for watt-hours to kilowatt-
hours.

    For portable ACs without a heating function, the overall energy 
efficiency metric, or CEER, would be equal to the CEERcm. 
However, for units with both cooling and heating mode, the overall 
CEER, a weighted average of the cooling and heating mode capacities and 
energy consumption in all applicable modes, would be calculated as 
follows.

[[Page 10235]]

[GRAPHIC] [TIFF OMITTED] TP25FE15.005

Where:

CEER is the combined energy efficiency ratio, in Btu/Wh.
ACC is the adjusted cooling capacity, in Btu/h.
AHC is the adjusted heating capacity, in Btu/h.
hcm and hhm are the cooling and heating mode 
operating hours, respectively.
AECcm is the annual energy consumption in cooling mode, 
in kWh/year.
AEChm is the annual energy consumption in heating mode, 
in kWh/year.
AECT is the total annual energy consumption attributed to 
all modes except cooling and heating, in kWh/year.
t is the number of hours per year, 8,760.
k is 0.001 kWh/Wh conversion factor for watt-hours to kilowatt-
hours.
b. Mode Annual Operating Hours
    DOE developed several estimates of portable AC annual operating 
mode hours for cooling, heating, off-cycle, and inactive or off modes. 
DOE proposes the CEER calculations and proposes one of the estimates of 
annual mode hours that would be used to obtain an integrated measure of 
energy use in all operating modes. DOE requests comment on the proposed 
CEER calculation and estimates.
    Because the primary function of portable ACs and room ACs is 
similar, DOE considered the room AC annual operating hours presented in 
the room AC test procedure NOPR (hereinafter referred to as ``the room 
AC test procedure NOPR'') \12\ as a proxy for portable AC usage in this 
analysis. In the room AC test procedure NOPR, DOE estimated that half 
of all room ACs are unplugged for half of the year. 73 FR 74639, 74648. 
Averaging this estimated unplugged time over all units resulted in a 
total 2,190 unplugged hours per unit in which no energy is consumed, 
leaving 6,570 hours in which the unit is plugged in. DOE further 
estimated that the primary cooling season is 90 days per year, or 2,160 
hours. Id. Portable ACs, however, are likely to be unplugged for a 
greater number of hours per year during the cooling season because, 
portable ACs are readily moveable products that are simpler to install 
and uninstall than room ACs. Additionally, because a portable AC and 
associated ducting extend into the room, consumers would be more likely 
to unplug and store a portable AC than a room AC, which does not extend 
far into the room. Therefore, DOE estimated that three quarters of all 
portable ACs are unplugged for all annual hours outside of the cooling 
season (6,600 hours per unit), and that the remaining one quarter of 
portable ACs are unplugged for half of the annual hours outside the 
cooling season (3,300 hours per unit). Based on the weighted average 
presented above, portable ACs would spend 5,775 unplugged hours and 825 
plugged-in hours outside of the cooling season.
---------------------------------------------------------------------------

    \12\ See 73 FR 74639 (Dec.9, 2008).
---------------------------------------------------------------------------

    However, DOE notes that these calculations consider use of portable 
ACs only during the cooling season. As discussed above in section 
III.1.b, certain portable ACs may provide a heating function and 
therefore may be operated during the heating season. Although DOE 
believes that the room AC cooling season length is relevant and 
representative of the portable AC cooling season due to the similar 
function provided to the consumer, DOE does not believe that the 2,160 
hours estimated for cooling season would be representative of the 
heating season length. Therefore, DOE researched portable AC heating 
season length. As a starting point, DOE looked to the furnace test 
procedure located at appendix N of 10 CFR part 430, which identifies 
the heating season length as 4,160 hours.
    To refine this estimate for portable ACs, DOE performed a climate 
analysis using 2012 hourly ambient temperature data from the National 
Climatic Data Center (NCDC) of the National Oceanic and Atmospheric 
Administration (NOAA), collected at weather stations in 44 
representative states. DOE first calculated the number of annual hours 
per state associated with each temperature (in 1 [deg]F intervals) from 
the NCDC data. DOE then reviewed data from the 2009 Residential Energy 
Consumption Survey (RECS) \13\ to identify room AC use in the different 
geographic regions. Because no portable AC-specific usage data were 
available through RECS, DOE assumed this data would be representative 
of portable AC use. DOE found that of the 25.9 million homes that 
reported using room ACs, the majority were in the Northeast region (9.6 
million homes), though significant usage was recorded in the remaining 
regions: Midwest (5.8 million), South (6.5 million), and West (4 
million). DOE observed that all sub-regions in the survey showed room 
AC use; therefore, all sub-regions were included in DOE's analysis, 
along with data for individual states or combinations of small numbers 
of states within these sub-regions where provided in RECS.
---------------------------------------------------------------------------

    \13\ RECS data are available at: http://www.eia.gov/consumption/
residential/data/2009/``www.eia.gov/consumption/residential/data/
2009/.
---------------------------------------------------------------------------

    Based on the RECS ownership data, DOE used a weighted-average 
approach to combine the individual states' total number hours per year 
at or below a certain temperature to determine the average number of 
hours at or below any given temperature for each sub-region represented 
by the RECS data. DOE used a similar weighted average to combine the 
sub-region data for each region and subsequently combine the regional 
data into a single representative number of hours per year at or below 
any given temperature. DOE found, on average, 4,388 hours per year with 
ambient temperatures at or below 55 [deg]F. DOE selected 55 [deg]F as a 
threshold for determining heating season based on a New York City 
regulation that requires buildings to be heated when the outdoor 
temperature drops below that level.\14\ However, DOE notes that 
portable ACs are typically not used as the primary heating appliance in 
a home, and therefore may be utilized to supplement the home's heating 
system. Because this supplemental heating is likely only necessary at 
low outdoor temperatures, DOE determined, as a third estimate, the 
number of hours in 2012 that average national ambient temperatures were 
at or below 45 [deg]F--2,903 hours. DOE then calculated the number of 
plugged in and unplugged hours outside of heating and cooling season 
for each of the three estimates presented above for portable ACs with 
heating mode. Table III.10 shows the operating season hourly breakdowns 
for four cases: Cooling Only Estimate, Cooling/Heating Estimate 1 (the 
furnace fan heating season length), Cooling/Heating Estimate 2 (heating 
season based on hours at or below 55 [deg]F), and Cooling/Heating 
Estimate 3 (heating season based on hours at or below 45 [deg]F).
---------------------------------------------------------------------------

    \14\ More information can be found at: www.nyc.gov/html/hpd/html/tenants/heat-and-hot-water.shtml.

[[Page 10236]]

                         Table III.10--Seasonal and Remaining Unplugged/Plugged-In Hours
----------------------------------------------------------------------------------------------------------------
                                                                     Cooling/        Cooling/        Cooling/
                                                   Cooling only       heating         heating         heating
                                                                    estimate 1      estimate 2      estimate 3
----------------------------------------------------------------------------------------------------------------
Annual Hours....................................           8,760           8,760           8,760           8,760
Cooling Season..................................           2,160           2,160           2,160           2,160
Heating Season..................................               0           4,160           4,388           2,903
Remaining Annual Unplugged Hours................           5,775           2,135           1,936           3,235
Remaining Annual Plugged-In Hours...............             825             305             277             462
----------------------------------------------------------------------------------------------------------------

    DOE further estimated the hours associated with each operating mode 
within the cooling and heating seasons. Because the primary cooling 
function is similar between portable ACs and room ACs, DOE believes 
that the mode hours in cooling season would be apportioned similarly 
for both products. In its room AC analysis, DOE determined that, for 
units capable of all operating modes, 750 operating hours would be in 
cooling mode, 440 hours would be in off-cycle mode, 440 hours would be 
in fan-only mode, 90 hours would be in delay-start mode, and 440 hours 
would be in inactive mode and/or off mode during the cooling season. 73 
FR 74639, 74648-74649 (December 9, 2008). In the room AC analysis, fan-
only mode was defined as ``an active mode in which the compressor shuts 
down when operating in constant-fan mode or user selection of fan-only 
operation.'' As discussed above, fan operation when the compressor has 
cycled off is considered as off-cycle mode for the purposes of this 
NOPR. Also, because DOE is not proposing to measure or allocate hours 
to air circulation mode, any hours associated with that mode would be 
attributed to off-cycle mode. For portable ACs, DOE also proposes to 
allocate any bucket-full and other low-power mode hours to inactive/off 
mode hours. For portable ACs with a heating function, DOE estimated 
that the same ratio of mode hours to season length for the cooling 
season would be applicable for the available modes during heating 
season. The operating hours in off mode and inactive mode include 
operation during heating and cooling season as well as the plugged-in 
hours during the remainder of the year. Applying all of these 
apportionments, DOE developed estimates for the hourly operation in 
each mode, shown in Table III.11, based on the three approaches 
described above for estimating heating season length.

                              Table III.11--Proposed Annual Operating Hours by Mode
----------------------------------------------------------------------------------------------------------------
                                                                     Cooling/        Cooling/        Cooling/
                      Modes                        Cooling only       heating         heating         heating
                                                                    estimate 1      estimate 2      estimate 3
----------------------------------------------------------------------------------------------------------------
Cooling Mode....................................             750             750             750             750
Heating Mode....................................               0           1,444           1,524           1,008
Off-Cycle Mode..................................             880           2,575           2,668           2,063
Off/Inactive Mode...............................           1,355           1,856           1,883           1,704
----------------------------------------------------------------------------------------------------------------

    DOE proposes that the annual operating mode hours in the ``Cooling 
Only'' scenario presented in Table III.11 be used when calculating 
CEERcm for all portable ACs. For the reasons discussed above 
regarding use of portables ACs for heating, DOE also proposes assigning 
the annual operating mode hours in the ``Cooling/Heating Estimate 3'' 
scenario in the CEER calculation for units with both cooling and 
heating modes. For portable ACs with no heating mode, CEER would equal 
CEERcm.
    DOE requests feedback on these proposed annual operating mode hours 
to be used in the CEERcm and CEER calculations, and on any 
alternate season durations and operating hour estimates.
    To provide further insight on these annual operating mode hours and 
explore possible alternate scenarios for operating mode allocations 
during the cooling season, DOE considered the analysis presented in the 
Burke Portable AC Study. In that study, metered data for 19 portable 
ACs were analyzed to develop models that estimate the percent of time 
spent in cooling, fan-only, and standby modes as a function of the 
outdoor temperature. DOE notes that these modes as defined in the Burke 
Portable AC Study are not entirely consistent with the mode definitions 
proposed in this NOPR; however, DOE expects that they would align 
reasonably well with cooling mode, off-cycle mode, and inactive or off 
mode, respectively. The models in the Burke Portable AC Study were 
developed for two applications for portable ACs: (1) Residential use, 
which DOE expects to represent daily consumer interaction with the 
portable AC (e.g., turning the unit off and on when leaving or entering 
the house, respectively, or turning the unit on only while sleeping); 
and (2) commercial use (i.e., a portable AC unit used in an office or 
similar environment), which DOE expects to represent units that are 
installed and turned on at a given temperature setpoint with minimal 
additional consumer interaction. Because the first application 
represents intermittent use and the second application represents 
continuous use of a portable AC, DOE expects that the model results for 
these two applications provide a minimum and maximum estimate for time 
spent in cooling mode for a typical portable AC, from which the 
corresponding variations in the annual operating hours for other modes 
could be calculated. DOE presents this sensitivity analysis in addition 
to its proposed annual mode hour allocation listed in Table III.11 
because the variation in results for the different applications can be 
significant. For example, the model suggests that the percent of time 
spent in cooling mode for each application differs by 50 percentage 
points when the outdoor temperature is 80 [deg]F.
    Because these two models present mode operation in cooling season 
as a function of outdoor temperature, DOE conducted further analysis 
based on consumer and climate data to determine the most representative 
average cooling season outdoor temperature for portable AC usage. To do 
so, DOE used the same analytical approach as it used to determine 
heating season length, based on the 2009 RECS and 2012 NCDC data. From 
the NCDC data, DOE calculated

[[Page 10237]]

the average monthly outdoor temperature for each of the 44 states from 
June through September. DOE selected these months as those with primary 
portable AC usage based on New York City Season Guidelines that 
identify the cooling season as running from the end of May through 
September 24.\15\ DOE also notes, for example, that utilities may 
define the cooling season as June through September.\16\ DOE welcomes 
input from interested parties on whether these are the most 
representative months for the portable AC cooling season.
---------------------------------------------------------------------------

    \15\ New York City Season Guidelines are available online at: 
http://www.nyc.gov/html/dem/downloads/pdf/NYC_Cooling_Season_Guidelines_2014.pdf.
    \16\ For example, see: https://www.dom/com/residential/dominion-virginia-power/ways-to-save/energy-conservation-programs/smart-cooling-rewards/smart-cooling-rewards-terms-conditions.
---------------------------------------------------------------------------

    DOE combined the individual states' average outdoor temperatures 
from June through September using a weighted-average approach based on 
the RECS ownership data to determine an average cooling season ambient 
temperature for each sub-region represented by the RECS data. DOE used 
a similar weighted average to combine the sub-region data for each 
region and subsequently combine the regional data into a single 
representative average cooling season temperature of 70 [deg]F for the 
United States as a whole.
    DOE used this outdoor temperature with the models developed in the 
Burke Portable AC Study to calculate the estimated percent of time 
spent in cooling, off-cycle, and off or inactive modes during the 
cooling season. The operating mode time as a percentage of cooling 
season hours for both residential applications (low-use Scenario 1) and 
commercial applications (high-use Scenario 2) are shown in Table 
III.12. DOE also presents a third scenario that is an average of the 
low-use and high-use scenarios to estimate overall typical portable AC 
usage patterns.

    Table III.12--Annual Operating Mode Hour Sensitivity Analysis--Percentage of Time in Each Mode During the
                                                 Cooling Season
----------------------------------------------------------------------------------------------------------------
                                                            Scenario 1--       Scenario 2--
                                                            residential         commercial        Scenario 3--
                         Modes                           application (low-  application (high-    Average-use
                                                           use) (percent)     use) (percent)       (percent)
----------------------------------------------------------------------------------------------------------------
Cooling Mode...........................................                5.9               41.1               23.5
Off-Cycle Mode.........................................                2.2               21.7               12.0
Off/Inactive Mode......................................               91.9               37.9               64.9
----------------------------------------------------------------------------------------------------------------

    For comparison with DOE's proposed cooling mode annual hour 
estimate of 750 hours, DOE applied these percentages to the estimated 
cooling season length of 2,160 hours. This results in cooling mode 
operating hours of 126, 887, and 507, for the usage patterns modeled in 
Scenario 1, Scenario 2, and Scenario 3, respectively. Note that if DOE 
were to use one of these model scenarios as the basis for all operating 
mode hours in cooling season, the proposed total annual off-cycle mode 
and total off/inactive mode hours would also be adjusted to account for 
the cooling season percentages in Table III.12. DOE notes that the 
cooling season mode operating hour percentages in these scenarios 
differ from the proposed approach that utilizes the room AC cooling 
season mode operating hour estimates.
    DOE requests feedback on the alternative scenarios presented in 
this NOPR or other data that may inform the allocation of annual 
operating hours in each mode.

C. Sampling Plan and Rounding Requirements

    DOE is proposing the following sampling plan and rounding 
requirements for portable ACs to enable manufacturers to make 
representations of energy consumption or efficiency metrics. The 
sampling requirements would be included in the proposed 10 CFR 429.62. 
Specifically, DOE is proposing that the general sampling requirements 
of 10 CFR 429.11 for selecting units to be tested be applicable to 
portable ACs. In addition, DOE is proposing that for each portable AC 
basic model, a sufficient sample size must be randomly selected to 
ensure that a representative value of energy consumption for a basic 
model is greater than or equal to the higher of the mean of the sample 
or upper 95 percent confidence limit (UCL) of the true mean divided by 
1.10. For EERcm, EERhm, CEER, or other measure of 
energy consumption where a higher value is preferable to the consumer, 
the representative value shall be less than or equal to the lower of 
the mean of the sample or the lower 95 percent confidence limit (LCL) 
of the true mean divided by 0.90. The mean, UCL, and LCL are calculated 
as follows:
[GRAPHIC] [TIFF OMITTED] TP25FE15.006

Where:

xx is the sample mean;
xi is the ith sample;
s is the sample standard deviation;
n is the number of units in the test sample; and
t0.95 is the t statistic for a 95% one-tailed confidence 
interval with n-1 degrees of freedom.

    This proposed sampling plan for portable ACs is consistent with 
sampling plans already established for dehumidifiers and other similar 
products. DOE notes that certification requirements for portable ACs, 
which would also be located at 10 CFR part 429, would be proposed in 
the concurrent energy conservation standards rulemaking.
    DOE also proposes that all calculations be performed with the 
unrounded measured values, and that the reported cooling or heating 
capacity

[[Page 10238]]

be rounded in accordance with Table 1 of PAC-1-2014, ``Multiples for 
reporting Dual Duct Cooling Capacity, Single Duct Cooling Capacity, 
Spot Cooling Capacity, Water Cooled Condenser Capacity and Power Input 
Ratings.'' DOE further proposes that EERcm, 
EERhm, CEERcm, CEER, or other energy efficiency 
metrics would be rounded to the nearest 0.1 Btu/Wh, in accordance with 
section 6.2.2 of AHAM PAC-1-2014 and consistent with the rounding 
instructions provided for room ACs at 10 CFR 430.23(f)(2). DOE notes 
that these rounding instructions would be included in the proposed 
sampling plan for portable ACs. The rounding instruction proposal would 
be updated to reference the certification and reporting requirements, 
which would be proposed as part of the energy conservation standards 
rulemaking for portable ACs.

D. Compliance With Other Energy Policy and Conservation Act 
Requirements

1. Test Burden
    EPCA requires that any test procedures prescribed or amended shall 
be reasonably designed to produce test results which measure energy 
efficiency, energy use, or estimated annual operating cost of a covered 
product during a representative average use cycle or period of use, and 
shall not be unduly burdensome to conduct. (42 U.S.C. 6293(b)(3)) For 
the reasons that follow, DOE has tentatively concluded that 
establishing a DOE test procedure to measure the energy consumption of 
portable ACs in active mode, standby mode, and off mode would produce 
the required test results and would not result in any undue burdens.
    As discussed in section IV.B of this NOPR, the proposed test 
procedure would require testing equipment and facilities that are not 
substantially different than those that manufacturers are currently 
using for testing in order to report portable AC ratings to the CEC and 
likely already using for certifying to DOE the performance of packaged 
terminal ACs (PTACs), which many of the portable AC manufacturers also 
produce. Thus, these manufacturers are likely already equipped to test 
portable ACs, or are testing their products in third-party laboratories 
that are similarly equipped. Therefore, the proposed test procedure 
would not require these manufacturers to make a significant investment 
in test facilities and new equipment.
    In addition, DOE carefully considered testing burden in proposing a 
modified air enthalpy method for measuring energy use in cooling mode 
and heating mode that is significantly less burdensome than the 
calorimeter method. DOE is also proposing an approach for measuring 
low-power mode energy use that would preclude testing of each possible 
mode individually and instead would require only testing modes in which 
the portable AC may consume significant amounts of energy, thereby 
reducing burden further.
    Therefore, DOE determined that the proposed portable AC test 
procedure would produce test results that measure energy consumption 
during representative use, and that the test procedure would not be 
unduly burdensome to conduct.
2. Potential Incorporation of International Electrotechnical Commission 
Standard 62087
    Under 42 U.S.C. 6295(gg)(2)(A), EPCA directs DOE to consider IEC 
Standard 62087 when amending test procedures for covered products to 
include standby mode and off mode power measurements. DOE reviewed IEC 
Standard 62087, ``Methods of measurement for the power consumption of 
audio, video, and related equipment'' (Edition 3.0 2011-04), and has 
tentatively determined that it would not be applicable to measuring 
power consumption of electrical appliances such as portable ACs. 
Therefore, DOE determined that referencing IEC Standards 62087 is not 
necessary for the proposed test procedure that is the subject of this 
rulemaking.

IV. Procedural Issues and Regulatory Review

A. Review Under Executive Order 12866

    The Office of Management and Budget (OMB) has determined that test 
procedure rulemakings do not constitute ``significant regulatory 
actions'' under section 3(f) of Executive Order 12866, Regulatory 
Planning and Review, 58 FR 51735 (Oct. 4, 1993). Accordingly, this 
action was not subject to review under the Executive Order by the 
Office of Information and Regulatory Affairs (OIRA) in the 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 (IFRA) 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 DOE rulemaking process. 68 FR 7990. DOE has made 
its procedures and policies available on the Office of the General 
Counsel's Web site: http://energy.gov/gc/office-general-counsel.
    DOE reviewed this proposed rule under the provisions of the 
Regulatory Flexibility Act and the procedures and policies published on 
February 19, 2003. The proposed rule prescribes the test procedure to 
measure the energy consumption of portable ACs in active modes, standby 
modes, and off mode. DOE tentatively concludes that this proposed rule 
would not have a significant impact on a substantial number of small 
entities. The factual basis for this certification is as follows:
    The Small Business Administration (SBA) considers a business entity 
to be small business, if, together with its affiliates, it employs less 
than a threshold number of workers specified in 13 CFR part 121. These 
size standards and codes are established by the North American Industry 
Classification System (NAICS). The threshold number for NAICS 
classification code 333415, ``Air-Conditioning and Warm Air Heating 
Equipment and Commercial and Industrial Refrigeration Equipment 
Manufacturing,'' which includes manufacturers of portable ACs, is 750 
employees.
    DOE surveyed the AHAM member directory to identify manufacturers of 
residential portable ACs. DOE then consulted publicly available data, 
purchased company reports from vendors such as Dun and Bradstreet, and 
contacted manufacturers, where needed, to determine if the number of 
manufacturers with manufacturing facilities located within the United 
States that meet the SBA's definition of a ``small business 
manufacturing facility.'' Based on this analysis, DOE estimates that 
there is one small business that manufactures portable ACs.
    This proposed rule would establish a DOE test procedure for 
portable ACs, which would require testing units according to an 
industry standard, AHAM PAC-1-2014, with additional calculations. 
Although there are no current DOE energy conservation standards for 
portable ACs, many manufacturers have reported cooling capacity and EER 
of these products to the CEC, which requires testing

[[Page 10239]]

according to ANSI/ASHRAE Standard 128-2001. The testing equipment and 
methodology for ANSI/ASHRAE Standard 128-2001 are similar to those 
required by AHAM PAC-1-2014, although the temperature conditions are 
different.
    The small business mentioned above does not list any portable AC 
models in the CEC product database, so DOE is uncertain whether it is 
currently testing portable ACs according to ANSI/ASHRAE Standard 128-
2001. However, DOE notes that the small business also manufactures and 
markets PTACs that must be certified to DOE according to ANSI/AHRI 
Standard 310/380-2004, ``Standard for Packaged Terminal Air-
Conditioners and Heat Pumps'' (ANSI/AHRI 310/380-2004). (10 CFR 430.96) 
Section 4.2.1 of ANSI/AHRI 310/380-2004 specifies that standard cooling 
ratings shall be verified by tests conducted in accordance with either 
ANSI/ASHRAE Standard 16-1999 or ANSI/ASHRAE Standard 37-1998. Due to 
the complexity of testing facilities required to implement the 
calorimeter method specified in ANSI/ASHRAE 16-1999, DOE believes that 
it is likely that the small business currently conducts compliance 
testing using the air enthalpy methods in ANSI/ASHRAE Standard 37-1998, 
which require comparable testing facilities and equipment as the 
methods proposed in this NOPR. In addition, the small business provides 
performance data in the literature for its portable AC model which 
indicates that testing was conducted at 80 [deg]F and 50-percent 
relative humidity. This testing would likely have required air enthalpy 
measurements equivalent to those specified in AHAM PAC-1-2014 at 80 
[deg]F and 49-percent relative humidity, and the same air enthalpy 
measurements would be made when testing at 70 [deg]F and 57-percent 
relative humidity according to the proposed method for portable AC 
heating mode. Therefore, DOE believes that no small businesses would 
require purchasing new equipment or modifying existing equipment in 
order to conduct the proposed test methods for measuring energy use in 
portable AC cooling mode and heating mode.
    The proposed rule would also require the measurement of power input 
during standby mode, off mode, and off-cycle mode. These tests could be 
conducted either in the same facilities used for the cooling mode and 
heating mode testing of these products, or in facilities that meet the 
requirements for testing conditions specified in IEC Standard 62301, 
which could consist of any space with temperature control typically 
found in an office or living space. Therefore, DOE does not expect that 
the small business would incur additional facilities costs required by 
the proposed rule. In addition, in the event that the manufacturer 
would be required to purchase a wattmeter for measuring power input in 
standby mode, off mode, and off-cycle mode, the investment required 
would likely be relatively modest. An Internet search of equipment that 
specifically meets the proposed requirements reveals a cost of 
approximately $2,000.
    The costs described above are small compared to the overall 
financial investment needed to undertake the business enterprise of 
developing and testing consumer products, which involves facilities, 
qualified staff, and specialized equipment. Based on its review of 
industry data,\17\ DOE estimates that the small portable AC business 
has annual revenues of approximately $20 million.
---------------------------------------------------------------------------

    \17\ Annual revenue estimates are based on financial reports 
obtained from Hoover's, Inc., available online at: www.hoovers.com.
---------------------------------------------------------------------------

    For these reasons, DOE concludes and certifies that the proposed 
rule would not have a significant economic impact on a substantial 
number of small entities. Accordingly, DOE has not prepared a 
regulatory flexibility analysis for this rulemaking. DOE will transmit 
the certification and supporting statement of factual basis to the 
Chief Counsel for Advocacy of the SBA for review under 5 U.S.C. 605(b).

C. Review Under the Paperwork Reduction Act of 1995

    All collections of information from the public by a Federal agency 
must receive prior approval from OMB. DOE has established regulations 
for the certification and recordkeeping requirements for covered 
consumer products and industrial equipment. 10 CFR part 429, subpart B. 
DOE published a notice of proposed determination regarding portable air 
conditioners on July 5, 2013. 78 FR 40403. In an application to renew 
the OMB information collection approval for DOE's certification and 
recordkeeping requirements, DOE included an estimated burden for 
manufacturers of portable air conditioners in case DOE ultimately 
issues a coverage determination and sets energy conservation standards 
for these products. OMB has approved the revised information collection 
for DOE's certification and recordkeeping requirements. 80 FR 5099 
(January 30, 2015). DOE estimated that it will take each respondent 
approximately 30 hours total per company per year to comply with the 
certification and recordkeeping requirements based on 20 hours of 
technician/technical work and 10 hours clerical work to actually submit 
the Compliance and Certification Management System (CCMS) templates. 
This rulemaking would include recordkeeping requirements on 
manufacturers that are associated with executing and maintaining the 
test data for these products. DOE notes that the certification 
requirements would be established in a final rule establishing energy 
conservation standards for portable ACs. DOE recognizes that 
recordkeeping burden may vary substantially based on company 
preferences and practices. DOE requests comment on this burden 
estimate.

D. Review Under the National Environmental Policy Act of 1969

    In this proposed rule, DOE proposes test procedure amendments that 
it expects will be used to develop and implement future energy 
conservation standards for portable ACs. DOE has determined that this 
rule falls into a class of actions that are categorically excluded from 
review under the National Environmental Policy Act of 1969 (42 U.S.C. 
4321 et seq.) and DOE's implementing regulations at 10 CFR part 1021. 
Specifically, this proposed rule would amend the existing test 
procedures without affecting the amount, quality or distribution of 
energy usage, and, therefore, would not result in any environmental 
impacts. Thus, this rulemaking is covered by Categorical Exclusion A5 
under 10 CFR part 1021, subpart D, which applies to any rulemaking that 
interprets or amends an existing rule without changing the 
environmental effect of that rule. Accordingly, neither an 
environmental assessment nor an environmental impact statement is 
required.

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

[[Page 10240]]

have Federalism implications. On March 14, 2000, DOE published a 
statement of policy describing the intergovernmental consultation 
process it will follow in the development of such regulations. 65 FR 
13735. DOE has examined this proposed rule and has determined that it 
would not have a substantial direct effect on the States, on the 
relationship between the national government and the States, or on the 
distribution of power and responsibilities among the various levels of 
government. EPCA governs and prescribes Federal preemption of State 
regulations as to energy conservation for the products that are the 
subject of this proposed rule. States can petition DOE for exemption 
from such preemption to the extent, and based on criteria, set forth in 
EPCA. (42 U.S.C. 6297(d)) No further action is required by Executive 
Order 13132.

F. Review Under Executive Order 12988

    Regarding the review of existing regulations and the promulgation 
of new regulations, section 3(a) of Executive Order 12988, ``Civil 
Justice Reform,'' 61 FR 4729 (Feb. 7, 1996), imposes on Federal 
agencies the general duty to adhere to the following requirements: (1) 
Eliminate drafting errors and ambiguity; (2) write regulations to 
minimize litigation; (3) provide a clear legal standard for affected 
conduct rather than a general standard; and (4) promote simplification 
and burden reduction. Section 3(b) of Executive Order 12988 
specifically requires that Executive agencies make every reasonable 
effort to ensure that the regulation: (1) Clearly specifies the 
preemptive effect, if any; (2) clearly specifies any effect on existing 
Federal law or regulation; (3) provides a clear legal standard for 
affected conduct while promoting simplification and burden reduction; 
(4) specifies the retroactive effect, if any; (5) adequately defines 
key terms; and (6) addresses other important issues affecting clarity 
and general draftsmanship under any guidelines issued by the Attorney 
General. Section 3(c) of Executive Order 12988 requires Executive 
agencies to review regulations in light of applicable standards in 
sections 3(a) and 3(b) to determine whether they are met or it is 
unreasonable to meet one or more of them. DOE has completed the 
required review and determined that, to the extent permitted by law, 
this proposed rule meets the relevant standards of Executive Order 
12988.

G. Review Under the Unfunded Mandates Reform Act of 1995

    Title II of the Unfunded Mandates Reform Act of 1995 (UMRA) 
requires each Federal agency to assess the effects of Federal 
regulatory actions on State, local, and Tribal governments and the 
private sector. Public Law 104-4, sec. 201 (codified at 2 U.S.C. 1531). 
For a proposed regulatory action likely to result in a rule that may 
cause the expenditure by State, local, and Tribal governments, in the 
aggregate, or by the private sector of $100 million or more in any one 
year (adjusted annually for inflation), section 202 of UMRA requires a 
Federal agency to publish a written statement that estimates the 
resulting costs, benefits, and other effects on the national economy. 
(2 U.S.C. 1532(a), (b)) The UMRA also requires a Federal agency to 
develop an effective process to permit timely input by elected officers 
of State, local, and Tribal governments on a proposed ``significant 
intergovernmental mandate,'' and requires an agency plan for giving 
notice and opportunity for timely input to potentially affected small 
governments before establishing any requirements that might 
significantly or uniquely affect small governments. On March 18, 1997, 
DOE published a statement of policy on its process for 
intergovernmental consultation under UMRA. 62 FR 12820; also available 
at /energy.gov/gc/office-general-counsel">http://energy.gov/gc/office-general-counsel">energy.gov/gc/office-general-counsel. DOE examined this proposed 
rule according to UMRA and its statement of policy and determined that 
the rule contains neither an intergovernmental mandate, nor a mandate 
that may result in the expenditure of $100 million or more in any year, 
so these requirements do not apply.

H. Review Under the Treasury and General Government Appropriations Act, 
1999

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

J. Review Under Treasury and General Government Appropriations Act, 
2001

    Section 515 of the Treasury and General Government Appropriations 
Act, 2001 (44 U.S.C. 3516 note) provides for agencies to review most 
disseminations of information to the public under guidelines 
established by each agency pursuant to general guidelines issued by 
OMB. OMB's guidelines were published at 67 FR 8452 (Feb. 22, 2002), and 
DOE's guidelines were published at 67 FR 62446 (Oct. 7, 2002). DOE has 
reviewed this proposed rule under the OMB and DOE guidelines and has 
concluded 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 OMB, 
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.
    This regulatory action to establish the test procedure for 
measuring the energy efficiency of portable ACs is not a significant 
regulatory action under Executive Order 12866. Moreover, it would not 
have a significant adverse effect on the supply, distribution, or use 
of energy, nor has it been designated as a significant energy action by 
the Administrator of OIRA. Therefore, it is not a significant energy 
action, and, accordingly, DOE has not prepared a Statement of Energy 
Effects.

[[Page 10241]]

L. Review Under Section 32 of the Federal Energy Administration Act of 
1974

    Under section 301 of the Department of Energy Organization Act 
(Pub. L. 95-91; 42 U.S.C. 7101), DOE must comply with section 32 of the 
Federal Energy Administration Act of 1974, as amended by the Federal 
Energy Administration Authorization Act of 1977. (15 U.S.C. 788; FEAA) 
Section 32 essentially provides in relevant part that, where a proposed 
rule authorizes or requires use of commercial standards, the notice of 
proposed rulemaking must inform the public of the use and background of 
such standards. In addition, section 32(c) requires DOE to consult with 
the Attorney General and the Chairman of the Federal Trade Commission 
(FTC) concerning the impact of the commercial or industry standards on 
competition.
     As discussed in this NOPR, the proposed rule incorporates testing 
methods contained in the following commercial standards: AHAM PAC-1-
2014, Portable Air Conditions; and IEC 62301, Household Electrical 
Appliances--Measurement of Standby Power. DOE 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 that fully provides for public participation, 
comment, and review). DOE will consult with the Attorney General and 
the Chairwoman of the FTC concerning the impact of these test 
procedures on competition, prior to prescribing a final rule.

M. Description of Materials Incorporated by Reference

    In this NOPR, DOE proposes to incorporate by reference the test 
standard published by AHAM, titled ``Portable Air Conditioners,'' AHAM 
PAC-1-2014. AHAM PAC-1-2014 is an industry accepted test procedure that 
measures portable AC performance in cooling mode and is applicable to 
products sold in North America. AHAM PAC-1-2014 specifies testing 
conducted in accordance with other industry accepted test procedures 
(already incorporated by reference) and determines energy efficiency 
metrics for various portable AC configurations. The test procedure 
proposed in this NOPR references various sections of AHAM PAC-1-2014 
that address test setup, instrumentation, test conduct, calculations, 
and rounding. AHAM PAC-1-2014 is readily available on AHAM's Web site 
at http://www.aham.org/ht/d/ProductDetails/sku/PAC12009/from/714/pid/.

V. Public Participation

A. Attendance at Public Meeting

    The time, date and location of the public meeting are listed in the 
DATES and ADDRESSES sections at the beginning of this document. If you 
plan to attend the public meeting, please notify Ms. Brenda Edwards at 
(202) 586-2945 or Brenda.Edwards@ee.doe.gov.
    Please note that foreign nationals participating in the public 
meeting are subject to advance security screening procedures which 
require advance notice prior to attendance at the public meeting. If a 
foreign national wishes to participate in the public meeting, please 
inform DOE of this fact as soon as possible by contacting Ms. Regina 
Washington at (202) 586-1214 or by email: Regina.Washington@ee.doe.gov 
so that the necessary procedures can be completed.
    DOE requires visitors with laptop computers and other devices, such 
as tablets, to be checked upon entry into the building. Any person 
wishing to bring these devices into the Forrestal Building will be 
required to obtain a property pass. Visitors should avoid bringing 
these devices, or allow an extra 45 minutes to check in. Please report 
to the visitor's desk to have devices checked before proceeding through 
security.
    Due to the REAL ID Act implemented by the Department of Homeland 
Security (DHS), there have been recent changes regarding ID 
requirements for individuals wishing to enter Federal buildings from 
specific states and U.S. territories. Driver's licenses from the 
following states or territory will not be accepted for building entry 
and one of the alternate forms of ID listed below will be required. DHS 
has determined that regular driver's licenses (and ID cards) from the 
following jurisdictions are not acceptable for entry into DOE 
facilities: Alaska, American Samoa, Arizona, Louisiana, Maine, 
Massachusetts, Minnesota, New York, Oklahoma, and Washington. 
Acceptable alternate forms of Photo-ID include: U.S. Passport or 
Passport Card; an Enhanced Driver's License or Enhanced ID-Card issued 
by the states of Minnesota, New York or Washington (Enhanced licenses 
issued by these states are clearly marked Enhanced or Enhanced Driver's 
License); a military ID or other Federal government issued Photo-ID 
card.
    In addition, you can attend the public meeting via webinar. Webinar 
registration information, participant instructions, and information 
about the capabilities available to webinar participants will be 
published on DOE's Web site http://www1.eere.energy.gov/buildings/appliance_standards/product.aspx/productid/79. Participants are 
responsible for ensuring their systems are compatible with the webinar 
software.

B. Procedure for Submitting Prepared General Statements for 
Distribution

    Any person who has plans to present a prepared general statement 
may request that copies of his or her statement be made available at 
the public meeting. Such persons may submit requests, along with an 
advance electronic copy of their statement in PDF (preferred), 
Microsoft Word or Excel, WordPerfect, or text (ASCII) file format, to 
the appropriate address shown in the ADDRESSES section at the beginning 
of this N. The request and advance copy of statements must be received 
at least one week before the public meeting and may be emailed, hand-
delivered, or sent by mail. DOE prefers to receive requests and advance 
copies via email. Please include a telephone number to enable DOE staff 
to make a follow-up contact, if needed.

C. Conduct of Public Meeting

    DOE will designate a DOE official to preside at the public meeting 
and may also use a professional facilitator to aid discussion. The 
meeting will not be a judicial or evidentiary-type public hearing, but 
DOE will conduct it in accordance with section 336 of EPCA (42 U.S.C. 
6306). A court reporter will be present to record the proceedings and 
prepare a transcript. DOE reserves the right to schedule the order of 
presentations and to establish the procedures governing the conduct of 
the public meeting. After the public meeting and until the end of the 
comment period, interested parties may submit further comments on the 
proceedings and any aspect of the rulemaking.
    The public meeting will be conducted in an informal, conference 
style. DOE will present summaries of comments received before the 
public meeting, allow time for prepared general statements by 
participants, and encourage all interested parties to share their views 
on issues affecting this rulemaking. Each participant will be allowed 
to make a general statement (within time limits determined by DOE), 
before the discussion of specific topics. DOE will permit, as time 
permits, other participants to comment briefly on any general 
statements.
    At the end of all prepared statements on a topic, DOE will permit 
participants to clarify their statements briefly and

[[Page 10242]]

comment on statements made by others. Participants should be prepared 
to answer questions by DOE and by other participants concerning these 
issues. DOE representatives may also ask questions of participants 
concerning other matters relevant to this rulemaking. The official 
conducting the public meeting will accept additional comments or 
questions from those attending, as time permits. The presiding official 
will announce any further procedural rules or modification of the above 
procedures that may be needed for the proper conduct of the public 
meeting.
    A transcript of the public meeting will be included in the docket, 
which can be viewed as described in the Docket section at the beginning 
of this notice. In addition, any person may buy a copy of the 
transcript from the transcribing reporter.

D. Submission of Comments

    DOE will accept comments, data, and information regarding this 
proposed rule before or after the public meeting, but no later than the 
date provided in the DATES section at the beginning of this proposed 
rule. Interested parties may submit comments using any of the methods 
described in the ADDRESSES section at the beginning of this notice.
    Submitting comments via www.regulations.gov. The regulations.gov 
Web page will require you to provide your name and contact information. 
Your contact information will be viewable to DOE Building Technologies 
staff only. Your contact information will not be publicly viewable 
except for your first and last names, organization name (if any), and 
submitter representative name (if any). If your comment is not 
processed properly because of technical difficulties, DOE will use this 
information to contact you. If DOE cannot read your comment due to 
technical difficulties and cannot contact you for clarification, DOE 
may not be able to consider your comment.
    However, your contact information will be publicly viewable if you 
include it in the comment or in any documents attached to your comment. 
Any information that you do not want to be publicly viewable should not 
be included in your comment, nor in any document attached to your 
comment. Persons viewing comments will see only first and last names, 
organization names, correspondence containing comments, and any 
documents submitted with the comments.
    Do not submit to www.regulations.gov information for which 
disclosure is restricted by statute, such as trade secrets and 
commercial or financial information (hereinafter referred to as 
Confidential Business Information (CBI)). Comments submitted through 
regulations.gov cannot be claimed as CBI. Comments received through the 
Web site will waive any CBI claims for the information submitted. For 
information on submitting CBI, see the Confidential Business 
Information section.
    DOE processes submissions made through regulations.gov before 
posting. Normally, comments will be posted within a few days of being 
submitted. However, if large volumes of comments are being processed 
simultaneously, your comment may not be viewable for up to several 
weeks. Please keep the comment tracking number that regulations.gov 
provides after you have successfully uploaded your comment.
    Submitting comments via email, hand delivery, or mail. Comments and 
documents submitted via email, hand delivery, or mail also will be 
posted to regulations.gov. If you do not want your personal contact 
information to be publicly viewable, do not include it in your comment 
or any accompanying documents. Instead, provide your contact 
information on a cover letter. Include your first and last names, email 
address, telephone number, and optional mailing address. The cover 
letter will not be publicly viewable as long as it does not include any 
comments.
    Include contact information each time you submit comments, data, 
documents, and other information to DOE. If you submit via mail or hand 
delivery, please provide all items on a CD, if feasible. It is not 
necessary to submit printed copies. No facsimiles (faxes) will be 
accepted.
    Comments, data, and other information submitted to DOE 
electronically should be provided in PDF (preferred), Microsoft Word or 
Excel, WordPerfect, or text (ASCII) file format. Provide documents that 
are not secured, written in English and free of any defects or viruses. 
Documents should not contain special characters or any form of 
encryption and, if possible, they should carry the electronic signature 
of the author.
    Campaign form letters. Please submit campaign form letters by the 
originating organization in batches of between 50 to 500 form letters 
per PDF or as one form letter with a list of supporters' names compiled 
into one or more PDFs. This reduces comment processing and posting 
time.
    Confidential Business Information. According to 10 CFR 1004.11, any 
person submitting information that he or she believes to be 
confidential and exempt by law from public disclosure should submit via 
email, postal mail, or hand delivery two well-marked copies: One copy 
of the document marked confidential including all the information 
believed to be confidential, and one copy of the document marked non-
confidential with the information believed to be confidential deleted. 
Submit these documents via email or on a CD, if feasible. DOE will make 
its own determination about the confidential status of the information 
and treat it according to its determination.
    Factors of interest to DOE when evaluating requests to treat 
submitted information as confidential include: (1) A description of the 
items; (2) whether and why such items are customarily treated as 
confidential within the industry; (3) whether the information is 
generally known by or available from other sources; (4) whether the 
information has previously been made available to others without 
obligation concerning its confidentiality; (5) an explanation of the 
competitive injury to the submitting person which would result from 
public disclosure; (6) when such information might lose its 
confidential character due to the passage of time; and (7) why 
disclosure of the information would be contrary to the public interest.
    It is DOE's policy that all comments may be included in the public 
docket, without change and as received, including any personal 
information provided in the comments (except information deemed to be 
exempt from public disclosure).

E. Issues on Which DOE Seeks Comment

    Although DOE welcomes comments on any aspect of this proposal, DOE 
is particularly interested in receiving comments and views of 
interested parties concerning the following issues:

    1.The description and definition for residential and commercial 
portable ACs, different configurations, and the clarification that 
commercial portable ACs are not considered a covered product. (See 
section III.A.)
    2.The definitions for active mode, cooling mode, and heating 
mode. DOE also seeks information on annual hours associated with the 
consumer initiated air-circulation mode. (See section III.B.1.)
    3.The proposal that AHAM PAC-1-2014 be used as the basis for the 
test procedure proposed in this NOPR (See section III.B.1.a.i.)
    4.The proposal to modify the cooling capacity equation as 
included in AHAM PAC-1-2014 to address the effects of infiltration 
air. In addition, DOE welcomes input on the proposed infiltration 
air conditions of 95 [deg]F dry-bulb temperature and

[[Page 10243]]

75.2 [deg]F wet-bulb temperature. (See section III.B.1.a.ii.)
    5.The proposal to specify a more stringent evaporator inlet air 
stream dry-bulb temperature tolerance for single-duct units and to 
not consider the effects of condenser exhaust air and inlet air 
mixing for dual-duct units. (See sectionIII.B.1.a.iii.)
    6.The proposal to use the manufacturer-supplied ducting 
components during performance testing and the approach to 
characterize and determine the condenser duct(s) heat transfer to 
the conditioned space. (See section III.B.1.a.iv.)
    7.The proposal and approach to include case heat transfer 
effects instead of the evaporator fan heat, based on the average 
case surface temperature and temperature. (See section III.B.1.a.v.)
    8. The test setup for portable ACs with and without means for 
auto-evaporation to remove the collected condensate, including the 
use of any internal pump only if it is specified by the manufacturer 
for use during typical cooling operation. (See section 
III.B.1.a.vi.)
    9. The proposed control settings for cooling mode and heating 
mode testing, which would require selecting the highest fan speed, 
for units with user-adjustable fan speed, and the lowest and highest 
available temperature settings for cooling mode and heating mode, 
respectively. Also, the proposed clarification that all portable AC 
performance testing be conducted with the maximum louver opening 
and, where applicable, with the louver oscillation feature disabled 
throughout testing. (See section III.B.1.a.vii.)
    10. The proposed minimum clearance between the test unit and 
chamber wall surfaces. (See section III.B.1.a.viii.)
    11. The proposed test setup, standard rating conditions, and 
conduct for determining heating mode performance for portable ACs. 
(See section III.B.1.b.)
    12. The provisions for measuring energy consumption in off-cycle 
mode, including the use of the maximum speed setting for those units 
with adjustable fan speed settings, the measurement period 
specifications. DOE seeks comment on whether off-cycle mode energy 
consumption is independent of ambient conditions. (See section 
III.B.2.)
    13. The proposed definitions and provisions for measuring energy 
consumption in various standby modes and off mode. (See section 
III.B.3.)
    14. The proposed equation for calculating individual cooling 
combined energy efficiency ratio (CEERcm) and an overall 
CEER that incorporates performance in both cooling and heating 
modes, in addition to other low power modes. DOE also seeks comment 
on the proposed annual operating hours and their implementation for 
calculating the CEERcm and CEER. (See section III.B.4.)
    15. The proposed reporting requirements including the sampling 
plan and rounding instructions. (See section III.C.)
    16. The testing burden, including DOE's determination that the 
test would not be unduly burdensome to conduct. (See section 
III.D.1.)

VI. Approval of the Office of the Secretary

    The Secretary of Energy has approved publication of this proposed 
rule.

List of Subjects

10 CFR Part 429

    Administrative practice and procedure, Buildings and facilities, 
Business and industry, Energy conservation, Grant programs-energy, 
Housing, Reporting and recordkeeping requirements, Technical 
assistance.

10 CFR Part 430

    Administrative practice and procedure, Confidential business 
information, Energy conservation, Household appliances, Imports, 
Incorporation by reference, Intergovernmental relations, Small 
businesses.

    Issued in Washington, DC, on February 12, 2015.
Kathleen B. Hogan,
Deputy Assistant Secretary for Energy Efficiency, Energy Efficiency and 
Renewable Energy.

    For the reasons stated in the preamble, DOE proposes to amend parts 
429 and 430 of Chapter II of Title 10, Code of Federal Regulations as 
set forth below:

PART 429--CERTIFICATION, COMPLIANCE, AND ENFORCEMENT FOR CONSUMER 
PRODUCTS AND COMMERCIAL AND INDUSTRIAL EQUIPMENT

0
1. The authority citation for part 429 continues to read as follows:

    Authority: 42 U.S.C. 6291-6317.

0
2. Add Sec.  429.62 to read as follows:

Sec.  429.62  Portable Air Conditioners.

    (a) Sampling plan for selection of units for testing. (1) The 
requirements of Sec.  429.11 are applicable to portable air 
conditioners; and
    (2) For each basic model of portable air conditioner, a sample of 
sufficient size shall be randomly selected and tested to ensure that--
    (i) Any represented value of energy consumption or other measure of 
energy consumption of a basic model for which consumers would favor 
lower values shall be greater than or equal to the higher of:
    (A) The mean of the sample:
    [GRAPHIC] [TIFF OMITTED] TP25FE15.007
    
Where:

xx is the sample mean;
xi is the ith sample; and
n is the number of units in the test sample.

    Or,
    (B) The upper 95 percent confidence limit (UCL) of the true mean 
divided by 1.10:
[GRAPHIC] [TIFF OMITTED] TP25FE15.008

Where:

xx is the sample mean;
s is the sample standard deviation;
n is the number of units in the test sample; and
t0.95 is the t statistic for a 95% one-tailed confidence 
interval with n - 1 degrees of freedom.

    And,
    (ii) Any represented value of the cooling or heating energy 
efficiency ratio, combined energy efficiency ratio, or other measure of 
energy consumption of a basic model for which consumers would favor 
higher values shall be less than or equal to the lower of:
    (A) The mean of the sample:
    [GRAPHIC] [TIFF OMITTED] TP25FE15.009
    
Where:

xx is the sample mean;
xi is the ith sample; and
n is the number of units in the test sample.

    Or,
    (B) The lower 95 percent confidence limit (LCL) of the true mean 
divided by 0.90:
[GRAPHIC] [TIFF OMITTED] TP25FE15.010

Where:

xx is the sample mean;
s is the sample standard deviation;
n is the number of units in the test sample; and
t0.95 is the t statistic for a 95% one-tailed confidence 
interval with n - 1 degrees of freedom.

    And,
    (3) The value of cooling or heating mode capacity of a basic model 
shall be the mean of the capacities for each tested unit of the basic 
model. Round the mean capacity value to the nearest 50, 100, 200, or 
500 Btu/h, depending on the value being rounded, in accordance with 
Table 1 of PAC-1-2014, ``Multiples for reporting Dual Duct Cooling 
Capacity, Single Duct Cooling Capacity, Spot Cooling Capacity, Water 
Cooled Condenser Capacity and Power Input Ratings.''
    (4) The value of energy efficiency ratio or combined energy 
efficiency ratio of a basic model shall be the mean of the efficiency 
metric for each tested unit of

[[Page 10244]]

the basic model. Round energy efficiency ratio or combined energy 
efficiency ratio to the, to the nearest 0.1 Btu/Wh.
    (b) [Reserved]

PART 430--ENERGY CONSERVATION PROGRAM FOR CONSUMER PRODUCTS

0
3. 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
4. Section 430.2 is amended by adding the definition of ``portable air 
conditioner'' in alphabetical order to read as follows:

Sec.  430.2  Definitions.

* * * * *
    Portable air conditioner means an encased assembly, other than a 
``packaged terminal air conditioner,'' ``room air conditioner,'' or 
``dehumidifier,'' designed as a portable unit for delivering cooled, 
conditioned air to an enclosed space, that is powered by single-phase 
electric current, which may rest on the floor or other elevated 
surface. It includes a source of refrigeration and may include 
additional means for air circulation and heating.
* * * * *
0
5. Section 430.3 is amended by adding paragraph (h)(8) and revising 
paragraph (o)(4) to read as follows:

Sec.  430.3  Materials incorporated by reference.

* * * * *
    (h) * * *
    (8) AHAM PAC-1-2014, Portable Air Conditioners, 2014, IBR approved 
for appendix CC to subpart B.
* * * * *
    (o) * * *
    (4) IEC 62301 (``IEC 62301''), Household electrical appliances--
Measurement of standby power, (Edition 2.0, 2011-01), IBR approved for 
appendices C1, D1, D2, G, H, I, J2, N, O, P, X, and CC to subpart B.
* * * * *
0
6. Section 430.23 is amended by adding paragraph (dd) to read as 
follows:

Sec.  430.23  Test procedures for the measurement of energy and water 
consumption.

* * * * *
    (dd) Portable air conditioners. (1) The adjusted cooling capacity, 
expressed in British thermal units per hour (Btu/h), the combined 
energy efficiency ratio in cooling mode, expressed in British thermal 
units per Watts per hour (Btu/W-h), and, for units equipped with a 
heating function, the adjusted heating capacity, expressed in Btu/h, 
and the total combined energy efficiency ratio, expressed in Btu/W-h, 
for portable air conditioners, shall be measured in accordance with 
section 5 of appendix CC of this subpart.
    (2) The estimated annual operating cost for portable air 
conditioners in cooling mode, expressed in dollars per year, shall be 
determined by multiplying the following two factors:
    (i) The sum of the AECcm and AECT as measured 
using the ``Cooling Only'' operating hours in accordance with section 
5.4 of appendix CC of this subpart, and
    (ii) A representative average unit cost of electrical energy in 
dollars per kilowatt-hour as provided by the Secretary, the resulting 
product then being rounded off to the nearest dollar per year.
0
7. Add appendix CC to read as follows:

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

1. Scope

    This appendix covers the test requirements used to measure the 
energy performance of single-duct and dual-duct portable air 
conditioners. It does not contain testing provisions for measuring the 
energy performance of spot coolers at this time.

2. Definitions

    2.1 Active mode means a mode in which a portable air conditioner is 
connected to a mains power source, has been activated, and is 
performing the main functions of cooling or heating the conditioned 
space, circulating air through activation of its fan or blower without 
activation of the refrigeration system, or defrosting the refrigerant 
coil.
    2.2 AHAM PAC-1 means the test standard published by the Association 
of Home Appliance Manufacturers, titled ``Portable Air Conditioners,'' 
AHAM PAC-1-2014 (incorporated by reference; see Sec.  430.3).
    2.3 Cooling mode means an active mode in which a portable air 
conditioner has activated the main cooling function according to the 
thermostat or temperature sensor signal, including activating the 
refrigeration system or the fan or blower without activation of the 
refrigeration system.
    2.4 Dual-duct portable air conditioner means a portable air 
conditioner that draws some or all of the condenser inlet air from 
outside the conditioned space through a duct, and may draw additional 
condenser inlet air from the conditioned space. The condenser outlet 
air is discharged outside the conditioned space by means of a separate 
duct.
    2.5 Energy efficiency ratio for portable air conditioners means a 
measure of energy efficiency of a portable air conditioner calculated 
by dividing the cooling mode or heating mode capacity by the power 
consumption in that mode, measured in Btu per watt-hours (Btu/Wh).
    2.6 Heating mode means an active mode in which a portable air 
conditioner has activated the main heating function according to the 
thermostat or temperature sensor signal, including activating a 
resistance heater, the refrigeration system with a reverse refrigerant 
flow valve, or the fan or blower without activation of the resistance 
heater or refrigeration system.
    2.7 IEC 62301 means the test standard published by the 
International Electrotechnical Commission, titled ``Household 
electrical appliances-Measurement of standby power,'' Publication 62301 
(Edition 2.0 2011-01) (incorporated by reference; see Sec.  430.3).
    2.8 Inactive mode means a standby mode that facilitates the 
activation of active mode by remote switch (including remote control), 
internal sensor, or timer, or that provides continuous status display.
    2.9 Off-cycle mode means a mode in which a portable air 
conditioner:
    (1) Has cycled off its main heating or cooling function by 
thermostat or temperature sensor signal;
    (2) May or may not operate its fan or blower; and
    (3) Will reactivate the main cooling or heating function according 
to the thermostat or temperature sensor signal.
    2.10 Off mode means a mode in which a portable air conditioner is 
connected to a mains power source and is not providing any active mode 
or standby mode function, and where the mode may persist for an 
indefinite time. An indicator that only shows the user that the 
portable air conditioner is in the off position is included within the 
classification of an off mode.
    2.11 Product capacity for portable air conditioners means a measure 
of either the cooling or heating, measured in Btu/h, provided to the 
indoor conditioned space, measured under the specified ambient 
conditions for each active mode. Separate product capacities are 
calculated for cooling and heating modes.
    2.12 Single-duct portable air conditioner means a portable air 
conditioner that draws all of the condenser inlet air from the 
conditioned

[[Page 10245]]

space without the means of a duct, and discharges the condenser outlet 
air outside the conditioned space through a single duct.
    2.13 Spot cooler means a portable air conditioner that draws 
condenser inlet air from and discharges condenser outlet air to the 
conditioned space, and draws evaporator inlet air from and discharges 
evaporator outlet air to a localized zone within the conditioned space.
     2.14 Standby mode means any mode where a portable air conditioner 
is connected to a mains power source and offers one or more of the 
following user-oriented or protective functions which may persist for 
an indefinite time:
     (1) To facilitate the activation of other modes (including 
activation or deactivation of active mode) by remote switch (including 
remote control), internal sensor, or timer; or
     (2) Continuous functions, including information or status displays 
(including clocks) or sensor-based functions. A timer is a continuous 
clock function (which may or may not be associated with a display) that 
provides regular scheduled tasks (e.g., switching) and that operates on 
a continuous basis.

3. Test Apparatus and General Instructions

    3.1 Active mode.
    3.1.1 Test conduct. The test apparatus and instructions for testing 
portable air conditioners in cooling mode and heating mode shall 
conform to the requirements specified in Section 4, ``Definitions'' and 
Section 7, ``Tests,'' of AHAM PAC-1-2014 (incorporated by reference; 
see Sec.  430.3), except as otherwise specified in this appendix. 
Measure duct heat transfer, case heat transfer, and infiltration air 
heat transfer according to section 4.1.1.1, section 4.1.1.2, and 
section 4.1.1.3 of this appendix, respectively.
    3.1.1.1 Duct setup. Use ducting components provided by the 
manufacturer during active mode testing, including, where provided by 
the manufacturer, ducts, connectors for attaching the duct(s) to the 
test unit, and window mounting fixtures. Do not apply additional 
sealing or insulation.
    3.1.1.2 Single-duct evaporator inlet test conditions. When testing 
single-duct units, maintain the evaporator inlet (or condenser inlet 
for heating mode) dry-bulb temperature within a range of 1.0 [deg]F 
with an average difference of 0.3 [deg]F.
    3.1.1.3 Condensate Removal--Cooling Mode. Setup the test unit in 
accordance with manufacturer instructions. If the unit has an auto-
evaporative feature, keep any provided drain plug installed as shipped 
and do not provide other means of condensate removal. If the internal 
condensate collection bucket fills during the test, halt the test, 
remove the drain plug, install a gravity drain line, and start the test 
from the beginning. If no auto-evaporative feature is available, remove 
the drain plug and install a gravity drain line. If no auto-evaporative 
feature or gravity drain is available and a condensate pump is 
included, or if the manufacturer specifies the use of an included 
condensate pump during cooling mode operation, then test the portable 
air conditioner with the condensate pump enabled. For units that shall 
be tested with a condensate pump, apply the provisions in Section 7.1.2 
of AHAM PAC-1-2014 (incorporated by reference; see Sec.  430.3) if the 
pump cycles on and off.
    3.1.1.4 Unit Placement. The evaporator inlet (condenser inlet in 
heating mode) must be no less than 6 feet from any test chamber wall 
surface. For single-duct units, the condenser inlet (evaporator inlet 
in heating mode) must be no less than 6 feet from any other wall 
surface. Additionally, there must be no less than 3 feet between any 
wall surfaces and the other surfaces of the portable air conditioner 
with no air inlet or exhaust.
    3.1.1.5 Electrical supply. For active mode testing, maintain the 
input standard voltage at 115 V 1 percent. Test at the 
rated frequency, maintained within 1 percent.
    3.1.2 Control settings. Set the controls to the lowest available 
temperature setpoint for cooling mode and the highest available 
temperature setpoint for heating mode. If the portable air conditioner 
has a user-adjustable fan speed, select the maximum fan speed setting. 
If the portable air conditioner has an automatic louver oscillation 
feature, disable that feature throughout testing. If the louver 
oscillation feature is included but there is no option to disable it, 
testing shall proceed with the louver oscillation enabled. If the 
portable air conditioner has adjustable louvers, position the louvers 
parallel with the airflow to maximize air flow and minimize static 
pressure loss.
    3.1.3 Measurement resolution and rounding. Record measurements at 
the resolution of the test instrumentation. Round the final cooling and 
heating capacity values in accordance with Table 1 of AHAM PAC-1-2014 
(incorporated by reference; see Sec.  430.3). Round EERcm, 
EERhm, CEERcm, and CEER, as calculated in section 
5 of this appendix, to the nearest 0.1 Btu/Wh.
    3.2 Standby mode and off mode.
    3.2.1 Installation requirements. For the standby mode and off mode 
testing, install the portable air conditioner in accordance with 
Section 5, Paragraph 5.2 of IEC 62301 (incorporated by reference; see 
Sec.  430.3), disregarding the provisions regarding batteries and the 
determination, classification, and testing of relevant modes.
    3.2.2 Electrical energy supply.
    3.2.2.1 Electrical supply. For the standby mode and off mode 
testing, maintain the input standard voltage at 115 V 1 
percent. Maintain the electrical supply at the rated frequency 1 percent.
    3.2.2.2 Supply voltage waveform. For the standby mode and off mode 
testing, maintain the electrical supply voltage waveform indicated in 
Section 4, Paragraph 4.3.2 of IEC 62301 (incorporated by reference; see 
Sec.  430.3).
    3.2.3 Standby mode and off mode wattmeter. The wattmeter used to 
measure standby mode and off mode power consumption must meet the 
requirements specified in Section 4, Paragraph 4.4 of IEC 62301 
(incorporated by reference; see Sec.  430.3).
    3.2.4 Standby mode and off mode ambient temperature. For standby 
mode and off mode testing, maintain room ambient air temperature 
conditions as specified in Section 4, Paragraph 4.2 of IEC 62301 
(incorporated by reference; see Sec.  430.3).
    3.2.5 Duct temperature measurements. Measure the surface 
temperatures of each duct using four equally spaced thermocouples per 
duct, adhered to the outer surface of the entire length of the duct. 
Temperature measurements must be accurate to within 0.5 
[deg]F.
    3.2.6 Case temperature measurements. Measure case surface 
temperatures using four equally spaced thermocouples adhered to each of 
the six case surfaces: front, right, left, back, top, and bottom. Place 
the thermocouples in a configuration that ensures that the case 
surface, when divided into quadrants, contains at least one 
thermocouple in each quadrant. If an evenly spaced case surface 
temperature thermocouple would otherwise be placed on an air inlet or 
exhaust grille, place the thermocouple adjacent to the inlet or exhaust 
grille, as close as possible to even spacing with the other 
thermocouples on that surface. Temperature measurements must be 
accurate to within 0.5 [deg]F.

4. Test Measurement

    4.1 Active mode.
    4.1.1 Cooling mode. Measure the indoor room cooling capacity, 
Capacitycm, in accordance with Section

[[Page 10246]]

7.1.b of AHAM PAC-1-2014 (incorporated by reference; see Sec.  430.3). 
Measure the overall power input in cooling mode, Pcm, in 
Watts, in accordance with Section 7.1.c of AHAM PAC-1-2014 
(incorporated by reference; see Sec.  430.3).
    4.1.1.1 Duct Heat Transfer. Measure the surface temperature of the 
condenser exhaust duct and condenser inlet duct, where applicable, 
calculating the average temperature on each duct (Tduct_j) 
from the average of the four temperature measurements taken on that 
duct. Calculate the surface area (Aduct_j) of each duct 
according to the following:

Aduct_j = [pi] x dj x Lj

Where:

dj is the outer diameter of duct ``j''.
Lj is the extended length of duct ``j'' while under test.
j represents the condenser exhaust duct and, for dual-duct units, 
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 
as follows.

Qduct_cm = [Sigma]j{h x Aduct\j x (Tduct\j - Tei){time} 

Where:

Qduct_cm is the total heat transferred from the duct(s) 
to the indoor conditioned space in cooling mode.
h is the convection coefficient, 4 Btu/h per square foot per [deg]F.
Aduct_j is the surface area of duct ``j'', in square 
feet.
Tduct_j is the average surface temperature for duct 
``j'', in [deg]F.
    j represents the condenser exhaust duct and, for dual-duct 
units, condenser inlet duct.
    Tei is the average evaporator inlet air dry-bulb 
temperature, in [deg]F.

    4.1.1.2 Case Heat Transfer. Determine the average surface 
temperature, Tcase_k, for each side of the test unit case by 
averaging the four temperature measurements on that side.
    Calculate the surface area of each case side as the product of the 
two primary surface dimensions. Calculate the surface area of the case 
side according to the following:

Acase_k = D1_k x D2_k

Where:
D1_k and D2_k are the two primary dimensions 
of the case side ``k'' exposed to ambient air.

    Calculate the heat transferred from all case sides to the indoor 
conditioned space according to the following:

Qcase_cm = [Sigma]k{h x Acase\k x (Tcase\k - Tei){time} 

Where:

Qcase_cm is the total heat transferred from all case 
sides to the indoor conditioned space in cooling mode.
h is the convection coefficient, 4 Btu/h per square foot per [deg]F.
k represents the case sides, including front, back, right, left, 
top, and bottom.
Acase_k is the surface area of case side ``k'', in square 
feet.
Tcase_k is the average surface temperature of case side 
``k'', in [deg]F.
Tei is the average evaporator inlet air dry-bulb 
temperature, in [deg]F.

    4.1.1.3 Infiltration Air Heat Transfer. Measure the heat 
contribution from infiltration air for single-duct units and dual-duct 
units that draw at least part of the condenser air from the conditioned 
space. The dry air mass flow rate of infiltration air shall be 
calculated according to the following.
[GRAPHIC] [TIFF OMITTED] TP25FE15.011

Where:

mmsd is the dry air mass flow rate of infiltration air 
for a single-duct unit, in pounds per minute (lb/m).
mmdd is the dry air mass flow rate of infiltration air 
for a dual-duct unit, in lb/m.
Vco is the volumetric flow rate of the condenser outlet 
air, in cubic feet per minute (cfm).
Vci is the volumetric flow rate of the condenser inlet 
air, in cfm.
[rho]co is the density of the condenser outlet air, in 
pounds mass per cubic foot (lbm/ft\3\).
[rho]ci is the density of the condenser inlet air, in 
lbm/ft\3\.
[omega]co is the humidity ratio of condenser outlet air, 
in pounds mass of water vapor per pounds mass of dry air 
(lbw/lbda).
[omega]ci is the humidity ratio of condenser inlet air, 
in lbw/lbda.

    Calculate the sensible component of infiltration air heat 
contribution according to the following:
[GRAPHIC] [TIFF OMITTED] TP25FE15.012

Where:

Qs is the sensible heat added to the room by infiltration 
air, in Btu/h.
mm is the dry air mass flow rate of infiltration air,
mmSD or
mmDD, in lb/m.
cp_da is the specific heat of dry air, 0.24 Btu/
lbm-[deg]F.
cp_wv is the specific heat of water vapor, 0.444 Btu/
lbm-[deg]F.
[omega]ia is the humidity ratio of the infiltration air, 
0.0141 lbw/lbda.
[omega]ei is the humidity ratio of the evaporator inlet 
air, in lbw/lbda.
60 is the conversion factor from minutes to hours.
Tei is the indoor chamber dry-bulb temperature measured 
at the evaporator inlet, in [deg]F.
Tia is the infiltration air dry-bulb temperature, 
95[emsp14][deg]F.

    Calculate the latent heat contribution of the infiltration air 
according to the following::
[GRAPHIC] [TIFF OMITTED] TP25FE15.013

Where:

Ql is the latent heat added to the room by infiltration 
air, in Btu/h.
mm is the mass flow rate of infiltration air,
mmSD or
mmDD, in lb/m.
[omega]ia is the humidity ratio of the infiltration air, 
0.0141 lbw/lbda.
[omega]ei is the humidity ratio of the evaporator inlet 
air, in lbw/lbda.
Hfg is the latent heat of vaporization for water vapor, 
1061 Btu/lbm.
60 is the conversion factor from minutes to hours.
    The total heat contribution of the infiltration air is the sum of 
the sensible and latent heat:

Qinfiltration\cm = Qs + Ql

Where:

Qinfiltration_cm is the total infiltration air heat in 
cooling mode, in Btu/h.
Qs is the sensible heat added to the room by infiltration 
air, in Btu/h.
Ql is the latent heat added to the room by infiltration 
air, in Btu/h.

    4.1.2 Heating Mode. Measure the indoor room heating capacity, 
Capacityhm, overall power input in heating mode, 
Phm, duct heat transfer, Qduct_hm, case heat 
transfer, Qcase_hm, and infiltration air heat transfer, 
Qinfiltration_hm, as for cooling in section 4.1.1 of this 
appendix, except that: (1) The terms ``Evaporator'' and ``Condenser'' 
shall refer to the heat exchanger configuration in cooling mode, not 
the reverse cycle heating mode; (2) the resulting Capacityhm 
shall be multiplied by -1 to convert from cooling capacity to heating

[[Page 10247]]

capacity; and (3) the temperatures provided in the table below shall be 
used in place of the standard rating conditions found in Table 2 of 
AHAM PAC-1-2014 (incorporated by reference; see Sec.  430.3).

----------------------------------------------------------------------------------------------------------------
                                                   Evaporator inlet air, [deg]F     Condenser inlet air, [deg]F
 Test Configuration from table 2 in AHAM PAC-1-              ([deg]C)                        ([deg]C)
                      2014                       ---------------------------------------------------------------
                                                     Dry-bulb        Wet-bulb        Dry-bulb        Wet-bulb
----------------------------------------------------------------------------------------------------------------
3...............................................     70.0 (21.1)     60.0 (15.6)     47.0 (8.33)     43.0 (6.11)
5...............................................     70.0 (21.1)     60.0 (15.6)     70.0 (21.1)     60.0 (15.6)
----------------------------------------------------------------------------------------------------------------

    4.2 Off-cycle mode. Establish the test conditions specified in 
section 3.1.1 of this appendix, except that the wattmeter specified in 
section 3.2.3 of this appendix shall be used. Begin the off-cycle mode 
test period 5 minutes following the cooling mode test period. Adjust 
the setpoint higher than the ambient temperature to ensure the product 
will not enter cooling mode and begin the test 5 minutes after the 
compressor cycles off due to the change in setpoint. The off-cycle mode 
test period shall be 2 hours in duration, during which the power 
consumption is recorded at the same intervals as recorded for cooling 
mode testing. Measure and record the average off-cycle mode power of 
the portable air conditioner, Poc, in watts.
    4.3 Standby mode and off mode. Establish the testing conditions set 
forth in section 3.2 of this appendix, ensuring that the portable air 
conditioner does not enter any active modes during the test. For 
portable air conditioners that take some time to enter a stable state 
from a higher power state as discussed in Section 5, Paragraph 5.1, 
Note 1 of IEC 62301, (incorporated by reference; see Sec.  430.3), 
allow sufficient time for the portable air conditioner to reach the 
lowest power state before proceeding with the test measurement. Follow 
the test procedure specified in Section 5, Paragraph 5.3.2 of IEC 62301 
(incorporated by reference; see Sec.  430.3) for testing in each 
possible mode as described in sections 4.2.1 and 4.2.2 of this 
appendix.
    4.3.1 If the portable air conditioner has an inactive mode, as 
defined in section 2.8 of this appendix, but not an off mode, as 
defined in section 2.10 of this appendix, measure and record the 
average inactive mode power of the portable air conditioner, 
Pia, in watts.
    4.3.2 If the portable air conditioner has an off mode, as defined 
in section 2.10 of this appendix, measure and record the average off 
mode power of the portable air conditioner, Pom, in watts.
5. Calculation of Derived Results From Test Measurements
    5.1 Adjusted Cooling Capacity. Calculate the adjusted cooling 
capacity for portable air conditioners, ACC, expressed in Btu/h, 
according to the following:

ACC = Capacitycm - Qduct\cm - Qcase\cm - Qinfiltration\cm

Where:

Capacitycm is the cooling capacity measured in section 
4.1.1 of this appendix.
Qduct_cm is the duct heat transfer while operating in 
cooling mode, measured in section 4.1.1.1 of this appendix.
Qcase_cm is the case heat transfer while operating in 
cooling mode, measured in section 4.1.1.2 of this appendix.
Qinfiltration_cm is the infiltration air heat transfer 
while operating in cooling mode, measured in section 4.1.1.3 of this 
appendix.

    5.2 Adjusted Heating Capacity. Calculate the adjusted heating 
capacity for portable air conditioners, AHC, expressed in Btu/h, 
according to the following:
AHC = Capacityhm + Qduct\hm + Qcase\hm + Qinfiltration\hm

Where:

Capacityhm is the heating capacity measured in section 
4.1.2 of this appendix.
Qduct_hm is the duct heat transfer while operating in 
heating mode, measured in section 4.1.2 of this appendix.
Qcase_hm is the case heat transfer while operating in 
heating mode, measured in section 4.1.2 of this appendix.
Qinfiltration_hm is the infiltration air heat transfer 
while operating in heating mode, measured in section 4.1.2 of this 
appendix.

    5.3 Energy Efficiency Ratio. Calculate the cooling energy 
efficiency ratio, EERcm, and heating energy efficiency 
ratio, EERhm, both expressed in Btu/Wh, according to the 
following: 
[GRAPHIC] [TIFF OMITTED] TP25FE15.014

Where:

ACC is the adjusted cooling capacity, in Btu/h, calculated in 
section 5.1 of this appendix.
AHC is the adjusted heating capacity, in Btu/h, calculated in 
section 5.2 of this appendix.
Pcm is the overall power input in cooling mode, in watts, 
measured in section 4.1.1 of this appendix.
Phm is the overall power input in heating mode, in watts, 
measured in section 4.1.2 of this appendix.

    5.4 Annual Energy Consumption. Calculate the annual energy 
consumption in each operating mode, AECm, expressed in 
kilowatt-hours per year (kWh/year). The annual hours of operation in 
each mode are estimated as follows:

------------------------------------------------------------------------
                                                 Annual operating hours
                                                    for calculating:
                Operating mode                 -------------------------
                                                  Cooling    Cooling and
                                                    only       heating
------------------------------------------------------------------------
Cooling.......................................          750          750
Heating.......................................            0        1,008
Off-Cycle.....................................          880        2,063
Inactive or Off...............................        1,355        1,704
------------------------------------------------------------------------

AECm = Pm x tm x k

Where:
AECm is the annual energy consumption in each mode, in 
kWh/year.
Pm is the average power in each mode, in watts.
t is the number of annual operating time in each mode, in hours.
m represents the operating mode (``cm'' cooling, ``hm'' heating, 
``oc'' off-cycle, and ``ia'' inactive or ``om'' off mode).
k is 0.001 kWh/Wh conversion factor from watt-hours to kilowatt-
hours.

    Total annual energy consumption in all modes except cooling and 
heating, is calculated according to the following:
AECT = [Sigma]m AECm

Where:

AECT is the total annual energy consumption attributed to 
all modes except cooling and heating, in kWh/year;
AECm is the total annual energy consumption in each mode, 
in kWh/year.
m represents the operating modes included in AECT (``oc'' 
off-cycle, and ``im'' inactive or ``om'' off mode).

    5.5 Combined Energy Efficiency Ratio in Cooling Mode. Using the 
annual operating hours for cooling only, as outlined in section 5.4 of 
this appendix, calculate the cooling mode combined energy efficiency 
ratio, CEERcm, expressed in Btu/Wh, according to the 
following:

[[Page 10248]]

[GRAPHIC] [TIFF OMITTED] TP25FE15.015

Where:

CEERcm is the combined energy efficiency ratio in cooling 
mode, in Btu/Wh.
ACC is the adjusted cooling capacity, in Btu/h, calculated in 
section 5.1 of this appendix.
AECcm is the annual energy consumption in cooling mode, 
in kWh/year, calculated in section 5.4 of this appendix.
AECT is the total annual energy consumption attributed to 
all modes except cooling and heating, in kWh/year, calculated in 
section 5.4 of this appendix.
t is the number of hours per year, 8,760.
k is 0.001 kWh/Wh conversion factor for watt-hours to kilowatt-
hours.

    5.6 Total Combined Energy Efficiency Ratio. For units with heating 
and cooling modes, use the annual operating hours for cooling and 
heating, as outlined in section 5.4 of this appendix to calculate the 
total combined energy efficiency ratio, CEER, expressed in Btu/Wh. For 
units with no heating mode, CEER shall be equal to CEERcm, 
calculated as described in section 5.5 of this appendix. 
[GRAPHIC] [TIFF OMITTED] TP25FE15.016

Where:

ACC is the adjusted cooling capacity, in Btu/h, calculated in 
section 5.1 of this appendix.
AHC is the adjusted heating capacity, in Btu/h, calculated in 
section 5.2 of this appendix.
hcm and hhm are the cooling and heating mode 
operating hours, respectively.
AECcm is the annual energy consumption in cooling mode, 
in kWh/year, calculated in section 5.4 of this appendix.
AEChm is the annual energy consumption in heating mode, 
in kWh/year, calculated in section 5.4 of this appendix.
AECT is the total annual energy consumption attributed to 
all modes except cooling and heating, in kWh/year, calculated in 
section 5.4 of this appendix.
t is the number of hours per year, 8,760.
k is 0.001 kWh/Wh conversion factor for watt-hours to kilowatt-
hours.

[FR Doc. 2015-03589 Filed 2-24-15; 8:45 am]
BILLING CODE 6450-01-P
```