[Federal Register Volume 80, Number 37 (Wednesday, February 25, 2015)]
[Proposed Rules]
[Pages 10212-10248]
From the Federal Register Online via the Government Publishing 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: [email protected]. 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:
[email protected].
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: [email protected].
Ms. Sarah Butler, U.S. Department of Energy, Office of the General
Counsel, Mailstop GC-33, 1000 Independence Ave. SW., Washington, DC
20585-0121. Telephone: 202-586-1777; Email: [email protected].
SUPPLEMENTARY INFORMATION: 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.
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(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 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 [email protected].
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: [email protected]
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