[Federal Register: May 12, 1997 (Volume 62, Number 91)]
[Rules and Regulations]
[Page 26139-26165]
From the Federal Register Online via GPO Access [wais.access.gpo.gov]
[DOCID:fr12my97-23]
[[Page 26139]]
_______________________________________________________________________
Part IV
Department of Energy
_______________________________________________________________________
Office of Energy Efficiency and Renewable Energy
_______________________________________________________________________
10 CFR Part 430
Energy Conservation Program for Consumer Products: Test Procedures for
Furnaces/Boilers, Vented Home Heating Equipment, and Pool Heaters;
Final Rule
[[Page 26140]]
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DEPARTMENT OF ENERGY
Office of Energy Efficiency and Renewable Energy
10 CFR Part 430
[Docket No. EE-RM-93-501]
RIN 1904-AA45
Energy Conservation Program for Consumer Products: Test
Procedures for Furnaces/Boilers, Vented Home Heating Equipment, and
Pool Heaters
AGENCY: Office of Energy Efficiency and Renewable Energy, Department of
Energy.
ACTION: Final rule.
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SUMMARY: The Energy Policy and Conservation Act, as amended, requires
the Department of Energy (DOE or the Department) to administer an
energy conservation program for certain major household appliances and
commercial equipment. Among other program elements, the Act requires
that standard methods of testing be prescribed for each covered
product. Today's final rule amends the test procedures for furnaces and
boilers, vented home heating equipment, and pool heaters.
EFFECTIVE DATE: This rule is effective November 10, 1997. The
incorporation by reference of certain publications listed in the
regulations is approved by the Director of the Federal Register as of
November 10, 1997.
ADDRESSES: The Department is incorporating by reference test standards
from the American Society of Heating, Refrigerating and Air-
Conditioning Engineers, Inc. (ASHRAE) and the American National
Standards Institute, Inc. (ANSI). These standards are listed below:
American National Standards Institute/American Society of Heating,
Refrigerating, and Air-Conditioning Engineers Standard 103-1993,
``Methods of Testing for Annual Fuel Utilization Efficiency of
Residential Central Furnaces and Boilers,'' and American National
Standards Institute Standard Z21.56-1994, ``Gas-Fired Pool Heaters.''
Copies of these standards may be viewed at the Department of Energy
Freedom of Information Reading Room, Forrestal Building, Room 1E-190,
1000 Independence Avenue, SW., Washington, DC 20585, (202) 586-6020
between the hours of 9 a.m. and 4 p.m., Monday through Friday, except
Federal holidays.
Copies of the ANSI/ASHRAE Standard 103-1993 can be obtained from
ASHRAE Publication Sales, 1791 Tullie Circle, NE, Atlanta, GA 30329,
(1-800-5-ASHRAE). Copies of the ANSI Standard Z21.56-1994 can be
obtained from the ANSI, Inc., 11 West 42nd Street, New York, N.Y.
10036, (212) 642-4936.
FOR FURTHER INFORMATION CONTACT:
Cyrus H. Nasseri, U.S. Department of Energy, Office of Energy
Efficiency and Renewable Energy, Mail Station, EE-43, 1000 Independence
Avenue, SW, Washington, D.C. 20585-0121, (202) 586-9142, FAX (202) 586-
4617.
Eugene Margolis, Esq., U.S. Department of Energy, Office of General
Counsel, Mail Station, GC-72, 1000 Independence Avenue, SW, Washington,
D.C. 20585-0103, (202) 586-9507.
SUPPLEMENTARY INFORMATION:
I. Introduction
A. Authority
B. Background
II. Discussion of Comments
A. Furnaces
B. Vented Home Heating Equipment
C. Pool Heaters
III. Procedural Requirements
A. Review Under the National Environmental Policy Act of 1969
B. Review Under Executive Order 12866, ``Regulatory Planning and
Review''
C. Review Under the Regulatory Flexibility Act
D. Review Under Executive Order 12612, ``Federalism''
E. Review Under Section 32 of the Federal Energy Administration
Act of 1974
F. Review Under Executive Order 12630, ``Governmental Actions
and Interference With Constitutionally Protected Property Rights''
G. Review Under the Paperwork Reduction Act of 1980
H. Review Under Executive Order 12988, ``Civil Justice Reform''
I. Unfunded Mandates Reform Act Review
J. Review Under Small Business Regulatory Enforcement Fairness
Act of 1996
I. Introduction
A. Authority
Part B of Title III of the Energy Policy and Conservation Act, Pub.
L. 94-163, as amended by the National Energy Conservation Policy Act
(NECPA) Pub. L. 95-619, the National Appliance Energy Conservation Act
(NAECA) of 1987, Pub. L. 100-12, the National Appliance Energy
Conservation Amendments of 1988 (NAECA 1988), Pub. L. 100-357 and the
Energy Policy Act of 1992 (EPACT), Pub. L. 102-486, created the Energy
Conservation Program for Consumer Products other than Automobiles
(Program).1 The 13 consumer household products currently
subject to this Program (referred to hereinafter as ``covered
products'') include furnaces/boilers, vented home heating equipment,
and pool heaters, the subjects of today's notice.
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\ 1\Part B of Title III of the Energy Policy and Conservation
Act , as amended, is referred to in this final rule as the ``Act''
or EPCA. Part B of Title III is codified at 42 U.S.C. 6291-6309.
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Under the EPCA, the Program consists essentially of three parts:
Testing, labeling, and Federal energy conservation standards. The
Department, in consultation with the National Institute of Standards
and Technology (NIST), is required to amend or establish new test
procedures as appropriate for each of the covered products. EPCA
section 323, 42 U.S.C. 6293. Test procedures appear at 10 CFR part 430,
subpart B. The purpose of the test procedures is 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. The procedures must not be unduly burdensome to
conduct. EPCA section 323(b)(3), 42 U.S.C. 6293 (b)(3). A test
procedure is not required if DOE determines by rule that one cannot be
developed. EPCA section 323(d)(1), 42 U.S.C. 6293(d)(1).
One hundred and eighty days after a test procedure for a product is
adopted, no manufacturer may represent the energy consumption of, or
the cost of energy consumed by, the product, except as reflected in
tests conducted according to the DOE procedure. EPCA section 323(c)(2),
42 U.S.C. 6293(c)(2). However, the 180-day period referred to in
section 323(c)(2) may be extended for up to an additional 180 days if
the Secretary determines that the requirements of section 323(c)(2)
would impose an undue burden. EPCA section 323(c)(3), 42 U.S.C. 6293
(c)(3).
Section 323(e) of the Act requires DOE to determine to what extent,
if any, a proposed test procedure would alter the measured energy
efficiency or measured energy use of any covered product as determined
under the existing test procedure. If DOE determines that an amended
test procedure would alter the measured efficiency or measured energy
use of a covered product, DOE is required to amend the related energy
conservation standard accordingly. In determining the amended standard,
DOE is required to measure the energy efficiency or energy use of
representative samples of covered products that minimally comply with
the existing standard. The average efficiency of these representative
samples, tested using the amended test procedure, constitutes the
[[Page 26141]]
amended standard. EPCA section 323(e)(2), 42 U.S.C. 6293(e)(2).
B. Background
On March 28, 1984, the Department published in the Federal Register
a final rule, hereinafter referred to as the 1984 Final Rule, amending
the test procedures for furnaces, vented home heating equipment, and
unvented home heating equipment. 49 FR 12148. For furnaces, the 1984
Final Rule referenced the ANSI/ASHRAE Standard 103-1982 entitled
``Methods of Testing for Heating Seasonal Efficiency of Central
Furnaces and Boilers.'' In addition, it prescribed furnace test
procedures for systems and issues that were not adequately covered by
the ANSI/ASHRAE Standard 103-1982. Those included, for example,
provisions for modulating and condensing furnaces and boilers.
Particularly impacted were units with thermal stack dampers. Other
deviations between the 1984 Final Rule and ANSI/ASHRAE Standard 103-
1982 related to oversize factors, furnaces without draft relief or
direct exhaust system, hot water boiler minimum return (inlet) water
temperature and minimum water temperature rise, pump delay on boiler
controls, an improved method for the determination of the S/F factor
(the ratio of stack gas mass flow rate to flue gas mass flow rate) for
furnaces and boilers, and the option of an assigned jacket loss value
instead of actual measurement.
The Department originally published a test procedure for vented
home heating equipment on May 2, 1978. 43 FR 20182. The Department
amended this test procedure in the 1984 Final Rule, to include a
simplified vented heater test procedure for heaters with modulating
controls, manually controlled vented heaters, vented heaters equipped
with thermal stack dampers, and floor furnaces. 49 FR 12169.
The Department published the pool heater test procedure final rule
on February 7, 1989, referencing ANSI Standard Z21.56-1986 for gas pool
heaters and extending the test procedure to cover oil-fired pool
heaters. 54 FR 6076.
Since 1984, through cooperative efforts with the furnace industry
and through the DOE test procedure waiver process, DOE has become aware
of several additional issues regarding furnace and vented home heating
equipment test procedures. On August 23, 1993, DOE published in the
Federal Register a proposed rule and notice of public hearing,
hereinafter referred to as the 1993 Proposed Rule, to amend the
furnace, vented home heating equipment, and pool heater test procedures
to address these issues. 58 FR 44538. A public hearing was held in
Washington, DC on January 5, 1994.
After reviewing the comments presented at the public hearing on
January 5, 1994, and additional written comments submitted following
the public hearing, the Department decided to reopen the public comment
period to solicit additional comments on one subject of particular
concern to commenters in the 1993 Proposed Rule--the application of a
multiplication factor to the auxiliary electricity consumption of a
fossil-fueled appliance. The proposed multiplication factor in the 1993
Proposed Rule consisted of the ratio of the electrical ``source
energy'' (the amount of energy used in producing the electricity
consumed by the appliance) to the electrical ``site energy'' (the
amount of electricity consumed by the appliance). The multiplication
factor was used in the two proposed new energy descriptors, named
Energy Factor (EF) and Annual Efficiency (AE), proposed by the
Department to include the auxiliary electrical energy consumption by
fossil-fueled appliances.
On January 20, 1995, the Department published a Federal Register
notice, reopening the comment period to seek comments on a revision of
the proposed definition of the multiplication factor. The new proposed
definition was the ratio of the cost of electricity to the cost of
fossil fuel to the consumer. 60 FR 4348. The 30-day public comment
period was extended by an additional 30 days at the request of
commenters and was closed on March 21, 1995.
Today's notice amends the test procedures for furnaces and boilers,
vented home heating equipment, and pool heaters as follows:
(1) DOE is amending the test procedure for furnaces and boilers
first, to incorporate provisions contained in test procedure waivers
granted to different manufacturers from 1985 to 1996 and secondly, to
include test procedures for new product designs. To accomplish this,
the ANSI/ASHRAE Standard 103-1993 is incorporated by reference into the
test procedure, in the place of ANSI/ASHRAE 103-1988 that was
referenced in the 1993 proposed rule. (See below at II. a. 23. ``ANSI/
ASHRAE Standard 103-1993.'') This incorporation establishes revised
test procedures for the following furnaces and features: Atmospheric
furnaces with burner air inlet dampers or flue dampers; the jacket loss
measurement for downflow furnaces; and furnaces and boilers employing
electro-mechanical stack dampers with delayed opening and power vented
units employing post purge during the off-cycle. In addition, however,
today's notice incorporates into DOE's test procedure provisions that
are modifications of certain sections of ANSI/ASHRAE Standard 103-1993.
Those modifications include the limit on air circulation blower delay
time at burner shut-off for furnaces with unvarying control on blower
delay time, deletion of the insulation requirement on the internal vent
pipe of downflow furnace during the cool-down and heat-up tests,
deletion of the requirement for the sealing of cabinet ventilation
openings during the jacket loss measurement, longer allowed free post
purge time for power vented units employing post purge, and input
requirement on interrupted ignition device. In addition, today's final
rule provides procedures for the calculation of the annual fossil fuel
and auxiliary electrical energy consumptions.
(2) DOE is amending the test procedure for vented home heating
equipment by, first, including modified calculation procedures for the
weighted average steady-state efficiency and Annual Fuel Utilization
Efficiency (AFUE) for certain manually-controlled heaters, and
secondly, adding a procedure for calculating the annual energy
consumption of fossil fuel and auxiliary electrical energy for vented
home heating equipment.
(3) DOE is amending the test procedure for pool heaters by updating
the referenced ANSI standard for pool heaters from ANSI Z21.56-1986 to
ANSI Z21.56-1994. DOE is also adding a procedure for calculating the
annual energy consumption of fossil fuel and auxiliary electrical
energy for pool heaters and a pool heater heating seasonal efficiency
descriptor that takes into account the energy consumption by the pilot
light during the standby period of the pool heating season.
II. Discussion of Comments
A. Furnaces
In general, the comments received were supportive of the goals of
the proposed amendments to incorporate provisions contained in waivers
previously granted, to include test procedures for new product designs,
and to capture the electrical consumption of furnaces. However, the
comments by various organizations presented disagreements with DOE's
proposal on the effect of some of the amendments on the measured AFUE.
Additionally, many comments were received on the proposed formulation
of energy descriptors to capture electrical
[[Page 26142]]
consumption, on both the 1993 Proposed Rule and the January 20, 1995,
Federal Register notice.
In its testimony and written statement, the Gas Appliance
Manufacturers Association (GAMA) classified the proposed revisions to
the current test procedure contained in the 1993 Proposed Rule into
three categories. (GAMA, No. 8, at 2).2
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\2\ Written comments on the 1993 Proposed Rule were assigned
docket numbers and are numbered consecutively. Comments presented at
the January 5, 1994, public hearing are contained in the transcript.
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The first category comprised changes that GAMA states would not
lower the measured AFUE of most existing furnace and boiler models,
including changes to bring the test procedures in line with waivers
previously granted. GAMA stated its support for the immediate
implementation of most of the first category of changes.
The second category included changes that GAMA states would lower
the measured AFUE of most existing furnace and boiler models. Such a
change, GAMA claimed, would require the Department to amend the furnace
and boiler efficiency standards because of the impact on existing
models that marginally meet the standard. According to GAMA, this would
cause confusion in the marketplace, accustomed as it is to the current
standard, a minimum AFUE of 78 percent for warm air furnaces.
Additionally, GAMA asserted that a reduction in the measured AFUE would
result in many units no longer qualifying for utility rebate programs
that require an AFUE of at least 80 percent. GAMA stated the view that
these changes would place a heavy burden on manufacturers and requested
a delay in the implementation of the second category of changes until
any revised efficiency standards went into effect. GAMA puts the
following changes in this category: Revised calculation for the
effectiveness of electro-mechanical stack dampers; power vented systems
employing post purge after burner shut-off; sealing of cabinet
ventilation openings during jacket loss test; insulation of horizontal
mounted external draft diverters; insulation of the flue collector box
for power vented units; insulation of the internal flue pipe for
downflow furnaces during heat-up and cool-down tests; minimum values
for the draft factor DP and DF; measurement of
water pump energy consumption; and test requirement for modulating
boilers.
The third category was the addition of the proposed AE energy
descriptor. GAMA suggested further study on the third category before
implementation.
Consolidated Industries, Carrier Corp., and Lennox Industries
supported GAMA's statement. (Consolidated, No. 21, at 1; Carrier, No.
12, at 1; and Lennox, Transcript, at 77). Inter-City Products presented
the same list of revisions regarding their potential impact on AFUE as
GAMA did. Many of the other commenters referred to GAMA's
classification of the three categories of proposed revisions to the DOE
test procedure in their oral and written statements and these
categories are referred to in the discussion of comments below.
The following discussion addresses the comments received on the
proposed rule.
1. Furnaces and Boilers With Small Air Passage in the Flue
In the 1993 Proposed Rule, DOE proposed to change the limiting
value of 10 percent from a flow rate ratio to an area ratio. Both GAMA
and Inter-City Products supported the proposed revision. (GAMA, No. 8,
at 2; and Inter-City, No. 7, at 4). No other commenters offered comment
on this issue. The Department is adopting the change in sections
8.2.1.2.2 and 8.3.1.2 of ANSI/ASHRAE Standard 103-1993 in today's final
rule.
2. Air Circulation Blower Delay at Burner Ignition
The 1993 Proposed Rule specified a minimum blower delay time of 20
seconds during the heat-up test for furnaces designed with non-
adjustable, unvarying delay time that is less than 20 seconds. The
current furnace test procedure requires a 1.5-minute delay between the
ignition of the burner and the starting of the blower. Manufacturers
have requested and been granted waivers from this requirement because
of an unvarying time delay designed into their specific models. The
designed time delay granted in the waivers varied from 20 seconds to 66
seconds among the specific models with 30 seconds as the predominant
time delay. The manufacturers claimed increases in the AFUE value of
from 0.4 to 2.0 percentage points if the designed time delays were used
in the rating test instead of the 1.5 minutes specified in the current
test procedure. The Department's granting of the waivers permitted
those manufacturers to test units with blowers having unvarying time
delay designed into them. In the 1993 Proposed Rule, the Department
proposed test procedures to allow testing with an unvarying time delay,
but also proposed a minimum blower delay time of 20 seconds during the
heat-up test. This is achieved by bypassing the electronic control, if
the designed non-adjustable, unvarying delay time is less than 20
seconds.
Both GAMA and Inter-City Products opposed the requirement of a
minimum 20-second delay during the heat-up test for furnaces with
designed, unvarying blower time delay at burner start-up. Amana
Refrigeration, Inc., stated that DOE's reason of avoiding a cold draft
in the occupied zone is an issue of comfort, not energy efficiency, and
that DOE should let the competitive marketplace design products that
fulfill consumers' desires. (Amana, No. 2, at 1). Inter-City Products
stated that DOE should not define what occupant comfort is, and as
advances in heat exchanger technology come about, low mass heat
exchanger with very short heat-up characteristics will evolve allowing
short on-time delays. Inter-City Products also stated that mandating
time delays as to occupant comfort is to prescribe the design of a
furnace and would not necessarily reflect the true operation and
efficiency of current or future furnace designs. (Inter-City, No. 7, at
2). GAMA and York International Corp. gave similar reasons as Inter-
City Products for opposing the 20-second requirement, and stated that
DOE is acting outside its authority in factoring occupant comfort into
the efficiency test procedure. Further they stated that it is for the
marketplace, not DOE, to discourage the sale of furnaces that do not
provide a reasonable level of occupant comfort. In addition, the
complexity of the electronic controls used in today's furnaces makes it
very difficult for a field installer or repairer to modify an unvarying
blower time delay. (GAMA, No. 8, at 16; and York, No. 10, at 3.)
Carrier Corp. and Consolidated Industries both supported GAMA's
statement. (Carrier No. 12, at 1; and Consolidated, No. 21, at 1.) Mr.
Woodworth stated that comfort should not be the basis for provisions
being included in a laboratory test procedure. Further, he suggested
that the procedure should be changed to agree with section 9.6.1 of
ANSI/ASHRAE Standard 103-1993, that does not include the 20-second
requirement. (Woodworth, No. 20, at 5).
In the current test procedure for furnaces, the 1.5-minute fan
delay at burner ignition was specified on the basis of obtaining a low
overall cost of combined fossil fuel and auxiliary electrical energy
consumption.3 This
[[Page 26143]]
was balanced with the historically accepted industry practice in
furnace operation of providing occupant comfort. In granting the waiver
requests, the Department recognized the advances made by manufacturers
on lighter weight heat exchanger designs with fan-assisted combustion
systems over the past decade. These advances permitted a faster heat-up
of the heat exchanger and a shorter fan delay time while still
achieving the desired low overall energy consumption. In the 1993
proposed rule, the Department believed that there is a limit to
reducing the weight of the heat exchanger and, in turn, a limit to the
achievable minimum fan delay time. This is evident from the fan delay
times in the waiver requests, that were mostly greater than or equal to
30 seconds. It is possible, however, that as new material and
technology evolve, an even lighter weight heat exchanger with better
heat transfer performance will be developed. Such a heat exchanger
could result in a faster furnace heat-up and allow a fan delay time of
less than 20 seconds. The 20-second minimum fan delay time might become
inappropriate for these better-designed furnaces of the future.
Nevertheless, for furnaces lacking such designs, the Department
believes that without the minimum fan delay requirement used during the
test for furnaces with non-adjustable, unvarying fan delay control, a
manufacturer could simply modify the furnace's electronic control
without any resulting improvement in its heat transfer performance.
Thus, the manufacturer would obtain a higher AFUE value. The Department
assumes that consideration of consumer satisfaction in the long term
will prevent that practice.
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\3\Unpublished National Bureau of Standards report, Joseph Chi,
``A Note on Effect of HX Weights on annual performance and cost of
Operation of a furnace,'' February, 1978.
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Based on the above reasons, the Department has decided to drop the
proposed requirement of a 20-second minimum fan delay for furnaces
designed with a non-adjustable, unvarying blower time delay during the
heat-up test. Instead, DOE is adopting the procedure specified in
section 9.6.1 of ANSI/ASHRAE Standard 103-1993 in today's final rule.
3. Air Circulation Blower Delay at Burner Shut-off
In the 1993 Proposed Rule, DOE proposed a modification to the ANSI/
ASHRAE Standard 103-1988 version of the procedure now specified in
section 9.5.1.2.2 of ANSI/ASHRAE Standard 103-1993. The modification
requires that a furnace, if designed with an unvarying time delay that
does not provide the same blower delay time that is specified for units
with adjustable blower control, shall be tested with the blower control
bypassed, and the blower manually controlled to give the delay time
specified during the cool-down test. This delay time is three minutes
for non-condensing, or 1.5 minutes for condensing furnaces, or 40 deg.F
temperature difference, whichever gives the longer time delay.
During the cool-down test, the extant test procedure allows a delay
in blower shut-off of three minutes (1.5 minutes for condensing
furnaces) or until the supply air temperature drops to a value of
40 deg.F above the inlet air temperature, whichever gives the longer
time delay. ANSI/ASHRAE Standard 103-1993 provided an additional
exception (section 9.5.1.2.2) that for a furnace without adjustable fan
control, the delay shall be as designed.
Both GAMA and Inter-City Products, as well as other commenters,
expressed opposition to the specified maximum time delays for blowers
with unvarying time delay in the proposed test procedure during the
cool-down test. Inter-City Products stated that older or heavier mass
heat exchangers may require more than three minutes of cool-down time.
They gave the same reasons as given in Inter-City Products' comments
against blower time delay at burner ignition in opposing the use of
occupant comfort as the criterion in determining the maximum allowable
time delay. (Inter-City, No. 7, at 2). GAMA gave similar reasons as
Inter-City Products in opposing the requirement with respect to high
mass heat exchangers. Further, they gave the same reasons as given in
GAMA's comments against blower time delay at burner ignition in
opposing the use of occupant comfort as a criterion in the test
procedure. GAMA also pointed out the difficulty of adjusting an
unvarying electronic time delay control in the field. (GAMA, No. 8, at
16). York International gave similar reasons as GAMA. (York
International, No. 10, at 3). Carrier Corp. and Consolidated Industries
both supported GAMA's statement. (Carrier, No. 12, at 1; and
Consolidated, No. 21, at 1). The California Energy Commission (CEC)
pointed out that the wording in section 8.4 of appendix N in the 1993
Proposed Rule is misleading. It stated that the time delay criterion of
40 deg.F temperature difference between supply air and return air for
units with adjustable fan control can be interpreted as not applying to
condensing furnaces. Also, the time to reach the 40 deg.F differential
after burner shut-off may be shorter than three minutes, resulting in
both a cold draft and a higher rating that fail to achieve a reasonable
level of occupant comfort. (CEC, No. 25, at 1).
In the current test procedure for furnaces, the requirement for
maximum fan delay time after burner shut-off was specified on the basis
of obtaining an overall low cost of combined fossil fuel and auxiliary
electrical energy consumption balanced with the historically accepted
industry practice in furnace operation to provide occupant comfort. The
after burner shut-off is defined as three minutes, or 1.5 minutes for
condensing furnaces, after the burner shuts off, or until the supply
air temperature drops to a value of 40 deg.F above the inlet air
temperature, whichever gives a longer fan-on time. The Department
recognized the heat capacity of a heavier mass heat exchanger in
retaining a greater amount of heat energy. This is evidenced by the
specification in the existing test procedure of either three minutes
(1.5 minutes for condensing furnaces) or 40 deg.F differential in
plenum to return air temperature, whichever gives a longer fan-on time.
The removal of the maximum fan-on time requirement could encourage some
manufacturers to lengthen the fan-on time after burner shut off without
an accompanying improvement in furnace design. The manufacturers could
do this by simply changing the electronics in the controller. Those
furnaces would be able to obtain a slightly higher calculated AFUE by
using a lower flue gas temperature measured at nine minutes after
burner shut-off when the fan runs longer. Those furnaces however, would
actually be consuming greater electrical energy than the savings in
fossil fuel. This would be contrary to the intent of EPCA to reduce the
nation's overall energy consumption.
Based on the reasons given above, and the fact that the proposed
provision does not affect the rating of any existing furnaces, today's
final rule prescribes the maximum blower delay time criterion specified
in the 1993 Proposed Rule. This specification is for a furnace designed
with an unvarying blower time delay during the cool-down test in
today's final rule.
With respect to the comment by the CEC, the Department agrees that
the wording in the 1993 Proposed Rule is misleading. In today's rule,
therefore, the wording of ANSI/ASHRAE Standard 103-1993, section
9.5.1.2.1, which includes the 40 deg.F temperature difference for
condensing furnaces, is adopted instead. CEC also commented that for
certain furnaces the 40 deg.F temperature differential could be reached
in less than three minutes and
[[Page 26144]]
thus creating a possible cold draft. The blower time delay criterion is
prescribed for blowers with adjustable time delay control in the
current furnace test procedure. Changing the criterion would require
the retesting of many existing furnaces. Also, the criterion was agreed
to by consensus of the ASHRAE Standard Project Committee (SPC) 103 and
specified in ANSI/ASHRAE Standard 103-1993. The Department sees no
reason to change that criterion presently.
In the 1993 Proposed Rule, the Department also specified an
exception to the delay time requirement for furnaces that employ a
single motor to drive a power burner and the air circulation blower. In
that case, the power burner and the blower would be stopped together.
The current test procedure includes this exception of simultaneous
start/stop operations during both the heat-up and the cool-down tests.
ANSI/ASHRAE Standard 103-1993 specifically includes this exception in
the heat-up test but it is not specified in the section for the cool-
down test. The Department considered it to be only an inadvertent
omission in ANSI/ASHRAE Standard 103-1993. There was no comment
received on this issue, and the Department is specifying, in today's
final rule, the modification to ANSI/ASHRAE Standard 103-1993. The
Department specifies that if a single motor drives a power burner and
the air circulating blower, the power burner and the blower shall be
stopped together during the cool-down test.
4. Burner Box Inlet Damper and Flue Damper
Both GAMA and Inter-City Products supported the proposal to include
a tracer gas test method for atmospheric furnaces with inlet or flue
dampers. (GAMA, No. 8, at 2; and Inter-City, No. 7, at 4). There were
no other comments on this issue. The Department has included this
provision in today's final rule.
5. Jacket Loss Test for Downflow Furnaces
The proposal in the 1993 Proposed Rule to include a jacket loss
test for downflow furnaces was supported by both GAMA and Inter-City
Products. (GAMA, No. 8, at 2; and Inter-City, No. 7, at 4). These were
the only comments on this issue. The Department is adopting the
proposed jacket loss test procedure for downflow furnaces as specified
in ANSI/ASHRAE Standard 103-1993 referenced in today's final rule.
6. Blower Compartment Heat Loss During Jacket Loss Test
Both GAMA and Inter-City Products supported the proposal in the
1993 Proposed Rule to exclude the surface area of the blower
compartment in the jacket loss test. The CEC believed that the blower
compartment should not be considered as part of the duct system and
that the heat loss through the blower compartment should be measured in
the jacket loss test. It stated that if the blower compartment is
considered as the duct system, then the insulation requirement for duct
systems in building codes will apply to the compartment. The CEC
believed that this is not presently done to the furnace cabinet in the
field and, in addition, manufacturers and others may recommend against
the insulation of the cabinet. (CEC, No. 25, at 2).
The Department believes that for most furnaces, the blower
compartment is in the return air side of the cabinet. The surface
temperature of the blower compartment will be nearly the same as the
air temperature around the compartment, and the heat loss from that
surface to the test room air will be negligible. The added burden of
instrumenting the blower compartment surface with thermocouples is not
justified. The Department is therefore not adopting the CEC's
suggestion of requiring some mechanism for measuring the heat loss from
the blower compartment. The Department is adopting the provision of
excluding the surface area of the blower compartment in the jacket loss
test as specified in the ANSI/ASHRAE Standard 103-1993 referenced in
today's final rule.
7. Revised Piping Arrangement for Hot Water Boilers
Both GAMA and Inter-City Products supported the proposal in the
1993 Proposed Rule for a revised piping arrangement for hot water
boilers. (GAMA, No. 8, at 2; and Inter-City, No. 7, at 4). This was the
only comment on this issue. The Department has adopted this provision
as specified in ANSI/ASHRAE Standard 103-1993, which is referenced in
today's final rule.
8. Maintaining of Draft During Off-Cycle
Both GAMA and Inter-City Products supported the proposal to
maintain draft during off-cycle for only those oil-fueled or power gas
burner furnaces that employ barometric dampers for draft control.
(GAMA, No. 8, at 2; and Inter-City, No. 7, at 4). This was the only
comment on this issue. The Department has adopted this provision as
specified in ANSI/ASHRAE Standard 103-1993, which is referenced in
today's final rule.
9. Tests Requirement for Modulating Units
In the 1993 Proposed Rule, DOE proposed to correct the following
discrepancy between the current DOE test procedure and ANSI/ASHRAE
Standard 103-1988, which DOE proposed to reference. The current DOE
test procedure requires that for step modulating units, the steady-
state efficiency test shall be conducted at both the maximum and the
reduced input rates. The ANSI/ASHRAE Standard 103-1988 required the
above tests at the reduced rate only. The 1993 Proposed Rule made clear
that DOE would continue to require testing at both rates.
Both GAMA and Inter-City Products supported the proposal for
testing modulating furnaces. GAMA put the proposed correction to ANSI/
ASHRAE Standard 103-1988 for testing modulating boilers into the
category of proposals on which it asked for delay in implementation
until revised efficiency standards are adopted. (GAMA, No. 8, at 4; and
Inter-City, No. 7, at 4). Carrier Corp. and Consolidated Industries
both supported GAMA's position. (Carrier, No. 12, at 1; and
Consolidated, No. 21, at 1). The Department does not agree with the
comments that the correction is a revision to the existing DOE test
procedure for modulating boilers. Such a test is already included.
Specifically, the conditions (at rated input or reduced input) under
which heat-up and cool-down tests are to be conducted are already
specified in the current DOE test procedure. (See sections 3.1, 3.2,
3.4, and 4.5 of appendix N to subpart B of part 430.) The proposed
clarification for the optional tracer gas test at rated input or at a
reduced input rate is to make certain that the resulting measured draft
factor DP value(s) would be consistent with the other
measured quantities when they are combined in the calculation procedure
for the off-cycle losses. The Department believes that this
clarification will have either no effect, or negligible effect on an
insignificant number of units.
Such a requirement was not clearly stated in ANSI/ASHRAE Standard
103-1988, but in DOE's view it was implicit in that standard. The
Department proposed this provision in the 1993 Proposed Rule only to
clarify the language in the then-referenced ANSI/ASHRAE Standard 103-
1988. The Department has therefore adopted this provision as specified
in ANSI/ASHRAE Standard 103-1993, which is referenced in today's final
rule.
[[Page 26145]]
10. On-Cycle Time Constant and Off-Cycle Time Constant
Both GAMA and Inter-City Products supported the proposal for the
on-cycle time constant and off-cycle time constant. (GAMA, No. 8, at 2;
and Inter-City, No. 7, at 4). The Department has adopted this provision
as specified in ANSI/ASHRAE Standard 103-1993, which is referenced in
today's final rule.
11. Multiplication Factor for Jacket Loss for Finned Tube Boilers for
Isolated Combustion System (ICS)
In the 1993 Proposed Rule, DOE proposed to use the multiplication
factor of Cj=0.50. Both GAMA and Inter-City Products supported the
proposal for the value of the multiplication factor for jacket loss for
finned tube boilers. (GAMA, No. 8, at 3; and Inter-City, No. 7, at 4).
The Department has adopted this provision as specified in ANSI/ASHRAE
Standard 103-1993, which is referenced in today's final rule.
12. Calculation Procedure for Electro-Mechanical Stack Dampers
GAMA commented that the proposed calculation procedure for
evaluating the effectiveness of a stack damper would reduce the
measured AFUE of both furnaces and boilers. (GAMA, No. 8, at 3). GAMA
believes that the proposed changes would affect the efficiency rating
of existing warm air furnaces.
In the case of warm air furnaces, the Department has considered the
comment and disagrees with the statement that the proposed changes
would affect the efficiency rating of existing warm air furnaces.
Referring to Table 6, System Numbers, and sections 11.2.9.18, 11.2.10.3
and 11.2.10.4 of ANSI/ASHRAE 103-1993, a stack damper's operation has
no effect on a warm air furnace installed as an Isolated Combustion
System (ICS) No. 9 or 10. Because the existing non-weatherized warm air
furnaces are rated as ICS systems, the problems cited by GAMA do not
apply to existing furnaces. Also, because any direct vent system is
defined as system No. 9 or 10, the problems likewise would not apply to
direct vent systems such as those used for most mobile home furnaces.
In the case of boilers, which are installed indoors and rated as
indoor systems, the effect of the revisions on the measured AFUE would
be very small. For most existing boilers the stack damper closes within
30 seconds after the main burner is shut off, and the effect will be on
the order of 0.1 percentage-point change in AFUE. The effect is
therefore negligible for any stack damper that is completely closed
within the 30-second interval. The effect, however, could be large if
the damper closing time delay were to be extended for a long period.
Such an extension would take advantage of the deficiency in the current
procedure, where the damper is assumed to close instantaneously after
the burner shut-off. The Department has therefore, adopted the revision
as proposed in the 1993 Proposed Rule (and as included in ANSI/ASHRAE
Standard 103-1993) in today's final rule.
13. Power Vented Systems Employing Post Purge After Burner Shut-Off
In the 1993 Proposed Rule, the maximum free post purge time was
specified to be five seconds for both gas-and oil-fired furnaces and
boilers. There were seven comments on this proposal. GAMA stated that
the proposed maximum free post purge time would significantly reduce
the measured AFUE of most existing models, and require DOE to amend the
NAECA furnace and boiler efficiency standards for existing models that
marginally meet the current minimum standard of 78 percent AFUE for
furnaces and 80 percent for boilers. (GAMA, No. 8, at 4). Carrier
Corp., Consolidated Industries, and Lennox Industries all supported
GAMA's position. (Carrier, No. 12, at 1; Consolidated, No. 21, at 1;
and Lennox, Transcript, at 77).
Inter-City Products requested that the implementation of this and
other category 2 revisions be postponed to a future rulemaking,
coordinated with implementation of amendments to furnace minimum
efficiency standards. To support its request, Inter-City Products
commented that DOE needs to lower the minimum standard on marginal
units to correspond to changes in test procedure measurements, and
address the problem associated with the utility rebate program. Inter-
City Products further stated that for the manufacturers to modify these
models, such that they attain the 80 percent AFUE value, the redesigned
equipment may operate in the condensing region that can affect
performance, reliability, and life of both the equipment and the
associated vent system. (Inter-City, No. 7, at 3).
Energy Kinetics, Inc. commented that the proposed revision does not
cover systems equipped with a power burner and a draft inducer. Energy
Kinetics stated that the off-cycle flue gas flow rate with only the
inducer on, but not the power burner, is significantly reduced from the
on-cycle flow rate. According to Energy Kinetics, since the proposed
revision in the 1993 Proposed Rule uses the on-cycle flue gas volume
flow rate as a base to compute the flue loss during the post purge
period, the loss will be higher than it should be. Energy Kinetics
suggests that a tracer gas option be allowed for this type of system.
(Energy Kinetics, No. 16, at 6).
The independent commenter, Mr. John Woodworth asserted that, based
on research conducted at Brookhaven National Laboratory, the post-purge
provisions are not accurate for oil-fired furnaces and boilers with
relatively long post purge-periods. He reasons that, to reduce the test
burden on manufacturers, the provisions assume a linearly decreasing
flue gas temperature between the beginning and the end of the post
purge period. Thus, measurements at only two points are required in the
calculation. According to Mr. Woodworth, this assumption of a linearly
varying temperature is valid only for a limited interval, since the
temperature will eventually level off to nearly ambient conditions over
a long purge period. Mr. Woodworth recommends that DOE adopt the
provisions of ANSI/ASHRAE Standard 103-1993 which limit the post purge
period during the test to 180 seconds. (Woodworth, No. 20, at 4).
The Department believes that the use of a post purge in power
vented units during the off-cycle, when longer than necessary, is a
waste of energy because a forced purge increases the loss of the
residue heat in the furnace or boiler through the vent system. A forced
purge is the forced combustion air flow through the heat exchanger.
Given the deficiencies in the existing test procedure described in the
1993 Proposed Rule, DOE is aware that the current procedure could
encourage a manufacturer to use a long post purge period to obtain a
higher calculated AFUE rating while actually wasting more energy
through the vent system. Tests conducted at NIST on a gas furnace with
an induced draft combustion blower showed that increasing the post
purge interval increased the flue loss, but the calculated AFUE based
on current test procedure showed an increase in value. The discrepancy
between the AFUE based on the current calculation procedure, and on the
proposed calculation procedure, becomes progressively greater with an
increasing post purge period. The difference was 0.9 percentage points
with 30 seconds post purge and increased to 4.5 percentage points with
180 seconds post purge. Yet the calculated AFUE based on the current
test procedure showed a gain (from the condition of no post purge) of
about 0.2 percentage points at 30 seconds post purge to nearly 1.0
[[Page 26146]]
percentage point at 180 seconds post purge.
Data gathered indicated that the six major control manufacturers
surveyed all have post purge timing of 30 seconds or less on their post
purge control equipment. The data was gathered by the Lawrence Berkeley
National Laboratory (LBNL) for DOE regarding the current practice of
the furnace industry. The survey showed that if the free post purge
time is extended from five seconds, as proposed in the 1993 Proposed
Rule, to 30 seconds before the post purge calculation method is
required, most of the existing furnace and boiler models that employ
post purge will be treated as if there is no post purge. With post
purge timing of 30 seconds, no retesting or re-rating will be required
and no reduction in AFUE will result for those existing furnaces and
boiler models.
Based on the above reasons, DOE is changing the maximum free post
purge time of five seconds in the 1993 Proposed Rule to 30 seconds.
That is, only units with post purge time longer than 30 seconds shall
be tested by the prescribed post purge test procedure. Further, units
with post purge periods of less than or equal to 30 seconds shall be
tested without the post purge test procedure. The Department agrees
with the commenters that if the maximum free post purge time is limited
to the proposed five seconds, some existing furnace and boiler models
that employ post purge time between five and thirty seconds would have
to be retested. The Department acts today to limit the burden on the
manufacturers of retesting those models and the possibility of lower
AFUE ratings. The Department is prescribing, in today's final rule, the
modified free post purge period of 30 seconds as the criterion for
applying the revised test and calculation procedures for units that
employ post purge after burner shut off.
DOE believes, however, that with this exception, where the maximum
free post purge time is thirty seconds, additional energy is being lost
through the venting system by the combustion blower. The Department
will continue to examine this subject and may consider later
implementation of the original five second criterion, which is based on
the technical judgement of the ASHRAE Standard Project Committee (SPC)
that developed ANSI/ASHRAE Standard 103-1993.
Secondly, on the issue of oil-fired furnaces and boilers that have
purge periods greater than three minutes, the Department acts to limit
the post purge time to 180 seconds during the rating test as suggested
by commenter Mr. John Woodworth. If the designed post purge time is
longer than 180 seconds, the blower control is to be bypassed and the
blower manually turned off during the cool-down test. This provision is
specified in ANSI/ASHRAE Standard 103-1993, which is referenced in
today's final rule.
The comment by Energy Kinetics on the difference in the flue gas
flow rate between the on-cycle (power burner and inducer on) and off-
cycle (only inducer on during post purge) on oil-fired boilers, if the
draft inducer is an integral part of the boiler supplied by the
manufacturer, would require additional study. Therefore, this type of
boiler is not covered by today's final rule. The Department will
continue to solicit additional data on the on-cycle and off-cycle
operations of this type of boilers, and will issue a revision to the
test procedure at a future time.
14. Sealing of Ventilation Openings During Jacket Loss Test
The 1993 Proposed Rule would require conducting the jacket loss
test with the ventilation openings sealed. There were six comments on
this issue. GAMA provided data from tests recently conducted at the ETL
Testing Laboratories of the Inchcape Testing Services (ETL). This data
showed that for four furnace models tested for sealing the ventilation
openings in jacket loss test, the percentage point reductions in AFUE
were 1.0, 0.5, 0.7 and 0.1 for models currently rated at AFUE of 78.7
percent, 80.0 percent, 80.0 percent and 78.0 percent, respectively.
Thus, two models would be below the 78 percent minimum and two models
would be below the 80 percent rebate criteria if tested pursuant to the
proposed revision. (GAMA, No. 8, at 4 and A-1). Carrier Corp.,
Consolidated Industries, and Lennox Industries all supported GAMA's
position (Carrier, No. 12, at 1; Consolidated, No. 21, at 1; and
Lennox, Transcript, at 77). Inter-City Products made several assertions
on this issue. First, it stated that sealing ventilation openings could
potentially reduce AFUE by 0.3-0.5 percent. Second, it stated that an
attempt to determine which louver openings are for ventilation air
egress and which are for intake cooling air would be a time-consuming
and subjective test procedure. Third, the company claimed that a louver
acting as ventilation air intake in one operating mode may be an
exhaust louver in another. Fourth, it asserted that additional test
time in development, agency certification, and independent efficiency
audits (by ETL) would increase manufacturers' costs substantially.
Finally, according to Inter-City, the revised procedure would lower the
baseline efficiencies of equipment currently at 78 percent. (Inter-
City, No.7, at 2). The CEC suggested that air leakage during the jacket
loss test from any part of the furnace cabinet should represent the
performance of the product as installed in the field. Any joints,
holes, or other openings should remain as shipped by the manufacturer
and should not be taped or sealed for the test. (CEC, No. 25, at 2).
Today's final rule does not include the sealing of furnace cabinet
ventilation openings during the jacket loss test, and the sealing
requirement specified in section 8.6.1.1 of the referenced ANSI/ASHRAE
Standard 103-1993 has not been included in today's rule. Upon review,
the Department considers that sealing of the ventilation openings will
result in a more accurate measure of the combined effects of conduction
and radiation heat loss. This is the heat loss from the cabinet surface
to the test room surroundings and the convective cooling of the airflow
into and out of the spaces adjacent to the inside surfaces of the
jacket. The Department, however, has decided not to incorporate this
provision into today's final rule. This is because the Department sees
some merit in the objections offered by commenters with respect to test
time, retesting and re-rating all the currently rated furnace units and
the associated costs, reduction in currently marginal AFUE ratings, and
the difficulty in objectively determining the most effective openings
to seal. DOE will continue to examine this subject and may consider
implementation of the provision at a later date.
15. Insulation Requirement for Units With Draft Diverter
The 1993 Proposed Rule would require insulation for units with a
draft diverter, when testing furnaces with exposed diverters. There
were three comments on this issue. GAMA objected to its immediate
implementation. In addition, GAMA provided data from tests recently
conducted at ETL. This data showed that, for two furnace models with
integral draft diverters tested with insulation added to the draft
diverter, the percentage point reductions in AFUE were 0.3 and 0.4 for
the two models currently rated at AFUE of 78.0 percent. They would be
below the 78 percent minimum standard if tested in accordance with the
proposed revision. (GAMA, No. 8, at 4 and A-2). Carrier Corp. and
Consolidated Industries both supported GAMA's position. (Carrier, No.
12, at 1; Consolidated, No. 21, at 1).
[[Page 26147]]
As described in the 1993 Proposed Rule on this issue, the ETL
stated that it insulates the exposed diverters (in horizontal furnaces)
when testing furnaces with exposed diverters. (April 30, 1991, letter
from ETL to NIST). Therefore, the rated AFUE values for horizontal
furnaces with exposed integral draft diverters in GAMA's Efficiency
Certification Directory were tested with the proposed insulation in
place. This means that the existing furnaces have already been tested
according to the proposed provision and found to meet the minimum
efficiency standard. Thus, no retesting or re-rating is required.
The Department therefore is not accepting GAMA's request that this
provision be omitted from the final rule, and instead has adopted this
provision as specified in ANSI/ASHRAE Standard 103-1993, which is
referenced in today's final rule.
16. Insulation Requirement for Flue Collector Box
In the 1993 Proposed Rule, DOE called for the insulation of the
flue collector box. Numerous comments were received on this issue.
Specifically, Inter-City Products requested that the implementation of
this provision be postponed to a later date. Inter-City Products cited
the reduced AFUE of existing marginal units, that would require DOE to
reduce the minimum standard, and the criterion of the 80 percent AFUE
by the utility rebate program in support of the request. (Inter-City,
No.7, at 1). Inter-City Products suggested that the flue collector box
on equipment with draft inducers is significantly smaller in area than
the sheet metal involved in an integral draft diverter, so losses are
consequently less. Inter-City Products estimated that this provision
would have an impact of lowering the efficiency by 0.3-0.4 percent in
AFUE. Inter-City Products also believed that the requirement of
insulating the collector box during the cool-down and heat-up tests,
but not during the jacket loss test, constitutes ``double dipping.''
This is because any loss in heat from the collector box would be
accounted for twice--first, as a reduced efficiency from a higher flue
gas temperature during the cool-down and heat-up tests (cyclic test)
due to the insulation requirement, and second, as a larger measured
jacket loss because the insulation is not applied during the steady-
state jacket loss test.
GAMA put this issue in its second category of proposed changes in
the 1993 Proposed Rule and objected to its immediate implementation. In
addition, GAMA provided data from tests recently conducted at ETL to
show that for eleven furnace models tested for insulation of the
exposed flue collector box, the percentage point reductions in AFUE
ranged from 0.5 to 2.8 for models currently rated at AFUE of 78.0
percent to 80.2 percent. Seven models will be below the 78 percent
minimum and five models will be below the 80 percent rebate criterion,
if tested in accordance with the proposed revision. (GAMA, No. 8, at 4
and A-2). Carrier Corp., Consolidated Industries, and Lennox Industries
all supported GAMA's position (Carrier, No. 12, at 1; Consolidated, No.
21, at 1; and Lennox, Transcript, at 77).
Energy Kinetics, Inc. commented that in addition to the cool-down
and heat-up tests, the flue collector box should be insulated for the
steady-state portion of the test also. It believed that without the
insulation, the measured steady state efficiency is higher due to a
lower measured flue gas temperature than that measured with the
insulation. (Energy Kinetics, No. 16, at 6).
The commenters are not correct in classifying the proposed
requirement of insulating the flue collector box on induced draft or
forced draft units as a revision of the furnace test procedure. This
requirement is already specified in the current test procedure, and has
been in the DOE test procedure since 1980. Compliance with this
requirement is demonstrated by a waiver request that was denied by DOE.
This request was from the Carrier Corporation in 1980 for an exemption
from the requirement of insulating the ``flue collector and inducer
housing'' on its induced draft gas furnace. 76 FR 22799, April 21,
1981. The current test procedure cited at section 3.0--Test procedure,
of appendix N to subpart B of part 430, 56 FR 12159, March 28, 1984
references section 9 of ANSI/ASHRAE Standard 103-1982 as the pertinent
test procedure. In ANSI/ASHRAE Standard 103-1982, the requirement of
section 9.1.1.6 specifies ``* * * cover the draft diverter and flue
gas collector box (on a power vented unit) with insulation having an R
value no less than 7. * * *'' Therefore, the provision is not a new
requirement and should require no retesting or re-rating of any
existing gas-fired, power vented units. The specification in the 1993
Proposed Rule was to: (1) Combine the requirement with the language in
section 9.1.4 of ANSI/ASHRAE Standard 103-1988 that does not
specifically include the language for a power vented unit in the
insulation requirement, as was done in ANSI/ASHRAE Standard 103-1982,
and (2) include any units that employ a power burner. The requirement
is now specifically included in sections 7.2.2.2, 7.3.2.2, and 9.1.4,
ANSI/ASHRAE Standard 103-1993.
DOE has reviewed the comments by Inter-City Products on ``double
dipping,'' and by Energy Kinetics on the steady state efficiency being
overstated due to an un-insulated flue gas collector box. The jacket
loss and the steady state efficiency are measured without the
insulation on the flue gas collector box because these conditions exist
in practice. The reason for insulating the flue gas collector box
during the transient cool-down and heat-up tests is to obtain a
measured flue gas temperature as close as possible to its true value
when the flue gas first exits from the heat exchanger. This allows a
better calculation of the off-cycle flow through the heat exchanger. In
the original development of the flue loss methodology, an assumption
was made on the flue gas temperature variation during the transient
condition of cool-down and heat-up. This assumption was based on the
value of a flue gas temperature exiting the heat exchanger, not on a
lowered value measured some distance away. This transient gas
temperature variation has never been used in the calculation for jacket
loss and steady state efficiency.
DOE has adopted this provision as specified in ANSI/ASHRAE Standard
103-1993, which is referenced in today's final rule. This action is
taken for the reasons described above, and because this is not a new
requirement for gas-fired units and no comments were received opposing
the requirement for insulation of the flue gas collector box on oil-
fired units.
17. Insulation Requirement for Downflow Furnaces
DOE proposed an insulation provision that specifies that during the
cool-down and heat-up tests, the internal section of the vent pipe is
to be insulated to an R value of not less than 7 ft\2\-h- deg.F/Btu.
GAMA and Inter-City Products both expressed their opposition to the
insulation requirement. They claim that the insulation requirement will
reduce the AFUE value of currently rated units, requiring the possible
lowering of the minimum standard on marginal units and affecting the
utility rebate program. GAMA provided data from tests recently
conducted at ETL to show that for twelve furnace models tested with
insulation of the internal vent pipe on downflow furnaces, the
percentage point reductions in AFUE range from 0.2 to 1.1 for models
currently rated at AFUE of from 78 percent to 80.2 percent. Eight of
the models will be
[[Page 26148]]
below the 78 percent minimum, and three will be below the 80 percent
rebate criterion, if tested pursuant to the proposed revision. (GAMA,
No. 8, at 2,4 and A-1; and Inter-City, No. 7, at 4). Carrier Corp.,
Consolidated Industries, and Lennox Industries all supported GAMA's
position. (Carrier, No. 12, at 1; Consolidated, No. 21, at 1; and
Lennox, Transcript, at 77).
The purpose of the proposal to require insulation of the flue pipe
is to obtain as nearly as possible the true flue gas temperature
required in the calculation of the flue loss. The assumption made in
the calculation procedure is that the flue gas temperature is the
temperature at the exit plane from the heat exchanger. Since this is
sometimes impossible to measure in practice, provisions are made in the
test procedure to measure the flue gas temperature in a more convenient
and accessible location such as in the flue pipe or stack. Insulation
of the sections of the flue gas passage between the heat exchanger exit
plane and the flue gas temperature measuring plane in the stack is not
for the purpose of reducing the heat loss through the jacket but to
obtain a more accurate flue gas temperature.
Today's final rule does not include the insulation of the internal
flue pipe during the cool-down and heat-up tests. Also, the insulation
requirement specified in section 7.2.2.5 of the referenced ANSI/ASHRAE
Standard 103-1993 has not been included in today's final rule. This
action is justified by the fact that for the downflow furnace, there is
no existing specification in the current DOE test procedure that covers
the internal flue pipe. The Department considers the insulation of the
internal flue pipe during the heat-up and cool-down tests as a
desirable procedure in obtaining a more accurate measure of the flue
gas temperatures. Commenters objected to immediate implementation,
however, because of the test time, retesting and re-rating of all the
currently rated downflow furnace units with the associated costs, and
the reduction in AFUE. The Department decided that the objections
offered by commenters warrant a delay in the implementation of this
provision. DOE will continue to examine this subject and may consider
the implementation of the insulation requirement at a later date.
18. Revised Minimum Value for the Draft Factor DP and
DF
DOE proposed that a value of 0.05 for the draft factor
DP be assigned for any units whose DP value, when
measured by the optional tracer gas method, is less than 0.10. This
action was based on the following circumstances. The current test
procedure allows the minimum value for the draft factor DP
and DF to equal 0.0 on units where absolutely no air flows
through the combustion chamber and heat exchanger when the burner is
off (section 9.4.4 of ANSI/ASHRAE Standard 103-1982 as referenced in
section 3.0 of appendix N to subpart B of part 430, 56 FR 12159, March
28, 1984). However, it is very difficult to verify an ``absolutely no
air-flow'' condition by current flow measurement technology.
Only two comments were received. GAMA objected to the immediate
implementation of these changes. (GAMA, No. 8, at 4). Carrier Corp. and
Consolidated Industries both supported GAMA's position. (Carrier, No.
12, at 1; and Consolidated, No. 21, at 1). Energy Kinetics, Inc.
commented that the values are too small to have any significant effect.
(Energy Kinetics, No. 16, at 6).
The Department does not agree with GAMA's position and has adopted
this provision as specified in ANSI/ASHRAE Standard 103-1993, which is
referenced in today's final rule. This action is founded upon the
following observations. The measurement of very low flow rates of flue
gas is very difficult, and replicating the measurement would be a
problem at the low flow rate encountered. The Department considers the
value of 0.05 to be reasonable. The Department believes that only pulse
combustion furnaces meet the requirement of no air flow during the off-
cycle. The effect of this change will be that more units can use a
lower draft factor DF (with a very slight increase in AFUE),
but it will not result in a lower AFUE for the set of units that are
minimally compliant with this provision, and will negate the necessity
of repeatedly conducting the tracer gas test to confirm the accuracy of
a measured value varying below the 0.1 range.
19. Water Pump Energy Consumption
DOE proposed the measurement of the electrical energy consumption
of the water pump for hot water boilers in the 1993 Proposed Rule. GAMA
put this requirement in its second category (GAMA, No. 8, at 4).
Carrier Corp. and Consolidated both supported GAMA's position.
(Carrier, No. 12, at 1; and Consolidated, No. 21, at 1). Hydronics
Institute (HI) stated that not all boilers are supplied with pumps.
Instead of measuring the pump power, HI suggested adopting the
requirement in ANSI/ASHRAE Standard 103-1993. This requirement
specifies the use of the nameplate wattage if the pump is supplied by
the manufacturers and a default value of 0.13 kW if no pump is
supplied. (HI, No. 15, at 3). Energy Kinetics stated that the value of
0.13 kW is too high and that the standard pumps shipped with
residential systems today consume no more than 60 watts (W). (Energy
Kinetics, No. 16, at 7). Mr. John Woodworth, independent commenter,
stated that the requirement would create a hardship and the results
would have an insignificant effect on the annual efficiency descriptor.
He stated that boilers are seldom tested with the ``standard pump'' in
the laboratory. Instead, test rigs in most laboratories include pumps
and mixing valves to test all sizes of boilers. When sold, a model
boiler may be equipped with as many as three different brands of pumps,
or shipped without a pump. Mr. Woodworth recommended that DOE adopt the
requirement of ANSI/ASHRAE Standard 103-1993 instead of the proposed
measurement requirement. (J. Woodworth, No. 20, at 3).
The Department, in today's final rule, adopts the requirement of
ANSI/ASHRAE Standard 103-1993 for pump power consumption. The
requirement states that if a pump is supplied with the boiler (as cited
by Energy Kinetics), then BE (electrical power to water pump) is the
nameplate wattage rating, and if no pump is supplied, then the current
default value of BE is 0.13 kW in calculation of annual electrical
energy consumption. By referencing the revised ANSI/ASHRAE Standard
103-1993, this is included in today's final rule. The Department does
not agree with GAMA's inclusion of this issue in its second category,
since pump power consumption is not involved with the calculation of
AFUE. DOE does agree that the 1993 Proposed Rule, by requiring an
additional measurement of pump power consumption, would impose a burden
that does not significantly improve the calculation of annual
electrical energy consumption. Hence, DOE adopts instead the ANSI/
ASHRAE provision.
20. Energy Factor and Annual Efficiency Descriptors
In the 1993 Proposed Rule, the Department proposed two energy
descriptors, the energy factor and annual efficiency, for both fossil-
fueled furnaces and boilers. The proposed energy factor includes the
auxiliary electrical energy consumption of the appliance, and is
identical to the energy factor term as defined in appendix B of ANSI/
ASHRAE Standard 103-1993, except that DOE proposed a different ``F-
factor.'' Appendix B defined ``energy
[[Page 26149]]
factor'' as the ratio of the annual output of heat energy provided to
the space to the total annual energy input required to operate the
appliance. The annual output of heat energy includes the contribution
from a portion of the auxiliary electrical energy that is recovered as
useful heat. The total annual energy input required includes both the
fossil fuel and the auxiliary electric energy. The F-factor, however,
equal to 3.0 in ANSI/ASHRAE Standard 103-1993, was 3.37 in the DOE
proposal. The modified F-factor then approximated the ratio of the
energy required to generate and transmit the auxiliary electricity
consumed by the appliance to the amount of such electrical energy. The
F-factor was applied to the auxiliary electrical consumption to reflect
the efficiency in the use of all energy used to run the appliance.
The purpose of the Department's proposal to establish the new
efficiency descriptor and the energy factor was to account for the
auxiliary electric energy in the operation of fossil-fueled furnaces
and boilers. The proposed descriptors would combine the consumption of
fossil fuel and auxiliary electricity into a single value that would
reflect the overall energy cost of a fossil-fueled appliance. The
current energy descriptor, AFUE, deals only with the primary type of
energy consumed by an appliance. Therefore, it does not give the
consumer a complete account of the overall energy and cost performance
of the appliance. On the basis of AFUE alone, a consumer would not be
able to compare the overall cost of operation of two or more different
models of fossil-fueled furnaces or boilers of comparable output
capacity with blowers of different motor efficiencies or on/off
controller timings. The proposed energy descriptors were intended to
give the consumer the necessary information for a more informed
decision. Another purpose for the proposed energy descriptors was to
provide an evaluation procedure for different design options for
fossil-fueled furnaces and boilers that involves auxiliary electric
energy consumption. This information would be considered in the
determination of energy efficiency standard levels.
At the public hearing and during the public comment period
following the publication of the 1993 Proposed Rule, twenty-one
commenters offered views on this issue. The comments ranged from
support for an energy descriptor that included both the fossil fuel and
the auxiliary electric energy consumption, to complete disagreement
with that concept. Nearly all commenters however, expressed
reservations on the source-based multiplication factor (the F-factor to
be applied to the auxiliary electrical energy consumption of fossil-
fueled appliances). A summary of the commenters' reasons for objection
include: (1) The use of source energy in determining the energy
efficiency, through the proposed F-factor, is not permitted by EPCA and
NAECA, which specify that efficiency must be determined by energy
consumption at the point of use (site) of the covered products; (2) the
application of the F-factor to the auxiliary electrical energy consumed
by fossil-fueled appliances, but not to all-electric furnaces, is
biased against fossil-fueled appliances; (3) a national average source
to site energy ratio ignores the variation in the value of the F-factor
due to different methods of power generation; (4) the value of the
proposed energy descriptor would be lower than the AFUE, creating
confusion for AFUE based rebate/incentive programs by utility
companies; (5) combination furnace/air-conditioning systems with a
single heating capacity may require different size blowers depending on
cooling load requirements; and (6) fuel switching and marketplace
distortion could result. A detailed summary of comments on the F-factor
and the proposed energy descriptor is found in the Federal Register
notice. 60 FR 4348 ( January 20, 1995).
In 1995 the Department reopened the comment period on the 1993
Proposed Rule, solely to address this issue, and the Department
proposed a revision of its 1993 proposal. In place of the 1993 Proposed
Rule's definition of the F-factor as a source-to-site based energy
ratio, the Department proposed a cost-based electricity-to-fossil fuel
price ratio with a value of 3.36 at the point of use. The proposed
revision was published in the Federal Register on January 20, 1995. 60
FR 4348.
Seventy comments were received concerning this proposed revision to
the F-factor. Many comments were similar to those received in response
to the original 1993 proposal, and disregarded the change to an F-
factor based on cost of energy. Most commenters considered the proposal
as violating the intent and language of EPCA and NAECA, asserting that
these statutes define energy efficiency with reference to energy
consumption at the point of use (site energy). Because comments were
similar or identical to those submitted following the 1993 proposal, a
commenter-by-commenter description of the comments is not presented
here. Virtually all of the commenters urged DOE to either withdraw or
modify the F-factor proposal.
One of the principal issues raised by the commenters is the
authority of DOE to establish an energy efficiency standard for
furnaces on the basis of either energy cost or source energy, as
opposed to site energy consumption in units of energy. Upon further
examination, it is the view of the Department of Energy that EPCA
requires the energy efficiency of a furnace to be based on consumption
of energy at the site of the furnace, and that the statute does not
permit the promulgation of an energy efficiency standard that is
expressed in terms of annual operating costs of the furnace.
EPCA defines the energy conservation standard of a covered
appliance as ``a performance standard which prescribes a minimum level
of energy efficiency or a maximum quantity of energy use.'' EPCA
section 321(6), 42 U.S.C. 6291(6). EPCA defines ``energy efficiency''
as the ratio of a product's useful output of services to its ``energy
use.'' EPCA section 321(5), 42 U.S.C. 6291(5). Thus, ``energy use'' is
a basis for any standard for furnaces and boilers. ``Energy use'' in
turn is defined in section 321(4), 42 U.S.C. 6291(4), as ``the quantity
of energy directly consumed by a consumer product at point of use.''
Therefore, furnace energy conservation standards must be based on
consumption of energy at the site of the appliance. The Department
believes that this conclusion is further supported by terminology used
in section 325(f) of EPCA, 42 U.S.C. 6295(f), which concerns standards
for furnaces. Section 325(f)(1)(B), for example, requires the
promulgation of an ``energy conservation standard'' for small furnaces,
and, as just discussed, such a standard must be based on energy
consumption at the site of the application.
Based on the above analysis, the Department is withdrawing the
proposed energy descriptor and energy factor in today's final rule. The
current procedures of determining AFUE from the energy efficiency
descriptor, and of calculating of the annual energy consumption of
fossil fuel and electrical energy for furnaces/boilers, therefore will
remain unchanged. In the meantime, the Department will continue to
explore and to solicit input from interested parties on various options
for the development of a descriptor that would take into account
separately both a new energy factor for fossil fueled furnaces and the
auxiliary electrical energy consumption of an appliance.
[[Page 26150]]
21. Measurement of Electric Energy Consumption for Interrupted Ignition
Device
The 1993 Proposed Rule required measurement of the energy
consumption by the interrupted ignition device. Both GAMA and Inter-
City Products argued that the electrical energy consumption of the
interrupted ignition device constitutes an extremely small amount of
all electrical consumption of a furnace. To include the measurement of
the energy consumption of the device is burdensome in time and effort.
Carrier Corp. and Consolidated Industries both supported GAMA's
position. (Inter-City, No. 7, at 3; GAMA, No. 8, at 18; Carrier, No.
12, at 1; and Consolidated, No. 21, at 1). HI and independent commenter
Mr. John Woodworth both stated that the energy consumption of these
ignition devices is small and will not affect the energy descriptors.
Additionally, according to HI and Mr. Woodworth, a separate test would
be required since the ignition devices are off during the steady state
test, and they are difficult to measure because the time duration and
power draw are not constant during ignition. Therefore, HI recommended
the deletion of the device in the proposed measurement requirement and
the calculation procedures. (HI, No. 15, at 3; and J. Woodworth, No.
20, at 4).
To assess the merits of these comments, and to determine the amount
of energy consumption of an interrupted ignition device, NIST measured
the power input, on-time duration and energy consumption of an electric
hot surface ignition device on a 90,000 Btu/h input gas-fired furnace.
It was found that the power input varied from 515 W to 470 W during the
40 seconds the device was on. Except for the first few seconds, the
power draw was approximately 470 W. This translated into an energy
consumption of approximately 18 Btu per burner on-cycle, or 63 Btu/h
for the assumed average 3.5 burner on-cycles per hour (3.87 minutes on
and 13.3 minutes off) for a single stage furnace. While this compares
favorably with the average 400 Btu/h energy consumption of a pilot
light, DOE does not agree that the energy consumption of the
interrupted ignition device should be completely ignored. DOE agrees,
however, that the energy consumption is small enough to justify the
deletion of the measurement requirement in the proposed test procedure.
Therefore, DOE is specifying in today's final rule that the on-time of
an interrupted ignition device, as specified in a furnace's nameplate,
should be used as the actual on-time. Further, the nameplate power
input rating, or 0.4 kW if none is specified on the nameplate, should
be used as the average power draw in the electrical energy calculation.
The device on-time will be measured with a stop watch if not specified
on the nameplate. The device on-time will be set to equal zero if the
nameplate or measured value is less than or equal to five seconds.
22. Measurement of Energy Consumption of Combustion Blower During Post
Purge
The test procedure of the proposed rule and ASHRAE 103-93 requires
the measurement of the energy consumption of combustion blowers during
a post purge. Commenters GAMA and Inter-City Products both argued that
the electrical energy consumption of the combustion blower during post
purge constitutes an extremely small amount of all electrical
consumption of a furnace, and that to include the measurement of the
energy consumption of the combustion blower is overly burdensome in
time and effort. Carrier Corp. and Consolidated Industries both
supported GAMA's position. (Inter-City, No. 7, at 3; GAMA, No. 8, at
18; Carrier, No. 12, at 1; and Consolidated, No. 21, at 1). Energy
Kinetics, while not commenting on the power consumption of the draft
inducer during post purge, pointed out that the power burner is off for
some oil-fired units during post purge and thus, only the draft inducer
is on. As a result, the auxiliary electrical energy consumption
measured during steady state may not be equal to the electrical energy
consumption during the post purge period. (Energy Kinetics, No. 16, at
6).
The 1989 ASHRAE Handbook of Fundamentals states that the power
consumption of motors with rated horsepowers of \1/20\ hp and \1/12\
hp, which would be typical for combustion blowers, are approximately
360 Btu/h and 580 Btu/h, respectively. For a post purge period of 30
seconds, the energy consumptions would be 3-5 Btu per off-cycle for the
two sizes of motors, and for a post purge period of 180 seconds, the
motor energy consumptions would be 18-29 Btu per off-cycle. For an
average 3.5 on-cycles per hour of furnace operation, the energy
consumption would be 10 Btu/h to 17 Btu/h for the 30-second post purge
and 60 Btu/h to 100 Btu/h for the 180-second post purge. For boilers
with an average of 1.3 on-cycles per hour, the values would be
approximately \1/3\ the above.
DOE does not agree that the energy consumption should be completely
ignored. Therefore, DOE is specifying in today's final rule that the
nameplate power rating of the combustion blower be used as the power
consumption in the calculation for the electrical energy consumption.
DOE agrees that the energy consumption is small enough to justify the
deletion of the electric power measurement requirement for the
combustion blower. But measurement of the full length of the post purge
period, easily determined with a stop watch, is still required as set
forth in the proposed rule.
23. ANSI/ASHRAE Standard 103-1993
The 1993 Proposed Rule referenced ANSI/ASHRAE Standard 103-1988 and
added additional amendments to cover the changes, revisions and
advances in technology between the years when the Standard was
published (1988) and the Proposed Rule was published (1993). Those
additional amendments included a revised calculation procedure for
units with stack dampers; revised test procedures for atmospheric
burner units with a burner inlet damper or flue damper; revised test
procedures for power burner units employing post purge during the off-
cycle; insulation requirements during heat-up and cool-down tests for
downflow furnaces; a jacket loss test for units with ventilation
openings on their cabinets; and other technical corrections.
Subsequent to the publication of the 1993 Proposed Rule, ASHRAE
published in October 1993 ANSI/ASHRAE Standard 103-1993 which
supersedes ANSI/ASHRAE Standard 103-1988. The revised ANSI/ASHRAE
Standard 103-1993 incorporated most of the revisions and additions to
ANSI/ASHRAE Standard 103-1988 that were included in the 1993 Proposed
Rule, with the following exceptions: (1) The requirement of a minimum
on-time delay for the blower at burner ignition and a maximum off-time
delay after burner shut-off for units with an unvarying blower timing
control; (2) the actual measurement of power input to hot water boiler
pumps; (3) the measurement of ignition energy input to interrupted
ignition devices; and (4) the measurement of combustion blower time
delay during post purge after burner shut-off in power vented units.
With the above exceptions, the revised ANSI/ASHRAE Standard 103-1993
and the 1993 Proposed Rule are nearly identical in content.
Commenters including GAMA stated that ANSI/ASHRAE Standard 103-1993
should be incorporated in the Department's test procedure rather than
ANSI/ASHRAE 103-1988 as proposed in the 1993 Proposed Rule. (GAMA,
Transcript, at 8). HI stated that since
[[Page 26151]]
ANSI/ASHRAE 103-1988 is no longer the current standard and will no
longer be published by ASHRAE, it would be difficult for manufacturers
to obtain additional copies for reference; therefore, the 1993 version
should be referenced. (HI, Transcript, at 74). Mr. John Woodworth, who
was Chairman of the SPC that developed ANSI/ASHRAE 103-1993, Secretary
of the SPC for ANSI/ASHRAE 103-1988 and Vice-Chairman of the SPC for
ANSI/ASHRAE 103-1982, suggested that DOE should reference the ANSI/
ASHRAE 103-1993 rather than ANSI/ASHRAE 103-1988. He asserts that, with
few exceptions, the requirements in ANSI/ASHRAE 103-1993 are the same
as the requirements in the 1993 Proposed Rule. In addition, ANSI/ASHRAE
103-1988 will no longer be available from ASHRAE. (John Woodworth, No.
20, at 2). The CEC stated that it supports the use of ANSI/ASHRAE
Standard 103-1993 with DOE-specified changes. (CEC, No. 25, at 3). It
was suggested by Lennox (Lennox Transcript, at 78) that the test
procedure be published in its entirety.
The Department agrees with the commenters on this issue and is
referencing the ANSI/ASHRAE Standard 103-1993 instead of the 1988
version in today's final rule. DOE decided not to publish the above
standard in its entirety, since it is the practice of the Department to
incorporate by reference any industry consensus standards, and the test
procedures adopted in today's final rule are nearly identical to ANSI/
ASHRAE Standard 103-1993.
24. Other Minor Modifications to ANSI/ASHRAE Standards 103-1988 and
103-1993
In the 1993 Proposed Rule, DOE also proposed to adopt corrections
and clarifications of several typographical errors and inconsistencies
identified by ASHRAE SPC 103 following publication of ASHRAE Standard
103-1988.
No commenter expressed objection to those specific revisions with
the exception of Mr. Woodworth on revision to section 9.7.3 of the
Standard. Therein, Mr. Woodworth stated that, since TF,OFF
is not needed in the calculation of off-period flue gas mass flow rate
if the draft is maintained during cool-down, the TF,OFF
reading is not necessary. The draft is maintained during cool-down for
units with barometric draft regulators. Therefore, the phrase ``if
draft is not maintained during cool-down'' should not be deleted. (J.
Woodworth, No. 20, at 4). DOE agrees with Mr. Woodworth's comment, and
the proposed revision is dropped from today's final rule.
DOE, by referencing ANSI/ASHRAE Standard 103-1993 today, has
included all the other minor revisions and corrections to ANSI/ASHRAE
Standard 103-1988 in today's final rule. With the exception of the item
commented on by Mr. Woodworth above, the revised ANSI/ASHRAE Standard
103-1993 incorporated all the other minor revisions and corrections to
ANSI/ASHRAE Standard 103-1988 described in the 1993 Proposed Rule.
After the publication of ANSI/ASHRAE Standard 103-1993, a few
typographical errors were identified. On October 24, 1996, ASHRAE
issued an Errata Sheet for ASHRAE Standard 103-1993, that listed the
typographical errors to be corrected in ANSI/ASHRAE 103-1993. This
ASHRAE Errata is incorporated by reference in today's final rule.
25. Other Issues
The following is a discussion of comments DOE received on issues
not raised by the proposed test procedure for furnaces and boilers. As
discussed below, however, in the 1993 Proposed Rule DOE had requested
comments on certain of these issues.
(1) Distribution System Efficiency.--First, commenters including
Dr. M. A. Habegger of Boulder, Colorado, remarked that in the field
installation, the air flow rate through the distribution system has a
large effect on the overall system efficiency. Further, the value of
AFUE obtained through the current test procedure is usually much higher
than the overall system efficiency. (M. A. Habegger, No. 22 at 1). The
Department agrees that a reduced air flow rate will reduce the overall
efficiency of the heating system due to a higher flue gas temperature
and duct air leakage.
Dr. Habegger further comments that the circulation air flow rate is
not considered in the current test procedure and that testing the
efficiency of equipment without considering the overall installed
system effect is meaningless. The Department disagrees. The rate of
circulation air flow is addressed in the test procedure by the limits
set on both the minimum external static pressure and the air
temperature rise between the supply and return air. This assures that
the circulation air blower will deliver the appropriate amount of air
flow at the required design conditions.
As the Department specifically pointed out in the preamble to the
1984 Final Rule for furnaces, boilers, and vented and unvented home
heaters, the test procedures cannot predict the energy performance of a
furnace in every installation. 49 FR 12153 (March 28, 1984). Rather,
their use is for comparison purposes and thus installation variables
are only representatively accounted for. That preamble continues to
state the Department's position on this issue.
(2) Input/Output Method.--Two commenters, Energy Kinetics and the
CEC, responded to the Department's request to comment on the
appropriateness of a test procedure for furnaces and boilers based on
an input/output method. Both suggested the development or adoption of
the input/output method as a more accurate method for rating furnaces
and boilers in place of the present flue loss method. (Energy Kinetics,
No. 16, at 7; and CEC, No. 25, at 3). GAMA, in response to questions
during the public hearing, stated that ETL researchers working on an
input/output method for GAMA experienced a great deal of difficulty in
repeating the test results and in correlating the resulting efficiency
rating with the current method. GAMA felt that more time is needed for
work in the input/output method. (GAMA, Transcript, at 35).
An analysis by Dr. D. R. Tree of Purdue University with data
supplied by NIST on the errors associated with the input/output method
showed that for warm air furnaces, the uncertainties in duct air flow
measurement and non-uniform temperature distribution in the duct,
during steady state and cyclic conditions, would result in an error
estimate of 12 percent for the AFUE value. This made the
input/output method unacceptable as a test procedure for warm air
furnaces.4 The problem of flow and temperature measurements
for hot water boilers would not be as severe. A detailed method,
however, on the transient performance of hot water boilers, both during
the on-cycle (energy delivered) and the off-cycle (heat loss) needs to
be developed and a consensus on the procedure agreed upon. The problems
of testing according to two different test procedures, one for warm air
furnaces and one for hydronic heating systems, also require further
discussion. The Department is, therefore, reserving action on the
possible adoption of an input/output method for hydronic heating
systems to a future rulemaking.
---------------------------------------------------------------------------
\4\David R. Tree, ``Error Analysis of Testing for Annual Fuel
Utilization Efficiency of Residential Central Furnace Boilers,
Report Number 4, Executive Summary,'' Ray W. Herrick Laboratories,
Purdue University.
---------------------------------------------------------------------------
(3) Test Procedure for Combined Space/Water Heating Appliances.--
Only Energy Kinetics raised this issue, and questioned the
appropriateness of the current ASHRAE Standard 124-
[[Page 26152]]
1991 that covers the testing and rating of combination appliances.
(Energy Kinetics, No. 16, at 8).
The Department is preparing to propose a test procedure for
combined space/water heating appliances in the future. DOE welcomes any
comments and input from industry and interested individuals and
organizations.
(4) Off-Cycle Draft Setting.--Only Energy Kinetics commented that
the operation and off-cycle draft conditions at the flue connection to
a unit affect the ratings of the unit, and suggested that the draft
value should not be left to be at the manufacturer's recommendation.
Energy Kinetics suggested a standard draft level of 0.05'' water column
to be maintained at both the on-cycle and off-cycle periods during the
test. (Energy Kinetics, No. 16, at 5).
DOE believes that this specification is not necessary as the draft
produced during the operation of the unit cannot be arbitrarily set by
the manufacturer if proper operation, such as smoke number,
CO2 concentration, and flame stability, of the unit is to be
maintained. DOE reasons that if the manufacturers do not require or
recommend the maintenance of a specific draft level during the off-
cycle for the normal operation of their unit, it should not be required
during the off-period test.
(5) Supply and Return Water Temperature Settings for Hot Water
Boilers.--Energy Kinetics stated that the hot water boiler temperature
settings of 120 deg.F return water temperature and 140 deg.F supply
water temperature during the tests, as prescribed in the current test
procedure, are too low. They are not the normal temperatures of
160 deg.F and 180 deg.F encountered in a home installation. (Energy
Kinetics, No. 16, at 4).
The Department prescribed the test conditions for hot water boilers
(boiler return water of at least 120 deg.F and a 20 deg.F temperature
rise) during the 1983 proposed rulemaking (48 FR 28014, June 17, 1983)
before the publication of the final rule for the current furnace test
procedure (49 FR 12148, March 24, 1984). In so doing, the Department
stated its belief that all non-condensing hot water boilers, including
finned tube boilers and low thermal mass boilers, generally operated at
these conditions, and the specifications would eliminate the need for
future test procedure waivers for specific types of hot water boilers
from a uniform test condition. At that time the boiler industry had
also indicated its desire to have these test conditions included. The
Department sees no fundamental change in the application of hot water
boilers to warrant revision to the current test procedure. In addition,
changing the test conditions to those suggested by Energy Kinetics
would result in a reduction of the AFUE for existing hot water boilers
as the flue loss would be slightly higher due to a higher flue gas
temperature. This would require the retesting and re-rating of most
existing hot water boilers.
For the reasons discussed above, today's final rule does not
include any changes to the test conditions with respect to the boiler
water return temperature and temperature rise for hot water boilers as
specified in the current test procedure.
(6) Energy Lost at Appliance Location (Boilers in Unheated
Space).--Energy Kinetics disagreed with the requirement that boilers be
tested as indoor installation. It claimed that most boilers are
installed in un-conditioned space. (Energy Kinetics, No. 16, at 4).
Since the minimum standard for boilers is based on a statutory
definition of AFUE which explicitly assumes that non-weatherized
boilers are located indoors, DOE will not consider any change in the
installation location for boilers at the present time.
(7) Setting Throughput Air Temperature Rise for Furnaces.--In the
current DOE test procedure and ANSI/ASHRAE Standard 103-1988, the
adjustment to the air throughput for warm air furnaces at steady state
operation is specified under the following conditions: a temperature
rise, across the heat exchanger, shall be the higher of (1) 15 deg.F
below the maximum temperature rise, or (2) 15 deg.F above the minimum
temperature rise, as specified by the manufacturer.
In the 1993 Proposed Rule and in the 1993 revision of ANSI/ASHRAE
Standard 103 (as 103-1993), a provision was added to the test setting
of the air temperature rise. The provision requires that, for furnaces
whose design does not permit a temperature rise range of 30 deg.F, the
furnace shall be tested at the midpoint of the rise range specified by
the manufacturer if the rise is less than 30 deg.F. Commenters GAMA and
Inter-City mentioned this provision for condensing furnaces whose
temperature rise range may be less than 30 deg.F, and listed this
provision in GAMA's first category of revisions for immediate
implementation. (GAMA, No. 8 at 3; Inter-City, No. 7 at 4).
DOE has adopted this provision as specified in ANSI/ASHRAE Standard
103-1993 referenced in today's final rule.
B. Vented Home Heating Equipment
The Department originally published the test procedure for vented
home heating equipment on May 2, 1978. 43 FR 20182. The Department
amended this test procedure on March 28, 1984, to include a simplified
vented heater test procedure for heaters with modulating controls,
manually controlled vented heaters, vented heaters equipped with
thermal stack dampers, and floor furnaces. 49 FR 12169.
In the 1993 Proposed Rule, DOE proposed the following amendments to
the vented home heating equipment test procedure: (1) To establish an
annual efficiency descriptor to account for the auxiliary electrical
energy consumed by the fan or blowers in addition to the fossil fuel
consumed; (2) to revise the calculation procedure for AFUE for manually
controlled heaters; and (3) to revise the calculation procedure for
weighted average steady-state efficiency for manually controlled
heaters with various input rates.
The following discussion addresses the comments received on the
proposed rule.
1. Annual Efficiency Descriptor
The Department proposed in the 1993 Proposed Rule to adopt the
energy factor as defined in appendix B of ANSI/ASHRAE Standard 103-1993
as the new energy descriptor for vented home heating equipment, and
renamed it the annual efficiency descriptor.
The Department's current test procedure for vented home heating
equipment prescribes the calculation of AFUE based on the energy
consumption of fossil fuel only. Since auxiliary electrical energy can
be consumed by these appliances such as for the operation of a blower,
DOE considered that a more appropriate energy descriptor was needed to
account for both fossil fuel and auxiliary electrical energy
consumption of the appliances. This energy descriptor would also be
used to address the electrical energy used by some of the design
options considered for energy standard level evaluation.
Seventeen commenters, directly or in support of another commenter,
have commented on this issue. The comments from each individual or
organization were discussed in the Federal Register notice of January
20, 1995. 60 FR 4348. This was described previously in the section for
the proposed energy factor and annual efficiency descriptors for
central furnaces and boilers. (See II.A. 20 above, ``Annual Efficiency
Descriptor and Energy Factor.'')
As concluded in the discussion above, DOE has decided to withdraw
the proposed energy descriptor from today's final rule. Since the
commenters
[[Page 26153]]
combined their comments on this proposed energy descriptor with those
for the central furnaces/boilers, readers are referred to that section
for a discussion of this issue. Therefore, the current procedures of
determining AFUE as the energy efficiency descriptor will remain
unchanged. However, the proposed procedure for the calculation of the
annual energy consumption of fossil fuel and electrical energy for the
vented home heating equipment is included in today's final rule. This
added procedure does not involve any additional testing beyond that
required by the current test procedure. The added calculation procedure
is intended to allow for the adequate and fair cost ranking of the
different design options that may be considered in future evaluations
of possible revisions of energy standard levels.
2. Pilot Light Energy Consumption for Manually Controlled Heaters
In the 1993 Proposed Rule, for manually controlled heaters, under
certain conditions, the measurement of pilot light energy is not
needed. Two comments on this issue were received. GAMA supported the
provision of not requiring the measurement of the pilot energy
consumption for manually controlled heaters equipped with a piezo
igniter. (GAMA, No. 8, at 20). The CEC stated that the language in the
provision should be more explicit in defining what is meant by the
phrase ``when the heater is not in use and instruction to do so is
given,'' in section 3.5.2 of appendix O to subpart B of part 430. The
CEC further stated that the manufacturer should only be allowed to
ignore the pilot energy use if the pilot extinguishes whenever the
burner is off. (CEC, No. 25, at 3).
The Department agrees with the suggestion of the CEC to clarify
when the proposed provision is applicable. This provision applies to a
heater that provides manually controlled settings for the control knob
in the operation of the appliance, and a clearly marked knob setting
such as the ``OFF'' knob setting shuts off the appliance completely
including the pilot light. DOE is today revising the section in
question to read as follows:
``3.5.2 For manually controlled heaters where the pilot light is
designed to be turned off by the user when the heater is not in use,
that is, turning the control to the OFF position will shut off the gas
supply to the burner(s) and to the pilot light, the measurement of
QP is not needed. This provision applies only if an
instruction to turn off the unit is provided on the heater near the gas
control valve (e.g., by label) by the manufacturer.''
3. Weighted Average Steady-State Efficiency
In the 1993 Proposed Rule, DOE proposed that for manually
controlled vented home heaters with multiple input rates whose design
is such that the specified minimum firing rate cannot be set at
505 percent of the unit's maximum firing rate, the test
will be conducted at the unit's minimum fuel input rate, provided that
the minimum input shall be no higher than \2/3\ of the maximum fuel
input rate of the heater.
GAMA supported this provision. (GAMA, No. 8, at 20). DOE is
adopting the provision in today's final rule.
C. Pool Heaters
The Department published the pool heater test procedure on February
7, 1989, referencing ANSI Standard Z21.56-1986 for gas-fired pool
heaters. 54 FR 6076. In the 1993 Proposed Rule, DOE proposed to amend
the pool heater test procedure, first, to include an annual efficiency
descriptor that accounts for the fossil fuel and the auxiliary
electrical energy consumed by any fan or pump and, second, to replace
the reference to ANSI Standard Z21.56-1986 with references to the then
updated version of ANSI Standard Z21.56.
Standard Z21.56 was updated again in 1994. But no substantive
changes were made in the portions of that Standard which DOE had
proposed, in the 1993 Proposed Rule, to incorporate into its pool
heater test procedure. DOE is therefore referencing ANSI Standard
Z21.56-1994 in the pool heater test procedure it adopts today.
All of the comments received on the proposed amendment to this test
procedure concerned the proposed annual efficiency descriptor. The
following discussion addresses those comments.
1. Annual Efficiency Descriptor
The Department proposed in the 1993 Proposed Rule a new energy
descriptor, the Annual Efficiency (AE), for pool heaters. The proposed
AE descriptor, was defined as the ratio of the annual output of energy
delivered to the heated pool water by fossil fuel to the total annual
energy input to the heater including auxiliary electrical energy. The
latter term, auxiliary electrical energy, was multiplied by a factor F
which represents the ratio of the heat energy required to generate and
transmit the electricity to the electrical energy delivered at the pool
heater. This was for the purpose of reflecting the efficiency of total
energy used to run the appliance.
The Department's current test procedure for pool heaters prescribes
the calculation of the thermal efficiency under steady state condition
only. The thermal efficiency is defined as the ratio of the useful
output of heated water to the sum of the input of fossil fuel energy
and auxiliary electric energy during the steady state test period. DOE
considered that a more appropriate energy descriptor was needed in
order to account for the energy consumption during the burner-off
periods of a pool heating season. DOE based this view on the fact that
a significant quantity of energy can be consumed by a continuous pilot
light and the auxiliary electrical energy consumption during the
burner-off periods of the pool heating season. The proposed energy
descriptor could also be used to address the energy savings by some of
the design options that might be considered in future evaluation of
possible revisions of energy standard levels. For example, to consider
electronic ignition, the evaluation would have to account for the
savings in gas consumption resulting from elimination of a continuous
burning pilot.
Seventeen commenters, directly or in support of another commenter,
have commented on this issue. The comments from each individual or
organization concerning the proposed multiplication factor F applied to
the auxiliary electric energy consumption are discussed in the Federal
Register notice of January 20, 1995 (60 FR 4348). This was described
previously in subsection 20 of section II.A of this notice, which
discusses the proposed energy factor and annual efficiency descriptors
for central furnaces and boilers. Readers are referred to that section
for the discussion of the F-factor issue.
GAMA also commented on the proposed annual efficiency descriptor
concerning pool heaters. GAMA stated that the use of a recirculating
pump should be factored into the AE descriptor only if the pump is used
during the thermal efficiency test under section 2.8.1 of ANSI Z21.56-
1990 standard. Further, GAMA claims, the pump or the pump/filter system
used in any given installation in the field that is not supplied by the
manufacturer should not be considered as part of the heater's auxiliary
components. GAMA commented that DOE should focus on addressing a pool
heater's primary electrical energy consumption rather than auxiliary
losses.
[[Page 26154]]
The Department believes that the above concerns expressed by GAMA
are unfounded. As shown in section 4 of appendix P of the 1993 Proposed
Rule, the determination of the auxiliary electrical energy consumption
of the pool heater is as specified in ANSI Z21.56-1990 standard, and
was not modified in the 1993 Proposed Rule. As proposed in section 4.4
of appendix P, the calculation of the annual auxiliary electrical
energy consumption is based on heater on-time only.
GAMA first stated that, since DOE defined the average number of
burner operating hours as 104 hours independent of pool and heater
size, then ``100,000 Btu/hr and 400,000 Btu/hr pool heaters can have
the same AE value, and would give the impression that a 400,000 Btu/hr
pool heater is an effective choice for heating a 500 gallon hot tub.''
GAMA then stated that during pool ``off-season'' hours, the continuous
pilot is usually shut off.
DOE disagrees with the first statement. If the output capacity of
the pool heater is properly selected by the contractor or installer
based on the size or load requirement of a particular pool, then the
burner operating time would be neither excessively long nor unduly
short. Moreover, although the selection of a particular pool heater
among models of similar capacity for a specific pool size may be based
on its energy efficiency, the selection of a correct capacity heater is
based on the pool size or load requirement. As to GAMA's statement
about the pilot light being off during the ``off season,'' the 1993
proposal already assumed that the continuous pilot light, if used, will
be off during non-heating season hours. (See section 4.2 of appendix P
to subpart B of part 430, on the definition of the average number of
seasonal pool operating hours (POH).)
In its statement, GAMA also suggested that, instead of the AE
descriptor, DOE should develop a methodology to calculate total annual
energy consumption, based on thermal efficiency, electrical energy
consumption, and continuous pilot light consumption. Thus, consumers
could use this information to estimate annual energy consumption and
operating costs for a specific pool size and season of operation.
DOE agrees with this suggestion. The calculation procedure in
today's final rule includes the calculation of the average annual
fossil fuel and auxiliary electric energy consumption.
The Department has decided to withdraw the proposed energy
descriptor with the proposed F-factor multiplier from today's final
rule, for the reasons discussed in subsection 20 of section II.A of
this notice. The current procedure for determining the energy
efficiency descriptor for pool heaters, the steady state thermal
efficiency, shall remain unchanged. A procedure, however, for the
calculation of the pool heater seasonal efficiency and the annual
energy consumption of fossil fuel and auxiliary electricity for the
pool heater is included in today's final rule. The pool heater seasonal
efficiency is defined as the ratio (in percent) of the useful output of
the heater in terms of heated pool water during the pool heating season
to the sum of the total energy input when the burner is on and the
energy consumption of the pilot light when the burner is off during the
pool heating season. The total burner-on hours and the length of the
pool heating season are assumed to be 104 hours and 4464 hours per
year, respectively. The heater is assumed to be in steady state
operation whenever the burner is on. The pilot light is assumed to be
off during the non-heating season hours (4296 hours) and on during the
pool heating season hours (4464 hours). The auxiliary electrical energy
consumption is assumed to be negligible when the burner is off. For
heaters which do not employ a continuous pilot light during the pool
heating season, the seasonal efficiency will be the same as the steady
state thermal efficiency. This procedure will account for the energy
consumption of those pool heaters that employ a continuous pilot light
during the pool heating season. As stated previously, the procedure
also provides a calculation procedure for the average annual fossil
fuel and auxiliary electric energy consumption. These calculations are
simply arithmetic exercises with no additional testing required. Since
these calculations could be used to address the energy savings by some
design options that might be considered in future evaluations of energy
standard levels, DOE believes it is justified to include these
additional calculations.
III. Procedural Requirements
A. Review Under the National Environmental Policy Act of 1969
The Department has concluded that this final rule falls into a
class of actions (categorical exclusion A5) that are categorically
excluded from the National Environmental Policy Act of 1969 (NEPA)
review because they would not individually or cumulatively have a
significant impact on the human environment, as determined by DOE's
regulations (10 CFR part 1021, appendix A to subpart D) implementing
the NEPA (42 U.S.C. 4321, 4331-35, 4341-47). Therefore this final rule
does not require an environmental impact statement or an environmental
assessment pursuant to NEPA.
B. Review Under Executive Order 12866, ``Regulatory Planning and
Review''
Today's regulatory action has been determined not to be a
``significant regulatory action'' under Executive Order 12866,
``Regulatory Planning and Review,'' 58 FR 51735, October 4, 1993.
Accordingly, today's action was not subject to review under the
Executive Order by the Office of Information and Regulatory Affairs.
C. Review Under the Regulatory Flexibility Act
The Regulatory Flexibility Act, 5 U.S.C. 603, requires the
preparation of an initial regulatory flexibility analysis for every
rule which 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.
A regulatory flexibility analysis examines the impact of the rule on
small entities and considers alternate ways of reducing negative
impacts.
The Department believes the final rule will not have a significant
impact on either small or large manufacturers of furnaces and boilers,
vented home heating equipment, and pool heaters under the provisions of
the Regulatory Flexibility Act. The final rule amends DOE's test
procedures, primarily to incorporate (1) test procedures already in use
by manufacturers pursuant to waivers that DOE previously granted to
those manufacturers, and (2) revisions to standard industry testing
methods, contained in American Society of Heating, Air-Conditioning and
Refrigerating Engineers (ASHRAE) Standard 103-1993, ``Methods of
Testing for Annual Fuel Utilization Efficiency of Residential Central
Furnaces and Boilers,'' and American National Standards Institute
Standard Z21.56-1994, ``Gas-Fired Pool Heaters.'' Examples of
amendments are:
The 90-second delay from burner ignition to activation of
the warm air circulation fan designed with an unvarying time delay in a
central furnace has been shortened to accommodate current manufacturers
designs.
There is no requirement to calculate the energy
consumption of a gas pilot light on manually controlled vented home
heaters provided that there is instruction for the user to turn the
pilot light off and restart it.
[[Page 26155]]
The test procedure for modulated, vented home heating
equipment allows testing at 100 percent and sixty six percent rated
input power, instead of 100 percent and fifty percent power, to
accommodate new designs.
Such requirements presented in the final rule incorporate
improvements in the current testing technology for furnaces and
boilers, vented home heating equipment, and pool heaters utilized by
industry. But they would not have a significant economic impact, since
they are methods already in use by manufacturers, and will not cause
manufacturers to purchase equipment, consume testing time, nor employ
technical staff beyond what is required by existing DOE test
procedures.
In addition, in some respects the test procedures in the final rule
are less burdensome than the current procedures. For example:
The formula to calculate the time delay and energy loss of
a stack damper traversing from fully open to fully closed has been
adjusted for greater accuracy. The revised formula has been
incorporated into the existing computer program for the calculation of
the AFUE and will require no additional hand calculations.
Therefore, DOE certifies that the final rule, if promulgated, would
not have a ``significant economic impact on a substantial number of
small entities'' and that the preparation of a regulatory flexibility
analysis is not warranted.
D. Review Under Executive Order 12612, ``Federalism'
Executive Order 12612 (52 FR 41685, October 30, 1987) requires that
regulations or rules be reviewed for any substantial direct effects on
States, on the relationship between the Federal Government and the
States, or on the distribution of power and responsibilities among
various levels of government. If there are sufficient substantial
direct effects, then Executive Order 12612 requires preparation of a
Federalism assessment to be used in all decisions involved in
promulgating and implementing a regulation or a rule.
The final rule published today would not alter the distribution of
authority and responsibility to regulate in this area. The final rule
would only revise a currently applicable DOE test procedure to improve
existing testing methods, and to add provisions that DOE might use in
future standard setting. Accordingly, DOE has determined that
preparation of a federation assessment is unnecessary.
E. Review Under Section 32 of the Federal Energy Administration Act of
1974
The test procedures in this final rule incorporate commercial
standards to measure the efficiency and capacity of furnaces and/
boilers, vented home heating equipment, and pool heaters. The
commercial standards are ANSI/ASHRAE Standard 103-1993, ``Method of
Testing for Annual Fuel utilization Efficiency of Residential Central
Furnaces and Boilers,'' and ANSI Standard Z21.56-1994, ``Gas Fired Pool
Heaters.''
Pursuant to section 301 of the Department of Energy Organization
Act (Pub. L. 95-91), DOE is required to comply with section 32 of the
Federal Energy Administration Act of 1974, as amended by section 9 of
the Federal Energy Administration Authorization Act of 1977 (FEAA) Pub.
L. 95-70, which imposes certain requirements where a proposed rule
contains commercial standards or authorizes or requires the use of such
standards. The findings required of DOE by section 32 serve to alert
the public and DOE regarding the use and background of commercial
standards in a proposal and through the rulemaking process. They allow
interested persons to make known their views regarding the
appropriateness of the use of any particular commercial standard in a
proposed rulemaking.
The Department has evaluated ANSI/ASHRAE Standard 103-1993 and ANSI
Standard Z21.56-1994 with regard to compliance with section 32(b) of
the FEAA. The Department is unable to conclude whether these standards
fully complied with the requirements of section 32(b), i.e., that they
are developed in a manner which fully provided for public
participation, comment, and review.
In addition, section 32(c) of the FEAA precludes the Department
from incorporating any commercial standard into a rule unless it has
consulted with the Attorney General and the Chairman of the Federal
Trade Commission (FTC) as to the impact of such standard on
competition, and neither individual recommends against its
incorporation. Pursuant to section 32(c), the Department advised these
individuals of its intention to incorporate Standards 103-1993 and
Z21.56-1991 into its final test procedure rules for furnaces/boilers
and pool heaters, respectively. Neither recommended against such
incorporation.
The Department notes that it is incorporating into today's rule the
method for testing pool heaters that is set forth in ANSI Standard
Z21.56-1994. Standard Z21.56-1994 was not specifically identified in
the aforementioned communications with the FTC and Department of
Justice. It is, however, a revised and updated version of Standard
Z21.56-1991, which was mentioned in those communications, and the
provisions DOE is incorporating from Z21.56-1994 are identical in
substance to the corresponding provisions in Z21.56-1991.5
---------------------------------------------------------------------------
\5\The Department has informally advised the Department of
Justice and the Federal Trade Commission of its intention to
incorporate the updated version of Standard Z21.56 into the final
rule.
---------------------------------------------------------------------------
F. Review Under Executive Order 12630, ``Governmental Actions and
Interference With Constitutionally Protected Property Rights''
It has been determined pursuant to Executive Order 12630 (52 FR
8859, March 18, 1988) that this final rule would not result in any
takings which might require compensation under the Fifth Amendment to
the United States Constitution.
The Department believes that test procedures implementing a long-
established statutory mandate in a manner calculated to minimize
adverse economic impacts does not constitute a ``taking'' of private
property. Thus, testing under the appliance standards program does not
invoke the provisions of E.O. 12630.
G. Review Under the Paperwork Reduction Act of 1980
No new information or record keeping requirements are imposed by
this rulemaking. Accordingly, no OMB clearance is required under the
Paperwork Reduction Act (44 U.S.C. 3501 et seq.).
H. Review Under Executive Order 12988, ``Civil Justice Reform''
With respect to the review of existing regulations and the
promulgation of new regulations, section 3(a) of Executive Order 12988,
``Civil Justice Reform,'' 61 FR 4729 (February 7, 1996), imposes on
Executive agencies the general duty to adhere to the following
requirements: (1) Eliminate drafting errors and ambiguity; (2) write
regulations to minimize litigation; and (3) provide a clear legal
standard for affected conduct rather than a general standard and
promote simplification and burden reduction. With regard to the review
required by section 3(a), section 3(b) of Executive Order 12988
specifically requires that Executive agencies make every reasonable
effort to ensure that the regulation: (1) Clearly
[[Page 26156]]
specifies the preemptive effect , if any; (2) clearly specifies any
effect on existing Federal law or regulation; (3) provides a clear
legal standard for affected conduct while promoting simplification and
burden reduction; (4) specifies the retroactive effect, if any; (5)
adequately defines key terms; and (6) addresses other important issues
affecting clarity and general draftsmanship under any guidelines issued
by the Attorney General. Section 3(c) of Executive Order 12988 requires
Executive agencies to review regulations in light of applicable
standards in section 3(a) and section 3(b) to determine whether they
are met or it is unreasonable to meet one or more of them. DOE has
completed the required review and determined that, to the extent
permitted by law, the final regulations meet the relevant standards of
Executive Order 12988.
I. Review Under Unfunded Mandates Reform Act of 1995
If any proposed or final rule includes a Federal mandate that may
result in expenditure by state, local, and tribal governments, in the
aggregate, or by the private sector, of $100 million or more in any one
year, the Unfunded Mandates Reform Act of 1995, signed into law on
March 22, 1995, requires an agency (prior to promulgation) to prepare a
budgetary impact statement and select the least costly, most cost
effective and least burdensome alternative that achieve the objectives
of the rule and is consistent with statutory requirements.
DOE has determined that the action promulgated today does not
include such a Federal mandate. Therefore, the requirements of the
Unfunded Mandates Act do not apply to this action.
J. Review Under Small Business Regulatory Enforcement Fairness Act of
1996
As required by 5 U.S.C. 801, DOE will report to Congress
promulgation of the rule prior to its effective date. 5 U.S.C. 801. The
report will state that it has been determined that the rule is not a
``major rule'' as defined by 5 U.S.C. 804(3).
List of Subjects in 10 CFR Part 430
Administrative practice and procedure, Energy conservation,
Household appliances, Incorporation by reference.
Issued in Washington, DC, on February 28, 1997.
Christine A. Ervin,
Assistant Secretary, Energy Efficiency and Renewable Energy.
For the reasons set forth in the preamble, part 430 of chapter II
of Title 10, Code of Federal Regulations, is amended as set forth
below.
PART 430--ENERGY CONSERVATION PROGRAM FOR CONSUMER PRODUCTS
1. The authority citation for part 430 continues to read as
follows:
Authority: 42 U.S.C. 6291-6309
2. Section 430.2 is amended by adding a definition for the term
``Mobile home furnace'' in alphabetical order, to read as follows:
Sec. 430.2 Definitions.
* * * * *
Mobile home furnace means a direct vent furnace that is designed
for use only in mobile homes.
* * * * *
3. Section 430.22 is amended by adding paragraph (a)(3)(iv) and
adding item numbers 13 and 14 to paragraph (a)(4) to read as follows:
Sec. 430.22 Reference sources.
(a) * * *
(3) * * *
(iv) American Society of Heating, Refrigerating and Air-
Conditioning Engineers, Inc., Publication Sales, 1791 Tullie Circle,
NE, Atlanta, GA 30329, (1-800-5-ASHRAE).
(4) * * *
13. American National Standards Institute/American Society of
Heating, Refrigerating, and Air-Conditioning Engineers Standard 103-
1993, ``Methods of Testing for Annual Fuel Utilization Efficiency of
Residential Central Furnaces and Boilers,'' (with Errata of October
24, 1996) except for sections 3.0, 7.2.2.5, 8.6.1.1, 9.1.2.2,
9.5.1.1, 9.5.1.2.1, 9.5.1.2.2, 9.5.2.1, 9.7.1, 10.0, 11.2.12,
11.3.12, 11.4.12, 11.5.12 and appendices B and C.
14. American National Standards Institute Standard Z21.56-1994,
``Gas-Fired Pool Heaters,'' section 2.9.
* * * * *
4. Section 430.23 is amended as follows:
A. In paragraph (n)(1)(i), the words ``section 4.8 or 4.10'' are
revised to read ``section 10.2.2 or 10.3'' and in paragraph (n)(1)(ii),
the words ``section 4.9'' are revised to read ``section 10.2.3'' and,
in the parenthetical phase, the words ``section 4'' are revised to read
``section 10.''
B. In paragraph (n)(2), the words ``section 4.6'' are revised to
read ``section 10.1'' and the words ``section 4.1 of appendix N of this
subpart'' are revised to read ``section 11.1 of American National
Standards Institute/American Society of Heating, Refrigerating, and
Air-Conditioning Engineers (ANSI/ASHRAE) Standard 103-1993.''
C. In paragraph (n)(3)(i), the words ``section 4.11 or 4.13'' are
revised to read ``section 10.5.1 or 10.5.3'' and in paragraph
(n)(3)(ii), the words ``section 4.12'' are revised to read ``section
10.5.2.''
D. In paragraph (n)(4), the words ``section 4.14'' are revised to
read ``section 10.4.''
E. Revise paragraphs (o)(2), and (p)(1) to read as follows:
Sec. 430.23 Test procedures for measures of energy consumption.
* * * * *
(o) Vented home heating equipment. * * *
(2) The estimated annual operating cost for vented home heating
equipment is the sum of:
(i) The product of the average annual fuel energy consumption, in
Btu's per year for natural gas, propane, or oil fueled vented home
heating equipment, determined according to section 4.6.2 of appendix O
of this subpart, and the representative average unit cost in dollars
per Btu for natural gas, propane, or oil, as appropriate, as provided
pursuant to section 323(b)(2) of the Act; plus
(ii) The product of the average annual auxiliary electric energy
consumption in kilowatt-hours per year determined according to section
4.6.3 of appendix O of this subpart, and the representative average
unit cost in dollars per kilowatt-hours as provided pursuant to section
323(b)(2) of the Act, the resulting sum then being rounded off to the
nearest dollar per year.
* * * * *
(p) Pool heaters. (1) The estimated annual operating cost for pool
heaters is the sum of: (i) The product of the average annual fuel
energy consumption, in Btu's per year, of natural gas or oil fueled
pool heaters, determined according to section 4.2 of appendix P of this
subpart, and the representative average unit cost in dollars per Btu
for natural gas or oil, as appropriate, as provided pursuant to section
323(b)(2) of the Act; plus (ii) the product of the average annual
auxiliary electric energy consumption in kilowatt-hours per year
determined according to section 4.3 of appendix P of this subpart, and
the representative average unit cost in dollars per kilowatt-hours as
provided pursuant to section 323(b)(2) of the Act, the resulting sum
then being
[[Page 26157]]
rounded off to the nearest dollar per year.
* * * * *
5. Appendix N to subpart B of part 430 is revised to read as
follows:
Appendix N to Subpart B of Part 430--Uniform Test Method for Measuring
the Energy Consumption of Furnaces and Boilers
1.0 Scope. The scope of this appendix is as specified in
section 2.0 of ANSI/ASHRAE Standard 103-1993.
2.0 Definitions. Definitions include the definitions specified
in section 3 of ANSI/ASHRAE Standard 103-1993 and the following
additional and modified definitions:
2.1 ANSI/ASHRAE Standard 103-1993 means the test standard
published in 1993 by ASHRAE, approved by the American National
Standards Institute (ANSI) on October 4, 1993, and entitled ``Method
of Testing for Annual Fuel Utilization Efficiency of Residential
Central Furnaces and Boilers'' (with errata of October 24, 1996).
2.2 ASHRAE means the American Society of Heating, Refrigerating
and Air-Conditioning Engineers, Inc.
2.3 Thermal stack damper means a type of stack damper which is
dependent for operation exclusively upon the direct conversion of
thermal energy of the stack gases to open the damper.
2.4 Isolated combustion system. The definition of isolation
combustion system in section 3 of ANSI/ASHRAE Standard 103-1993 is
incorporated with the addition of the following: ``The unit is
installed in an un-conditioned indoor space isolated from the heated
space.''
3.0 Classifications. Classifications are as specified in
section 4 of ANSI/ASHRAE Standard 103-1993.
4.0 Requirements. Requirements are as specified in section 5 of
ANSI/ASHRAE Standard 103-1993.
5.0 Instruments. Instruments must be as specified in section 6
of ANSI/ASHRAE Standard 103-1993.
6.0 Apparatus. The apparatus used in conjunction with the
furnace or boiler during the testing must be as specified in section
7 of ANSI/ASHRAE Standard 103-1993 except for section 7.2.2.5; and
as specified in section 6.1 of this appendix:
6.1 Downflow furnaces. Install the internal section of vent
pipe the same size as the flue collar for connecting the flue collar
to the top of the unit, if not supplied by the manufacturer. Do not
insulate the internal vent pipe during the jacket loss test (if
conducted) described in section 8.6 of ANSI/ASHRAE Standard 103-1993
or the steady-state test described in section 9.1 of ANSI/ASHRAE
Standard 103-1993. Do not insulate the internal vent pipe before the
cool-down and heat-up tests described in sections 9.5 and 9.6,
respectively, of ANSI/ASHRAE Standard 103-1993. If the vent pipe is
surrounded by a metal jacket, do not insulate the metal jacket.
Install a 5-ft test stack of the same cross sectional area or
perimeter as the vent pipe above the top of the furnace. Tape or
seal around the junction connecting the vent pipe and the 5-ft test
stack. Insulate the 5-ft test stack with insulation having an R-
value not less than 7 and an outer layer of aluminum foil. (See
Figure 3-E of ANSI/ASHRAE Standard 103-1993.)
7.0 Testing conditions. The testing conditions shall be as
specified in section 8 of ANSI/ASHRAE Standard 103-1993 with errata
of October 24, 1996, except for section 8.6.1.1; and as specified in
section 7.1 of this appendix.
7.1 Measurement of jacket surface temperature. The jacket of
the furnace or boiler shall be subdivided into 6-inch squares when
practical, and otherwise into 36-square-inch regions comprising 4
in. x 9 in. or 3 in. x 12 in. sections, and the surface temperature
at the center of each square or section shall be determined with a
surface thermocouple. The 36-square-inch areas shall be recorded in
groups where the temperature differential of the 36-square-inch area
is less than 10 deg.F for temperature up to 100 deg.F above room
temperature and less than 20 deg.F for temperature more than
100 deg.F above room temperature. For forced air central furnaces,
the circulating air blower compartment is considered as part of the
duct system and no surface temperature measurement of the blower
compartment needs to be recorded for the purpose of this test. For
downflow furnaces, measure all cabinet surface temperatures of the
heat exchanger and combustion section, including the bottom around
the outlet duct, and the burner door, using the 36 square-inch
thermocouple grid. The cabinet surface temperatures around the
blower section do not need to be measured (See figure 3-E of ANSI/
ASHRAE Standard 103-1993.)
8.0 Test procedure. Testing and measurements shall be as
specified in section 9 of ANSI/ASHRAE Standard 103-1993 except for
sections 9.5.1.1, 9.5.1.2.1, 9.5.1.2.2, 9.5.2.1, and section 9.7.1.
; and as specified in sections 8.1, 8.2, 8.3, 8.4, and 8.5, of this
appendix.
8.1 Input to interrupted ignition device. For burners equipped
with an interrupted ignition device, record the nameplate electric
power used by the ignition device, PEIG, or use
PEIG=0.4 kW if no nameplate power input is provided.
Record the nameplate ignition device on-time interval,
tIG, or measure the on-time period at the beginning of
the test at the time the burner is turned on with a stop watch, if
no nameplate value is given. Set tIG=0 and
PEIG=0 if the device on-time is less than or equal to 5
seconds after the burner is on.
8.2 Gas- and oil-fueled gravity and forced air central furnaces
without stack dampers cool-down test. Turn off the main burner after
steady-state testing is completed, and measure the flue gas
temperature by means of the thermocouple grid described in section
7.6 of ANSI/ASHRAE 103-1993 at 1.5 minutes
(TF,OFF(t3)) and 9 minutes
(TF,OFF(t4)) after the burner shuts off. An
integral draft diverter shall remain blocked and insulated, and the
stack restriction shall remain in place. On atmospheric systems with
an integral draft diverter or draft hood, equipped with either an
electromechanical inlet damper or an electro-mechanical flue damper
that closes within 10 seconds after the burner shuts off to restrict
the flow through the heat exchanger in the off-cycle, bypass or
adjust the control for the electromechanical damper so that the
damper remains open during the cool-down test. For furnaces that
employ post purge, measure the length of the post-purge period with
a stopwatch. The time from burner OFF to combustion blower OFF
(electrically de-energized) shall be recorded as tp. For
the case where tp is intended to be greater than 180
seconds, stop the combustion blower at 180 seconds and use that
value for tp. Measure the flue gas temperature by means
of the thermocouple grid described in section 7.6 of ANSI/ASHRAE
103-1993 at the end of post-purge period, tp
(TF,OFF(tp)), and at the time (1.5 +
tp) minutes (TF,OFF(t3)) and (9.0 +
tp) minutes (TF,OFF(t4)) after the
main burner shuts off. For the case where the measured tp is less
than or equal to 30 seconds, it shall be tested as if there is no
post purge and tp shall be set equal to 0.
8.3 Gas- and oil-fueled gravity and forced air central furnaces
without stack dampers with adjustable fan control--cool-down test.
For a furnace with adjustable fan control, this time delay will be
3.0 minutes for non-condensing furnaces or 1.5 minutes for
condensing furnaces or until the supply air temperature drops to a
value of 40 deg.F above the inlet air temperature, whichever results
in the longest fan on-time. For a furnace without adjustable fan
control or with the type of adjustable fan control whose range of
adjustment does not allow for the delay time specified above, the
control shall be bypassed and the fan manually controlled to give
the delay times specified above. For a furnace which employs a
single motor to drive the power burner and the indoor air
circulating blower, the power burner and indoor air circulating
blower shall be stopped together.
8.4 Gas-and oil-fueled boilers without stack dampers cool-down
test. After steady-state testing has been completed, turn the main
burner(s) OFF and measure the flue gas temperature at 3.75
(TF,OFF(t3)) and 22.5
(TF,OFF(t4)) minutes after the burner shut
off, using the thermocouple grid described in section 7.6 of ANSI/
ASHRAE 103-1993. During this off-period, for units that do not have
pump delay after shutoff, no water shall be allowed to circulate
through the hot water boilers. For units that have pump delay on
shutoff, except those having pump controls sensing water
temperature, the pump shall be stopped by the unit control and the
time t+, between burner shutoff and pump shutoff shall be
measured within one-second accuracy. For units having pump delay
controls that sense water temperature, the pump shall be operated
for 15 minutes and t+ shall be 15 minutes. While the pump
is operating, the inlet water temperature and flow rate shall be
maintained at the same values as used during the steady-state test
as specified in sections 9.1 and 8.4.2.3 of ANSI/ASHRAE 103-1993.
For boilers that employ post purge, measure the length of the
post-purge period with a stopwatch. The time from burner OFF to
combustion blower OFF (electrically de-energized) shall be recorded
as tP. For the case where tP is intended to be
greater than
[[Page 26158]]
180 seconds, stop the combustion blower at 180 seconds and use that
value for tP. Measure the flue gas temperature by means
of the thermocouple grid described in section 7.6 of ANSI/ASHRAE
103-1993 at the end of the post purge period
tP(TF,OFF(tP)) and at the time
(3.75 + tP) minutes (TF,OFF(t3))
and (22.5 + tP) minutes
(TF,OFF(t4)) after the main burner shuts off.
For the case where the measured tP is less or equal to 30
seconds, it shall be tested as if there is no post purge and
tP shall be set to equal 0.
8.5 Direct measurement of off-cycle losses testing method.
[Reserved.]
9.0 Nomenclature. Nomenclature shall include the nomenclature
specified in section 10 of ANSI/ASHRAE Standard 103-1993 and the
following additional variables:
Effmotor=Efficiency of power burner motor
PEIG=Electrical power to the interrupted ignition device,
kW
RT,a=RT,F if flue gas is measured
=RT,S if stack gas is measured
RT,F=Ratio of combustion air mass flow rate to
stoichiometric air mass flow rate
RT,S=Ratio of the sum of combustion air and relief air
mass flow rate to stoichiometric air mass flow rate
tIG=Electrical interrupted ignition device on-time, min.
Ta,SS,X=TF,SS,X if flue gas temperature is
measured, deg.F
=TS,SS,X if stack gas temperature is measured, deg.F
yIG=ratio of electrical interrupted ignition device on-
time to average burner on-time
yP=ratio of power burner combustion blower on-time to
average burner on-time
10.0 Calculation of derived results from test measurements.
Calculations shall be as specified in section 11 of ANSI/ASHRAE
Standard 103-1993 and the October 24, 1996, Errata Sheet for ASHRAE
Standard 103-1993, except for appendices B and C; and as specified
in sections 10.1 through 10.8 and Figure 1 of this appendix.
10.1 Annual fuel utilization efficiency. The annual fuel
utilization efficiency (AFUE) is as defined in sections 11.2.12
(non-condensing systems), 11.3.12 (condensing systems), 11.4.12
(non-condensing modulating systems) and 11.5.12 (condensing
modulating systems) of ANSI/ASHRAE Standard 103-1993, except for the
definition for the term EffyHS in the defining equation
for AFUE. EffyHS is defined as:
EffyHS=heating seasonal efficiency as defined in sections
11.2.11 (non-condensing systems), 11.3.11 (condensing systems),
11.4.11 (non-condensing modulating systems) and 11.5.11 (condensing
modulating systems) of ANSI/ASHRAE Standard 103-1993 and is based on
the assumptions that all weatherized warm air furnaces or boilers
are located out-of-doors, that warm air furnaces which are not
weatherized are installed as isolated combustion systems, and that
boilers which are not weatherized are installed indoors.
10.2 National average burner operating hours, average annual
fuel energy consumption and average annual auxiliary electrical
energy consumption for gas or oil furnaces and boilers.
10.2.1 National average number of burner operating hours. For
furnaces and boilers equipped with single stage controls, the
national average number of burner operating hours is defined as:
BOHSS=2,080 (0.77) A DHR-2,080 B
where:
2,080=national average heating load hours
0.77=adjustment factor to adjust the calculated design heating
requirement and heating load hours to the actual heating load
experienced by the heating system
DHR=typical design heating requirements as listed in Table 8 (in
unit of kBtu/h) of ANSI/ASHRAE Standard 103-1993, using the proper
value of QOUT defined in 11.2.8.1 of ANSI/ASHRAE Standard
103-1993
A=100,000 /
[341,300(yPPE+yIGPEIG+yBE)+(QIN
-QP)EffyHS], for forced draft unit, indoors
=100,000 / [341,300(yPPE
Effmotor+yIGPEIG+y
BE)+(QIN-QP)EffyHS], for forced
draft unit, ICS,
=100,000 / [341,300(yPPE(1-
Effmotor)+yIGPEIG+y
BE)+(QIN-QP)EffyHS], for induced
draft unit, indoors, and
=100,000 /
[341,300(yIGPEIG+yBE)+(QIN-
QP)EffyHS], for induced draft unit, ICS
B=2 QP(EffyHS)(A) / 100,000
where:
Effmotor=Power burner motor efficiency provided by
manufacturer,
=0.50, an assumed default power burner efficiency if not
provided by manufacturer.
100,000=factor that accounts for percent and kBtu
PE=burner electrical power input at full-load steady-state
operation, including electrical ignition device if energized, as
defined in 9.1.2.2 of ANSI/ASHRAE Standard 103-1993
yP=ratio of induced or forced draft blower on-time to
average burner on-time, as follows:
1 for units without post purge;
1+(tP/3.87) for single stage furnaces with post
purge;
1+(tP/10) for two-stage and step modulating furnaces
with post purge;
1+(tP/9.68) for single stage boilers with post purge;
or
1+(tP/15) for two stage and step modulating boilers
with post purge.
PEIG=electrical input rate to the interrupted ignition
device on burner (if employed), as defined in 8.1 of this appendix
yIG=ratio of burner interrupted ignition device on-time
to average burner on-time, as follows:
0 for burners not equipped with interrupted ignition device;
(tIG/3.87) for single stage furnaces;
(tIG/10) for two-stage and step modulating furnaces;
(tIG/9.68) for single stage boilers; or
(tIG/15) for two stage and step modulating boilers.
tIG=on-time of the burner interrupted ignition device, as
defined in 8.1 of this appendix
tP=post purge time as defined in 8.2 (furnace) or 8.4
(boiler) of this appendix
=0 if tP is equal to or less than 30 second.
y=ratio of blower or pump on-time to average burner on-time, as
follows:
1 for furnaces without fan delay;
1 for boilers without a pump delay;
1+(t+--t-)/3.87 for single stage furnaces
with fan delay;
1+(t+--t-)/10 for two-stage and step
modulating furnaces with fan delay;
1+(t+/9.68) for single stage boilers with pump delay;
or
1+(t+/15) for two stage and step modulating boilers
with pump delay.
BE=circulating air fan or water pump electrical energy input rate at
full load steady-state operation, as defined in ANSI/ASHRAE Standard
103-1993
QIN=as defined in 11.2.8.1 of ANSI/ASHRAE Standard 103-
1993
QP=as defined in 11.2.11 of ANSI/ASHRAE Standard 103-1993
EffyHS=as defined in 11.2.11 (non-condensing systems) or
11.3.11.3 (condensing systems) of ANSI/ASHRAE Standard 103-1993,
percent, and calculated on the basis of:
ICS installation, for non-weatherized warm air furnaces;
indoor installation, for non-weatherized boilers; or
outdoor installation, for furnaces and boilers that are
weatherized.
2=ratio of the average length of the heating season in hours to the
average heating load hours
t+=as defined in 9.5.1.2 of ANSI/ASHRAE Standard 103-1993
or 8.4 of this appendix
t-=as defined in 9.6.1 of ANSI/ASHRAE Standard 103-1993
10.2.1.1 For furnaces and boilers equipped with two stage or
step modulating controls the average annual energy used during the
heating season, EM, is defined as:
EM=(QIN-QP)
BOHSS+(8,760-4,600)QP
where:
QIN=as defined in 11.4.8.1.1 of ANSI/ASHRAE Standard 103-
1993
QP=as defined in 11.4.12 of ANSI/ASHRAE Standard 103-1993
BOHSS=as defined in section 10.2.1 of this appendix, in
which the weighted EffyHS as defined in 11.4.11.3 or
11.5.11.3 of ANSI/ASHRAE Standard 103-1993 is used for calculating
the values of A and B, the term DHR is based on the value of
QOUT defined in 11.4.8.1.1 or 11.5.8.1.1 of ANSI/ASHRAE
Standard 103-1993, and the term
(yPPE+yIGPEIG+yBE) in the factor A
is increased by the factor R, which is defined as:
R=2.3 for two stage controls
=2.3 for step modulating controls when the ratio of minimum-to-
maximum output is greater than or equal to 0.5
=3.0 for step modulating controls when the ratio of minimum-to-
maximum output is less than 0.5
A=100,000/[341,300(yPPE+yIGPEIG+y
BE) R+(QIN-QP) EffyHS], for forced
draft unit, indoors
=100,000/[341,300(yPPE
Effmotor+yIGPEIG+y BE)
R+(QIN-QP)EffyHS], for forced draft
unit, ICS,
[[Page 26159]]
=100,000/[341,300(yPPE(1-
Effmotor)+yIGPEIG+y BE)
R+(QIN-QP) EffyHS], for induced
draft unit, indoors, and
=100,000/[341,300(yIGPEIG+y BE)
R+(QIN-QP) EffyHS], for induced
draft unit, ICS
where:
Effmotor=Power burner motor efficiency provided by
manufacturer,
=0.50, an assumed default power burner efficiency if none
provided by manufacturer.
EffyHS=as defined in 11.4.11.3 or 11.5.11.3 of ANSI/
ASHRAE Standard 103-1993, and calculated on the basis of:
--ICS installation, for non-weatherized warm air furnaces
--indoor installation, for non-weatherized boilers
--outdoor installation, for furnaces and boilers that are
weatherized
8,760=total number of hours per year
4,600=as specified in 11.4.12 of ANSI/ASHRAE Standard 103-1993
10.2.1.2 For furnaces and boilers equipped with two stage or
step modulating controls the national average number of burner
operating hours at the reduced operating mode is defined as:
BOHR=XREM/QIN,R
where:
XR=as defined in 11.4.8.7 of ANSI/ASHRAE Standard 103-
1993
EM=as defined in section 10.2.1.1 of this appendix
QIN,R=as defined in 11.4.8.1.2 of ANSI/ASHRAE Standard
103-1993
10.2.1.3 For furnaces and boilers equipped with two stage
controls the national average number of burner operating hours at
the maximum operating mode (BOHH) is defined as:
BOHH=XHEM/QIN
where:
XH=as defined in 11.4.8.6 of ANSI/ASHRAE Standard 103-
1993
EM=as defined in section 10.2.1.1 of this appendix
QIN=as defined in 11.4.8.1.1 of ANSI/ASHRAE Standard 103-
1993
10.2.1.4 For furnaces and boilers equipped with step modulating
controls the national average number of burner operating hours at
the modulating operating mode (BOHM) is defined as:
BOHM=XHEM/QIN,M
where:
XH=as defined in 11.4.8.6 of ANSI/ASHRAE Standard 103-
1993
EM=as defined in section 10.2.1.1 of this appendix
QIN,M=QOUT,M/(EffySS,M/100)
QOUT,M=as defined in 11.4.8.10 or 11.5.8.10 of ANSI/
ASHRAE Standard 103-1993, as appropriate
EffySS,M=as defined in 11.4.8.8 or 11.5.8.8 of ANSI/
ASHRAE Standard 103-1993, as appropriate, in percent
100=factor that accounts for percent
10.2.2 Average annual fuel energy consumption for gas or oil
fueled furnaces or boilers. For furnaces or boilers equipped with
single stage controls the average annual fuel energy consumption
(EF) is expressed in Btu per year and defined as:
EF=BOHSS(QIN-QP)+8,760
QP
where:
BOHSS=as defined in 10.2.1 of this appendix
QIN=as defined in 11.2.8.1 of ANSI/ASHRAE Standard 103-
1993
QP=as defined in 11.2.11 of ANSI/ASHRAE Standard 103-1993
8,760=as specified in 10.2.1 of this appendix
10.2.2.1 For furnaces or boilers equipped with either two stage
or step modulating controls EF is defined as:
EF=EM + 4,600QP
where:
EM=as defined in 10.2.1.1 of this appendix
4,600=as specified in 11.4.12 of ANSI/ASHRAE Standard 103-1993
QP=as defined in 11.2.11 of ANSI/ASHRAE Standard 103-1993
10.2.3 Average annual auxiliary electrical energy consumption
for gas or oil fueled furnaces or boilers. For furnaces or boilers
equipped with single stage controls the average annual auxiliary
electrical consumption (EAE) is expressed in kilowatt-
hours and defined as:
EAE=BOHSS(yPPE
+yIGPEIG+yBE)
where:
BOHSS=as defined in 10.2.1 of this appendix
PE=as defined in 10.2.1 of this appendix
yP=as defined in 10.2.1 of this appendix
yIG=as defined in 10.2.1 of this appendix
PEIG=as defined in 10.2.1 of this appendix
y=as defined in 10.2.1 of this appendix
BE=as defined in 10.2.1 of this appendix
10.2.3.1 For furnaces or boilers equipped with two stage
controls EAE is defined as:
EAE=BOHR(yPPER+yIG
PEIG+yBER) +
BOHH(yPPEH+yIGPEIG
+y BEH)
where:
BOHR=as defined in 10.2.1.2 of this appendix
yP=as defined in 10.2.1 of this appendix
PER=as defined in 9.1.2.2 and measured at the reduced
fuel input rate, of ANSI/ASHRAE Standard 103-1993
yIG=as defined in 10.2.1 of this appendix
PEIG=as defined in 10.2.1 of this appendix
y=as defined in 10.2.1 of this appendix
BER=as defined in 9.1.2.2 of ANSI/ASHRAE Standard 103-
1993, measured at the reduced fuel input rate
BOHH=as defined in 10.2.1.3 of this appendix
PEH=as defined in 9.1.2.2 of ANSI/ASHRAE Standard 103-
1993, measured at the maximum fuel input rate
BEH=as defined in 9.1.2.2 of ANSI/ASHRAE Standard 103-
1993, measured at the maximum fuel input rate
10.2.3.2 For furnaces or boilers equipped with step modulating
controls EAE is defined as:
EAE=BOHR(yP
PER+yIGPEIG+y
BER)+BOHM(yPPEH+yIG
PEIG+y BEH)
where:
BOHR=as defined in 10.2.1.2 of this appendix
yP=as defined in 10.2.1 of this appendix
PER=as defined in 9.1.2.2 of ANSI/ASHRAE Standard 103-
1993, measured at the reduced fuel input rate
yIG=as defined in 10.2.1 of this appendix
PEIG=as defined in 10.2.1 of this appendix
y=as defined in 10.2.1. of this appendix
BER=as defined in 9.1.2.2 of ANSI/ASHRAE Standard 103-
1993, measured at the reduced fuel input rate
BOHM=as defined in 10.2.1.4 of this appendix
PEH=as defined in 9.1.2.2 of ANSI/ASHRAE Standard 103-
1993, measured at the maximum fuel input rate
BEH=as defined in 9.1.2.2 of ANSI/ASHRAE Standard 103-
1993, measured at the maximum fuel inputs rate
10.3 Average annual electric energy consumption for electric
furnaces or boilers. For electric furnaces and boilers the average
annual energy consumption (EE) is expressed in kilowatt-
hours and defined as:
EE=100(2,080)(0.77)DHR/(3.412 AFUE)
where:
100=to express a percent as a decimal
2,080=as specified in 10.2.1 of this appendix
0.77=as specified in 10.2.1 of this appendix
DHR=as defined in 10.2.1 of this appendix
3.412=conversion to express energy in terms of watt-hours instead of
Btu
AFUE=as defined in 11.1 of ANSI/ASHRAE Standard 103-1993, in
percent, and calculated on the basis of:
ICS installation, for non-weatherized warm air furnaces;
indoor installation, for non-weatherized boilers; or
outdoor installation, for furnaces and boilers that are
weatherized.
10.4 Energy factor.
10.4.1 Energy factor for gas or oil furnaces and boilers.
Calculate the energy factor, EF, for gas or oil furnaces and boilers
defined as, in percent:
[GRAPHIC][TIFF OMITTED]TR12MY97.038
where:
EF=average annual fuel consumption as defined in 10.2.2
of this appendix.
EAE=as defined in 10.2.3 of this appendix.
EffyHS=Annual Fuel Utilization Efficiency as defined in
11.2.11, 11.3.11, 11.4.11 or 11.5.11 of ANSI/ASHRAE Standard 103-
1993, in percent, and calculated on the basis of:
ICS installation, for non-weatherized warm air furnaces;
indoor installation, for non-weatherized boilers; or
outdoor installation, for furnaces and boilers that are
weatherized.
3,412=conversion factor from kilowatt to Btu/h
10.4.2 Energy factor for electric furnaces and boilers. The
energy factor, EF, for electric furnaces and boilers is defined as:
EF=AFUE
where:
AFUE=Annual Fuel Utilization Efficiency as defined in section 10.3
of this appendix, in percent
10.5 Average annual energy consumption for furnaces and boilers
located in a different geographic region of the United States and in
[[Page 26160]]
buildings with different design heating requirements.
10.5.1 Average annual fuel energy consumption for gas or oil-
fueled furnaces and boilers located in a different geographic region
of the United States and in buildings with different design heating
requirements. For gas or oil-fueled furnaces and boilers the average
annual fuel energy consumption for a specific geographic region and
a specific typical design heating requirement (EFR) is
expressed in Btu per year and defined as:
EFR=(EF-8,760 QP)(HLH/2,080)+8,760
QP
where:
EF=as defined in 10.2.2 of this appendix
8,760=as specified in 10.2.1 of this appendix
QP=as defined in 11.2.11 of ANSI/ASHRAE Standard 103-1993
HLH=heating load hours for a specific geographic region determined
from the heating load hour map in Figure 1 of this appendix
2,080=as defined in 10.2.1 of this appendix
10.5.2 Average annual auxiliary electrical energy consumption
for gas or oil-fueled furnaces and boilers located in a different
geographic region of the United States and in buildings with
different design heating requirements. For gas or oil-fueled
furnaces and boilers the average annual auxiliary electrical energy
consumption for a specific geographic region and a specific typical
design heating requirement (EAER) is expressed in
kilowatt-hours and defined as:
EAER=EAE (HLH/2,080)
where:
EAE=as defined in 10.2.3 of this appendix
HLH=as defined in 10.5.1 of this appendix
2,080=as specified in 10.2.1 of this appendix
10.5.3 Average annual electric energy consumption for electric
furnaces and boilers located in a different geographic region of the
United States and in buildings with different design heating
requirements. For electric furnaces and boilers the average annual
electric energy consumption for a specific geographic region and a
specific typical design heating requirement (EER) is
expressed in kilowatt-hours and defined as:
EER=100 (0.77) DHR HLH/(3.412 AFUE)
where:
100=as specified in 10.3 of this appendix
0.77=as specified in 10.2.1 of this appendix
DHR=as defined in 10.2.1 of this appendix
HLH=as defined in 10.5.1 of this appendix
3.412=as specified in 10.3 of this appendix
AFUE=as defined in 10.3 of this appendix, in percent
10.6 Annual energy consumption for mobile home furnaces
10.6.1 National average number of burner operating hours for
mobile home furnaces (BOHSS). BOHSS is the
same as in 10.2.1 of this appendix, except that the value of
EffyHS in the calculation of the burner operating hours,
BOHSS, is calculated on the basis of a direct vent unit
with system number 9 or 10.
10.6.2 Average annual fuel energy for mobile home furnaces
(EF). EF is same as in 10.2.2 of this appendix
except that the burner operating hours, BOHSS, is
calculated as specified in 10.6.1 of this appendix.
10.6.3 Average annual auxiliary electrical energy consumption
for mobile home furnaces (EAE). EAE is the
same as in 10.2.3 of this appendix, except that the burner operating
hours, BOHSS, is calculated as specified in 10.6.1 of
this appendix.
10.7 Calculation of sales weighted average annual energy
consumption for mobile home furnaces. In order to reflect the
distribution of mobile homes to geographical regions with average
HLHMHF value different from 2,080, adjust the annual
fossil fuel and auxiliary electrical energy consumption values for
mobile home furnaces using the following adjustment calculations.
10.7.1 For mobile home furnaces the sales weighted average
annual fossil fuel energy consumption is expressed in Btu per year
and defined as:
EF,MHF=(EF-8,760
QP)HLHMHF/2,080+8,760 QP
where:
EF=as defined in 10.6.2 of this appendix
8,760=as specified in 10.2.1 of this appendix
QP=as defined in 11.2.11 of ANSI/ASHRAE Standard 103-1993
HLHMHF=1880, sales weighted average heating load hours
for mobile home furnaces
2,080=as specified in 10.2.1 of this appendix
10.7.2 For mobile home furnaces the sales weighted average
annual auxiliary electrical energy consumption is expressed in
kilowatt-hours and defined as:
EAE,MHF=EAEHLHMHF/2,080
where:
EAE=as defined in 10.6.3 of this appendix
HLHMHF=as defined in 10.7.1 of this appendix
2,080=as specified in 10.2.1 of this appendix
10.8 Direct determination of off-cycle losses for furnaces and
boilers equipped with thermal stack dampers. [Reserved.]
BILLING CODE 6450-01-P
[[Page 26161]]
[GRAPHIC][TIFF OMITTED]TR12MY97.039
BILLING CODE 6450-01-C
[[Page 26162]]
6. Appendix O to subpart B of part 430 is amended as follows:
Appendix O to Subpart B of Part 430--Uniform Test Method for Measuring
the Energy Consumption of Vented Home Heating Equipment
a. Section 3.5 is revised to read as follows:
3.5 Pilot light measurement.
3.5.1 Measure the energy input rate to the pilot light
(QP) with an error no greater than 3 percent for vented
heaters so equipped.
3.5.2 For manually controlled heaters where the pilot light is
designed to be turned off by the user when the heater is not in use,
that is, turning the control to the OFF position will shut off the
gas supply to the burner(s) and to the pilot light, the measurement
of QP is not needed. This provision applies only if an
instruction to turn off the unit is provided on the heater near the
gas control valve (e.g. by label) by the manufacturer.
b. Section 4.2.4 is revised to read as follows:
4.2.4 Weighted-average steady-state efficiency.
4.2.4.1 For manually controlled heaters with various input
rates the weighted average steady-state efficiency
(SS-WT), is determined as follows:
(1) at 50 percent of the maximum fuel input rate as measured in
either section 3.1.1 of this appendix for manually controlled gas
vented heaters or section 3.1.2 of this appendix for manually
controlled oil vented heaters, or
(2) at the minimum fuel input rate as measured in either section
3.1.1 to this appendix for manually controlled gas vented heaters or
section 3.1.2 to this appendix for manually controlled oil vented
heaters if the design of the heater is such that the 5
percent of 50 percent of the maximum fuel input rate cannot be set,
provided this minimum rate is no greater than \2/3\ of maximum input
rate of the heater.
4.2.4.2 For manually controlled heater with one single firing
rate the weighted average steady-state efficiency is the steady-
state efficiency measured at the single firing rate.
c. Section 4.2.6 is revised to read as follows:
4.2.6 Annual Fuel Utilization Efficiency.
4.2.6.1 For manually controlled vented heaters, calculate the
AFUE expressed as a percent and defined as:
[GRAPHIC][TIFF OMITTED]TR12MY97.040
where:
2,950=average number of heating degree days
SS=as defined as SS-WT in
4.2.4 of this appendix
u=as defined in 4.2.5 of this appendix
Qin-max=as defined as Qin at the maximum fuel
input rate, as defined in 3.1 of this appendix
4,600=average number of non-heating season hours per year
QP=as defined in 3.5 of this appendix
2.083=(65-15)/24=50/24
65=degree day base temperature, deg.F
15=national average outdoor design temperature for vented heaters as
defined in section 4.1.10 of this appendix
24=number of hours in a day
4.2.6.2 For manually controlled vented heaters where the pilot
light can be turned off by the user when the heater is not in use as
described in section 3.5.2, calculate the AFUE expressed as a
percent and defined as:
AFUE=u
where:
u=as defined in section 4.2.5 of this appendix
d. Section 4.3.7 is revised to read as follows:
4.3.7 Annual Fuel Utilization Efficiency.
Calculate the AFUE expressed as a percent and defined as:
[GRAPHIC][TIFF OMITTED]TR12MY97.041
where:
2,950=average number of heating degree days
SS-WT=as defined in 4.1.16 of this appendix
u=as defined in 4.3.6 of this appendix
Qin-max=as defined in 4.2.6 of this appendix
4,600=as specified in 4.2.6 of this appendix
QP=as defined in 3.5 of this appendix
2.083=as specified in 4.2.6 of this appendix
e. Add section 4.6 after section 4.5.3 and before the table 1 to
read as follows:
4.6 Annual energy consumption.
4.6.1 National average number of burner operating hours. For
vented heaters equipped with single stage controls or manual
controls, the national average number of burner operating hours
(BOH) is defined as:
BOHSS=1,416AFA DHR-1,416 B
where:
1,416=national average heating load hours for vented heaters based
on 2,950 degree days and 15 deg.F outdoor design temperature
AF=0.7067, adjustment factor to adjust the calculated
design heating requirement and heating load hours to the actual
heating load experienced by the heating system
DHR=typical design heating requirements based on QOUT,
from Table 4 of this appendix.
QOUT=[(SS/100)-Cj
(Lj/100)] Qin
Lj=jacket loss as defined in 4.1.5 of this appendix
Cj=2.8, adjustment factor as defined in 4.3.6 of this
appendix
SS=steady-state efficiency as defined in 4.1.10
of this appendix, percent
Qin=as defined in 3.1 of this appendix at the maximum
fuel input rate
A=100,000/
[341,300PE+(Qin-QP)u
]
B=2.938(QP) u A/100,000
100,000=factor that accounts for percent and kBtu
PE=as defined in 3.1.3 of this appendix
QP=as defined in 3.5 of this appendix
u=as defined in 4.3.6 of this appendix for
vented heaters using the tracer gas method, percent
=as defined in 4.2.5 of this appendix for manually controlled
vented heaters, percent
=2,950 AFUESS Qin/[2,950
SS Qin--
AFUE(2.083)(4,600)QP], for vented heaters equipped
without manual controls and without thermal stack dampers and not
using the optional tracer gas method, where:
AFUE=as defined in 4.1.17 of this appendix, percent
2,950=average number of heating degree days as defined in 4.2.6 of
this appendix
4,600=average number of non-heating season hours per year as defined
in 4.2.6 of this appendix
[[Page 26163]]
2.938=(4,160/1,416)=ratio of the average length of the heating
season in hours to the average heating load hours
2.083=as specified in 4.2.6 of this appendix
4.6.1.1 For vented heaters equipped with two stage or step
modulating controls the national average number of burner operating
hours at the reduced operating mode is defined as:
BOHR=X1EM/Qred-in
where:
X1=as defined in 4.1.14 of this appendix
Qred-in=as defined in 4.1.11 of this appendix
EM=average annual energy used during the heating season
=(Qin-QP)BOHSS+(8,760-4,600)QP
Qin=as defined in 3.1 of this appendix at the maximum
fuel input rate
QP=as defined in 3.5 of this appendix
BOHSS=as defined in 4.6.1 of this appendix, in which the
term PE in the factor A is increased by the factor R,
which is defined in 3.1.3 of this appendix as:
R=1.3 for two stage controls
=1.4 for step modulating controls when the ratio of minimum-to-
maximum fuel input is greater than or equal to 0.7
=1.7 for step modulating controls when the ratio of minimum-to-
maximum fuel input is less than 0.7 and greater than or equal to 0.5
=2.2 for step modulating controls when the ratio of minimum-to-
maximum fuel input is less than 0.5
A=100,000/[341,300 PE
R+(Qin-QP)u]
8,760=total number of hours per year
4,600=as specified in 4.2.6 of this appendix
4.6.1.2 For vented heaters equipped with two stage or step
modulating controls the national average number of burner operating
hours at the maximum operating mode (BOHH) is defined as:
BOHH=X2EM/Qin
where:
X2=as defined in 4.1.15 of this appendix
EM=average annual energy used during the heating season
=(Qin-QP)BOHSS+(8,760-4,600)QP
Qin=as defined in 3.1 of this appendix at the maximum
fuel input rate
4.6.2 Average annual fuel energy for gas or oil fueled vented
heaters. For vented heaters equipped with single stage controls or
manual controls, the average annual fuel energy consumption
(EF) is expressed in Btu per year and defined as:
EF=BOHSS (Qin-QP)+8,760
QP
where:
BOHSS=as defined in 4.6.1 of this appendix
Qin=as defined in 3.1 of this appendix
QP=as defined in 3.5 of this appendix
8,760=as specified in 4.6.1 of this appendix
4.6.2.1 For vented heaters equipped with either two stage or
step modulating controls EF is defined as:
EF=EM+4,600QP
where:
EM=as defined in 4.6.1.2 of this appendix
4,600=as specified 4.2.6 of this appendix
QP=as defined in 3.5 of this appendix
4.6.3 Average annual auxiliary electrical energy consumption
for vented heaters. For vented heaters with single stage controls or
manual controls the average annual auxiliary electrical consumption
(EAE) is expressed in kilowatt-hours and defined as:
EAE=BOHSSPE
where:
BOHSS=as defined in 4.6.1 of this appendix
PE=as defined in 3.1.3 of this appendix
4.6.3.1 For vented heaters equipped with two stage or
modulating controls EAE is defined as:
EAE=(BOHR+BOHH)PE
where:
BOHR=as defined in 4.6.1 of this appendix
BOHH=as defined in 4.6.1 of this appendix
PE=as defined in 3.1.3 of this appendix
4.6.4 Average annual energy consumption for vented heaters
located in a different geographic region of the United States and in
buildings with different design heating requirements.
4.6.4.1 Average annual fuel energy consumption for gas or oil
fueled vented home heaters located in a different geographic region
of the United States and in buildings with different design heating
requirements. For gas or oil fueled vented heaters the average
annual fuel energy consumption for a specific geographic region and
a specific typical design heating requirement (EFR) is
expressed in Btu per year and defined as:
EFR=(EF-8,760 QP)(HLH/
1,416)+8,760QP
where:
EF=as defined in 4.6.2 of this appendix
8,760=as specified in 4.6.1 of this appendix
QP=as defined in 3.5 of this appendix
HLH=heating load hours for a specific geographic region determined
from the heating load hour map in Figure 3 of this appendix
1,416=as specified in 4.6.1 of this appendix
4.6.4.2 Average annual auxiliary electrical energy consumption
for gas or oil fueled vented home heaters located in a different
geographic region of the United States and in buildings with
different design heating requirements. For gas or oil fueled vented
home heaters the average annual auxiliary electrical energy
consumption for a specific geographic region and a specific typical
design heating requirement (EAER) is expressed in
kilowatt-hours and defined as:
EAER=EAE HLH/1,416
where:
EAE=as defined in 4.6.3 of this appendix
HLH=as defined in 4.6.4.1 of this appendix
1,416=as specified in 4.6.1 of this appendix
f. Table 4 and Figure 3 are added to the end of appendix O to
subpart B of 10 CFR part 430 to read as follows:
Table 4.--Average Design Heating Requirements for Vented Heaters With
Different Output Capacities
------------------------------------------------------------------------
Average
design
Vented heaters output capacity Qout--(Btu/hr) heating
requirements
(kBtu/hr)
------------------------------------------------------------------------
5,000-7,499............................................... 5.0
7,500-10,499.............................................. 7.5
10,500-13,499............................................. 10.0
13,500-16,499............................................. 12.5
16,500-19,499............................................. 15.0
19,500-22,499............................................. 17.5
22,500-26,499............................................. 20.5
26,500-30,499............................................. 23.5
30,500-34,499............................................. 26.5
34,500-38,499............................................. 30.0
38,500-42,499............................................. 33.5
42,500-46,499............................................. 36.5
46,500-51,499............................................. 40.0
51,500-56,499............................................. 44.0
56,500-61,499............................................. 48.0
61,500-66,499............................................. 52.0
66,500-71,499............................................. 56.0
71,500-76,500............................................. 60.0
------------------------------------------------------------------------
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7. Appendix P to Subpart B of Part 430 is revised to read as
follows:
Appendix P to Subpart B of Part 430--Uniform Test Method for Measuring
the Energy Consumption of Pool Heaters
1. Test method. The test method for testing pool heaters is as
specified in American National Standards Institute Standard for Gas-
Fired Pool Heaters, Z21.56-1994.
2. Test conditions. Establish the test conditions specified in
section 2.9 of ANSI Z21.56-1994.
3. Measurements. Measure the quantities delineated in section
2.9 of ANSI Z21.56-1994. The measurement of energy consumption for
oil-fired pool heaters in Btu is to be carried out in appropriate
units, e.g., gallons.
4. Calculations.
4.1 Thermal efficiency. Calculate the thermal efficiency,
Et (expressed as a percent), as specified in section 2.9
of ANSI Z21.56-1994. The expression of fuel consumption for oil-
fired pool heaters shall be in Btu.
4.2 Average annual fossil fuel energy for pool heaters. The
average annual fuel energy for pool heater, EF, is
defined as:
EF=BOH QIN+(POH-BOH)QP
where:
BOH=average number of burner operating hours=104 h
POH=average number of pool operating hours=4464 h
QIN=rated fuel energy input as defined according to 2.9.1
or 2.9.2 of ANSI Z21.56-1994, as appropriate
QP=energy consumption of continuously operating pilot
light if employed, in Btu/h.
4.3 Average annual auxiliary electrical energy consumption for
pool heaters. The average annual auxiliary electrical energy
consumption for pool heaters, EAE, is expressed in Btu
and defined as:
EAE=BOH PE
where:
PE=2Ec if heater tested according to 2.9.1 of ANSI
Z21.56-1994
=3.412 PErated if heater tested according to 2.9.2 of
ANSI Z21.56-1994, in Btu/h
Ec=Electrical consumption of the heater (converted to
equivalent unit of Btu), including the electrical energy to the
recirculating pump if used, during the 30-minute thermal efficiency
test, as defined in 2.9.1 of ANSI Z21.56-1994, in Btu per 30 min.
2=Conversion factor to convert unit from per 30 min. to per h.
PErated=nameplate rating of auxiliary electrical
equipment of heater, in Watts
BOH=as defined in 4.2 of this appendix
4.4 Heating seasonal efficiency.
4.4.1 Calculate the seasonal useful output of the pool heater
as:
EOUT=BOH [(Et/100)(QIN+PE)]
where:
BOH=as defined in 4.2 of this appendix
Et=thermal efficiency as defined in 4.1 of this appendix
QIN=as defined in 4.2 of this appendix
PE=as defined in 4.3 of this appendix
100=conversion factor, from percent to fraction
4.4.2 Calculate the seasonal input to the pool heater as:
EIN=BOH (QIN+PE)+(POH-BOH) QP
where:
BOH=as defined in 4.2 of this appendix
QIN=as defined in 4.2 of this appendix
PE=as defined in 4.3 of this appendix
POH=as defined in 4.2 of this appendix
QP=as defined in 4.2 of this appendix
4.4.3 Calculate the pool heater heating seasonal efficiency (in
percent).
4.4.3.1 For pool heaters employing a continuous pilot light:
EFFYHS=100(EOUT/EIN)
where:
EOUT=as defined in 4.4.1 of this appendix
EIN=as defined in 4.4.2 of this appendix
100=to convert a fraction to percent
4.4.3.2 For pool heaters without a continuous pilot light:
EFFYHS=Et
where:
Et=as defined in 4.1 of this appendix.
[FR Doc. 97-10608 Filed 5-9-97; 8:45 am]
BILLING CODE 6450-01-P