Appendix C to Subpart B of Part 431 - Compliance Certification
10:3.0.1.4.19.2.54.17.46 : Appendix C
Appendix C to Subpart B of Part 431 - Compliance Certification
Certification of Compliance With Energy Efficiency Standards for
Electric Motors (Office of Management and Budget Control Number:
1910-1400. Expires February 13, 2014)
An electronic form is available at
https://www.regulations.doe.gov/ccms/.
1. Name and Address of Company (the “company”):
2. Name(s) to be Marked on Electric Motors to Which this
Compliance Certification Applies:
3. If manufacturer or private labeler wishes to receive a unique
Compliance Certification number for use with any particular brand
name, trademark, or other label name, fill out the following two
items:
A. List each brand name, trademark, or other label name for
which the company requests a Compliance Certification number:
B. List other name(s), if any, under which the company sells
electric motors (if not listed in item 2 above):
Submit electronically at
https://www.regulations.doe.gov/ccms.
Submit paper form by Certified Mail to: U.S. Department
of Energy, Office of Energy Efficiency and Renewable Energy,
Building Technologies (EE-2J), Forrestal Building, 1000
Independence Avenue, SW., Washington, DC 20585-0121.
This Compliance Certification reports on and certifies
compliance with requirements contained in 10 CFR Part 431 (Energy
Conservation Program for Certain Commercial and Industrial
Equipment) and Part C of the Energy Policy and Conservation Act
(Pub. L. 94-163), and amendments thereto. It is signed by a
responsible official of the above named company. Attached and
incorporated as part of this Compliance Certification is a Listing
of Electric Motor Efficiencies. For each rating of electric motor*
for which the Listing specifies the nominal full load efficiency of
a basic model, the company distributes no less efficient basic
model with that rating and all basic models with that rating comply
with the applicable energy efficiency standard.
* For this purpose, the term “rating” means one of the
combinations of an electric motor's horsepower (or standard
kilowatt equivalent), number of poles, motor type, and open or
enclosed construction, with respect to which § 431.25 of 10 CFR
Part 431 prescribes nominal full load efficiency standards.
If any part of this Compliance Certification, including the
Attachment, was prepared by a third party organization under the
provisions of 10 CFR 431.36, the company official authorizing third
party representations:
Third Party Organization Officially Acting as
Representative:
Third Party Organization: Responsible Person at the Organization:
Address: Telephone Number: Facsimile Number:
All required determinations on which this Compliance
Certification is based were made in conformance with the applicable
requirements in 10 CFR Part 431, subpart B. All information
reported in this Compliance Certification is true, accurate, and
complete. The company is aware of the penalties associated with
violations of the Act and the regulations thereunder, and is also
aware of the provisions contained in 18 U.S.C. 1001, which
prohibits knowingly making false statements to the Federal
Government.
Signature: Date: Name: Title: Firm or Organization: Attachment of
Certification of Compliance With Energy Efficiency Standards for
Electric Motor Efficiencies Date: Name of Company:
Motor Type (i.e., general purpose electric motor (subtype I),
fire pump electric motor, general purpose electric motor (subtype
II), NEMA Design B general purpose electric motor)
Motor
horsepower/standard kilowatt equivalent
Least efficient
basic model - (model numbers(s))
Nominal full-load efficiency
Open motors
(number of poles)
Enclosed
motors
(number of poles)
8
6
4
2
8
6
4
2
1/.75
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Note: Place an asterisk beside each reported
nominal full load efficiency that is determined by actual testing
rather than by application of an alternative efficiency
determination method. Also list below additional basic models that
were subjected to actual testing.
Basic Model means all units of a given type of electric
motor (or class thereof) manufactured by a single manufacturer, and
which (i) have the same rating, (ii) have electrical design
characteristics that are essentially identical, and (iii) do not
have any differing physical or functional characteristics that
affect energy consumption or efficiency.
Rating means one of the combinations of an electric
motor's horsepower (or standard kilowatt equivalent), number of
poles, motor type, and open or enclosed construction, with respect
to which § 431.25 of 10 CFR Part 431 prescribes nominal full load
efficiency standards.
Models Actually Tested and Not Previously
Identified
Motor
horsepower/standard kilowatt equivalent
Least efficient
basic model - (model numbers(s))
Nominal full-load efficiency
Open motors
(number of poles)
Enclosed
motors
(number of poles)
8
6
4
2
8
6
4
2
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[69 FR 61923, Oct. 21, 2004, as amended at 76 FR 59006, Sept. 23,
2011]
Appendix C to Subpart G of Part 431 - Uniform Test Method for the Measurement of Thermal Efficiency and Standby Loss of Gas-Fired and Oil-Fired Instantaneous Water Heaters and Hot Water Supply Boilers (Other Than Storage-Type Instantaneous Water Heaters)
10:3.0.1.4.19.7.64.6.53 : Appendix C
Appendix C to Subpart G of Part 431 - Uniform Test Method for the
Measurement of Thermal Efficiency and Standby Loss of Gas-Fired and
Oil-Fired Instantaneous Water Heaters and Hot Water Supply Boilers
(Other Than Storage-Type Instantaneous Water Heaters) Note:
Prior to November 6, 2017, manufacturers must make any
representations with respect to the energy use or efficiency of the
subject commercial water heating equipment in accordance with the
results of testing pursuant to this appendix or the procedures in
10 CFR 431.106 that were in place on January 1, 2016. On and after
November 6, 2017, manufacturers must make any representations with
respect to energy use or efficiency of gas-fired and oil-fired
instantaneous water heaters and hot water supply boilers (other
than storage-type instantaneous water heaters) in accordance with
the results of testing pursuant to this appendix to demonstrate
compliance with the energy conservation standards at 10 CFR
431.110.
1. General
Determine the thermal efficiency and standby loss (as
applicable) in accordance with the following sections of this
appendix. Certain sections reference sections of Annex E.1 of ANSI
Z21.10.3-2015 (incorporated by reference; see § 431.105). Where the
instructions contained in the sections below conflict with
instructions in Annex E.1 of ANSI Z21.10.3-2015, the instructions
contained in this appendix control.
2. Test Set-Up
2.1. Placement of Water Heater. A water heater for
installation on combustible floors must be placed on a 3/4-inch
plywood platform supported by three 2 x 4-inch runners. If the
water heater is for installation on noncombustible floors, suitable
noncombustible material must be placed on the platform. When the
use of the platform for a large water heater is not practical, the
water heater may be placed on any suitable flooring. A wall-mounted
water heater must be mounted on a simulated wall section.
2.2. Test Configuration. If the instantaneous
water heater or hot water supply boiler is not required to be
tested using a recirculating loop, then set up the unit in
accordance with Figures 2.1, 2.2, or 2.3 of this appendix (as
applicable). If the unit is required to be tested using a
recirculating loop, then set up the unit as per Figure 2.4 of this
appendix.
2.2.1. If the instantaneous water heater or hot water supply
boiler does not have any external piping, install an outlet water
valve within 10 inches of piping length of the water heater jacket
or enclosure. If the instantaneous water heater or hot water supply
boiler includes external piping assembled at the manufacturer's
premises prior to shipment, install water valves in the outlet
piping within 5 inches of the end of the piping supplied with the
unit.
2.2.2. If the water heater is not able to achieve an
outlet water temperature of 70 °F ± 2 °F (TOWT) above the supply
water temperature at full firing rate, a recirculating loop with
pump as shown in Figure 2.4 of this appendix must be used.
2.2.2.1. If a recirculating loop with a pump is used, then
ensure that the inlet water temperature labeled as TIWT in Figure
2.4 of this appendix, is greater than or equal to 70 °F and less
than or equal to 120 °F at all times during the thermal efficiency
test and steady-state verification period (as applicable).
2.3. Installation of Temperature Sensors
2.3.1. Without Recirculating Loop.
2.3.1.1. Vertical Connections. Use Figure 2.1 (for top
connections) and 2.2 (for bottom connections) of this appendix.
2.3.1.2. Horizontal Connections. Use Figure 2.3 of this
appendix.
2.3.2. With Recirculating Loop. Set up the recirculating
loop as shown in Figure 2.4 of this appendix.
2.3.3. For water heaters with multiple outlet water connections
leaving the water heater jacket that are required to be operated to
achieve the rated input, temperature sensors must be installed for
each outlet water connection leaving the water heater jacket or
enclosure that is used during testing, in accordance with the
provisions in sections 2.3.1 and 2.3.2 of this appendix (as
applicable).
2.4. Piping Insulation. Insulate all water piping
external to the water heater jacket or enclosure, including piping
that is installed by the manufacturer or shipped with the unit, for
at least 4 ft of piping length from the connection at the appliance
with material having an R-value not less than 4 °F·ft 2·h/Btu.
Ensure that the insulation does not contact any appliance surface
except at the location where the pipe connections penetrate the
appliance jacket or enclosure.
2.5. Temperature and Pressure Relief Valve Insulation. If
the manufacturer has not provided a temperature and pressure relief
valve, one shall be installed and insulated as specified in section
2.4 of this appendix. The temperature and pressure relief valve
must be installed in the outlet water piping, between the unit
being tested and the outlet water valve.
2.6. Vent Requirements. Follow the requirements
for venting arrangements specified in paragraph c of Annex E.1 of
ANSI Z21.10.3-2015 (incorporated by reference; see § 431.105).
2.7. Energy Consumption. Install equipment that
determines, within ± 1 percent:
2.7.1. The quantity and rate of fuel consumed.
2.7.2. The quantity of electricity consumed by factory-supplied
water heater components, and of the test loop recirculating pump,
if used.
3. Test Conditions 3.1. Water Supply
3.1.1. Water Supply Pressure. The pressure of the water
supply must be maintained between 40 psi and the maximum pressure
specified by the manufacturer of the unit being tested. The
accuracy of the pressure-measuring devices must be within ± 1.0
psi.
3.1.2. Water Supply Temperature. During the
thermal efficiency test and steady-state verification period (as
applicable), the temperature of the supply water (TSWT) must be
maintained at 70 °F ± 2 °F.
3.2. Gas Pressure for Gas-Fired Equipment. The
supply gas pressure must be within the range specified by the
manufacturer on the nameplate of the unit being tested. The
difference between the outlet pressure of the gas appliance
pressure regulator and the value specified by the manufacturer on
the nameplate of the unit being tested must not exceed the greater
of: ± 10 percent of the nameplate value or ± 0.2 inches water
column (in. w.c.). Obtain the higher heating value of the gas
burned.
3.3. Ambient Room Temperature. Maintain the ambient room
temperature at 75 °F ± 10 °F at all times during the steady-state
verification period, the thermal efficiency test, and the standby
loss test (as applicable). Measure the ambient room temperature at
1-minute intervals during these periods. Measure the ambient room
temperature at the vertical mid-point of the water heater and
approximately 2 feet from the water heater jacket or enclosure.
Shield the sensor against radiation. Calculate the average ambient
room temperature separately for the thermal efficiency test and the
standby loss test. During the thermal efficiency and standby loss
tests, the ambient room temperature must not vary by more than ±
5.0 °F at any reading from the average ambient room
temperature.
3.4. Test Air Temperature. During the steady-state
verification period, the thermal efficiency test, and the standby
loss test (as applicable), the test air temperature must not vary
by more than ± 5 °F from the ambient room temperature at any
reading. Measure the test air temperature at 1-minute intervals
during these periods and at a location within two feet of the air
inlet of the water heater or the combustion air intake vent, as
applicable. Shield the sensor against radiation. For units with
multiple air inlets, measure the test air temperature at each air
inlet, and maintain the specified tolerance on deviation from the
ambient room temperature at each air inlet. For units without a
dedicated air inlet, measure the test air temperature within two
feet of any location on the water heater where combustion air is
drawn.
3.5. Maximum Air Draft. During the steady-state
verification period, the thermal efficiency test, and the standby
loss test (as applicable), the water heater must be located in an
area protected from drafts of more than 50 ft/min. Prior to
beginning the steady-state verification period and the standby loss
test, measure the air draft within three feet of the jacket or
enclosure of the water heater to ensure this condition is met.
Ensure that no other changes that would increase the air draft are
made to the test set-up or conditions during the conduct of the
tests.
3.6. Primary Control
3.6.1. Thermostatically-Activated Water Heaters With an
Internal Thermostat. Before starting the thermal efficiency
test and the standby loss test (unless the thermostat is already
set before the thermal efficiency test), the thermostat setting
must be obtained. Set the thermostat to ensure:
3.6.1.1. With supply water temperature set as per section 3.1.2
of this appendix (i.e., 70 °F ± 2 °F) the water flow rate
can be varied so that the outlet water temperature is constant at
70 °F ± 2 °F above the supply water temperature, while the burner
is firing at full firing rate; and
3.6.1.2. After the water supply is turned off and the thermostat
reduces the fuel supply to a minimum, the maximum heat exchanger
outlet water temperature (TOHX) is 140 °F ± 5 °F.
3.6.1.3. If the water heater includes a built-in safety
mechanism that prevents it from achieving a heat exchanger outlet
water temperature of 140 °F ± 5 °F, adjust the thermostat to its
maximum setting.
3.6.2. Flow-Activated Instantaneous Water Heaters and
Thermostatically-Activated Instantaneous Water Heaters With an
External Thermostat. Energize the primary control such that it
is always calling for heating and the burner is firing at the full
firing rate. Maintain the supply water temperature as per section
3.1.2 of this appendix (i.e., 70 °F ± 2 °F). Set the control
so that the outlet water temperature (TOWT) is 140 °F ± 5 °F. If
the water heater includes a built-in safety mechanism that prevents
it from achieving a heat exchanger outlet water temperature of 140
°F ± 5 °F, adjust the control to its maximum setting.
3.7. Units With Multiple Outlet Water Connections
3.7.1. For each connection leaving the water heater that is
required for the unit to achieve the rated input, the outlet water
temperature must not differ from that of any other outlet water
connection by more than 2 °F during the steady-state verification
period and thermal efficiency test.
3.7.2. Determine the outlet water temperature representative for
the entire unit at every required measurement interval by
calculating the average of the outlet water temperatures measured
at each connection leaving the water heater jacket or enclosure
that is used during testing. Use the outlet water temperature
representative for the entire unit in all calculations for the
thermal efficiency and standby loss tests, as applicable.
3.8. Additional Requirements for Oil-Fired Equipment.
3.8.1. Venting Requirements. Connect a vertical
length of flue pipe to the flue gas outlet of sufficient height so
as to meet the minimum draft specified by the manufacturer.
3.8.2. Oil Supply. Adjust the burner rate so that the
following conditions are met:
3.8.2.1. The CO2 reading is within the range specified by the
manufacturer;
3.8.2.2. The fuel pump pressure is within ± 10 percent of
manufacturer's specifications;
3.8.2.3. If either the fuel pump pressure or range for CO2
reading are not specified by the manufacturer on the nameplate of
the unit, in literature shipped with the unit, or in supplemental
test report instructions included with a certification report, then
a default value of 100 psig is to be used for fuel pump pressure,
and a default range of 9-12 percent is to be used for CO2 reading;
and
3.8.2.4. Smoke in the flue does not exceed No. 1 smoke as
measured by the procedure in ASTM D2156-09 (Reapproved 2013)
(incorporated by reference, see § 431.105). To determine the smoke
spot number, the smoke measuring device shall be connected to an
open-ended tube. This tube must project into the flue 1/4 to 1/2 of
the pipe diameter.
3.8.2.5. If no settings on the water heater have been changed
and the water heater has not been turned off since the end of a
previously run thermal efficiency (or standby loss test for
thermostatically-activated instantaneous water heaters with an
internal thermostat), measurement of the CO2 reading and conduct of
the smoke spot test are not required prior to beginning a test.
Otherwise, measure the CO2 reading and determine the smoke spot
number, with the burner firing, before beginning measurements for
the steady-state verification period (prior to beginning the
thermal efficiency test or standby loss test, as applicable).
However, measurement of the CO2 reading and conduct of the smoke
spot test are not required for the standby loss test for
thermostatically-activated instantaneous water heaters with an
external thermostat and flow-activated instantaneous water
heaters.
3.9. Data Collection Intervals. Follow the data
recording intervals specified in the following sections.
3.9.1. Steady-State Verification Period and Thermal
Efficiency Test. For the steady-state verification period and
the thermal efficiency test, follow the data recording intervals
specified in Table 3.1 of this appendix. These data recording
intervals must also be followed if conducting a steady-state
verification period prior to conducting the standby loss test.
Table 3.1 - Data To Be Recorded Before and
During the Steady-State Verification Period and Thermal Efficiency
Test
Item recorded
Before
steady-state
verification period
Every 1
minute a
Every 10
minutes
Gas supply
pressure, in w.c.
X
Gas outlet
pressure, in w.c.
X
Barometric
pressure, in Hg
X
Fuel higher
heating value, Btu/ft 3 (gas) or Btu/lb (oil)
X
Oil pump pressure,
psig (oil only)
X
CO2 reading, %
(oil only)
X b
Oil smoke spot
reading (oil only)
X b
Air draft,
ft/min
X
Time,
minutes/seconds
X
Fuel weight or
volume, lb (oil) or ft 3 (gas)
X c
Supply water
temperature (TSWT), °F
X
Inlet water
temperature (TIWT), °F
X d
Outlet water
temperature (TOWT), °F
X
Ambient room
temperature, °F
X
Test air
temperature, °F
X
Water flow rate,
gpm
X
Notes:
a These measurements are to be
recorded at the start and end of both the steady-state verification
period and the thermal efficiency test, as well as every minute
during both periods.
b The smoke spot test and CO2
reading are not required prior to beginning the steady-state
verification period if no settings on the water heater have been
changed and the water heater has not been turned off since the end
of a previously-run efficiency test (i.e., thermal efficiency or
standby loss).
c Fuel and electricity
consumption over the course of the entire thermal efficiency test
must be measured and used in calculation of thermal efficiency.
d Only measured when a
recirculating loop is used.
3.9.2. Standby Loss Test. For the standby loss test,
follow the data recording intervals specified in Table 3.2 of this
appendix. (Follow the data recording intervals specified in Table
3.1 of this appendix of the steady-state verification period, if
conducted prior to the standby loss test.) Additionally, the fuel
and electricity consumption over the course of the entire test must
be measured and used in calculation of standby loss.
Table 3.2 - Data To Be Recorded Before and
During the Standby Loss Test
Item recorded
Before test
Every 1
minute a
Gas supply
pressure, in w.c.
X
Gas outlet
pressure, in w.c.
X
Barometric
pressure, in Hg
X
Fuel higher
heating value, Btu/ft 3 (gas) or Btu/lb (oil)
X
Oil pump pressure,
psig (oil only)
X
Air draft,
ft/min
X
Time,
minutes/seconds
X
Heat exchanger
outlet water temperature (TOHX), °F
X
Ambient room
temperature, °F
X
Test air
temperature, °F
X
Water flow rate,
gpm
X b
Inlet water
temperature (TIWT), °F
X b
Notes:
a These measurements are to be
recorded at the start and end of the test, as well as every minute
during the test.
b The water flow rate and supply
water temperature and inlet water temperature (if a recirculating
loop is used) must be measured during the steady-state verification
period at 1-minute intervals. After the steady-state verification
period ends, flow rate, supply water temperature, and inlet water
temperature (if measured) are not required to be measured during
the standby loss test, as there is no flow occurring during the
standby loss test.
4. Determination of Storage Volume. Determine the storage
volume by subtracting the tare weight, measured while the system is
dry and empty, from the weight of the system when filled with water
and dividing the resulting net weight of water by the density of
water at the measured water temperature. The volume of water
contained in the water heater must be computed in gallons.
5. Fuel Input Rate
5.1. Determination of Fuel Input Rate. During the
steady-state verification period and thermal efficiency test, as
applicable, record the fuel consumption at 10-minute intervals.
Calculate the fuel input rate for each 10-minute period using the
equations in section 5.2 of this appendix. The measured fuel input
rates for these 10-minute periods must not vary by more than ± 2
percent between any two readings. Determine the overall fuel input
rate using the fuel consumption for the entire duration of the
thermal efficiency test.
5.2. Fuel Input Rate Calculation. To calculate the fuel
input rate, use the following equation:
Where: Q
= Fuel input rate, expressed in Btu/h Qs = Total fuel flow as
metered, expressed in ft 3 for gas-fired equipment and lb for
oil-fired equipment Cs = Correction applied to the heating value of
a gas H, when it is metered at temperature and/or pressure
conditions other than the standard conditions for which the value
of H is based. Cs=1 for oil-fired equipment. H = Higher heating
value of the fuel, expressed as Btu/ft 3 for gas-fired equipment
and Btu/lb for oil-fired equipment. t = Duration of measurement of
fuel consumption
6. Thermal Efficiency Test. Before beginning the
steady-state verification period, record the applicable parameters
as specified in section 3.9.1 of this appendix. Begin drawing water
from the unit by opening the main supply and outlet water valve,
and adjust the water flow rate to achieve an outlet water
temperature of 70 °F ± 2 °F above supply water temperature. The
thermal efficiency test shall be deemed complete when there is a
continuous, one-hour-long period where the steady-state conditions
specified in section 6.1 of this appendix have been met, as
confirmed by consecutive readings of the relevant parameters at
1-minute intervals (except for fuel input rate, which is determined
at 10-minute intervals, as specified in section 5.1 of this
appendix). During the one-hour-long period, the water heater must
fire continuously at its full firing rate (i.e., no
modulation or cut-outs) and no settings can be changed on the unit
being tested at any time. The first 30 minutes of the
one-hour-period where the steady-state conditions in section 6.1 of
this appendix are met is the steady-state verification period. The
final 30 minutes of the one-hour-period where the steady-state
conditions in section 6.1 of this appendix are met is the thermal
efficiency test. The last reading of the steady-state verification
period must be the first reading of the thermal efficiency test
(i.e., the thermal efficiency test starts immediately once
the steady-state verification period ends).
6.1. Steady-State Conditions. The following conditions
must be met at consecutive readings taken at 1-minute intervals
(except for fuel input rate, for which measurements are taken at
10-minute intervals) to verify the water heater has achieved
steady-state operation during the steady-state verification period
and the thermal efficiency test.
6.1.1. The water flow rate must be maintained within ± 0.25
gallons per minute (gpm) of the initial reading at the start of the
steady-state verification period.
6.1.2. Outlet water temperature must be maintained at 70 °F ± 2
°F above supply water temperature.
6.1.3. Fuel input rate must be maintained within ± 2 percent of
the rated input certified by the manufacturer.
6.1.4. The supply water temperature (TSWT) (or inlet water
temperature (TIWT) if a recirculating loop is used) must be
maintained within ± 0.50 °F of the initial reading at the start of
the steady-state verification period.
6.1.5. The rise between supply (or inlet if a recirculating loop
is used) and outlet water temperatures must be maintained within ±
0.50 °F of its initial value taken at the start of the steady-state
verification period for units with rated input less than 500,000
Btu/h, and maintained within ± 1.00 °F of its initial value for
units with rated input greater than or equal to 500,000 Btu/h.
6.2. Water Flow Measurement. Measure the total weight of
water heated during the 30-minute thermal efficiency test with
either a scale or a water flow meter. With either method, the error
of measurement of weight of water heated must not exceed 1 percent
of the weight of the total draw.
6.3. Thermal Efficiency Calculation. Thermal efficiency
must be calculated using data from the 30-minute thermal efficiency
test. Calculate thermal efficiency, Et, using the following
equation:
Where: K
= 1.004 Btu/lb· °F, the nominal specific heat of water at 105 °F W
= Total weight of water heated, lb θ1 = Average supply water
temperature, expressed in °F θ2 = Average outlet water temperature,
expressed in °F Q = Total fuel flow as metered, expressed in ft 3
(gas) or lb (oil) Cs = Correction applied to the heating value of a
gas H, when it is metered at temperature and/or pressure conditions
other than the standard conditions for which the value of H is
based. Cs=1 for oil-fired equipment. H = Higher heating value of
the fuel, expressed in Btu/ft 3 (gas) or Btu/lb (oil) Ec =
Electrical consumption of the water heater and, when used, the test
set-up recirculating pump, expressed in Btu
7. Standby Loss Test. If the standby loss test is
conducted immediately after a thermal efficiency test and no
settings or conditions have been changed since the completion of
the thermal efficiency test, then skip to section 7.2 or 7.3 of
this appendix (as applicable). Otherwise, perform the steady-state
verification in section 7.1 of this appendix. For
thermostatically-activated instantaneous water heaters with an
internal thermostat, use section 7.2 of this appendix to conduct
the standby loss test, and for flow-activated and/or
thermostatically-activated instantaneous water heaters with an
external thermostat use section 7.3 of this appendix to conduct the
standby loss test.
7.1. Steady-State Verification Period. For water heaters
where the standby loss test is not conducted immediately following
the thermal efficiency test, the steady-state verification period
must be conducted before starting the standby loss test. Set the
primary control in accordance with section 3.6 of this appendix,
such that the primary control is always calling for heat and the
water heater is firing continuously at the full firing rate
(i.e., no modulation or cut-outs). Begin drawing water from
the unit by opening the main supply and the outlet water valve, and
adjust the water flow rate to achieve an outlet water temperature
of 70 °F ± 2 °F above supply water temperature. The steady-state
verification period is complete when there is a continuous
30-minute period where the steady-state conditions specified in
section 7.1.1 of this appendix are met, as confirmed by consecutive
readings of the relevant parameters recorded at 1-minute intervals
(except for fuel input rate, which is determined at 10-minute
intervals, as specified in section 5.1 of this appendix).
7.1.1. Steady-State Conditions. The following conditions
must be met at consecutive readings taken at 1-minute intervals
(except for fuel input rate, for which measurements are taken at
10-minute intervals) to verify the water heater has achieved
steady-state operation during the steady-state verification period
prior to conducting the standby loss test.
7.1.1.1. The water flow rate must be maintained within ± 0.25
gallons per minute (gpm) of the initial reading at the start of the
steady-state verification period;
7.1.1.2. Fuel input rate must be maintained within ± 2 percent
of the rated input certified by the manufacturer;
7.1.1.3. The supply water temperature (TSWT) (or inlet water
temperature (TIWT) if a recirculating loop is used) must be
maintained within ± 0.50 °F of the initial reading at the start of
the steady-state verification period; and
7.1.1.4. The rise between the supply (or inlet if a
recirculating loop is used) and outlet water temperatures must be
maintained within ± 0.50 °F of its initial value taken at the start
of the steady-state verification period for units with rated input
less than 500,000 Btu/h, and maintained within ± 1.00 °F of its
initial value for units with rated input greater than or equal to
500,000 Btu/h.
7.2. Thermostatically-Activated Instantaneous Water Heaters
with an Internal Thermostat. For water heaters that will
experience cut-in based on a temperature-activated control that is
internal to the water heater, use the following steps to conduct
the standby loss test.
7.2.1. Immediately after the thermal efficiency test or the
steady-state verification period (as applicable), turn off the
outlet water valve(s) (installed as per the provisions in section
2.2 of this appendix), and the water pump (if applicable)
simultaneously and ensure that there is no flow of water through
the water heater.
7.2.2. After the first cut-out following the end of the
thermal efficiency test or steady-state verification period (as
applicable), allow the water heater to remain in standby mode. Do
not change any settings on the water heater at any point until
measurements for the standby loss test are finished. Begin
recording the applicable parameters specified in section 3.9.2 of
this appendix.
7.2.3. At the second cut-out, record the time and ambient
room temperature, and begin measuring the fuel and electricity
consumption. Record the initial heat exchanger outlet water
temperature (TOHX) and initial ambient room temperature. For the
remainder of the test, continue recording the applicable parameters
specified in section 3.9.2 of this appendix.
7.2.4. Stop the test after the first cut-out that occurs
after 24 hours, or at 48 hours, whichever comes first.
7.2.5. Immediately after conclusion of the standby loss
test, record the total fuel flow and electrical energy consumption,
the final ambient room temperature, the duration of the standby
loss test, and if the test ends at 48 hours without a cut-out, the
final heat exchanger outlet temperature, or if the test ends after
a cut-out, the maximum heat exchanger outlet temperature that
occurs after the cut-out. Calculate the average of the recorded
values of the heat exchanger outlet water temperature and the
ambient room temperature taken at each measurement interval,
including the initial and final values.
7.2.6. Standby Loss Calculation. To calculate the
standby loss, follow the steps below:
7.2.6.1. The standby loss expressed as a percentage (per
hour) of the heat content of the stored water above room
temperature must be calculated using the following equation:
Where:
ΔT3 = Average value of the heat exchanger outlet water temperature
(TOHX) minus the average value of the ambient room temperature,
expressed in °F ΔT4 = Final heat exchanger outlet water temperature
(TOHX) measured at the end of the test minus the initial heat
exchanger outlet water temperature (TOHX) measured at the start of
the test, expressed in °F K = 8.25 Btu/gallon· °F, the nominal
specific heat of water Va = Volume of water contained in the water
heater in gallons measured in accordance with section 4 of this
appendix Et = Thermal efficiency of the water heater determined in
accordance with section 6 of this appendix, expressed in % Ec =
Electrical energy consumed by the water heater during the duration
of the test in Btu T = Total duration of the test in hours Cs =
Correction applied to the heating value of a gas H, when it is
metered at temperature and/or pressure conditions other than the
standard conditions for which the value of H is based. Cs=1 for
oil-fired equipment. Qs = Total fuel flow as metered, expressed in
ft 3 (gas) or lb (oil) H = Higher heating value of gas or oil,
expressed in Btu/ft 3 (gas) or Btu/lb (oil) S = Standby loss, the
average hourly energy required to maintain the stored water
temperature expressed as a percentage of the initial heat content
of the stored water above room temperature
7.2.6.2. The standby loss expressed in Btu per hour must be
calculated as follows:
SL (Btu per hour) = S (% per hour) × 8.25 (Btu/gal- °F) ×
Measured Volume (gal) × 70 ( °F).
Where, SL refers to the standby loss of the water heater,
defined as the amount of energy required to maintain the stored
water temperature expressed in Btu per hour.
7.3. Flow-Activated and Thermostatically-Activated
Instantaneous Water Heaters with an External Thermostat. For
water heaters that are either flow-activated or
thermostatically-activated with an external thermostat, use the
following steps to conduct the standby loss test.
7.3.1. Immediately after the thermal efficiency test or the
steady-state verification period (as applicable), de-energize the
primary control to end the call for heating. If the main burners do
not cut out, then turn off the fuel supply.
7.3.1.1. If the unit does not have an integral pump purge
functionality, then turn off the outlet water valve and water pump
at this time.
7.3.1.2. If the unit has an integral pump purge functionality,
allow the pump purge operation to continue. After the pump purge
operation is complete, immediately turn off the outlet water valve
and water pump and continue recording the required parameters for
the remainder of the test.
7.3.2. Recording Data
7.3.2.1. For units with pump purge functionality, record the
initial heat exchanger outlet water temperature (TOHX), and ambient
room temperature when the main burner(s) cut-out or the fuel supply
is turned off. After the pump purge operation is complete, record
the time as t = 0 and the initial electricity meter reading.
Continue to monitor and record the heat exchanger outlet water
temperature (TOHX) and time elapsed from the start of the test, and
the electricity consumption as per the requirements in section
3.9.2 of this appendix.
7.3.2.2. For units not equipped with pump purge
functionality, begin recording the measurements as per the
requirements of section 3.9.2 of this appendix when the main
burner(s) cut-out or the fuel supply is turned off. Specifically,
record the time as t = 0, and record the initial heat exchanger
outlet water temperature (TOHX), ambient room temperature, and
electricity meter readings. Continue to monitor and record the heat
exchanger outlet water temperature (TOHX) and the time elapsed from
the start of the test as per the requirements in section 3.9.2 of
this appendix.
7.3.3. Stopping Criteria. Stop the test when one of the
following occurs:
7.3.3.1. The heat exchanger outlet water temperature (TOHX)
decreases by 35 °F from its value recorded immediately after the
main burner(s) has cut-out, and the pump purge operation (if
applicable) is complete; or
7.3.3.2. 24 hours have elapsed from the start of the test.
7.3.4. At the end of the test, record the final heat exchanger
outlet water temperature (TOHX), fuel consumed, electricity
consumed from time t=0, and the time elapsed from the start of the
test.
7.3.5. Standby Loss Calculation
7.3.5.1. Once the test is complete, use the following equation
to calculate the standby loss as a percentage (per hour) of the
heat content of the stored water above room temperature:
Where,
ΔT1 = Heat exchanger outlet water temperature (TOHX) measured after
the pump purge operation is complete (if the unit is integrated
with pump purge functionality); or after the main burner(s) cut-out
(if the unit is not equipped with pump purge functionality) minus
heat exchanger outlet water temperature (TOHX) measured at the end
of the test, expressed in °F ΔT2 = Heat exchanger outlet water
temperature (TOHX) minus the ambient temperature, both measured
after the main burner(s) cut-out, at the start of the test,
expressed in °F K = 8.25 Btu/gallon· °F, the nominal specific heat
of water Va = Volume of water contained in the water heater in
gallons measured in accordance with section 4 of this appendix Et =
Thermal efficiency of the water heater determined in accordance
with section 6 of this appendix, expressed in % Ec = Electrical
energy consumed by the water heater during the duration of the test
in Btu t = Total duration of the test in hours S = Standby loss,
the average hourly energy required to maintain the stored water
temperature expressed as a percentage of the initial heat content
of the stored water above room temperature
7.3.5.2. The standby loss expressed in terms of Btu per hour
must be calculated as follows:
SL (Btu per hour) = S (% per hour) × 8.25 (Btu/gal- °F) ×
Measured Volume (gal) × 70 ( °F)
Where, SL refers to the standby loss of the water heater,
defined as the amount of energy required to maintain the stored
water temperature expressed in Btu per hour.
[81 FR 79332, Nov. 10, 2016]
Appendix C to Subpart R of Part 431 - Uniform Test Method for the Measurement of Net Capacity and AWEF of Walk-In Cooler and Walk-In Freezer Refrigeration Systems
10:3.0.1.4.19.18.85.7.61 : Appendix C
Appendix C to Subpart R of Part 431 - Uniform Test Method for the
Measurement of Net Capacity and AWEF of Walk-In Cooler and Walk-In
Freezer Refrigeration Systems 1.0 Scope
This appendix covers the test requirements used to determine the
net capacity and the AWEF of the refrigeration system of a walk-in
cooler or walk-in freezer.
2.0 Definitions
The definitions contained in § 431.302 and AHRI 1250-2009
(incorporated by reference; see § 431.303) apply to this appendix.
When definitions in standards incorporated by reference are in
conflict or when they conflict with this section, the hierarchy of
precedence shall be in the following order: § 431.302, AHRI
1250-2009, and then either AHRI 420-2008 (incorporated by
reference; see § 431.303) for unit coolers or ASHRAE 23.1-2010
(incorporated by reference; see § 431.303) for dedicated condensing
units.
3.0 Test Methods, Measurements, and Calculations
Determine the Annual Walk-in Energy Factor (AWEF) and net
capacity of walk-in cooler and walk-in freezer refrigeration
systems by conducting the test procedure set forth in AHRI
1250-2009 (incorporated by reference; see § 431.303), with the
modifications to that test procedure provided in this section. When
standards that are incorporated by reference are in conflict or
when they conflict with this section, the hierarchy of precedence
shall be in the following order: § 431.302, AHRI 1250-2009, and
then either AHRI 420-2008 (incorporated by reference; see §
431.303) or ASHRAE 23.1-2010 (incorporated by reference; see §
431.303).
3.1. General modifications: Test Conditions and
Tolerances.
When conducting testing in accordance with AHRI 1250-2009
(incorporated by reference; see § 431.303), the following
modifications must be made.
3.1.1. In Table 1, Instrumentation Accuracy, refrigerant
temperature measurements shall have a tolerance of ±0.5 F for unit
cooler in/out, ±1.0 F for all other temperature measurements.
3.1.2. In Table 2, Test Operating and Test Condition Tolerances
for Steady-State Test, electrical power frequency shall have a Test
Condition Tolerance of 1 percent.
3.1.3. In Table 2, the Test Operating Tolerances and Test
Condition Tolerances for Air Leaving Temperatures shall be
deleted.
3.1.4. In Tables 2 through 14, the Test Condition Outdoor Wet
Bulb Temperature requirement and its associated tolerance apply
only to units with evaporative cooling.
3.1.5. Tables 15 and 16 shall be modified to read as
follows:
Table 15 - Refrigerator Unit Cooler
Test
description
Unit cooler air entering
dry-bulb, °F
Unit cooler air entering
relative
humidity, %
Saturated
suction temp, °F
Liquid inlet saturation temp,
°F
Liquid inlet subcooling temp,
°F
Compressor
capacity
Test objective
Off Cycle Fan
Power
35
<50
-
-
-
Compressor Off
Measure fan input power during
compressor off cycle.
Refrigeration
Capacity Suction A
35
<50
25
105
9
Compressor On
Determine Net Refrigeration
Capacity of Unit Cooler.
Refrigeration
Capacity Suction B
35
<50
20
105
9
Compressor On
Determine Net Refrigeration
Capacity of Unit Cooler.
Note: Superheat to be set according to
equipment specification in equipment or installation manual. If no
superheat specification is given, a default superheat value of 6.5
°F shall be used. The superheat setting used in the test shall be
reported as part of the standard rating.
Table 16 - Freezer Unit Cooler
Test
description
Unit cooler air entering
dry-bulb, °F
Unit cooler air entering
relative
humidity, %
Saturated
suction temp, °F
Liquid inlet saturation temp,
°F
Liquid inlet subcooling temp,
°F
Compressor
capacity
Test objective
Off Cycle Fan
Power
−10
<50
-
-
-
Compressor Off
Measure fan input power during
compressor off cycle.
Refrigeration
Capacity Suction A
−10
<50
−20
105
9
Compressor On
Determine Net Refrigeration
Capacity of Unit Cooler.
Refrigeration
Capacity Suction B
−10
<50
−26
105
9
Compressor On
Determine Net Refrigeration
Capacity of Unit Cooler.
Defrost
−10
Various
-
-
-
Compressor Off
Test according to Appendix C
Section C11.
Note: Superheat to be set according to
equipment specification in equipment or installation manual. If no
superheat specification is given, a default superheat value of 6.5
°F shall be used. The superheat setting used in the test shall be
reported as part of the standard rating.
3.2. General Modifications: Methods of Testing
When conducting testing in accordance with appendix C of AHRI
1250-2009 (incorporated by reference; see § 431.303), the following
modifications must be made.
3.2.1. In appendix C, section C3.1.6, any refrigerant
temperature measurements upstream and downstream of the unit cooler
may use sheathed sensors immersed in the flowing refrigerant
instead of thermometer wells.
3.2.2. It is not necessary to perform composition analysis of
refrigerant (appendix C, section C3.3.6) or refrigerant oil
concentration testing (appendix C, section C3.4.6).
3.2.3. In appendix C, section C3.4.5, for verification of
sub-cooling downstream of mass flow meters, only the sight glass
and a temperature sensor located on the tube surface under the
insulation are required.
3.2.4. In appendix C, section C3.5, regarding unit cooler fan
power measurements, for a given motor winding configuration, the
total power input shall be measured at the highest nameplate
voltage. For three-phase power, voltage imbalances shall be no more
than 2 percent from phase to phase.
3.2.5. In the test setup (appendix C, section C8.3), the liquid
line and suction line shall be constructed of pipes of the
manufacturer-specified size. The pipe lines shall be insulated with
a minimum total thermal resistance equivalent to 1/2-inch thick
insulation having a flat-surface R-Value of 3.7 ft 2- °F-hr/Btu per
inch or greater. Flow meters need not be insulated but must not be
in contact with the floor. The lengths of the connected liquid line
and suction line shall be 25 feet ± 3 inches, not including the
requisite flow meters, each. Of this length, no more than 15 feet
shall be in the conditioned space. Where there are multiple
branches of piping, the maximum length of piping applies to each
branch individually as opposed to the total length of the
piping.
3.3. Matched systems, single-package dedicated systems, and
unit coolers tested alone: Use the test method in AHRI
1250-2009 (incorporated by reference; see § 431.303), appendix C as
the method of test for matched refrigeration systems,
single-package dedicated systems, or unit coolers tested alone,
with the following modifications:
3.3.1. For unit coolers tested alone, use test procedures
described in AHRI 1250-2009 (incorporated by reference; see §
431.303) for testing unit coolers for use in mix-match system
ratings, except that for the test conditions in Tables 15 and 16,
use the Suction A saturation condition test points only. Also for
unit coolers tested alone, use the calculations in section 7.9 to
determine AWEF and net capacity described in AHRI 1250-2009 for
unit coolers matched to parallel rack systems.
3.3.2. In appendix C, section C.13, the version of AHRI Standard
420 used for test methods, requirements, and procedures shall be
AHRI 420-2008 (incorporated by reference; see § 431.303).
3.3.3. Use appendix C, section C10 of AHRI 1250-2009 for
off-cycle evaporator fan testing, with the exception that
evaporator fan controls using periodic stir cycles shall be
adjusted so that the greater of a 50% duty cycle (rather than a 25%
duty cycle) or the manufacturer default is used for measuring
off-cycle fan energy. For adjustable-speed controls, the greater of
50% fan speed (rather than 25% fan speed) or the manufacturer's
default fan speed shall be used for measuring off-cycle fan energy.
Also, a two-speed or multi-speed fan control may be used as the
qualifying evaporator fan control. For such a control, a fan speed
no less than 50% of the speed used in the maximum capacity tests
shall be used for measuring off-cycle fan energy.
3.3.4. Use appendix C, section C11 of AHRI 1250-2009
(incorporated by reference, see § 431.303) for defrost testing. The
Frost Load Condition Defrost Test (C11.1.1) is optional.
3.3.4.1. If the frost load condition defrost test is
performed:
3.3.4.1.1 Operate the unit cooler at the dry coil conditions as
specified in appendix C, section C11.1 to obtain dry coil defrost
energy, DFd, in W-h.
3.3.4.1.2 Operate the unit cooler at the frost load conditions
as specified in appendix C, sections C11.1 and C11.1.1 to obtain
frosted coil defrost energy, DFf, in W-h.
3.3.4.1.3 The number of defrosts per day, NDF, shall be
calculated from the time interval between successive defrosts from
the start of one defrost to the start of the next defrost at the
frost load conditions.
3.3.4.1.4 Use appendix C, equations C13 and C14 in section C11.3
to calculate, respectively, the daily average defrost energy, DF,
in W-h and the daily contribution of the load attributed to defrost
QDF in Btu.
3.3.4.1.5 The defrost adequacy requirements in appendix C,
section C11.3 shall apply.
3.3.4.2 If the frost load test is not performed:
3.3.4.2.1 Operate the unit cooler at the dry coil conditions as
specified in appendix C, section C11.1 to obtain dry coil defrost
energy, DFd, in W-h.
3.3.4.2.2 The frost load defrost energy, DFf, in W-h shall be
equal to 1.05 multiplied by the dry coil energy consumption, DFd,
measured using the dry coil condition test in appendix C, section
C11.1.
3.3.4.2.3 The number of defrosts per day NDF used in subsequent
calculations shall be 4.
3.3.4.2.4 Use appendix C, equation C13 in section C11.3 to
calculate the daily average defrost energy, DF, in W-h.
3.3.4.2.5 The daily contribution of the load attributed to
defrost QDF in Btu shall be calculated as follows:
Where:
DFd = the defrost energy, in W-h, measured at the dry coil
condition
3.3.5. If a unit has adaptive defrost, use appendix C, section
C11.2 of AHRI 1250-2009 as follows:
3.3.5.1. When testing to certify to the energy conservation
standards in § 431.306, do not perform the optional test for
adaptive or demand defrost in appendix C, section C11.2.
3.3.5.2. When determining the represented value of the
calculated benefit for the inclusion of adaptive defrost, conduct
the optional test for adaptive or demand defrost in appendix C,
section C11.2 to establish the maximum time interval allowed
between dry coil defrosts. If this time is greater than 24 hours,
set its value to 24 hours. Then, calculate NDF (the number of
defrosts per day) by averaging the time in hours between successive
defrosts for the dry coil condition with the time in hours between
successive defrosts for the frosted coil condition, and dividing 24
by this average time. (The time between successive defrosts for the
frosted coil condition is found as specified in section 3.3.4 of
this appendix C of AHRI 1250-2009: That is, if the optional frosted
coil test was performed, the time between successive defrosts for
the frosted coil condition is found by performing the frosted coil
test as specified in section 3.3.4.1 of this appendix; and if the
optional frosted coil test was not performed, the time between
successive defrosts for the frosted coil condition shall be set to
4 as specified in section 3.3.4.2. of this appendix) Use this new
value of NDF in subsequent calculations.
3.3.6. For matched refrigeration systems and single-package
dedicated systems, calculate the AWEF using the calculations in
AHRI 1250-2009 (incorporated by reference; see § 431.303), section
7.4, 7.5, 7.6, or 7.7, as applicable.
3.3.7. For unit coolers tested alone, calculate the AWEF and net
capacity using the calculations in AHRI 1250-2009, (incorporated by
reference; see § 431.303), section 7.9. If the unit cooler has
variable-speed evaporator fans that vary fan speed in response to
load, then:
3.3.7.1. When testing to certify compliance with the energy
conservation standards in § 431.306, fans shall operate at full
speed during on-cycle operation. Do not conduct the calculations in
AHRI 1250-2009, section 7.9.3. Instead, use AHRI 1250-2009, section
7.9.2 to determine the system's AWEF.
3.3.7.2. When calculating the benefit for the inclusion of
variable-speed evaporator fans that modulate fan speed in response
to load for the purposes of making representations of efficiency,
use AHRI 1250-2009, section 7.9.3 to determine the system AWEF.
3.4. Dedicated condensing units that are not matched for testing
and are not single-package dedicated systems
3.4.1. Refer to appendix C, section C.12 of AHRI 1250-2009
(incorporated by reference; see § 431.303), for the method of test
for dedicated condensing units. The version of ASHRAE Standard 23
used for test methods, requirements, and procedures shall be
ANSI/ASHRAE Standard 23.1-2010 (incorporated by reference; see §
431.303). When applying this test method, use the applicable test
method modifications listed in sections 3.1 and 3.2 of this
appendix. For the test conditions in AHRI 1250-2009, Tables 11, 12,
13, and 14, use the Suction A condition test points only.
3.4.2. Calculate the AWEF and net capacity for dedicated
condensing units using the calculations in AHRI 1250-2009
(incorporated by reference; see § 431.303) section 7.8. Use the
following modifications to the calculations in lieu of unit cooler
test data:
3.4.2.1. For calculating enthalpy leaving the unit cooler to
calculate gross capacity, (a) The saturated refrigerant temperature
(dew point) at the unit cooler coil exit, Tevap, shall be 25 °F for
medium-temperature systems (coolers) and −20 °F for low-temperature
systems (freezers), and (b) the refrigerant temperature at the unit
cooler exit shall be 35 °F for medium-temperature systems (coolers)
and −14 °F for low-temperature systems (freezers). For calculating
gross capacity, the measured enthalpy at the condensing unit exit
shall be used as the enthalpy entering the unit cooler.
3.4.2.2. The on-cycle evaporator fan power in watts, EFcomp,on,
shall be calculated as follows:
For medium-temperature systems (coolers), EFcomp,on = 0.013 ×
qmix,cd
For low-temperature systems (freezers), EFcomp,on = 0.016 ×
qmix,cd
Where: qmix,cd is the gross cooling capacity of the system in
Btu/h, found by a single test at the Capacity A, Suction A
condition for outdoor units and the Suction A condition for indoor
units.
3.4.2.3. The off-cycle evaporator fan power in watts,
EFcomp,off, shall be calculated as follows:
EFcomp,off = 0.2 × EFcomp,on
Where: EF comp,on is the on-cycle evaporator fan power in watts.
3.4.2.4. The daily defrost energy use in watt-hours, DF, shall
be calculated as follows:
For medium-temperature systems (coolers), DF = 0
For low-temperature systems (freezers), DF = 8.5 × 10−3 ×
qmix,cd 1.27 × NDF
Where: qmix,cd is the gross cooling capacity of the system in
Btu/h, found by a single test at the Capacity A, Suction A
condition for outdoor units and the Suction A condition for indoor
units, and NDF is the number of defrosts per day, equal to 4.
3.4.2.5. The daily defrost heat load contribution in Btu, QDF,
shall be calculated as follows:
For medium-temperature systems (coolers), QDF = 0
For low-temperature systems (freezers), QDF = 0.95 × DF ×
3.412
Where: DF is the daily defrost energy use in watt-hours. 3.5 Hot
Gas Defrost Refrigeration Systems
For all hot gas defrost refrigeration systems, remove the hot
gas defrost mechanical components and disconnect all such
components from electrical power.
3.5.1 Hot Gas Defrost Dedicated Condensing Units Tested Alone:
Test these units as described in section 3.4 of this appendix for
electric defrost dedicated condensing units that are not matched
for testing and are not single-package dedicated systems.
3.5.2 Hot Gas Defrost Matched Systems, Single-package Dedicated
Systems, and Unit Coolers Tested Alone: Test these units as
described in section 3.3 of this appendix for electric defrost
matched systems, single-package dedicated systems, and unit coolers
tested alone, but do not conduct defrost tests as described in
sections 3.3.4 and 3.3.5 of this appendix. Calculate daily defrost
energy use as described in section 3.4.2.4 of this appendix.
Calculate daily defrost heat contribution as described in section
3.4.2.5 of this appendix.
[81 FR 95803, Dec. 28, 2016]
Appendix C to Subpart Y of Part 431 - Uniform Test Method for the Measurement of Energy Efficiency of Dedicated-Purpose Pool Pumps
10:3.0.1.4.19.25.89.7.66 : Appendix C
Appendix C to Subpart Y of Part 431 - Uniform Test Method for the
Measurement of Energy Efficiency of Dedicated-Purpose Pool Pumps
Note:
Any representations made on or after July 19, 2021, with respect
to the energy use or efficiency of dedicated-purpose pool pumps
subject to testing pursuant to 10 CFR 431.464(b) must be made in
accordance with the results of testing pursuant to this
appendix.
I. Test Procedure for Dedicated-Purpose Pool Pumps A. General
A.1 Test Method. To determine the weighted energy factor (WEF)
for dedicated-purpose pool pumps, perform “wire-to-water” testing
in accordance with HI 40.6-2014-B, except section 40.6.4.1,
“Vertically suspended pumps”; section 40.6.4.2, “Submersible
pumps”; section 40.6.5.3, “Test report”; section 40.6.5.5, “Test
conditions”; section 40.6.5.5.2, “Speed of rotation during
testing”; section 40.6.6.1, “Translation of test results to rated
speed of rotation”; section 40.6.6.2, “Pump efficiency”; section
40.6.6.3, “Performance curve”; section A.7, “Testing at
temperatures exceeding 30 °C (86 °F)”; and appendix B, “Reporting
of test results”; (incorporated by reference, see § 431.463) with
the modifications and additions as noted throughout the provisions
below. Do not use the test points specified in section 40.6.5.5.1,
“Test procedure” of HI 40.6-2014-B and instead use those test
points specified in section D.3 of this appendix for the applicable
dedicated-purpose pool pump variety and speed configuration. When
determining overall efficiency, best efficiency point, or other
applicable pump energy performance information, section 40.6.5.5.1,
“Test procedure”; section 40.6.6.2, “Pump efficiency”; and section
40.6.6.3, “Performance curve” must be used, as applicable. For the
purposes of applying this appendix, the term “volume per unit
time,” as defined in section 40.6.2, “Terms and definitions,” of HI
40.6-2014-B shall be deemed to be synonymous with the term “flow
rate” used throughout that standard and this appendix .
A.2 Calculations and Rounding. All terms and quantities refer to
values determined in accordance with the procedures set forth in
this appendix for the rated pump. Perform all calculations using
raw measured values without rounding. Round WEF, maximum head,
vertical lift, and true priming time values to the tenths place
(i.e., 0.1) and rated hydraulic horsepower to the
thousandths place (i.e., 0.001). Round all other reported
values to the hundredths place unless otherwise specified.
B. Measurement Equipment
B.1 For the purposes of measuring flow rate, speed of rotation,
temperature, and pump power output, the equipment specified in HI
40.6-2014-B Appendix C (incorporated by reference, see § 431.463)
necessary to measure head, speed of rotation, flow rate, and
temperature must be used and must comply with the stated accuracy
requirements in HI 40.6-2014-B Table 40.6.3.2.3, except as
specified in sections B.1.1 and B.1.2 of this appendix. When more
than one instrument is used to measure a given parameter, the
combined accuracy, calculated as the root sum of squares of
individual instrument accuracies, must meet the specified accuracy
requirements.
B.1.1 Electrical measurement equipment for determining the
driver power input to the motor or controls must be capable of
measuring true root mean squared (RMS) current, true RMS voltage,
and real power up to the 40th harmonic of fundamental supply source
frequency, and have a combined accuracy of ±2.0 percent of the
measured value at the fundamental supply source frequency.
B.1.2 Instruments for measuring distance (e.g., height
above the reference plane or water level) must be accurate to and
have a resolution of at least ±0.1 inch.
B.2 Calibration. Calibration requirements for instrumentation
are specified in appendix D of HI 40.6-2014-B (incorporated by
reference, see § 431.463). Historical calibration data may be used
to justify time periods up to three times longer than those
specified in table D.1 of HI 40.6-2014-B provided the supporting
historical data shows maintenance of calibration of the given
instrument up to the selected extended calibration interval on at
least two unique occasions, based on the interval specified in HI
40.6-2014-B.
C. Test Conditions and Tolerances
C.1 Pump Specifications. Conduct testing at full impeller
diameter in accordance with the test conditions, stabilization
requirements, and specifications of HI 40.6-2014-B section 40.6.3,
“Pump efficiency testing”; section 40.6.4, “Considerations when
determining the efficiency of a pump”; section 40.6.5.4 (including
appendix A), “Test arrangements”; and section 40.6.5.5, “Test
conditions” (incorporated by reference, see § 431.463).
C.2 Power Supply Requirements. The following conditions also
apply to the mains power supplied to the DPPP motor or controls, if
any:
(1) Maintain the voltage within ±5 percent of the rated value of
the motor,
(2) Maintain the frequency within ±1 percent of the rated value
of the motor,
(3) Maintain the voltage unbalance of the power supply within ±3
percent of the value with which the motor was rated, and
(4) Maintain total harmonic distortion below 12 percent
throughout the test.
C.3 Test Conditions. Testing must be carried out with water that
is between 50 and 107 °F with less than or equal to 15
nephelometric turbidity units (NTU).
C.4 Tolerances. For waterfall pumps, multi-speed self-priming
and non-self-priming pool filter pumps, and variable-speed
self-priming and non-self-priming pool filter pumps all measured
load points must be within ±2.5 percent of the specified head value
and comply with any specified flow values or thresholds. For all
other dedicated-purpose pool pumps, all measured load points must
be within the greater of ±2.5 percent of the specified flow rate
values or ±0.5 gpm and comply with any specified head values or
thresholds.
D. Data Collection and Stabilization
D.1 Damping Devices. Use of damping devices, as described in
section 40.6.3.2.2 of HI 40.6-2014-B (incorporated by reference,
see § 431.463), are only permitted to integrate up to the data
collection interval used during testing.
D.2 Stabilization. Record data at any tested load point only
under stabilized conditions, as defined in HI 40.6-2014-B section
40.6.5.5.1 (incorporated by reference, see § 431.463), where a
minimum of two measurements are used to determine
stabilization.
D.3 Test Points. Measure the flow rate in gpm, pump total head
in ft, the driver power input in W, and the speed of rotation in
rpm at each load point specified in Table 1 of this appendix for
each DPPP variety and speed configuration:
Table 1 - Load Points (i) and Weights (wi)
for Each DPPP Variety and Speed Configuration
DPPP
varieties
Speed
configuration(s)
Number of load
points
(n)
Load point
(i)
Test points
Flow rate
(Q) (GPM)
Head
(H) (ft)
Speed
(rpm)
Self-Priming Pool
Filter Pumps And Non-Self-Priming Pool Filter Pumps
Single-speed dedicated-purpose
pool pumps and all self-priming and non-self-priming pool filter
pumps not meeting the definition of two-*, multi-, or
variable-speed dedicated-purpose pool pump
1
High
Qhigh (gpm) = Qmax_speed@C
**
H = 0.0082 × Qhigh
2
Maximum speed.
Two-speed dedicated-purpose
pool pumps *
2
Low
Qlow (gpm) = Flow rate
associated with specified head and speed that is not below:
• 31.1 gpm if rated hydraulic horsepower is >0.75 or
• 24.7 gpm if rated hydraulic horsepower is ≤0.75
H = 0.0082 × Qlow
2
Lowest speed capable of
meeting the specified flow and head values, if any. ***
High
Qhigh (gpm) = Qmax_speed@C
**
H = 0.0082 × Qlow
2
Maximum speed.
Multi-speed and variable-speed
dedicated-purpose pool pumps
2
Low
Qlow (gpm) =
• If rated hydraulic horsepower is >0.75, then Qlow ≥31.1
gpm
• If rated hydraulic horsepower is ≤0.75, then Qlow ≥24.7 gpm
H = 0.0082 × Qlow
2
Lowest speed capable of
meeting the specified flow and head values.
High
Qhigh (gpm) ≥0.8 ×
Qmax_speed@C **
H = 0.0082 × Qhigh
2
Lowest speed capable of
meeting the specified flow and head values.
Waterfall
Pumps
Single-speed dedicated-purpose
pool pumps
1
High
Qlow (gpm) = Flow
corresponding to specified head
17.0 ft
Maximum speed.
Pressure Cleaner
Booster Pumps
Any
1
High
10.0 gpm
≥60.0 ft
Lowest speed capable of
meeting the specified flow and head values.
* In order to apply the test points for
two-speed self-priming and non-self-priming pool filter pumps,
self-priming pool filter pumps that are greater than or equal to
0.711 rated hydraulic horsepower that are two-speed
dedicated-purpose pool pumps must also be distributed in commerce
either: (1) With a pool pump control (variable speed drive and user
interface or switch) that changes the speed in response to
pre-programmed user preferences and allows the user to select the
duration of each speed and/or the on/off times or (2) without a
pool pump control that has such capability, but without which the
pump is unable to operate. Two-speed self-priming pool filter pumps
greater than or equal to 0.711 rated hydraulic horsepower that do
not meet these requirements must be tested using the load point for
single-speed self-priming or non-self-priming pool filter pumps, as
appropriate.
** Qmax_speed@C = Flow at max speed on curve
C (gpm).
*** If a two-speed pump has a low speed that
results in a flow rate below the specified values, the low speed of
that pump shall not be tested.
E. Calculations
E.1 Determination of Weighted Energy Factor. Determine the WEF
as a ratio of the measured flow and driver power input to the
dedicated-purpose pool pump in accordance with the following
equation:
Where:
WEF = Weighted Energy Factor in kgal/kWh; Wi =
weighting factor at each load point i, as specified in
section E.2 of this appendix; Qi = flow at each load point
i, in gpm; Pi = driver power input to the motor (or
controls, if present) at each load point i, in watts;
i = load point(s), defined uniquely for each DPPP variety
and speed configuration as specified in section D.3 of this
appendix; and n = number of load point(s), defined uniquely
for each DPPP variety and speed configuration as specified in
section D.3 of this appendix.
E.2 Weights. When determining WEF, apply the weights specified
in Table 2 of this appendix for the applicable load points, DPPP
varieties, and speed configurations:
Table 2 - Load Point Weights (wi)
DPPP
varieties
Speed
configuration(s)
Load point(s)
i
Low flow
High flow
Self-Priming Pool
Filter Pumps and Non-Self-Priming Pool Filter Pumps
Single-speed dedicated-purpose
pool pumps and all self-priming and non-self-priming pool filter
pumps not meeting the definition of two-*, multi-, or
variable-speed dedicated-purpose pool pump
1.0
Two-speed dedicated-purpose
pool pumps *
0.80
0.20
Multi-speed and variable-speed
dedicated-purpose pool pumps
0.80
0.20
Waterfall
Pumps
Single-speed dedicated-purpose
pool pumps
1.0
Pressure Cleaner
Booster Pump
Any
1.0
* In order to apply the test points for
two-speed self-priming and non-self-priming pool filter pumps,
self-priming pool filter pumps that are greater than or equal to
0.711 rated hydraulic horsepower that are two-speed
dedicated-purpose pool pumps must also be distributed in commerce
either: (1) With a pool pump control (variable speed drive and user
interface or switch) that changes the speed in response to
pre-programmed user preferences and allows the user to select the
duration of each speed and/or the on/off times or (2) without a
pool pump control that has such capability, but without which the
pump is unable to operate. Two-speed self-priming pool filter pumps
greater than or equal to 0.711 rated hydraulic horsepower that do
not meet these requirements must be tested using the load point for
single-speed self-priming or non-self-priming pool filter pumps, as
appropriate.
E.3 Determination of Horsepower and True Power Factor
Metrics
E.3.1 Determine the pump power output at any load point i
using the following equation:
Where:
Pu,i = the measured pump power output at load point i
of the tested pump, in hp; Qi = the measured flow rate at
load point i of the tested pump, in gpm; Hi = pump
total head at load point i of the tested pump, in ft; and
SG = the specific gravity of water at specified test
conditions, which is equivalent to 1.00.
E.3.1.1 Determine the rated hydraulic horsepower as the pump
power output measured on the reference curve at maximum rotating
speed and full impeller diameter for the rated pump.
E.3.2 For dedicated-purpose pool pumps with single-phase AC
motors or DC motors, determine the dedicated-purpose pool pump
nominal motor horsepower as the product of the measured full load
speed and torque, adjusted to the appropriate units, as shown in
the following equation:
Where:
Pnm = the dedicated-purpose pool pump nominal total
horsepower at full load, in hp; T = output torque at full
load, in lb-ft; and n = the motor speed at full load, in rpm.
Full-load speed and torque shall be determined based on the
maximum continuous duty motor power output rating allowable for the
motor's nameplate ambient rating and insulation class.
E.3.2.1 For single-phase AC motors, determine the measured speed
and torque at full load according to either section E.3.2.1.1 or
E.3.2.1.2 of this appendix.
E.3.2.1.1 Use the procedures in section 3.2, “Tests with load”;
section 4 “Testing facilities”; section 5.2 “Mechanical
measurements”; section 5.3 “Temperature measurements”; and section
6 “Tests” of IEEE 114-2010 (incorporated by reference, see §
431.463), or
E.3.2.1.2 Use the applicable procedures in section 5, “General
test requirements” and section 6, “Tests” of CSA C747-2009 (RA
2014); except in section 6.4(b) the conversion factor shall be
5252, only measurements at full load are required in section 6.5,
and section 6.6 shall be disregarded (incorporated by reference,
see § 431.463).
E.3.2.2 For DC motors, determine the measured speed and torque
at full load according to either section E.3.2.2.1 or E.3.2.2.2 of
this appendix.
E.3.2.2.1 Use the procedures in section 3.1, “Instrument
Selection Factors”; section 3.4 “Power Measurement”: Section 3.5
“Power Sources”; section 4.1.2 “Ambient Air”; section 4.1.4
“Direction of Rotation”; section 5.4.1 “Reference Conditions”; and
section 5.4.3.2 “Dynomometer or Torquemeter Method” of IEEE
113-1985 (incorporated by reference, see § 431.463), or
E.3.2.2.2 Use the applicable procedures in section 5, “General
test requirements” and section 6, “Tests” of CSA C747-2009 (RA
2014); except in section 6.4(b) the conversion factor shall be
5252, only measurements at full load are required in section 6.5,
and section 6.6 shall be disregarded (incorporated by reference,
see § 431.463).
E.3.3 For dedicated-purpose pool pumps with single-phase AC
motors or DC motors, the dedicated-purpose pool pump service factor
is equal to 1.0.
E.3.4 Determine the dedicated-purpose pool pump motor total
horsepower according to section E.3.4.1 of this appendix for
dedicated-purpose pool pumps with single-phase AC motors or DC
motors and section E.3.4.2 of this appendix for dedicated-purpose
pool pumps with polyphase AC motors.
E.3.4.1 For dedicated-purpose pool pumps with single-phase AC
motors or DC motors, determine the dedicated-purpose pool pump
motor total horsepower as the product of the dedicated-purpose pool
pump nominal motor horsepower, determined in accordance with
section E.3.2 of this appendix, and the dedicated-purpose pool pump
service factor, determined in accordance with section E.3.3 of this
appendix.
E.3.4.2 For dedicated-purpose pool pumps with polyphase AC
induction motors, determine the dedicated-purpose pool pump motor
total horsepower as the product of the rated nominal motor
horsepower and the rated service factor of the motor.
E.3.5 Determine the true power factor at each applicable load
point specified in Table 1 of this appendix for each DPPP variety
and speed configuration as a ratio of driver power input to the
motor (or controls, if present) (Pi), in watts, divided by
the product of the voltage in volts and the current in amps at each
load point i, as shown in the following equation:
Where:
PFi = true power factor at each load point i,
dimensionless; Pi = driver power input to the motor (or
controls, if present) at each load point i, in watts;
Vi = voltage at each load point i, in volts;
Ii = current at each load point i, in amps; and
i = load point(s), defined uniquely for each DPPP variety
and speed configuration as specified in section D.3 of this
appendix.
E.4 Determination of Maximum Head. Determine the maximum head
for self-priming pool filter pumps, non-self-priming pool filter
pumps, and waterfall pumps by measuring the head at maximum speed
and the minimum flow rate at which the pump is designed to operate
continuously or safely, where the minimum flow rate is assumed to
be zero unless stated otherwise in the manufacturer literature.
F. Determination of Self-Priming Capability
F.1 Test Method. Determine the vertical lift and true priming
time of non-self-priming pool filter pumps and self-priming pool
filter pumps that are not already certified as self-priming under
NSF/ANSI 50-2015 (incorporated by reference, see § 431.463) by
testing such pumps pursuant to section C.3 of appendix C of
NSF/ANSI 50-2015, except for the modifications and exceptions
listed in the following sections F.1.1 through F.1.5 of this
appendix:
F.1.1 Where section C.3.2, “Apparatus,” and section C.3.4,
“Self-priming capability test method,” of NSF/ANSI 50-2015
(incorporated by reference, see § 431.463) state that the “suction
line must be essentially as shown in annex C, figure C.1;” the
phrase “essentially as shown in Annex C, figure C.1” means:
(1) The centerline of the pump impeller shaft is situated a
vertical distance equivalent to the specified vertical lift (VL),
calculated in accordance with section F.1.1.1. of this appendix,
above the water level of a water tank of sufficient volume as to
maintain a constant water surface level for the duration of the
test;
(2) The pump draws water from the water tank with a riser pipe
that extends below the water level a distance of at least 3 times
the riser pipe diameter (i.e., 3 pipe diameters);
(3) The suction inlet of the pump is at least 5 pipe diameters
from any obstructions, 90° bends, valves, or fittings; and
(4) The riser pipe is of the same pipe diameter as the pump
suction inlet.
F.1.1.1 The vertical lift (VL) must be normalized to 5.0 feet at
an atmospheric pressure of 14.7 psia and a water density of 62.4
lb/ft 3 in accordance with the following equation:
Where:
VL = vertical lift of the test apparatus from the waterline
to the centerline of the pump impeller shaft, in ft; ρtest =
density of test fluid, in lb/ft 3; and Pabs,test = absolute
barometric pressure of test apparatus location at centerline of
pump impeller shaft, in psia.
F.1.2 The equipment accuracy requirements specified in section
B, “Measurement Equipment,” of this appendix also apply to this
section F, as applicable.
F.1.2.1 All measurements of head (gauge pressure), flow, and
water temperature must be taken at the pump suction inlet and all
head measurements must be normalized back to the centerline of the
pump impeller shaft in accordance with section A.3.1.3.1 of HI
40.6-2014-B (incorporated by reference, see § 431.463).
F.1.3 All tests must be conducted with clear water that meets
the requirements adopted in section C.3 of this appendix.
F.1.4 In section C.3.4, “Self-priming capability test method,”
of NSF/ANSI 50-2015 (incorporated by reference, see § 431.463),
“the elapsed time to steady discharge gauge reading or full
discharge flow” is determined when the changes in head and flow,
respectively, are within the tolerance values specified in table
40.6.3.2.2, “Permissible amplitude of fluctuation as a percentage
of mean value of quantity being measured at any test point,” of HI
40.6-2014-B (incorporated by reference, see § 431.463). The
measured priming time (MPT) is determined as the point in time when
the stabilized load point is first achieved, not when stabilization
is determined. In addition, the true priming time (TPT) is
equivalent to the MPT.
F.1.5 The maximum true priming time for each test run must not
exceed 10.0 minutes. Disregard section C.3.5 of NSF/ANSI 50-2015
(incorporated by reference, see § 431.463).
G. Optional Testing and Calculations
G.1 Replacement Dedicated-Purpose Pool Pump Motors. To determine
the WEF for replacement DPPP motors, test each replacement DPPP
motor paired with each dedicated-purpose pool pump bare pump for
which the replacement DPPP motor is advertised to be paired, as
stated in the manufacturer's literature for that replacement DPPP
motor model, according to the testing and calculations described in
sections A, B, C, D, and E of this appendix. Alternatively, each
replacement DPPP motor may be tested with the most consumptive
dedicated-purpose pool pump bare pump for which it is advertised to
be paired, as stated in the manufacturer's literature for that
replacement DPPP motor model. If a replacement DPPP motor is not
advertised to be paired with any specific dedicated-purpose pool
pump bare pumps, test with the most consumptive dedicated-purpose
pool pump bare pump available.
Where: Q
= Fuel input rate, expressed in Btu/h Qs = Total fuel flow as
metered, expressed in ft 3 for gas-fired equipment and lb for
oil-fired equipment Cs = Correction applied to the heating value of
a gas H, when it is metered at temperature and/or pressure
conditions other than the standard conditions for which the value
of H is based. Cs=1 for oil-fired equipment. H = Higher heating
value of the fuel, expressed as Btu/ft 3 for gas-fired equipment
and Btu/lb for oil-fired equipment. t = Duration of measurement of
fuel consumption
Where: K
= 1.004 Btu/lb· °F, the nominal specific heat of water at 105 °F W
= Total weight of water heated, lb θ1 = Average supply water
temperature, expressed in °F θ2 = Average outlet water temperature,
expressed in °F Q = Total fuel flow as metered, expressed in ft 3
(gas) or lb (oil) Cs = Correction applied to the heating value of a
gas H, when it is metered at temperature and/or pressure conditions
other than the standard conditions for which the value of H is
based. Cs=1 for oil-fired equipment. H = Higher heating value of
the fuel, expressed in Btu/ft 3 (gas) or Btu/lb (oil) Ec =
Electrical consumption of the water heater and, when used, the test
set-up recirculating pump, expressed in Btu
Where:
ΔT3 = Average value of the heat exchanger outlet water temperature
(TOHX) minus the average value of the ambient room temperature,
expressed in °F ΔT4 = Final heat exchanger outlet water temperature
(TOHX) measured at the end of the test minus the initial heat
exchanger outlet water temperature (TOHX) measured at the start of
the test, expressed in °F K = 8.25 Btu/gallon· °F, the nominal
specific heat of water Va = Volume of water contained in the water
heater in gallons measured in accordance with section 4 of this
appendix Et = Thermal efficiency of the water heater determined in
accordance with section 6 of this appendix, expressed in % Ec =
Electrical energy consumed by the water heater during the duration
of the test in Btu T = Total duration of the test in hours Cs =
Correction applied to the heating value of a gas H, when it is
metered at temperature and/or pressure conditions other than the
standard conditions for which the value of H is based. Cs=1 for
oil-fired equipment. Qs = Total fuel flow as metered, expressed in
ft 3 (gas) or lb (oil) H = Higher heating value of gas or oil,
expressed in Btu/ft 3 (gas) or Btu/lb (oil) S = Standby loss, the
average hourly energy required to maintain the stored water
temperature expressed as a percentage of the initial heat content
of the stored water above room temperature
Where,
ΔT1 = Heat exchanger outlet water temperature (TOHX) measured after
the pump purge operation is complete (if the unit is integrated
with pump purge functionality); or after the main burner(s) cut-out
(if the unit is not equipped with pump purge functionality) minus
heat exchanger outlet water temperature (TOHX) measured at the end
of the test, expressed in °F ΔT2 = Heat exchanger outlet water
temperature (TOHX) minus the ambient temperature, both measured
after the main burner(s) cut-out, at the start of the test,
expressed in °F K = 8.25 Btu/gallon· °F, the nominal specific heat
of water Va = Volume of water contained in the water heater in
gallons measured in accordance with section 4 of this appendix Et =
Thermal efficiency of the water heater determined in accordance
with section 6 of this appendix, expressed in % Ec = Electrical
energy consumed by the water heater during the duration of the test
in Btu t = Total duration of the test in hours S = Standby loss,
the average hourly energy required to maintain the stored water
temperature expressed as a percentage of the initial heat content
of the stored water above room temperature
Where:
DFd = the defrost energy, in W-h, measured at the dry coil
condition
Where:
WEF = Weighted Energy Factor in kgal/kWh; Wi =
weighting factor at each load point i, as specified in
section E.2 of this appendix; Qi = flow at each load point
i, in gpm; Pi = driver power input to the motor (or
controls, if present) at each load point i, in watts;
i = load point(s), defined uniquely for each DPPP variety
and speed configuration as specified in section D.3 of this
appendix; and n = number of load point(s), defined uniquely
for each DPPP variety and speed configuration as specified in
section D.3 of this appendix.
Where:
Pu,i = the measured pump power output at load point i
of the tested pump, in hp; Qi = the measured flow rate at
load point i of the tested pump, in gpm; Hi = pump
total head at load point i of the tested pump, in ft; and
SG = the specific gravity of water at specified test
conditions, which is equivalent to 1.00.
Where:
Pnm = the dedicated-purpose pool pump nominal total
horsepower at full load, in hp; T = output torque at full
load, in lb-ft; and n = the motor speed at full load, in rpm.
Where:
PFi = true power factor at each load point i,
dimensionless; Pi = driver power input to the motor (or
controls, if present) at each load point i, in watts;
Vi = voltage at each load point i, in volts;
Ii = current at each load point i, in amps; and
i = load point(s), defined uniquely for each DPPP variety
and speed configuration as specified in section D.3 of this
appendix.
Where:
VL = vertical lift of the test apparatus from the waterline
to the centerline of the pump impeller shaft, in ft; ρtest =
density of test fluid, in lb/ft 3; and Pabs,test = absolute
barometric pressure of test apparatus location at centerline of
pump impeller shaft, in psia.