Loading (50 kb)...'
(continued)
where V S, V mx, v'n (or vn), and Wn are defined following Equation 3–1. For each outdoor bin temperature listed in Table 17, calculate the nominal temperature of the air leaving the heat pump condenser coil using,
Evaluate eh(Tj)/N , RH(Tj)/N, X(Tj), PLFj, and d(Tj) as specified in section 4.2.1 with the exception of replacing references to the H1C Test and section 3.6.1 with the H1C1 Test and section 3.6.2. For each bin calculation, use the space heating capacity and electrical power from Case 1 or Case 2, whichever applies.
Case 1. For outdoor bin temperatures where To(Tj) is equal to or greater than TCC (the maximum supply temperature determined according to section 3.1.9), determine Q h(Tj) and E h(Tj) as specified in section 4.2.2 (i.e. Q h(Tj) = Q hp(Tj) and E h(Tj) = E hp(Tj)). Note: Even though To(Tj) = TCC, resistive heating may be required; evaluate Equation 4.2.1–2 for all bins.
Case 2. For outdoor bin temperatures where To(Tj) < TCC, determine Q h(Tj) and E h(Tj) using,
Q h(Tj) = Q hp(Tj) + Q CC(Tj)
E h(Tj) = E hp(Tj) + E CC(Tj)
where,
Q CC(Tj) = m da · Cp,da · [TCC - To(Tj)]
Note: Even though To(Tj) < Tcc, additional resistive heating may be required; evaluate Equation
4.2.1–2 for all bins.
4.2.5.3 Heat pumps having a heat comfort controller: additional steps for calculating the HSPF of a heat pump having a two-capacity compressor. Calculate the space heating capacity and electrical power of the heat pump without the heat comfort controller being active as specified in section 4.2.3 for both high and low capacity and at each outdoor bin temperature, Tj, that is listed in Table 17. Denote these capacities and electrical powers by using the subscript “hp” instead of “h.” For the low capacity case, calculate the mass flow rate (expressed in pounds-mass of dry air per hour) and the specific heat of the indoor air (expressed in Btu/lbmda · °F) from the results of the H11 Test using:
where V s, V mx, v'n (or vn), and Wn are defined following Equation 3–1. For each outdoor bin temperature listed in Table 17, calculate the nominal temperature of the air leaving the heat pump condenser coil when operating at low capacity using,
Repeat the above calculations to determine the mass flow rate (m dak=2) and the specific heat of the indoor air (Cp,dak=2) when operating at high capacity by using the results of the H12 Test. For each outdoor bin temperature listed in Table 17, calculate the nominal temperature of the air leaving the heat pump condenser coil when operating at high capacity using,
Evaluate eh(Tj)/N, RH(Tj)/N, Xk=1(Tj), and/or Xk=2(Tj), PLFj, and d'(Tj) or d"(Tj) as specified in section 4.2.3.1. 4.2.3.2, 4.2.3.3, or 4.2.3.4, whichever applies, for each temperature bin. To evaluate these quantities, use the low-capacity space heating capacity and the low-capacity electrical power from Case 1 or Case 2, whichever applies; use the high-capacity space heating capacity and the high-capacity electrical power from Case 3 or Case 4, whichever applies.
Case 1. For outdoor bin temperatures where Tok=1(Tj) is equal to or greater than TCC (the maximum supply temperature determined according to section 3.1.9), determine Q hk=1(Tj) and E hk=1(Tj) as specified in section 4.2.3 (i.e., Q hk=1(Tj) = Q hpk=1(Tj) and E hk=1(Tj) = E hpk=1(Tj).
Note: Even though Tok=1(Tj) = TCC, resistive heating may be required; evaluate RH(Tj)/N for all bins.
Case 2. For outdoor bin temperatures where Tok=1(Tj) < TCC, determine Q hk=1(Tj) and E hk=1(Tj) using,
Q hk=1(Tj) = Q hpk=1(Tj) + Q CCk=1(Tj)
E hk=1(Tj) = E hpk=1(Tj) + E CCk=1(Tj)
where,
Note: Even though Tok=1(Tj) = Tcc, additional resistive heating may be required; evaluate RH(Tj)/N for all bins.
Case 3. For outdoor bin temperatures where Tok=2(Tj) is equal to or greater than TCC, determine Q hk=2(Tj) and E hk=2(Tj) as specified in section 4.2.3 (i.e., Q hk=2(Tj) = Q hpk=2(Tj) and E hk=2(Tj) = E hpk=2(Tj)).
Note: Even though Tok=2(Tj) < TCC, resistive heating may be required; evaluate RH(Tj)/N for all bins.
Case 4. For outdoor bin temperatures where Tok=2(Tj) < TCC, determine Q hk=2(Tj) and E hk=2(Tj) using,
where,
Note: Even though Tok=2(Tj) < Tcc, additional resistive heating may be required; evaluate RH(Tj)/N for all bins.
4.2.5.4 Heat pumps having a heat comfort controller: additional steps for calculating the HSPF of a heat pump having a variable-speed compressor. [Reserved]
4.3 Calculations of the Actual and Representative Regional Annual Performance Factors for Heat Pumps.
4.3.1 Calculation of actual regional annual performance factors (APFA) for a particular location and for each standardized design heating requirement.
where,
CLHA = the actual cooling hours for a particular location as determined using the map given in Figure 3, hr.
Q ck(95) = the space cooling capacity of the unit as determined from the A or A2 Test, whichever applies, Btu/h.
HLHA = the actual heating hours for a particular location as determined using the map given in Figure 2, hr.
DHR = the design heating requirement used in determining the HSPF; refer to section 4.2 and Definition 1.22, Btu/h.
C = defined in section 4.2 following Equation 4.2–2, dimensionless.
SEER = the seasonal energy efficiency ratio calculated as specified in section 4.1, Btu/W·h.
HSPF = the heating seasonal performance factor calculated as specified in section 4.2 for the generalized climatic region that includes the particular location of interest (see Figure 2), Btu/W·h. The HSPF should correspond to the actual design heating requirement (DHR), if known. If it does not, it may correspond to one of the standardized design heating requirements referenced in section 4.2.
4.3.2 Calculation of representative regional annual performance factors (APFR) for each generalized climatic region and for each standardized design heating requirement.
where,
CLHR = the representative cooling hours for each generalized climatic region, Table 19, hr.
HLHR = the representative heating hours for each generalized climatic region, Table 19, hr.
HSPF = the heating seasonal performance factor calculated as specified in section 4.2 for the each generalized climatic region and for each standardized design heating requirement within each region, Btu/W.h.
The SEER, Q ck(95), DHR, and C are the same quantities as defined in section 4.3.1. Figure 2 shows the generalized climatic regions. Table 18 lists standardized design heating requirements.
Table 19_Representative Cooling and Heating Load Hours for Each
Generalized Climatic Region
------------------------------------------------------------------------
Region CLHR HLHR
------------------------------------------------------------------------
I................................................. 2400 750
II................................................ 1800 1250
III............................................... 1200 1750
IV................................................ 800 2250
V................................................. 400 2750
VI................................................ 200 2750
------------------------------------------------------------------------
4.4. Rounding of SEER, HSPF, and APF for reporting purposes. After calculating SEER according to section 4.1, round it off as specified in subpart B 430.23(m)(3)(i) of Title 10 of the Code of Federal Regulations. Round section 4.2 HSPF values and section 4.3 APF values as per §430.23(m)(3)(ii) and (iii) of Title 10 of the Code of Federal Regulations.
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[70 FR 59135, Oct. 11, 2005]
Appendix N to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Furnaces and Boilers
top
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 shall be as specified in section 7 of ANSI/ASHRAE Standard 103–1993 except for the second paragraph of section 7.2.2.2 and 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. × 9 in. or 3 in. × 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 °F for temperature up to 100 °F above room temperature and less than 20 °F for temperature more than 100 °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 °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 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, °F
=TS,SS,X if stack gas temperature is measured, °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,
=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+yIGPEIG+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+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 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:
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 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.]
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[62 FR 26157, May 12, 1997, as amended at 62 FR 53510, Oct. 14, 1997]
Appendix O to Subpart B of Part 430–Uniform Test Method for Measuring the Energy Consumption of Vented Home Heating Equipment
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1.0 Definitions
1.1 “Air shutter” means an adjustable device for varying the size of the primary air inlet(s) to the combustion chamber power burner.
1.2 “Air tube” means a tube which carries combustion air from the burner fan to the burner nozzle for combustion.
1.3 “Barometic draft regulator or barometric damper” means a mechanical device designed to maintain a constant draft in a vented heater.
1.4 “Draft hood” means an external device which performs the same function as an integral draft diverter, as defined in section 1.17 of this appendix.
1.5 “Electro-mechanical stack damper” means a type of stack damper which is operated by electrical and/or mechanical means.
1.6 “Excess air” means air which passes through the combustion chamber and the vented heater flues in excess of that which is theoretically required for complete combustion.
1.7 “Flue” means a conduit between the flue outlet of a vented heater and the integral draft diverter, draft hood, barometric damper or vent terminal through which the flue gases pass prior to the point of draft relief.
1.8 “Flue damper” means a device installed between the furnace and the integral draft diverter, draft hood, barometric draft regulator, or vent terminal which is not equipped with a draft control device, designed to open the venting system when the appliance is in operation and to close the venting system when the appliance is in a standby condition.
1.9 “Flue gases” means reaction products resulting from the combustion of a fuel with the oxygen of the air, including the inerts and any excess air.
1.10 “Flue losses” means the sum of sensible and latent heat losses above room temperature of the flue gases leaving a vented heater.
1.11 “Flue outlet” means the opening provided in a vented heater for the exhaust of the flue gases from the combustion chamber.
1.12 “Heat input” (Qin) means the rate of energy supplied in a fuel to a vented heater operating under steady-state conditions, expressed in Btu's per hour. It includes any input energy to the pilot light and is obtained by multiplying the measured rate of fuel consumption by the measured higher heating value of the fuel.
1.13 “Heating capacity” (Qout) means the rate of useful heat output from a vented heater, operating under steady-state conditions, expressed in Btu's per hour. For room and wall heaters, it is obtained by multiplying the “heat input” (Qin) by the steady-state efficency (?ss) divided by 100. For floor furnaces, it is obtained by multiplying (A) the “heat input” (Qin) by (B) the steady-state efficiency divided by 100, minus the quantity (2.8) (Lj) divided by 100, where Lj is the jacket loss as determined in section 3.2 of this appendix.
1.14 “Higher heating value” (HHV) means the heat produced per unit of fuel when complete combustion takes place at constant pressure and the products of combustion are cooled to the initial temperature of the fuel and air and when the water vapor formed during combustion is condensed. The higher heating value is usually expressed in Btu's per pound, Btu's per cubic foot for gaseous fuel, or Btu's per gallon for liquid fuel.
1.15 “Induced draft” means a method of drawing air into the combustion chamber by mechanical means.
1.16 “Infiltration parameter” means that portion of unconditioned outside air drawn into the heated space as a consequence of loss of conditioned air through the exhaust system of a vented heater.
1.17 “Integral draft diverter” means a device which is an integral part of a vented heater, designed to: (1) Provide for the exhaust of the products of combustion in the event of no draft, back draft, or stoppage beyond the draft diverter, (2) prevent a back draft from entering the vented heater, and (3) neutralize the stack action of the chimney or gas vent upon the operation of the vented heater.
1.18 “Manually controlled vented heaters” means either gas or oil fueled vented heaters equipped without thermostats.
1.19 “Modulating control” means either a step-modulating or two-stage control.
1.20 “Power burner” means a vented heater burner which supplies air for combustion at a pressure exceeding atmospheric pressure, or a burner which depends on the draft induced by a fan incorporated in the furnace for proper operation.
1.21 “Reduced heat input rate” means the factory adjusted lowest reduced heat input rate for vented home heating equipment equipped with either two stage thermostats or step-modulating thermostats.
1.22 “Single stage thermostat” means a thermostat that cycles a burner at the maximum heat input rate and off.
1.23 “Stack” means the portion of the exhaust system downstream of the integral draft diverter, draft hood or barometric draft regulator.
1.24 “Stack damper” means a device installed downstream of the integral draft diverter, draft hood, or barometric draft regulator, designed to open the venting system when the appliance is in operation and to close off the venting system when the appliance is in the standby condition.
1.25 “Stack gases” means the flue gases combined with dilution air that enters at the integral draft diverter, draft hood or barometric draft regulator.
1.26 “Steady-state conditions for vented home heating equipment” means equilibrium conditions as indicated by temperature variations of not more than 5 °F (2.8C) in the flue gas temperature for units equipped with draft hoods, barometric draft regulators or direct vent systems, in three successive readings taken 15 minutes apart or not more than 3 °F (1.7C) in the stack gas temperature for units equipped with integral draft diverters in three successive readings taken 15 minutes apart.
1.27 “Step-modulating control” means a control that either cycles off and on at the low input if the heating load is light, or gradually, increases the heat input to meet any higher heating load that cannot be met with the low firing rate.
1.28 “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 into movement of the damper plate.
1.29 “Two stage control” means a control that either cycles a burner at the reduced heat input rate and off or cycles a burner at the maximum heat input rate and off.
1.30 “Vaporizing-type oil burner” means a device with an oil vaporizing bowl or other receptacle designed to operate by vaporizing liquid fuel oil by the heat of combustion and mixing the vaporized fuel with air.
1.31 “Vent/air intake terminal” means a device which is located on the outside of a building and is connected to a vented heater by a system of conduits. It is composed of an air intake terminal through which the air for combustion is taken from the outside atmosphere and a vent terminal from which flue gases are discharged.
1.32 “Vent limiter” means a device which limits the flow of air from the atmospheric diaphragm chamber of a gas pressure regulator to the atmosphere. A vent limiter may be a limiting orifice or other limiting device.
1.33 “Vent pipe” means the passages and conduits in a direct vent system through which gases pass from the combustion chamber to the outdoor air.
2.0 Testing conditions.
2.1 Installation of test unit.
2.1.1 Vented wall furnaces (including direct vent systems). Install gas fueled vented wall furnaces for test as specified in sections 2.1.3 and 2.1.4 of ANSI Z21.49–1975. Install gas fueled wall furnaces with direct vent systems for test as described in sections 2.1.3 and 2.1.4 of ANSI Z21.44–1973. Install oil fueled vented wall furnaces as specified in UL–730–1974, section 33. Install oil fueled vented wall furnaces with direct vent systems as specified in UL–730–1974, section 34.
2.1.2 Vented floor furnaces. Install vented floor furnaces for test as specified in sections 35.1 through 35.5 of UL–729–1976.
2.1.3 Vented room heaters. Install in accordance with manufacturer's instructions.
2.2 Flue and stack requirements.
2.2.1 Gas fueled vented home heating equipment employing integral draft diverters and draft hoods (excluding direct vent systems). Attach to, and vertically above the outlet of gas fueled vented home heating equipment employing draft diverters or draft hoods with vertically discharging outlets, a five (5) foot long test stack having a cross sectional area the same size as the draft diverter outlet.
Attach to the outlet of vented heaters having a horizontally discharging draft diverter or draft hood outlet a 90 degree elbow, and a five (5) foot long vertical test stack. A horizontal section of pipe may be used on the floor furnace between the diverter and the elbow if necessary to clear any framing used in the installation. Use the minimum length of pipe possible for this section. Use stack, elbow, and horizontal section with same cross sectional area as the diverter outlet.
2.2.2 Oil fueled vented home heating equipment (excluding direct vent systems). Use flue connections for oil fueled vented floor furnaces as specified in section 35 of UL 729–1976, sections 34.10 through 34.18 of UL 730–1974 for oil fueled vented wall furnaces and sections 36.2 and 36.3 of UL 896–1973 for oil fueled vented room heaters.
2.2.3 Direct vent systems. Have the exhaust/air intake system supplied by the manufacturer in place during all tests. Test units intended for installation with a variety of vent pipe lengths with the minimum length recommended by the manufacturer. Do not connect a heater employing a direct vent system to a chimney or induced draft source. Vent the gas solely on the provision for venting incorporated in the heater and the vent/air intake system supplied with it.
2.3 Fuel supply.
2.3.1 Natural gas. For a vented heater utilizing natural gas, maintain the gas supply to the unit under test at a normal inlet test pressure immediately ahead of all controls at 7 to 10 inches water column. Maintain the regulator outlet pressure at normal test pressure approximately at that recommended by the manufacturer. Use natural gas having a specific gravity of approximately 0.65 and a higher heating value within ±5 percent of 1,025 Btu's per standard cubic foot. Determine the actual higher heating value in Btu's per standard cubic foot for the natural gas to be used in the test with an error no greater than one percent.
2.3.2 Propane gas. For a vented heater utilizing propane gas, maintain the gas supply to the unit under test at a normal inlet pressure of 11 to 13 inches water column and a specific gravity of approximately 1.53. Maintain the regulator outlet pressure, on units so equipped, approximately at that recommended by the manufacturer. Use propane having a specific gravity of approximately 1.53 and a higher heating value within ±5 percent of 2,500 Btu's per standard cubic foot. Determine the actual higher heating value in Btu's per standard cubic foot for the propane to be used in the test with an error no greater than one percent.
2.3.3 Other test gas. Use other test gases with characteristics as described in section 2.2, table VII, of ANSI Standard Z21.11.1–1974. Use gases with a measured higher heating value within ±5 percent of the values specified in the above ANSI standard. Determine the actual higher heating value of the gas used in the test with an error no greater than one percent.
2.3.4 Oil supply. For a vented heater utilizing fuel oil, use No. 1, fuel oil (kerosene) for vaporizing-type burners and either No. 1 or No. 2 fuel oil, as specified by the manufacturer, for mechanical atomizing type burners. Use No. 1 fuel oil with a viscosity meeting the specifications as specified in UL–730–1974, section 36.9. Use test fuel conforming to the specifications given in tables 2 and 3 of ANSI Standard Z91.1–1972
for No. 1 and No. 2 fuel oil. Measure the higher heating value of the test fuel with an error no greater than one percent.
2.3.5 Electrical supply. For auxiliary electric components of a vented heater, maintain the electrical supply to the test unit within one percent of the nameplate voltage for the entire test cycle. If a voltage range is used for nameplate voltage, maintain the electrical supply within one percent of the mid-point of the nameplate voltage range.
2.4 Burner adjustments.
2.4.1 Gas burner adjustments. Adjust the burners of gas fueled vented heaters to their maximum Btu ratings at the test pressure specified in section 2.3 of this appendix. Correct the burner volumetric flow rate to 60 °F (15.6C) and 30 inches of mercury barometric pressure, set the fuel flow rate to obtain a heat rate of within ±2 percent of the hourly Btu rating specified by the manufacturer as measured after 15 minutes of operation starting with all parts of the vented heater at room temperature. Set the primary air shutters in accordance with the manufacturer's recommendations to give a good flame at this adjustment. Do not allow the deposit of carbon during any test specified herein.
If a vent limiting means is provided on a gas pressure regulator, have it in place during all tests.
For gas fueled heaters with modulating controls adjust the controls to operate the heater at the maximum fuel input rate. Set the thermostat control to the maximum setting. Start the heater by turning the safety control valve to the “on” position. In order to prevent modulation of the burner at maximum input, place the thermostat sensing element in a temperature control bath which is held at a temperature below the maximum set point temperature of the control. (continued)