NISTIR 7225 

A Curve-Based Mixed System Rating Method for 

Unitary Air Conditioners 

W. Vance Payne 

Piotr A. Domanski 

U.S. DEPARTMENT OF COMMERCE 

National Institute of Standards and Technology 

Building Environment Division 

Building and Fire Research Laboratory 

Gaithersburg, Maryland 20899-8631 

National Institute of Standards and Technology

Technology Administration

United States Department of Commerce 
NISTIR 7225 

A Curve-Based Mixed System Rating Method for 

Unitary Air Conditioners 

W. Vance Payne 

Piotr A. Domanski 

U.S. DEPARTMENT OF COMMERCE 

National Institute of Standards and Technology 

Building Environment Division 

Building and Fire Research Laboratory 

Gaithersburg, Maryland 20899-8631 

May 2005 

U.S. DEPARTMENT OF COMMERCE 

Carlos M. Gutierrez, Secretary 

TECHNOLOGY ADMINISTRATION 

Phillip J. Bond, Under Secretary of Commerce for Technology 

National Institute of Standards and Technology

Hratch Semerjian, Acting Director 

ii
TABLE OF CONTENTS 

List of Tables....................................................................................................................... iv 

List of Figures ..................................................................................................................... v 

Nomenclature...................................................................................................................... vii 

Abstract............................................................................................................................... 1 

Acknowledgement............................................................................................................... 2

 1: Introduction ............................................................................................................... 3 

 2: Tested Mixed Evaporators ........................................................................................ 4 

 3: Mixed Evaporator Capacity Determination ............................................................... 5 

3.1: Experimental setup....................................................................................... 5 

3.2: Data acquisition and measurement uncertainty ........................................... 6 

3.3: Test conditions and procedure..................................................................... 7 

3.4: Evaporator capacity curve fits and characterization..................................... 8 

 4: Mixed System Performance Prediction..................................................................... 16 

4.1: Calculation of Q(95), Q(82) and EER(82) .................................................... 16 

4.2: Calculation of SEER..................................................................................... 18 

 5: NIST Predictions and ARI Database Comparison .................................................... 20 

5.1: A-Test capacity comparison......................................................................... 20 

5.2: B-Test EER comparison............................................................................... 24 

5.3: SEER comparison........................................................................................ 27 

 6: Generating an Evaporator Capacity Line Using EVAP-COND ................................. 28 

 7: Uncertainty of the C-B Method.................................................................................. 30 

7.1: Uncertainty of the evaporator capacity linear fit ........................................... 30 

7.2: Uncertainty of C-B Method Q(95) and EER ................................................. 33 

 8: Concluding Remarks................................................................................................. 34 

References.......................................................................................................................... 37 

Appendix A: Evaporator Coil Descriptions ......................................................................... 39 

Appendix B: Uncertainty Analysis ...................................................................................... 48 

Appendix C: Cooling Measurement Summary Sheets....................................................... 57 

iii
List of Tables 

2.1: Tested mixed evaporators .......................................................................................... 5 

3.2.1: Measurement uncertainty ........................................................................................ 7 

3.3.1: Refrigerant conditions during evaporator tests ........................................................ 7 

3.4.1: Mixed evaporator capacity linear fit coefficients 

 and fan powers from NIST coil tests ........................................................................ 13 

4.1.1: CD Unit linear coefficients for power and capacity 

 at A-Test and B-Test conditions from ARI ............................................................... 16 

4.1.2: Mixed system A-Test capacity from the C-B Method............................................... 17 

4.1.3: Mixed system B-Test capacity, power, and EER from the C-B Method................... 18 

4.2.1: System classifications for cyclic degradation coefficient analysis............................ 19 

4.2.2: Cyclic degradation coefficient values for different system categories...................... 19 

4.2.3: Mixed system SEER calculated using statistically 

 determined CD for 95th and 99th percentiles............................................................. 20 

5.1.1: Mixed system A-Test capacities from ARI Tests and C-B Method .......................... 20 

5.1.2: Mixed system A-Test capacities from the ARI tests, 

 condensing unit capacities from CD Unit curves, and evaporator 

 capacities from NIST-developed evaporator capacity curves 

 at the ARI-test evaporating temperature.................................................................. 23 

5.1.3: Mixed system A-test capacities from ARI values 

 and evaporator capacities from NIST-developed evaporator 

 capacity curves at the ARI-test evaporating temperature ........................................ 23 

5.2.1: Mixed system B-Test comparison of ARI tested and C-B Method results ............... 26 

5.3.1: SEERs from ARI database and C-B Method ........................................................... 27 

6.1: EVAP-COND correction parameters for Coil 9 ........................................................... 28 

7.1.1: Coil 9 evaporator linear fit equation statistics .......................................................... 30 

7.1.2: Evaporator Q(95) linear fit uncertainty ..................................................................... 32 

7.2.1: C-B Method Q(95), Q(82), P(82), and EER uncertainty 

 at the 95 % confidence level on the mean value .................................................... 34 

iv
List of Figures 

1.1: Graphical illustration of the curve-based rating procedure ......................................... 4 

3.1.1: Evaporator test arrangement ................................................................................... 6 

3.4.1: Coil 1 cooling capacity as a function of outlet saturation temperature..................... 8 

3.4.2: Coil 2 cooling capacity as a function of outlet saturation temperature..................... 9 

3.4.3: Coil 3 cooling capacity as a function of outlet saturation temperature..................... 9 

3.4.4: Coil 4 cooling capacity as a function of outlet saturation temperature..................... 10 

3.4.5: Coil 5 cooling capacity as a function of outlet saturation temperature..................... 10 

3.4.6: Coil 6 cooling capacity as a function of outlet saturation temperature..................... 11 

3.4.7: Coil 7 cooling capacity as a function of outlet saturation temperature..................... 11 

3.4.8: Coil 8 cooling capacity as a function of outlet saturation temperature..................... 12 

3.4.9: Coil 9 cooling capacity as a function of outlet saturation temperature..................... 12 

3.4.10: Cooling capacity, q(95), for all evaporators based on NIST linear-fit..................... 14 

3.4.11: Airflow rate relative to cooling capacity from the NIST linear 

 fit for all coils at an evaporation temperature of 7.2 oC (45 oF) ............................. 15 

3.4.12: NIST measured SHR as a function of airflow rate per unit of cooling capacity 

 at an evaporator exit saturation temperature of 16.2 °C (50.0 °F)........................ 15 

5.1.1: Comparison of mixed system A-test capacities 

 from the ARI tests and the C-B method .................................................................. 21 

5.2.1: Percent differences between ARI Values and the 

 C-B Method for the EER(82) calculation.................................................................. 24 

5.3.1: ARI Values and C-B Method SEER/EER Multiplier, EER, and SEER ..................... 27 

6.1: Coil 9 simulated and measured cooling capacity........................................................ 29 

6.2: C-B Method Q(95), EER(82) and SEER ratio with 

 respect to the ARI database using the measured 

 and simulated Coil 9 capacity ..................................................................................... 29 

v
7.1.1: Coil 9 evaporator cooling capacity, confidence and error 

 bands on the mean predicted value of the cooling capacity 

 sampled at a particular evaporator saturation temperature ................................... 32 

vi
Nomenclature 

A EVAP-COND air-side heat transfer coefficient correction factor 

A-Test refers to ARI Standard 210/240 steady-state test conditions of 35 oC (95 oF)

outdoor air and 16.7 oC (80 oF) dry-bulb/ 19.4 oC (67 oF) wet-bulb indoor air 

conditions 

B-Test refers to ARI Standard 210/240 steady-state test conditions of 27.8 oC (82 oF) 

outdoor air and 16.7 oC (80 oF) dry-bulb/ 19.4 oC (67 oF) wet-bulb indoor air 

conditions 

CD cyclic degradation coefficient as defined in ARI Standard 210/240-2003 

C-B Method curve-based method as presented in this report 

CD Unit condensing unit, the outdoor section of the split air-conditioner 

CLF Cooling Load Factor as defined in ARI Standard 210/240-2003 

Diff abbreviation for difference 

DOF degrees of freedom 

EVAP-COND refers to evaporator and condenser simulation software available from NIST 

EER Energy Efficiency Ratio as calculated in ARI Standard 210/240-2003, W/W 

(Btu/W·h) 

m& mass flow rate, kg/h (lb/h) 

matched refers to a split air-conditioning system, an indoor section/condensing unit

combination, which rated performance is determined by laboratory testing; 

also may refer to the evaporator which is used in the matched system. 

mixed refers to a split air-conditioning system, an indoor section/condensing unit

combination, which rated performance is not determined by laboratory 

testing; also may refer to the evaporator which is used in the mixed system. 

n number of tests or number of data points 

P electrical power, W 

p(82) condensing unit power at B-Test condition (indoor fan power not included), W 

P(82) total power of air conditioner at B-Test condition (condensing unit power plus 

indoor fan power), W 

∆P EVAP-COND refrigerant-side pressure drop correction factor 

vii
Q Cooling capacity, W (Btu/h) 

q(82) cooling capacity at B-Test condition without accounting for indoor fan heat 

input, W (Btu/h) 

Q(82) cooling capacity at B-Test conditions with the indoor fan heat input

accounted for , W (Btu/h) 

q(95) cooling capacity at A-Test conditions without accounting for indoor fan heat

input, W (Btu/h) 

Q(95) cooling capacity at A-Test conditions with the indoor fan heat input

accounted for, W (Btu/h) 

ρ correlation coefficient 

R EVAP-COND refrigerant-side heat transfer coefficient correction factor 

scfm standard cubic feet per minute, which is equal to the equivalent volumetric

flowrate of air with a density of 0.075 lbm/ft3

SEER Seasonal Energy Efficiency Ratio as defined in ARI Standard 210/240-2003,

Btu/(W·h) 

SHR sensible heat ratio; the ratio of sensible capacity to total capacity 

σˆ data standard deviation or fit standard error 

SSE sum of squares of the error 

t or t-value percentage points of the t-distribution (Ott 1984) 

ton cooling or heating capacity equal to 12 000 Btu/h or 3.517 kW 

U absolute value of a quantity’s uncertainty 

Subscripts 

CD condensing unit of the split system air conditioner 

cyc cyclic testing 

diff difference 

dry dry-coil testing 

evap refers to the indoor coil or evaporator at saturated refrigerant conditions 

fan refers to the indoor coil fan 

mixed refers to the evaporator coil alone with respect to a system 

ref refrigerant 

ss steady-state 

viii
A Curve-Based Mixed System Rating Method 

for Unitary Air Conditioners 

W. Vance Payne and Piotr A. Domanski 

National Institute of Standards and Technology 

Abstract 

The curve-based method was evaluated based on performance predictions and independent 

laboratory testing for nine mixed systems. Capacity predictions were within ±5 % of the tested 

values for six of the mixed systems, and four of the SEER predictions were within ±5 % of the

tested SEERs. Predictions for SEER showed an under prediction bias due to the wide variation 

of possible values for the cyclic degradation coefficient (CD) and the necessity of assuming a

conservative value of CD in mixed system rating calculations. This report includes detailed

measurement data for the tested evaporators and an uncertainty analysis of the rating 

methodology. 

Keywords: air conditioner, cooling capacity, cyclic degradation coefficient, mixed system, rating

procedure, SEER 

1
ACKNOWLEDGEMENT*

This study was sponsored by the United States Department of Energy, Office of Building

Technology, State and Community Programs under contract DE-AI01-99EE27572 under 

project manager Michael Raymond. Mr. John Wamsley and Mr. Glen Glaeser provided

assistance with testing of the evaporator coils, operating the chambers, and analyzing data. Mr.

Brian Dougherty provided critical information on values of the degradation coefficient for cyclic 

operation for different equipment options. Mr. Stefan Leigh, of the NIST Statistical Engineering 

Division, assisted in the uncertainty analysis. Mr. Tim Corcoran and his staff at Intertek Testing 

Services (ITS) provided results from system tests. Mr. Michael Woodford and Ms. Sarah 

Medepalli of ARI provided technical and logistical support. Mr. Chad Kirkwood of United

Technologies, Carrier Corporation aided in formulating the scope of this project. The reviewers 

of the draft of this report were Mr. David Yashar of NIST, Mr. Carl Bergt of Rheem 

Manufacturing Company, Mr. Chad Kirkwood of United Technologies Carrier Corporation, and

Mr. Michael Woodford of the Air-Conditioning and Refrigeration Institute. 

 * Use of Non-SI Units in a NIST Publication: The policy of the National Institute of Standards and Technology is to

use the International System of Units (metric units) in all of its publications. However, in North America in the 

heating, ventilation and air-conditioning industry, certain non-SI units are so widely used instead of SI units that it is 

more practical and less confusing to include some measurement values in customary units only. 

2
1: INTRODUCTION 

A given condensing unit (outdoor section consisting of a condenser, compressor, and 

associated tubing) is typically offered on the market in several air-conditioner models, which

differ by the indoor sections they employ. For all models, the manufacturers must provide

performance information, which consists of the Seasonal Energy Efficiency Ratio (SEER) and

capacity at the 35 °C (95 °F) rating point, Q(95). Federal regulations require that only the

highest sales volume indoor-section/outdoor-section combination, referred to as the matched

system, be tested in a laboratory to obtain the ratings (CFR 2004a). For other combinations of

indoor and outdoor sections, so called mixed systems, the federal regulations allow the use of

simplified analytical methodologies upon approval by the U.S. Department of Energy (CFR 

2004b). 

The most commonly used simplified methodologies for rating mixed systems are those based

upon publicly available Q(95) and SEER of the matched systems (e.g., Domanski 1989). The 

application of these methods requires the rater to predict the capacity of the matched

evaporator, which is a major shortcoming because the rater is not often familiar with the

matched system product line. Since an inaccurate prediction of the matched evaporator leads 

directly to inaccurate mixed system ratings, a different rating method that would not include this 

step, e.g. the performance curve-based method (C-B Method), has the inherent potential to be a 

better rating approach than the one currently used. Recently, both coil and condensing unit 

manufacturers expressed interest in using the C-B Method to predict mixed system 

performance. 

Figure 1.1 shows the application of the C-B Method in a graphical form. This method uses

linear fits to the cooling capacity for the mixed coil, and cooling capacities, q(82) and q(95), and

power, p(82), for the condensing unit (CD Unit). The lines are presented as a function of the

compressor suction saturation temperature. Overlapping of the evaporator and CD Unit 

capacities provides mixed system capacities at 27.8 oC (82 oF) and 35.0 oC (95 oF) ambient 

temperatures. Projecting the saturation temperature corresponding with operation at the

27.8 oC (82 oF) ambient temperature on the CD Unit power chart provides the power 

requirement for the CD Unit at the 27.8 oC (82 oF) rating point. Figure 1.1 is convenient for 

explaining the C-B method. In real applications, this method is best implemented numerically 

using a computer. 

It should be noted that the rating process explained above is exclusive of the indoor fan power. 

Before the rating of the mixed system is finalized, the indoor fan power must be added to the 

CD Unit power to produce the power for the system at the 27.8 oC (82 oF) rating point P(82) The

indoor fan heat must also be included as heat reducing the cooling capacities q(95) and q(82)

obtained from overlapping the capacity lines of the CD Unit and mixed evaporator to produce 

actual mixed system capacities, Q(82) and Q(95). The energy efficiency ratio at the 27.8 oC 

(82 oF) rating point (EER(82)) can then be calculated using the corrected values of capacity,

Q(82), and power, P(82). 

(82)

(82) EER(82) PQ= 1.1

 

To conclude with the SEER calculation, the value of the cyclic degradation coefficient, CD, is 

required. 

3
SEER (1 0.5 C )EER(82) D = − ⋅ 1.2

The cyclic degradation coefficient, CD, has to be obtained from a separate analysis or the 

default value of 0.25 may be assumed. Condensing Unit Capacity

Saturation Temperature

q(82)

q(95)

Evaporator Capacit

y

Saturation Temperature

Po

wer

Saturation Temperature

p(82)

Compressor Condenser

Evaporator

Expansion

Device

CONDENSING UNIT

INDOOR AIR-HANDLER

Figure 1.1: Graphical illustration of the curve-based rating procedure 

The goal of this study was to evaluate the practicality and accuracy of the curve-based method 

through its application to nine mixed systems. In this effort, NIST assumed the role of an

evaporator manufacturer and developed cooling capacity lines for nine mixed evaporator coils.

After obtaining the needed condensing unit performance curves from the Air-Conditioning and

Refrigeration Institute (ARI) database, NIST developed mixed system ratings, and then

compared them to laboratory derived ratings obtained at an independent testing laboratory for

the ARI Unitary Equipment Certification Program. 

2: TESTED MIXED EVAPORATORS 

Table 2.1 shows basic information on the tested mixed evaporators. They were manufactured 

by several different companies and had different capacities. All evaporators were of the finnedtube design. Three evaporators were inclined slabs, four coils were constructed in an A-shape

configuration, and one in a semi-A-shape configuration. Three of the coils tested were 

equipped with a fan and required indoor fan power measurement. The remaining six coils were

intended to have field-installed fans. Appendix A presents detailed design data, circuitry 

configuration, and pictures of the coils. 

4
Table 2.1: Tested mixed evaporators 

Coil 

Number 

Coil 

Designation 

Coil 

Configuration

Airflow 

Direction 

Tube Outside

Diameter

Expansion 

Device Refrigerant 

1 A01102 A Horizontal 9.5 mm (0.375 in) TXV R22 

2 A01070 Semi A Horizontal 9.5 mm (0.375 in) Piston R22 

3 A01148 A Upflow 9.5 mm (0.375 in) TXV R22 

4 A01138 A Upflow 9.5 mm (0.375 in) Piston R22 

5 A01060* Inclined Slab Upflow/ 

Horizontal 9.5 mm (0.375 in) Piston R22 

6 A01125* Inclined Slab Horizontal 9.5 mm (0.375 in) TXV R22 

7 H5326 A Horizontal 9.5 mm (0.375 in) Piston R22 

8 H5321 A Upflow 9.5 mm (0.375 in) Piston R22 

9 A01154* Inclined Slab Horizontal 9.5 mm (0.375 in) TXV R410A 

*indoor fan included 

3: MIXED EVAPORATOR CAPACITY DETERMINATION 

3.1: Experimental setup 

Figure 3.1.1 shows the experimental setup. The evaporator was installed in the indoor

environmental chamber, where air conditions were controlled by a chiller/air handler system. Air 

was pulled through the evaporator by a centrifugal fan located at the outlet of the nozzle

chamber ductwork. The adjacent outdoor chamber housed the water-cooled condensing unit 

and the laboratory water-chiller. Two different condensing units were used for R22 and R410A 

evaporators due to lubricant-related considerations. Each condensing unit was equipped with a

variable-speed compressor, condenser, and subcooler. The water chiller control system 

manipulated the temperature and mass flow rate of the water delivered to the condensing unit. 

The chiller rejected heat to the in-house chilled water loop. Heat rejection was to water and did

not require maintaining the outdoor chamber conditions. 

 

The installation of the evaporator and test instrumentation conformed to ASHRAE Standard 37-

1989. We used the air enthalpy method for the primary measurement of the evaporator

capacity with the refrigerant enthalpy method providing the secondary measurement. Air dewpoint temperature was measured at the inlet of the evaporator ductwork and in the ductwork 

after the evaporator and several mixers. Twenty-five node thermocouple grids, located on each

side of the evaporator, were used to verify that the air was well mixed at each point. A 25-

junction thermopile measured the air temperature change across the evaporator. Barometric

pressure, evaporator air pressure drop, air temperature and pressure drop in the nozzle, and 

nozzle temperature were used along with the dew-point measurements to establish the 

thermodynamic state of the air. The refrigerant enthalpy method required measurement of the

evaporator inlet and exit refrigerant temperatures and pressures in addition to mass flowrate. 

The agreement between the air-side and refrigerant-side methods was always within 4 %. 

5
BOOSTER FAN NOZZLE CHAMBER

OUTDOOR CHAMBER

INDOOR CHAMBER

AIRFLOW

TEST EVAPORATOR

WATER-COOLED

CONDENSING UNIT

CONDENSER WATER LINES

Figure 3.1.1: Evaporator test arrangement 

3.2: Data acquisition and measurement uncertainty

The measurement points consisted of temperature, pressure, pressure difference, temperature

difference, dew-point temperature, fan amps, fan volts, and fan power. Table 3.2.1 lists the 

measured quantities and their uncertainties for a 95 % confidence limit (two sigma on the mean

value) (Taylor and Kuyatt 1994). The uncertainty for the evaporator capacity was calculated

using a propagation of uncertainty technique, considering the uncertainty in each of the

parameters associated with the capacity measurement. Appendix B explains the application of

this technique in more detail. 

6
Table 3.2.1: Measurement uncertainty 

Quantity Range Uncertainty

Pressure 0 kPa to 3447 kPa 

(0 psia to 500 psia) 

±3.4 kPa 

(±0.5 psi) 

Temperature -26.1 °C to 93.3 °C 

(-15 °F to 200 °F) 

±0.3 °C 

(±0.5 °F) 

Temperature Difference 0 °C to 27.8 °C 

(0 °F to 50 °F) 

±0.3 °C 

(±0.5 °F) 

Barometric Pressure 0 mm Hg to 1270 mm Hg 

(0 in Hg to 50 in Hg) 

±0.34 mm Hg 

(±0.0135 in Hg) 

Dew-point Temperature 0 °C to 50 °C 

(32 °F to 122 °F) 

±0.2 °C 

(±0.4 °F) 

Pressure Difference 0 Pa to 1244 Pa 

(0 in H2O to 5 in H2O) 

±24.4 Pa 

(±0.098 in H2O) 

Mass Flow 0 kg/h to 544.3 kg/h 

(0 lb/h to 1200.0 lb/h) ±1 % 

Evaporator Capacity 5.56 kW to 14.4 kW 

(19 kBtu/h to 49 kBtu/h) ±3 % to ±7 % 

3.3: Tests conditions and procedure 

Each evaporator coil was tested at the air volumetric flow rate that was used during mixed 

system tests carried out at an independent testing laboratory for the ARI certification program.

For all tests, constant indoor conditions of 16.7 °C (80.0 °F) dry-bulb and 15.8 °C (60.4 °F) dewpoint temperatures were applied according to ARI Standard 210/240 (2003). 

On the refrigerant side, the tests were constrained by the refrigerant inlet condition, defined by 

the liquid line temperature and subcooling, and the outlet condition, defined by the vapor line

saturation temperature and superheat. The tests of each evaporator involved three vapor

suction line saturation temperatures. The evaporator capacity line was generated as a function 

of the evaporator exit saturation temperature from these points. Table 3.3.1 lists the refrigerant 

conditions imposed during the evaporator tests for all coils. 

Table 3.3.1: Refrigerant conditions during evaporator tests 

Liquid line Vapor line 

Temperature 

 °C (°F) 

Subcooling 

°C (°F) 

Sat. temperature* 

 °C (°F) 

Superheat 

°C (°F) 

40.6 ± 0.8 

(105.0 ± 1.5) 

5.6 to 8.3 

(10.0 to 15.0) 

4.4, 7.2, 10.0 

(40.0, 45.0, 50.0) 

5.6 to 8.3 

(10.0 to 15.0) 

*Three nominal conditions 

The expansion devices supplied with the various evaporators were removed and replaced by 

precision needle valves. The liquid line temperature and subcooling, and evaporator superheat 

were controlled by adjusting the refrigerant charge and by changing the needle valve settings to 

produce the required superheat at the exit of the evaporator. In addition to compressor speed

7
control, an evaporator pressure regulating valve was used to produce the desired exit pressure. 

Liquid line temperature at the inlet to the expansion valves was also controlled by varying the 

water flow rates through the liquid cooled subcooler and condensing unit heat exchangers. At

least five tests were performed for each evaporator. If the evaporator was equipped with a fan,

its power was also measured and recorded for each test. 

3.4: Evaporator capacity curve fits and characterization 

Figures 3.4.1 through 3.4.9 present measured coil capacities, excluding fan heat when a fan

was used, as a function of the coil outlet saturation temperature. The figures also include a

linear fit to capacity data obtained for each evaporator and the fit coefficients. Examination of

the figures indicates that a linear capacity fit is an adequate representation of the measured 

data. Table 3.4.1 summarizes the cooling capacity linear slopes and intercepts. Appendix C 

gives detailed data summaries of the tests performed for each coil. 

We may note that the presented evaporator test data – including the performance lines – refers 

to the evaporator exit saturation temperature. The CD Unit curves also use the evaporator exit 

saturation temperature to calculate cooling capacity; i.e., they include the effect of refrigerant

pressure drop and heat transfer in the suction line. 

35 40 45 50 55

Evaporator Saturation Temperature (oF)

26000

28000

30000

32000

34000

36000

38000

40000

42000

44000

Capacity (Btu/h)

2 4 6 8 10 12

Evaporator Saturation Temperature (oC)

7.5

8

8.5

9

9.5

10

10.5

11

11.5

12

12.5

13

Capacity (kW)

Q = -1408.169088 * T(oF) + 99713.83312 [Btu/h]

 R-squared = 0.92746

Figure 3.4.1: Coil 1 cooling capacity as a function of outlet saturation temperature 

8
35 40 45 50 55

Evaporator Saturation Temperature (oF)

12000

14000

16000

18000

20000

22000

24000

26000

28000

30000

Capacity (Btu/h)

2 4 6 8 10 12

Evaporator Saturation Temperature (oC)

4

4.5

5

5.5

6

6.5

7

7.5

8

8.5

Cap

acity (kW)

Q = -1260.927942 * T(oF) + 76257.53535 [Btu/h]

 R-squared = 0.982203

Figure 3.4.2: Coil 2 cooling capacity as a function of outlet saturation temperature 

35 40 45 50 55

Evaporator Saturation Temperature (oF)

26000

28000

30000

32000

34000

36000

38000

40000

42000

44000

Capacit

y (Btu/h)

2 4 6 8 10 12

Evaporator Saturation Temperature (oC)

7.5

8

8.5

9

9.5

10

10.5

11

11.5

12

12.5

13

Capacity (kW)

Q = -1230.094948 * T(oF) + 90810.30383 [Btu/h]

 R-squared = 0.983193

Figure 3.4.3: Coil 3 cooling capacity as a function of outlet saturation temperature 

9
35 40 45 50 55

Evaporator Saturation Temperature (oF)

12000

14000

16000

18000

20000

22000

24000

26000

28000

30000

Capacity (Btu/h)

2 4 6 8 10 12

Evaporator Saturation Temperature (oC)

4

4.5

5

5.5

6

6.5

7

7.5

8

8.5

Capacity (kW)

Q = -921.2524165 * T(oF) + 63652.93591 [Btu/h]

 R-squared = 0.997177

Figure 3.4.4: Coil 4 cooling capacity as a function of outlet saturation temperature 

35 40 45 50 55

Evaporator Saturation Temperature (oF)

20000

22000

24000

26000

28000

30000

32000

34000

Capacity (Btu/h)

2 4 6 8 10 12

Evaporator Saturation Temperature (oC)

6

6.5

7

7.5

8

8.5

9

9.5

Capacity (kW)

Q = -999.4551142 * T(oF) + 73475.36349 [Btu/h]

 R-squared = 0.992904

Figure 3.4.5: Coil 5 cooling capacity as a function of outlet saturation temperature 

10
46 48 50 52 54 56 58 60

Evaporator Saturation Temperature (oF)

26000

28000

30000

32000

34000

36000

38000

40000

42000

44000

46000

48000

50000

Capacity (Btu/h)

8 10 12 14

Evaporator Saturation Temperature (oC)

7.5

8

8.5

9

9.5

10

10.5

11

11.5

12

12.5

13

13.5

14

14.5

Capacity (kW)

Q = -1985.52291 * T(oF) + 142185.5856 [Btu/h]

 R-squared = 0.966309

Figure 3.4.6: Coil 6 cooling capacity as a function of outlet saturation temperature 

30 35 40 45 50 55

Evaporator Saturation Temperature (oF)

20000

22000

24000

26000

28000

30000

32000

34000

Capacity (Btu/h)

0 2468 10 12

Evaporator Saturation Temperature (oC)

6

6.5

7

7.5

8

8.5

9

9.5

Capacity (kW)

Q = -840.9072638 * T(oF) + 63743.21106 [Btu/h]

 R-squared = 0.994431

Figure 3.4.7: Coil 7 cooling capacity as a function of outlet saturation temperature 

11
30 35 40 45 50 55

Evaporator Saturation Temperature (oF)

26000

28000

30000

32000

34000

36000

38000

40000

42000

44000

Capacity (Btu/h)

0 2468 10 12

Evaporator Saturation Temperature (oC)

8

8.5

9

9.5

10

10.5

11

11.5

12

12.5

Capacity (kW)

Q = -1453.11796 * T(oF) + 100753.6496 [Btu/h]

 R-squared = 0.985722

Figure 3.4.8: Coil 8 cooling capacity as a function of outlet saturation temperature 

35 40 45 50 55

Evaporator Saturation Temperature (oF)

10000

12000

14000

16000

18000

20000

22000

24000

26000

28000

30000

Ca

p

acity (Btu/h)

2468 10 12

Evaporator Saturation Temperature (oC)

3

3.5

4

4.5

5

5.5

6

6.5

7

7.5

8

8.5

Ca

p

a

city (kW)

Q = -1088.664402 * T(oF) + 71346.67439 [Btu/h]

 R-squared = 0.972835

Figure 3.4.9: Coil 9 cooling capacity as a function of outlet saturation temperature 

12
Table 3.4.1: Mixed evaporator capacity linear fit coefficients and fan powers from NIST coil 

tests 

Cooling Capacity Linear Coefficients Coil 

Number 

Evaporator 

Airflow 

m3

/h (scfm)

Fan 

Power 

W 

Slope 

W/oC (Btu/h·°F)

Intercept 

W (Btu/h) 

1 1699 (1000) 0 -742.8 (-1408.17) 29223.85 (99713.83) 

2 1368 (805) 0 -665.1(-1260.93) 22348.89 (76257.54) 

3 1621 (954) 0 -648.9 (-1230.09) 26613.89 (90810.3) 

4* 1342 (790) 0 -486.0 (-921.25) 18654.84 (63652.94) 

5 1279 (753) 271 -527.2 (-999.46) 21533.51 (73475.36) 

6 1954 (1150) 784 -1047.4 (-1985.52) 41670.51 (142185.6)

7 2047 (1205) 0 -443.6 (-840.91) 18681.3 (63743.21) 

8 2360 (1389) 0 -766.6 (-1453.12) 29527.99 (100753.65) 

9 849 (500) 364 -574.3 (-1088.66) 20909.65 (71346.67) 

* Coil 4 airflow was too high and results cannot be compared directly to ARI tests 

Figures 3.4.10 thru 3.4.12 help to characterize and contrast the performance of the nine 

evaporators with respect to one another. Figure 3.4.10 shows the cooling capacity of each coil 

as a function of the evaporator saturation temperature generated from the capacity linear fits at 

an evaporator temperature of 7.2 oC (45 oF). The plot indicates the relative values of a change

in capacity with respect to a change in evaporation temperature (slope) for each coil. 

Figure 3.4.11 presents the airflow rate per unit of capacity for all coils, which is an indication of

air temperature change across the coil. These values are from NIST tests at an evaporator

saturation temperature of 10 oC (50 oF). All NIST tests were intended to be performed at the

ARI Test airflow rates. Inadvertently, Coil 4 airflow was 262 m3

/h (154 scfm) higher than the

ARI Tests. Consequently, NIST capacity measurements and predictions for Coil 4 were

significantly higher (approximately 24 %) than would have been the case with correct lower

airflow rate. The results for Coil 4 have been included in this report, but they cannot be directly 

compared with the ARI Tests. The airflow rates at the other tests differed from the ARI Test 

values on average by 0.14 % with a standard deviation of 1.8 %. The average airflow rate per

unit cooling capacity was 0.1852 m3

/W h (383.5 scfm/ton) with a standard deviation of 0.0518

m3

/W h (107.1 scfm/ton). Coil 6 had the smallest airflow rate per unit capacity [0.1261 m3/W h 

(262 scfm/ton)] as well as the largest change in cooling capacity with respect to a change in

evaporator saturation temperature (see Figure 3.4.10). Coil 6 also had the lowest sensible heat 

ratio (SHR) of 0.710 (Fig. 3.4.12). Fig. 3.4.12 shows a linear trend of SHR with respect to 

airflow rate per unit capacity, which is consistent with general experience. The high sensible

heat ratios were due to the high evaporating temperature of 10 oC (50 oF). At the lowest 

evaporating temperatures tested at NIST, the highest SHR’s occurred for Coils 2, 7, and 8 with 

values of 0.77, 0.81, and 0.78, respectively. All other coils had SHR’s less than 75 % at the 

lowest tested evaporating temperature. 

13
35 40 45 50 55 60

Evaporator Saturation Temperature (oF)

10000

20000

30000

40000

50000

60000

Capacity (Btu/h)

R22, Coil #1, Horizontal, A-Coil

R22, Coil #2, Horizontal, U-Coil Slab

R22, Coil #3, A-Coil, Upflow

R22, Coil #4, A-Coil, Upflow

R22, Coil #5, Horizontal, Tilted Slab

2 4 6 8 10 12 14

Evaporator Saturation Temperature (oC)

2

4

6

8

10

12

14

16

18

Capacity (kW)

R22, Coil #6, Horizontal, Tilted Slab

R22, Coil #7, Horizontal, A-Coil

R22, Coil #8, A-Coil, Upflow

R410A, Coil #9, Horizontal, Tilted Slab

Figure 3.4.10: Cooling capacity, q(95), for all evaporators based on the NIST linear fit 

14
0.000

0.025

0.050

0.075

0.100

0.125

0.150

0.175

0.200

0.225

0.250

0.275

m3/(W.h)

0

100

200

300

400

500

600

SCFM / Ton

Coil 1

Coil 7

il 3

Coil 4

Coil 8

Co Coil 5

Coil 6 Coil 9

Coil 2

A-Coil Horizontal Flow

A-Coil Upflow

Slab Horizontal Flow

U-Coil Horizontal Flow

Figure 3.4.11: Airflow rate relative to cooling capacity from the NIST linear fit for all coils at an 

evaporation temperature of 7.2 oC (45 oF) 

(Note: Coil 4 airflow was too high and results cannot be compared directly to ARI tests)

200 300 400 500 600

SCFM / Ton 

0.6

0.7

0.8

0.9

1

Sensible Heat Ratio (Sensible Capacity / Total Capacity)

Coil 1

Coil 7

Coil 3

Coil 4

Coil 8

Coil 5

Coil 6

Coil 9

Coil 2

0.120 0.160 0.200 0.240 0.280

m3/W.h

0.6

0.7

0.8

0.9

1

Figure 3.4.12: NIST measured SHR as a function of airflow rate per unit of cooling capacity at 

an evaporator exit saturation temperature of 16.2 °C (50.0 °F) 

15
4: MIXED SYSTEM PERFORMANCE PREDICTION 

4.1: Calculation of Q(95), Q(82) and EER(82) 

With the coil capacity coefficients from Table 3.4.1 and CD Unit capacity coefficients from Table 

4.1.1, the C-B Method was used to calculate cooling capacity and EER at 27.8 °C (82.0 °F), and

cooling capacity at 35.0 °C (95.0 °F) for all coils. 

Table 4.1.1: CD Unit linear coefficients for power and capacity at A-Test and B-Test conditions 

from ARI 

q(82) p(82) q(95) p(95)

Coil Slope 

W/oC 

(Btu/h oF) 

Intercept 

W (Btu/h) 

Slope 

W/oC 

(W/oF) 

Intercept 

W 

Slope 

W/oC 

(Btu/h oF)

Intercept 

W (Btu/h) 

Slope 

W/oC 

(W/oF) 

Intercept 

W 

1 312.7

(592.7)

2092.9 

(7141.5) 

7.38 

(4.1) 

2340.0 300.2

(569.1)

2217.7 

(7567.0) 

5.76 

(3.2) 

2717.1 

2 184.7

(350.2)

2979.2 

(10165.6)

31.14 

(17.3)

1242.9 163.2

(309.3)

2785.3 

(9503.9) 

35.64 

(19.8)

1289.6 

3 312.7

(592.7)

2092.9 

(7141.5) 

7.38 

(4.1) 

2340.0 300.2

(569.1)

2217.7 

(7567.0) 

5.76 

(3.2) 

2717.1 

4* 237.1 

(449.5)

-622.6 

(-2124.6)

22.14 

(12.3)

880.9 232.2 

(440.2)

-1253.0 

(-4275.5)

26.1 

(14.5)

877.7 

5 266.2

(504.7)

674.2 

(2300.5) 

32.22 

(17.9)

1177.1 263.3

(499.2)

22.7 

(77.3)

38.7 

(21.5)

1069.6 

6 581.6

(1102.5) 

3886.6 

(13261.7)

28.98 

(16.1)

3584.9 564.6

(1070.2) 

2995.4 

(10220.7)

32.94 

(18.3)

4123.4 

7 484.1

(917.6)

-148.4 

(-506.2) 

31.68 

(17.6)

2253.8 508.6

(964.1)

-2569.6 

(-8767.8)

38.34 

(21.3)

2278.8 

8 96.8

(735.5)

3140.6 

(10716.2)

138.24 

(76.8)

36.4 336.6

(638) 

3420.9 

(11672.7)

172.8 

(96)

-697.3 

9 286.6

(543.2)

984.7 

(3359.9) 

10.8 

(6.0) 

1692.8 278.5

(528.0)

423.0 

(1443.2) 

11.52 

(6.4) 

1990.9 

*Coil 4 airflow was too high and results cannot be compared directly to ARI tests 

The calculation procedure, which we illustrated graphically in Figure 1.1, was implemented 

computationally by solving the set of two linear equations for the evaporation temperature at 

which the cooling capacity of the mixed coil equals the cooling capacity of the CD Unit: 

 

qCD = BCD + A CDTevap = qmixed = Bmixed + TevapA mixed 4.1.1

( )

( ) CD mixed

mixed CD

evap A A

B B

−

− T = 4.1.2

In the equations above, B represents the intercept and A represents the slope for the CD Unit

(CD subscript) and mixed evaporator (mixed subscript), respectively. Applying the obtained

value of the saturation temperature into either capacity equation yields the capacity of the

evaporator of the mixed system. The rated cooling capacity of the mixed system was obtained

by reducing the evaporator capacity by the fan heat. For coils equipped with a fan, the fan heat 

was measured; for other coils it was calculated according to ARI Standard 210/240 (ARI 2003). 

Q = q + Qfan 4.1.3

16
Similarly, the power of the mixed system was obtained by applying the value of the evaporator 

saturation temperature from equation 4.1.2 into the condensing unit power equation 4.1.4 and 

making adjustment for the indoor fan power as shown in equation 4.1.5. 

pCD = bCD + aCDTevap 4.1.4 

PCD = pCD + Pfan 4.1.5 

Table 4.1.2 shows the results for A-Test mixed system capacities. Table 4.1.3 presents the

results for B-Test capacity, power, and EER. 

Table 4.1.2: Mixed system A-Test capacity from the C-B Method 

Coil Tevap

°C (°F) 

q(95)

W 

(Btu/h) 

Indoor 

Airflow 

m3

/h 

(scfm) 

Qfan

(1)

W 

(Btu/h) 

Q(95)

W 

(Btu/h) 

1 8.1 (46.6) 9990 (34089) 1699 (1000) 366.3 (1250.0) 9624 (32839) 

2 5.8 (42.5) 6639 (22653) 1368 (805) 294.9 (1006.3) 6344 (21647) 

3 7.9 (46.3) 9935 (33898) 1621 (954) 349.5 (1192.5) 9585 (32705) 

4* 9.9 (49.9) 5184 (17688) 1342 (790) 289.4 (987.5) 4894 (16700) 

5 9.4 (49.0) 7188 (24526) 1279 (753) 271.0 (925.5) 6917 (23601) 

6 6.2 (43.2) 16541 (56439) 1954 (1150) 784.0 (2677.5) 15756 (53761) 

7 4.5 (40.2) 8781 (29962) 2047 (1205) 441.5 (1506.3) 8340 (28456) 

8 5.9 (42.6) 11386 (38851) 2360 (1389) 507.0 (1736.3) 10877 (37115) 

9 6.2 (43.2) 7114 (24274) 849 (500) 364.0 (1243.1) 6749 (23030) 

(1) For units with no fan Qfan was calculated to be 1250 Btu/h per 1000 scfm of airflow (ARI 210/240-2003). 

*Coil 4 airflow was too high and results cannot be compared directly to ARI tests 

17
Table 4.1.3: Mixed system B-Test capacity, power, and EER from the C-B Method 

Coil Tevap

 °C (°F)

q(82)

 W 

(Btu/h) 

pCD(82) 

 W 

Indoor 

Airflow, 

m3

/h (scfm) 

Qfan

(1)

 W 

(Btu/h) 

Pfan

(2)

W 

Q(82)

W, (Btu/h) 

EER(82) 

 W/W 

(Btu/W h) 

1 7.93 

(46.3)

10192 

(34563) 2530 1699 

(1000) 

365.0 

(1250.0) 365.0 9763 

(33313) 

3.37 

(11.51) 

2 5.01 

(41.0)

7190 

(24532) 1953 1368  (805) 

293.8 

(1006.3) 293.8 6895 (23525) 

3.07 

(10.47) 

3 7.72 

(45.9)

10066 

(34347) 2528 1621 

 (954) 

348.2 

(1192.5) 348.2 9717 

(33155) 

3.38 

(11.53) 

4* 8.88 

(48.0)

5699 

(19445) 1471 1342  (790) 

288.4 

(987.5) 288.4 5410 (18458) 

3.07 

(10.49) 

5 8.51 

(47.3)

7666 

(26182) 2024 1279 

 (753) 

271 

(924.7) 271.0 7402 

(25258) 

3.27 

(11.01) 

6 5.42 

(41.7)

17361 

(59291) 4257 1954 

(1150) 

784 

(2675.0) 784.0 16593 

(56616) 

3.29 

(11.23) 

7 2.52 

(36.5)

9677 

(33019) 2897 2047 

(1205) 

439.8 

(1506.3) 439.8 9236 

(31513) 

2.77 

(9.44)

8 5.11 

(41.1)

12009 

(40974) 3196 2360 

(1389) 

507.0 

(1736.3) 507.0 11500 

(39238) 

3.11 

(10.6)

9 5.37 

(41.7)

7610 

(25991) 1943 849 

 (500) 

364 

(1241.9) 364.0 7253 

(24749) 

3.14 

(10.73) 

(1) For units with no fan Qfan is calculated to be 1250 Btu/h per 1000 scfm of airflow (ARI 210/240-2003). 

(2) For units with no fan Pfan is calculated to be 365 W per 1000 scfm of airflow (ARI 210/240-2003). 

Coil 4 airflow was too high and results cannot be compared directly to ARI tests. 

4.2: Calculation of SEER 

The calculation of SEER involves the value of EER(82) and the cyclic degradation coefficient

CD. 

SEER (1 0.5 C )EER(82) D = − ⋅ 1.2 

For the tested systems, CD was typically obtained by conducting dry-coil steady-state and cyclic 

tests (C and D tests of ARI Standard 210/240, (ARI 2003)). Alternatively, the rater may use the

0.25 default value instead of performing the tests. In practice, CD values fall between 0.0 and 

0.25. Since, by definition, the mixed system is not tested, the CD value must be obtained from 

some engineering analysis or the default value of 0.25 must be taken. 

Dougherty (2004), working with DOE and ARI, performed a statistical analysis of experimentally

determined CD values for a large sample of systems. He grouped the studied systems into four

basic categories shown in Table 4.2.1. The analysis of CD values for these four system

categories produced the CD percentiles shown in Table 4.2.2. 

18
Table 4.2.1: System classifications for cyclic degradation coefficient analysis 

System 

Category

Equalize During Off 

Cycle Indoor Fan Off Delay System 

Components 

A Yes No

Cap Tube 

Orifice 

Bleed TXV 

B1 No No

Non-Bleed TXV 

Electronic Expansion Device 

Liquid Line Solenoid 

B2 Yes Yes

Cap Tube 

Orifice 

Bleed TXV 

C No Yes

Non-Bleed TXV 

Electronic Expansion Device 

Liquid Line Solenoid 

The range of CD values is rather significant in each equipment category. In category A, for

example, the classification for all nine mixed systems tested for this project, the difference 

between the 50th and 99th percentiles is 0.24-0.09=0.15. This means that assuming the 50th

percentile value for the mixed system with an actual CD of 0.24 will result in a SEER prediction 

error of 7.5 %. For illustration in Table 4.2.3, we generated two SEER numbers for mixed 

systems using CD values of 0.22 and 0.24, which correspond to the 95th and 99th percentiles,

respectively. While both choices are conservative statistically, they still represent a risk of 

SEER overprediction by 1.5 % and 0.5 %, respectively, should the actual CD value be the

maximum of 0.25. We believe that the most accurate assignment of CD for the mixed system 

would be that of the matched system if the changes implemented in the mixed system do not

move it to a different equipment category, as defined in Table 4.2.1. 

Table 4.2.2: Cyclic degradation coefficient values for different system categories 

Percentile A B1 B2 C

99th 0.24 0.16 0.22 0.15

95th 0.22 0.14 0.14 0.12

90th 0.16 0.14 0.12 0.10

85th 0.14 0.12 0.11 0.09

80th 0.12 0.12 0.10 0.08

75th 0.12 0.11 0.10 0.07

70th 0.11 0.11 0.09 0.06

60th 0.10 0.9 0.08 0.05

50th 0.09 0.07 0.07 0.04

Sample Size 77 58 109 78 

19
Table 4.2.3: Mixed system SEERs calculated using statistically determined CD for 95th and 99th

percentiles 

Cyclic Degradation 

Coefficient, Cd

SEER (Btu/W·h) Coil 

95th 99 th 95 th 99 th

1 0.22 0.24 10.24 10.13

2 0.22 0.24 9.32 9.22

3 0.22 0.24 10.26 10.14

4* 0.22 0.24 9.34 9.23 

5 0.22 0.24 10.08 9.97

6 0.22 0.24 10.33 10.21

7 0.22 0.24 8.41 8.31

8 0.22 0.24 9.43 9.32

9 0.22 0.24 9.89 9.78

Coil 4 airflow was too high and results cannot be compared directly to ARI tests. 

5: NIST PREDICTIONS AND ARI DATABASE COMPARISON 

5.1: A-Test capacity comparison 

Table 5.1.1 and Figure 5.1.1 present mixed system capacities, Q(95), from the C-B Method and

the ARI database for the A-Test conditions. Capacity predictions from the C-B Method were 

within ±5 % of the ARI tests for five of eight coils. Among the three cases with poor predictions, 

the disagreement was as high as 17.6 %. 

Table 5.1.1: Mixed system A-Test capacities from ARI Tests and C-B Method 

Coil 

C-B 

Method 

Tevap

°C (°F) 

ARI 

Test 

Tevap

°C (°F) 

C-B 

Method 

q(95)

W 

(Btu/h) 

Indoor 

Airflow 

m3

/h 

(scfm) 

Qfan

W 

(Btu/h) 

ARI Test

Q(95)

W 

(Btu/h) 

C-B 

Method 

Q(95)

W 

(Btu/h) 

Qdiff

100%(NIST – 

ARI)/ARI 

1 8.1 

(46.6)

7.2 

(45.0)

9991 

(34089) 

1699 

(1000) 

366.3(1) 

(1250.0) 

10034 

(34238) 

9624 

(32839) -4.1 

2 5.8 

(42.5)

6.1 

(43.0)

6639 

(22653) 

1368 

(805) 

294.9(1) 

(1006.3) 

6529 

(22278) 

6344 

(21647) -2.8 

3 7.9 

(46.3)

7.6 

(45.6)

9935 

(33898) 

1621 

(954) 

349.5(1) 

(1192.5) 

9609 

(32786) 

9585 

(32705) -0.2 

4* 9.9 

(49.9)

8.4 

(47.2)

5184 

(17688) 

1342 

(790) 

289.4(1) 

(987.5)

5073 

(17311) 

4894 

(16700) -3.5 

5 9.4 

(49.0)

10.5 

(50.9)

7188 

(24526) 

1279 

(753) 

271.0(1) 

(925.5)

6787 

(23157) 

6917 

(23601) 1.9 

6 6.2 

(43.2)

7.2 

(44.9)

16541 

(56439) 

1954 

(1150) 

784.0(2) 

(2677.5) 

14407 

(49159) 

15756 

(53761) 9.4 

7 4.5 

(40.2)

6.8 

(44.3)

8781 

(29962) 

2047 

(1205) 

441.5(2) 

(1506.3) 

10122 

(34537) 

8340 

(28456) -17.6 

8 5.9 

(42.6)

5.7 

(42.2)

11387 

(38851) 

2360 

(1389) 

507.0(1) 

(1736.3) 

12591 

(42963) 

10878 

(37115) -13.6 

9 6.2 

(43.2)

4.1 

(44.2)

7114 

(24274) 

849 

(500) 

364(2)

(1243.1) 

6480 

(22112) 

6749 

(23030) 4.2 

(1) Coil without a fan; Qfan was calculated to be 1250 Btu/h per 1000 scfm of airflow (ARI 210/240-2003)

(2) Coil equipped with a fan; fan power measured by NIST

*Coil 4 airflow was too high and results cannot be compared directly to ARI tests. 

20
-20.0

-15.0

-10.0

-5.0

0.0

5.0

10.0

15.0

1 234 567 8 9

Coil Number

Q diff 100% ((C-B Method - A

RI)/A

RI)

Figure 5.1.1: Comparison of mixed system A-test capacities from the ARI tests 

 and the C-B Method 

 (Note: Coil 4 airflow was too high and results cannot be compared directly to ARI tests) 

Table 5.1.1 also shows evaporator saturation temperatures obtained from the C-B Method and

measured during mixed system certification tests. Ideally, these temperatures should be the

same or very close for good capacity predictions. One can rationalize that a saturation

temperature from the C-B Method that is lower than that from the certification tests should result

in an overprediction of capacity while a higher C-B Method saturation temperature should drive 

toward the opposite effect. This physical rationale holds somewhat for Coils 1, 5, and 6, while 

other coils do not conform. In particular, Coil 7, associated with the largest underprediction of

Q(95) of 17.6 % has a 4.5 °C (40.2 °F) C-B Method saturation temperature versus a 6.8 °C 

(44.3 °F) saturation temperature measured during certification tests. 

To further explore the reasons for inconsistent Q(95) predictions, we compared test-obtained

mixed system Q(95) capacities with those calculated for mixed evaporators from NISTdeveloped capacity lines and those calculated for condensing units from condensing

performance curves using the same evaporator saturation temperature as measured during the 

mixed system certification tests. Table 5.1.2 presents the data. It is desirable for these three 

capacities to be close, ideally equal, to each other. The table shows that NIST-calculated

capacities agreed with the certification test capacities for Coils 1, 3, 6, and 9 within ± 2.5 %, 

which is a remarkable agreement. The capacities for coils 2 and 5 are underpredicted within 

6.5 %. The largest disagreement of -27.6 % is for Coil 7. For condensing unit capacities, the

21
agreement with mixed system data was within ± 6.5 % for six cases. In the remaining cases, 

the deviations from mixed system capacities were as much as -14.2 %. 

Looking back at the predicted Q(95) presented in Table 5.1.1, we can see that we obtained

good predictions of Q(95) in every case where the capacities from three sources shown in Table

5.1.2 are in good agreement (Coils 1, 2, 3, and 9). Also good Q(95) predictions are for Coil 5 in

Table 5.1.1; in this case the capacity calculated from evaporator and condensing unit 

correlations in Table 5.1.2 underpredicted and overpredicted the mixed system capacity by a

similar percentage. The result is a good prediction of Q(95) at a somewhat different evaporator

saturation temperature than that measured during a system test. 

In the cases with the largest Q(95) prediction errors, Coils 6, 7 and 8, no offsetting of errors

took place; even for Coil 8 where the C-B Method predicted the evaporator saturation

temperature within 0.2 °C (0.4 °F). Since evaporator capacity and mixed system capacity for 

Coil 6 in Table 5.1.2 agree within 2.5 % while the condensing unit capacity deviates by 13.1 %,

a suggestion can be made that the condensing unit correlation could be faulted for the Q(95) 

underprediction. Using the same rationale, a case against the evaporator capacity correlation

could be made for Coil 7. For Coil 8, the evaporator and condensing unit correlations yield

similar capacities and disagree with the system test data by a similar capacity percentage, 

-12.2 % and -14.2 %, respectively, suggesting some testing irregularity or an error in data

handling. 

Table 5.1.3 allows additional analysis of capacity predictions from the NIST-developed capacity 

lines. The table shows the tested mixed system capacities and those calculated using capacity

lines (adjusted for the indoor fan heat) as presented in Table 5.1.2, but it includes temperature

and subcooling of the refrigerant entering the expansion valve and the refrigerant superheat at 

the evaporator exit. Since values of these parameters are different for most cases, it was of 

interest to assess the extent to which these differences could affect the evaporator capacity

predictions. For this purpose, we used the EVAP-COND simulation package (NIST 2003) to

simulate coil performance at different inlet refrigerant temperatures and outlet superheats. 

For example, for Coil 7, the ARI superheat was 2.4 oC (4.3 oF) and the NIST superheat was 

7.3 oC (13.2 oF); a difference of 4.9 oC (8.9 oF). Keeping the same evaporator saturation

temperature and liquid temperature (inlet quality), and changing the superheat to the ARI value

increased the predicted Coil 7 capacity by 494 W (1686 Btu/h) to 7818 W (26 675 Btu/h), thus

reducing the percent difference from -27.6 % to -22.8 %. Changing the liquid temperature from

40.6 oC (105.1 oF) to the ARI value of 49.4 oC (120.9 oF) and keeping the same subcooling of

7.7 oC (13.8 oF), increased the capacity by an additional 222 W (758 Btu/h) to 8038 W

(27 433 Btu/h), thus reducing the ARI-NIST percent difference to -20.5 %. It appears that some

installation and test condition related factors are responsible for the remaining -20.5 % deviation 

in the Coil 7 results. 

22
Table 5.1.2: Mixed system A-Test capacities from the ARI tests, condensing unit capacities from CD Unit cu

capacities from NIST-developed evaporator capacity curves at the ARI-test evaporating temper

Coil 1 Coil 2 Coil 3 Coil 4* Coil 5 Coil 6 Coil 7 

W Btu/h W Btu/h W Btu/h W Btu/h W Btu/h W Btu/h W Btu/h 

ARI Value Q(95) 10034 34238 6529 22278 9609 32786 5073 17311 6787 23157 14407 49159 10122 34537 

NIST Q(95) 10282 35083 6163 21029 9829 33536 5622 19183 6353 21679 14760 50363 7324 24989 

CD Unit Q(95) 10338 35273 6388 21796 9475 32330 4548 15518 7198 24562 16294 55598 9508 3244

NIST/ARI % 2.5 -5.6 2.3 10.8 -6.4 2.5 -27.6 

CD Unit/ARI % 3.0 -2.2 -1.4 -10.4 6.1 13.1 -6.1 

 (1)Mixed system evaporating temperature, Tevap, is listed in Tables 5.1.1. (2) Indoor fan heat from the mixed system accounted for in all capacity calculations (3) Qdiff = 100% (NIST – ARI)/ARI (4) Qdiff = 100% (CD Unit – ARI)/ARI

*Coil 4 airflow was too high and results cannot be compared directly to ARI tests 

Table 5.1.3: Mixed system A-test capacities from ARI values and evaporator capacities from NIST-develope

curves at the ARI-test evaporating temperature(1)

Coil 1 Coil 2 Coil 3 Coil 4* Coil 5 Coil 6 Coil 7 

ARI NIST ARI NIST ARI NIST ARI NIST ARI NIST ARI NIST ARI NIST 

Tliq °C 

(°F)

37.2 

(99.0) 

40.7 

(105.3) 

41.1 

(106.0) 

40.5 

(104.9) 

35.2 

(95.4) 

40.5 

(104.9) 

42.2 

(108.0) 

40.7 

(105.3) 

40.3 

(104.6) 

40.4 

(104.8) 

40.3 

(104.6) 

40.4 

(104.8) 

49.4 

(120.9) 

40.6 

(105.1

Tsub °C 

(°F)

6.9 

(12.5) 

6.2 

(11.1) 

11.8 

(21.2) 

6.6 

(11.9) 

7.7 

(13.8) 

7.7 

(13.9) 

13.8 

(24.9) 

7.6 

(13.6) 

7.7 

(13.9) 

7.7 

(13.9) 

6.4 

(11.6) 

7.7 

(13.9) 

6.7 

(12.0) 

7.7 

(13.8) 

Tevap °C 

(°F)

7.2 

(45.0) 

7.2 

(45.0) 

6.1 

(43.0) 

6.1 

(43.0) 

7.6 

(45.6) 

7.6 

(45.6) 

8.4 

(47.2) 

8.4 

(47.2) 

10.5 

(50.9) 

10.5 

(50.9) 

7.2 

(44.9) 

7.2 

(44.9) 

6.8 

(44.3) 

6.8 

(44.3) 

Tsuph °C 

(°F)

6.2 

(11.2) 

7.1 

(12.8) 

4.7 

(8.5) 

8.1 

(14.6) 

11.6 

(20.9) 

7.4 

(13.4) 

2.1 

(3.8) 

7.4 

(13.3) 

0.8 

(1.5) 

7.8 

(14.0) 

7.1 

(12.7) 

7.6 

(13.6) 

2.4 

(4.3) 

7.3 

(13.2) 

Q, W 

(Btu/h) 

10034 

(34238) 

10282 

(35083) 

6529 

(22278) 

6163 

(21029) 

9609 

(32786) 

9829 

(33536) 

5073 

(17311) 

5622 

(19183) 

6787 

(23157) 

6353 

(21679) 

14407 

(49159) 

14760 

(50363) 

10122 

(34537) 

7324 

(24989

Qdiff (%)(2) 2.5 -5.6 2.3 10.8 -6.4 2.5 -27.6 

 (1) Indoor fan heat from the mixed system accounted for in all capacity calculations (2) Qdiff = 100% (NIST – ARI)/ARI 

*Coil 4 airflow was too high and results cannot be compared directly to ARI tests 

23
5.2: B-Test EER comparison 

Table 5.2.1 shows EER values from the ARI tests and the C-B Method. Coils 5 and 7 show 

an agreement within ±5 %. The C-B Method overpredicted the ARI values by more than

5 % in four cases. System power, fan power, Q(82), and EER(82) were compared in Figure 

5.2.1 to illustrate the sources of disagreement between the C-B Method and the ARI tests. 

-30.0

-20.0

-10.0

0.0

10.0

20.0

30.0

1 2 3 4 5 6 7 8 9

Coil Number

(C-B Method - ARI) / ARI * 100%

CD Unit Power

Fan Power

Q(82)

EER(82)

Figure 5.2.1: Percent differences between ARI Values and the C-B Method for the 

EER(82) calculation (Note: Coil 4 airflow was too high and results cannot be compared directly to ARI 

tests) 

We may note that the largest EER disagreement was a 15.4 % underprediction and a

15.4 % over prediction for Coil 1 and Coil 8, respectively. For Coil 1 the 17.9 % higher 

power and the 2.5 % lower capacity caused the C-B Method EER(82) to be 15.4 % lower

than the ARI Test EER(82). Since the evaporator saturation temperatures were equal for

this coil, the 400 W difference in ARI Test and CD Unit linear fit power is the main 

contributor to the EER(82) difference. If the ARI Test CD Unit power were used in the C-B 

Method calculation of EER(82), the percent difference in EER(82) would only be -2.4 %. 

Coil 8 had a 22.9 % under prediction in CD Unit power compared to the ARI Test results. 

The C-B Method’s lower power was not completely mitigated by a lower capacity, resulting

in the EER(82) being 15.4 % higher than the ARI Test EER(82). The lower evaporating 

temperature for the C-B Method would tend to produce a higher capacity than the ARI Test

capacity, but this was not the case. According to the CD Unit capacity linear fit, a 1.3 oC 

(2.4 oF) lower evaporating temperature should increase capacity by 517 W (1765 Btu/h). 

24
This does not equal the 1518 W (5179 Btu/h) difference between the C-B Method and ARI 

Test capacities. If the ARI Test value of power were used with the C-B Method capacity, the 

resulting EER(82) percent difference would be -8.1 %. 

The C-B Method produced a 13.9 % underprediction of EER(82) for Coil 3. The ARI Test

and C-B Method evaporating temperature were within 3.6 %. The CD Unit power and the

ARI Test power differed by 12.1 %. The higher C-B Method power and the lower C-B 

Method capacity produced the 13.9 % lower EER(82). If the ARI Test power were used with 

the C-B Method capacity, the EER(82) difference would be -4.9 %. 

From examining Table 5.2.1, the clear factor in EER(82) disagreement is the system power

difference between actual tests and the power fits. This is true for all cases except Coil 7. 

For Coil 7, the evaporating temperatures differed by almost 19 %. The C-B Method’s lower

evaporating temperature should produce a higher capacity than the ARI Test evaporating 

temperature, but this was not the case. The lower evaporating temperature produced a 

12.3 % lower capacity which was combined with a 14.3 % lower CD Unit power to produce

an almost equivalent EER(82). 

25
26

Table 5.2.1: Mixed system B-Test comparison of ARI tested and C-B Method results 

Coil 

Tevap

 °C (°F) 

CD Unit Power 

W 

Fan Power 

W 

Q(82)c

W (Btu/h) 

C-B 

Method 

ARI 

Test 

Difference 

(C-B 

Method - 

ARI) 

C-B 

Method 

ARI 

Test 

Percent 

Diff 

% 

C-B 

Method 

ARI 

Test 

Percent 

Diff 

% 

C-B 

Method 

ARI 

Test 

Percent 

Diff 

% 

M

1 7.94 (46.3) 7.94 (46.3) 0.0 (0.0) 2530 2146 17.9 365 368 -0.7 9763 (33313) 10017 (34178) -2.5 

(1

2 5.0 (41.0) 6.50 (43.7) -1.5 (-2.7) 1953 2090 -6.6 294 294 -0.1 6895 (23525) 6559 (22381) 5.1 

(1

3 7.72 (45.9) 6.83 (44.3) 0.9 (1.6) 2528 2255 12.1 348 334 4.1 9717 (33155) 10164 (34680) -4.4 

(1

4d 8.89 (48.0) 9.72 (49.5) -0.8 (-1.5) 1471 1670 -11.9 288 232 24.2 5410 (18458) 5338 (18215) 1.3 

(1

5 8.50 (47.3) 9.67 (49.4) -1.2 (-2.1) 2024 1840 10.0 271 310 -12.6 7402 (25258) 7207 (24591) 2.7 

(1

6 5.39 (41.7) 6.50 (43.7) -1.1 (-2.0) 4257 4340 -1.9 784a 848b -7.5 16593 (56616) 15613 (53274) 6.3 

(1

7 2.50 (36.5) 7.22 (45.0) -4.7 (-8.5) 2897 3380 -14.3 440a 439b 0.1 9236 (31513) 10529 (35926) -12.3 

(

8 5.06 (41.1) 6.39 (43.5) -1.3 (-2.4) 3196 4143 -22.9 507 507 -0.1 11500 (39238) 12508 (42680) -8.1 

(1

9 5.39 (41.7) 5.89 (42.6) -0.5 (-0.9) 1943 1954 -0.6 364a 382b -4.7 7253 (24749) 6972 (23790) 4.0 

(1

a) Fan power measured by NIST. b) Fan power measured by ARI contracted testing facility. c) Q(82) included the fan heat correction fod) NIST airflow was 262 m3/h (154 scfm) higher than the ARI tested airflow for Coil 4. 
5.3: SEER comparison 

Table 5.3.1 presents SEER values from the ARI database and the C-B Method for the 99th

percentile cyclic degradation coefficients. With the exception of Coil 6, where the predicted

SEER exceeds the measured SEER by 0.6 %, the SEER values obtained from the C-B 

Method are lower than the measured values by as much as 27 %. Four C-B Method SEERs

agreed to within ±5 % of the measured SEERs. Figure 5.3.1 shows that this level of

agreement can be attributed to offsetting errors between EERs and SEER/EER Multipliers, 

(1-0.5 CD), especially considering the large differences in cyclic degradation coefficient

between the NIST 99th percentile and ARI database. These large differences in degradation 

coefficient indicate that more information is needed to accurately determine a representative 

CD value. Clearly, the use of a fixed value for the degradation coefficient cannot reliably

reproduce ARI database values. 

Table 5.3.1: SEERs from ARI value and C-B Method 

Coil 

SEER 

from ARI 

values 

 Btu/(W·h) 

SEER 

from C-B 

Method 

using 99th

percentile Cd

SEER (1) 

Diff 

% 

ARI 

SEER/EER 

Multiplier(2)

(1-0.5 Cd) 

NIST 99th

Percentile 

SEER/EER 

Multiplier 

(1-0.5 Cd) 

(ARI - NIST 99th) 

SEER/EER 

Multiplier 

1 13.87 10.13 -27.0 0.931 0.880 0.051

2 9.63 9.22 -4.3 0.983 0.880 0.103

3 13.33 10.14 -23.9 0.964 0.880 0.084

4* 9.79 9.23 -5.7 0.980 0.880 0.100 

5 10.01 9.68 -3.3 0.876 0.880 -0.004

6 9.82 9.88 0.6 0.976 0.880 0.096

7 9.56 8.31 -13.1 0.977 0.880 0.097

8 10.17 9.32 -8.4 0.949 0.880 0.069

9 9.78 9.44 -3.5 0.961 0.880 0.081

(1)

 SEER Diff = 100% (NIST – ARI)/ARI 

(2)

ARI SEER/EER multiplier was calculated from SEER = (1-0.5 Cd)EER(82) 

*Coil 4 airflow was too high and results cannot be compared directly to ARI tests.

-30

-28

-26

-24

-22

-20

-18

-16

-14

-12

-10

-8

-6

-4

-2

0

2

4

6

8

10

12

14

Coil Number

% Difference = 100%((C-B Method - ARI)/ARI)

EER

SEER/EER Multiplier

SEER

1 2 3 4 5 6 7 8 9

Figure 5.3.1: ARI Values and C-B Method SEER/EER Multiplier, EER, and SEER 

27
6: GENERATING AN EVAPORATOR CAPACITY LINE USING 

EVAP-COND 

In this study, we developed evaporator capacity lines based on measured capacities at 

several different evaporator exit saturation temperatures with constant superheat and inlet 

quality. Controlling these three parameters makes coil tests more time consuming than 

complete system tests. For this reason, we explored the possibility to minimize the 

laboratory effort by using an evaporator simulation model. A simulation model can be tuned 

to predict the measured capacity, which can then be used to provide capacities at other

saturation temperatures needed to generate the evaporator capacity line. To demonstrate

this approach, we used the EVAP-COND finned-tube heat exchanger simulation package 

(NIST 2003). 

EVAP-COND uses coil design parameters (including refrigerant circuitry) and refrigerant and 

air parameters as input to calculate the capacity of the heat exchanger. The model allows 

the user to tune its prediction to experimental data by adjusting the correction factors for the

air-side heat transfer coefficient, refrigerant-side heat transfer coefficient, and refrigerantside pressure drop. In our case, we considered Coil 9 and selected appropriate values for 

these factors, shown in Table 6.1, so the model predictions agreed with the test results at 

the 7.4 oC (45.4  ̊F) saturation temperature. Simulations at additional saturation

temperatures allowed generation of a linear capacity fit for the coil. 

Table 6.1: EVAP-COND correction parameters for Coil 9 

Tevap

oC 

(oF) 

R ∆P A 

q

Predicted 

W (Btu/h) 

q

Measured 

W (Btu/h) 

qdiff

% 

7.4 

(45.4) 1.15 2.00 1.30 6249 

(21323) 

6242 

(21300) 0.1 

R - refrigerant-side heat transfer coefficient correction factor 

∆P - refrigerant pressure drop correction factor 

A - air-side heat transfer coefficient correction factor

 qdiff = 100%(Predicted-Measured)/Measured 

Figure 6.1 shows cooling capacities for Coil 9 from the laboratory measurements, the EVAPCOND simulations, and the corresponding capacity lines as a function of evaporating 

temperature. The capacity lines almost overlap. Consequently, the C-B Method 

performance predictions for mixed system using Coil 9 were within 0.5 % for the two

capacity lines, as shown in Figure 6.2. 

It is possible that the approach presented here could be extended to other evaporators that

use the same air-side and refrigerant-side heat transfer surfaces; i.e., once EVAP-COND 

adjustable factors for air-side heat transfer, refrigerant-side heat transfer, and refrigerant 

pressure drop are determined for one coil, they could be applied to other coils using the 

same surfaces. 

28
36 38 40 42 44 46 48 50 52 54

Evaporator Saturation Temperature (oF)

10000

12000

14000

16000

18000

20000

22000

24000

26000

28000

30000

32000

34000

Cooling Capacity (Btu/h)

2 3 456 789 10 11 12

Evaporator Saturation Temperature (oC)

5000

5500

6000

6500

7000

7500

8000

8500

9000

9500

Cooling Capacity (W)

EVAP-COND Simulated

Linear Fit to EVAP-COND

Measured Data

Linear Fit to Measured Data

EVAP-COND Fit: Q(Btu/h) = -1032 * Tevap(oF) + 68711.33

Data Fit: Q(Btu/h) = -1088.6 * Tevap(oF) + 71346.7

Figure 6.1: Coil 9 simulated and measured cooling capacity

0.960

0.970

0.980

0.990

1.000

1.010

1.020

1.030

1.040

1.050

1.060

1.070

1.080

1.090

1.100

Ratio with respect to ARI Database Values

1.042

1.038

1.054

1.05

0.965

0.962

Q(95) Ratio

EER(82) Ratio

SEER Ratio

Measurment Based

CB Method

Simulation Based

CB Method

Figure 6.2: C-B Method Q(95), EER(82) and SEER ratio with respect to the ARI database 

using the measured and simulated Coil 9 capacity 

29
7: UNCERTAINTY OF THE C-B METHOD 

7.1: Uncertainty of the evaporator capacity linear fit 

We used Coil 9 data as an example to evaluate the uncertainty of the evaporator capacity

linear fit. This is the uncertainty that would result if someone used this linear fit to calculate

capacity at a known evaporator temperature. The data set used to generate the linear fit 

consisted of 8 tests. A linear equation has two adjustable parameters; therefore, the fit had 

6 degrees of freedom (DOF= n-2). Table 7.1.1 summarizes the linear fit parameters (slope

and intercept) and related fit statistics. 

Table 7.1.1: Coil 9 evaporator linear fit equation statistics 

Correlation 

Coefficient 

R2

DOF 

Adjusted R2

Fit Standard 

Error, W (Btu/h) F-Value 

0.972835 0.961969 226.28 

(772.093) 214.872 

n = 8 data points 

DOF = n-2 = 6 

Parameter Value Standard Error t-value

95 % Confidence Limits on the 

Mean Value 

Minimum Maximum 

B (intercept), W 

(Btu/h) 

20909.6 

(71346.5)

1058.35

(3611.22) 19.757 18309.1 (62473.4)

23510.1 

(80219.6)

A (slope), W/oC 

(Btu/h oF) 

-574.32

(-1088.7)

39.18 

(74.27) -14.659 -670.56(-1271.2)

-478.0 

(-906.2) 

Sxx 108.0774

Mean Tevap

9.2 

(48.5) Mean q

5440 

(18562.8)

At a 95 % confidence level, the linear intercept is equal to 20909.6 ± 2600.45 W (71346.5 ± 

8873.1 Btu/h), and the linear slope is equal to -574.32 ± 39.18 W/oC (-1088.7 ± 

182.5 Btu/h oF). The confidence bands are determined by subtracting the minimum 95 % 

limit from the maximum 95 % limit and dividing by two (or taking the fit standard error and

multiplying by the appropriate t-value). With confidence limits as a percentage value, the

linear intercept is 20909.6 W (71346.5 Btu/h) ± 12.4 %, and the linear slope is 

-574.32 W/oC (-1088.7 Btu/h oF) ± 16.8 %. 

For capacity predictions using the linear correlation, the confidence interval for the mean 

value at a particular point is given by (Ott 1984): 

( )

Sxx

ˆ

2 1 x x

n

t − ± ⋅σ + 7.1.1 

where - 2

SSE ˆ n

σ = = fit standard error 

 ( ) ( ) ∑ ∑ = − n

x

xx x

2

2 S 

t - two tailed t-value for the appropriate confidence level with DOF = n - 2

σˆ - estimated standard deviation equal to the fit standard error 

30
x - mean value of the x-variables or, in this case, the mean value of the evaporating 

temperatures used to generate the linear fit 

x - independent variable or, in this case, the evaporator temperature 

At a 95 % confidence level, the t-value for six DOF is 2.447 from a table of the percentage 

points of the t-distribution (Ott 1984). From Table 7.1.1, the fit standard error was 226.28 W 

(772.093 Btu/h), and Sxx was 33.36 oC2

 (108.08 oF2). Substituting these values into

Equation 7.1.1 yields: 

( )

108.08

x 48.485 2.447 772.093 0.125

2 − ± ⋅ + 7.1.2 

Knowing the confidence interval for a given confidence level and the predicted value, we 

can calculate the upper and lower confidence bands for the mean value of the cooling

capacity sampled multiple times at a particular value of the evaporator saturation 

temperature within the range of the evaporator saturation temperature data. Figure 7.1.1 

plots the evaporator capacity line, 90 % and 95 % confidence bands, and 5 % offset lines for 

Coil 9. The figure shows that the 90% and 95% confidence lines are very close to each 

other; they are within the ± 5 % offset lines for the majority of the saturation temperature 

range except the lowest and highest saturation temperatures due to the smaller number of

data points associated with the end points of the temperature range. 

Once the rater has used the C-B Method (Equation 4.1.2) to determine the evaporating

temperature for the condensing unit and the mixed evaporator, the analysis of section 7.1

provides the uncertainty in the mean value of the cooling capacity sampled at that particular

evaporator temperature. For Coil 9 and its CD Unit, the evaporating temperature was 6.2 oC 

(43.2 oF) which produced a cooling capacity, q(95), of 7114 W (24 273 Btu/h) with an

uncertainty of ± 341 W (1164 Btu/h) or ± 4.8 % on the mean value at a 95 % confidence

level. Subtracting the fan heat, which has a ± 3 % uncertainty, yields the numbers seen in 

Table 5.1.1 or a rated Q(95) of 6749 W (23 030 Btu/h) ± 341 W (1165 Btu/h) (± 5.1 %) at a 

95 % confidence level. Table 7.1.2 summarizes the uncertainty results for the remaining

evaporators. 

31
38 40 42 44 46 48 50 52 54 56

Evaporator Saturation Temperature (oF)

9000

12000

15000

18000

21000

24000

27000

30000

Capacity (Btu/h)

456789 10 11 12 13

Evaporator Saturation Temperature (oC)

3000

4000

5000

6000

7000

8000

Capacity (W)

Coil 9 Cooling Capacity

Upper and Lower 95 % Confidence Band

Upper and Lower 90 % Confidence Band

Upper and Lower 5 % Offset Line

Figure 7.1.1: Coil 9 evaporator cooling capacity, confidence and error bands on the mean 

predicted value of the cooling capacity sampled at a particular evaporator 

saturation temperature 

Table 7.1.2: Evaporator Q(95) linear fit uncertainty 

Coil Tevap

°C (°F) 

Q(95)

W (Btu/h) 

95 % Confidence Level on 

the Mean, 

Uncertainty Q(95)

% Uncertainty 

1 8.11 (46.60) 9624 (32839) 541 (1847) 5.6 

2 5.84 (42.51) 6344 (21647) 334 (1138) 5.3 

3 7.93 (46.27) 9585 (32705) 267 (910) 2.8 

4* 9.94 (49.89) 4894 (16700) 127 (434) 2.6 

5 9.43 (48.98) 6917 (23601) 192 (655) 2.8 

6 6.2 (43.19) 15756 (53761) 939 (3205) 6.0 

7 4.5 (40.17) 8340 (28456) 124 (424) 1.5 

8 5.9 (42.6) 10878 (37115) 260 (886) 2.4 

9 6.2 (43.24) 6749 (23030) 342 (1166) 5.1 

*Coil 4 airflow was too high and results cannot be compared directly to ARI tests.

32
7.2: Uncertainty of C-B Method Q(95) and EER 

The ARI database, q(95), q(82) and p(82) linear fits of Table 4.1.1, NIST capacity linear fits 

of Table 3.4.1, Equation 4.1.2, and fan heat were used to calculate the uncertainty in the CB Method Q(95) and EER. 

qCD = ACDTevap + BCD = qmixed = AmixedTevap + Bmixed 4.1.1

CD mixed

mixed CD

evap A A

B B T −

− = 4.1.2

pCD = bCD + aCDTevap 4.1.4

Substituting Equation 4.1.2 into Equation 4.1.1 and 4.1.4 yields an expression for the

cooling capacity and CD Unit power of the mixed system. 

CD

CD mixed

mixed CD

CD mixed CD B

A A

B B

q q A +















−

− = = 7.2.1 

















−

− = +

CD mixed

mixed CD

CD CD A A

B B

pCD b a 7.2.2 

The fit standard errors for the CD Unit capacity and power linear coefficients are unknown.

If we assume the fit standard error for the CD Unit capacity is similar (the same percentage) 

to that obtained for the evaporator tests, power coefficient uncertainties are 3 %, power and

capacity fits have no covariance, and the covariance of the slope and intercept are equal for

the CD Unit and evaporator tests, then we may calculate an uncertainty for the mixed

system capacity and power. 

In general the capacity is a function of the four linear fit coefficients and the power is a

function of six linear fit coefficients: 

( , , , ) CD mixed ACD BCD Amixed Bmixed q = q = f 7.2.3 

( , , , , , ) CD mixed aCD bCD ACD BCD Amixed Bmixed q = q = f 7.2.4 

Since the slope and intercept are not independent in Equations 7.2.1 and 7.2.2, we must

include covariance in the form of a correlation coefficient (Coleman and Steele 1989). In

general terms this becomes: 

2 2 2 2

2

















∂

∂

+ 















∂

∂

+ 















∂

∂

+ 















∂

∂ = CD CD mixed Bmixed

mixed

A

mixed

B

CD

A

CD

q U

B

q U

A

q U

B

q U

A

q U

CD CD CD CD AmixedBmixed Amixed Bmixed

mixed mixed

A B A B

CD CD

U U

B

q

A

q U U

B

q

A

q ρ ρ















∂

∂

















∂

∂

+ 















∂

∂

















∂

∂

+ 2 2 7.2.5 

Here the partial derivatives are taken from Equation 7.2.1 with respect to the various

coefficients. A similar procedure is necessary for the CD Unit power equation with the 

addition of the two extra terms for the power equation linear fit coefficients. The fan power 

and resulting heat were assumed to have an uncertainty of ±3 %. The fan heat must be

33
subtracted from the cooling capacity, and the fan power must be added to the CD Unit

power with their variances added to produce the cooling capacity and total power final 

values and associated uncertainties. 

EER is the ratio of Q(82) and P(82). 

(82)

(82) EER

P

Q= 1.1

The propagation of the capacity uncertainty and the power uncertainty through Equation 1.1

produces a resulting uncertainty in the EER. We assumed no covariance between capacity

and power. The resulting uncertainty in EER is shown below in Table 7.2.1. 

Table 7.2.1: C-B Method Q(95), Q(82), P(82), and EER uncertainty at the 95 % confidence 

level on the mean value

Coil Tevap(82) Tevap(95)

Q(95)

W 

(Btu/h) 

*% 

UQ(95)

Q(82)

W 

(Btu/h) 

a

% 

UQ(82)

P(82)

W 

% 

UP(82)

EER 

W/W 

(Btu/W h) 

% 

UEER

1 7.9 

(46.3)

8.1 

(46.6)

9624 

(32839) 15.3 9763 (33313) 15.7 2895 3.7 3.37 (11.51) 16.1 

2 5.0 

(41.0)

5.8 

(42.5)

6344 

(21647) 4.4 6895 

(23525) 4.5 2246 9.7 3.07 

(10.47) 10.7 

3 7.7 

(45.9)

7.9 

(46.3)

9585 

(32705) 8.3 9717 (33155) 8.5 2876 2.8 3.38 (11.53) 9.0 

4* 8.9 

(48.0)

9.9 

(49.9)

4894 

(16700) 7.5 5410 (18458) 6.2 1760 3.4 3.07 (10.49) 7.1 

5 8.5 

(47.3)

9.4 

(49.0)

6917 

(23601) 8.2 7402 

(25258) 7.0 2295 5.8 3.23 

(11.01) 9.1 

6 5.4 

(41.7)

6.2 

(43.2)

15756 

(53761) 9.0 16593 (56616) 8.1 5041 4.1 3.29 (11.23) 9.1 

7 2.5 

(36.5)

4.5 

(40.2)

8340 

(28456) 6.3 9236 

(31513) 4.6 3337 2.5 2.77 

(9.44) 5.2 

8 5.1 

(41.1)

5.9 

(42.6)

10877 

(37115) 5.2 11500 

(39238) 5.6 3703 16.9 3.11 

(10.60) 17.8 

9 5.4 

(41.7)

6.2 

(43.2)

6749 

(23030) 10.8 7253 (24749) 9.3 2307 3.3 3.14 (10.73) 9.9 

a

 U: uncertainty

*Coil 4 airflow was too high and results cannot be compared directly to ARI tests.

The uncertainty values may be skewed higher by the assumption of equal percentage

uncertainties for the evaporator and CD Unit linear fit capacity coefficients. It is likely that 

the manufacturers of the CD Units have much larger data sets than those collected in this 

work; therefore, the uncertainty percentages may be lower than those presented in Table 

7.2.1. 

8: CONCLUDING REMARKS 

This report examines the application of the C-B Method to determine Q(95) and SEER of 

mixed air conditioners was studied on a sample of eight mixed systems. An independent

certification laboratory performed mixed system tests and shipped the mixed evaporators to

NIST for testing in NIST’s environmental chambers. We implemented the C-B Method for 

34
Q(95) and SEER ratings using condensing unit performance correlations obtained from ARI,

the evaporator capacity correlations developed at NIST, and the 99th percentile value of 

cyclic degradation coefficients identified for the equipment studied. We compared the

obtained Q(95) and SEER ratings to the test-obtained values from the certification 

laboratory (referred to as ARI values). 

The C-B Method produced Q(95) results that were within ± 5 % of the ARI tested values for

five of eight coils. Among the remaining cases, one Q(95) was overpredicted by 9.4 % and 

two Q(95) were underpredicted by 13.6 % and 17.6 %. In two of the five cases with ± 5 %

agreement, the good Q(95) predictions were obtained as a result of error offsetting between 

evaporator and condensing unit performance correlations with respect to the system tested 

capacities, as evidenced by the misprediction of the evaporator saturation temperature by 

the C-B Method in these two cases. 

The Q(82) values from the C-B method were within ± 5 % of the ARI tested values for four of 

eight coils with six of eight coils being within ± 7 %. Of all the factors contributing to the

differences in EER(82), the CD Unit power had the largest effect. Using the CD Unit linear

fits for power, the C-B Method predicted EER(82) to within ± 5 % for only two coils. Using

the ARI Test values for CD Unit power, the C-B Method predicted EER(82) to within ± 5 % 

for four of eight coils and within ± 8 % for six of eight coils. Clearly good representations of 

CD Unit power must be attained to produce consistently correct values of EER(82). 

Regarding SEER values, four of eight predictions were within ± 5 % of the ARI tested 

values, but offsetting of errors played a role in this agreement due to conservative (99th

percentile) selection of the cyclic degradation coefficient used by the C-B Method. For the 

same reason seven of eight SEER predictions were below the test-derived SEERs. 

The uncertainty analysis of the C-B Method showed that the 95 % confidence level on the 

mean predictions averaged 3.8 % for A-Test capacity and 10.4 % for EER. The analysis 

also showed the importance of careful collection of data; when the evaporator capacity 

linear fits had a lower standard error, the uncertainty in capacity and EER for a given

evaporator temperature was also low. 

We demonstrated that EVAP-COND can be used effectively in developing evaporator 

capacity correlations, which will facilitate the use of the C-B Method. 

The C-B Method does not have any inherent features that would produce a bias in 

predicting Q(95) and EER(82) values. The values obtained in this study for Q(95) and

EER(82), under predictions or over predictions, are caused by random deviations between

the obtained system test results and evaporator and condensing unit performance

correlations. 

Predicted values of SEER have strong under predicting tendencies due to the conservative 

99th percentile selection of the cyclic degradation coefficient. The category of equipment

involved in this study can have a CD in the range from 0.09 to 0.25, with 0.24 being the 99th

percentile value that was used in our SEER calculations. It appears that there is no other 

way to improve SEER predictions other than providing the matched system CD value along 

with condensing unit performance correlations for the application of the C-B Method. It is 

reasonable to assume that a mixed system would have a CD very similar to that of the 

matched system if only the evaporator and indoor fan are the replaced system components. 

35
As compared to the traditional approach for rating mixed systems that is based on the

matched system Q(95) and SEER values and adjusting them using coil capacity ratios (or

similar scaling parameters), the C-B Method is an inherently more accurate methodology;

the selected prediction problems encountered in this study should be studied further to

tighten this procedure. 

Some of the procedural issues that must be stipulated before a working standard is 

produced include the following: 

1) Standard superheats for evaporator curve development with a method to

accommodate different superheat for evaporator capacity determination 

2) Liquid line temperatures for evaporator curve development

3) Cyclic degradation coefficients for comparable systems with different

expansion devices 

4) Cyclic degradation coefficient for matched system provided to coil 

manufacturers, or a method developed to determine a default value 

5) Procedure for developing CD Unit curves; it should include a method for

accommodating different superheats at the evaporator exit 

As an alternative to the C-B Method, the traditional method for testing mixed systems could 

be revisited if the evaporator saturation temperature from the Q(95) matched system test 

was made available for the mixed system rater. This would facilitate an accurate estimation 

of the capacity ratio of the mixed and matched coils, which is used as the most influential 

scaling factor in the traditional rating method. This methodology does not require the

matched system CD since it is included in the matched system SEER, which is available for

rating. 

36
REFERENCES 

ASHRAE 1988. ANSI/ASHRAE Standard 37. Methods of testing for rating unitary air

conditioning and heat pump equipment. American Society of Heating, Refrigerating

and Air-Conditioning Engineers. 1791 Tullie Circle NE, Atlanta, GA, USA. 

ARI 2003. Standard 210/240, Standard for unitary air-conditioning and air-source heat

pump equipment, Air-Conditioning and Refrigeration Institute, 4100 North Fairfax 

Drive, Suite 200, Arlington, VA 22203. 

CFR, 2004a. Code of Federal Regulations, Part 430, Appendix M to Subpart B, Uniform test

method for measuring the energy consumption of central air conditioners, Office of

the Federal Register, National Archives and Records Administration, Washington, 

DC. 

CFR, 2004b. Code of Federal Regulations, Part 430.24, Subsection m1, Units to be tested,

Federal Register, National Archives and Records Administration, Washington, DC. 

Coleman, H.W. and Steele, W.G., 1989. Experimentation and uncertainty analysis for

engineers, John Wiley and Sons, New York, NY USA. 

Domanski, P.A., 1989. Rating procedure for mixed air-source unitary air conditioners and 

heat pumps operating in the cooling mode – revision 1, NISTIR 89-4071, U. S. Dept 

of Commerce, Natn’l Institute of Standards and Technology, Gaithersburg, Maryland

USA 20899.

Domanski, P.A., 1999. “Finned-Tube Evaporator Model With a Visual Interface”, 20th Int.

Congress of Refrigeration, Sydney, Australia, September 19-24, 1999, International 

Institute of Refrigeration, Paris. 

Dougherty, B., 2004. Personal communications, National Institute of Standards and 

Technology, Gaithersburg, Maryland, USA, 20899. 

Graybill, F. A. and Iyer, H. K., 1994. Regression Analysis: Concepts and Applications, 

Duxbury Press, Wadsworth Publishing Company, Belmont, California USA 94002,

pp. 194-209. 

Lemmon, E. W., McLinden, M. O., and Huber, M. L., 2002. NIST Standard Reference 

Database 23: NIST Reference Fluid Thermodynamic and Transport Properties –

REFPROP, Version 7, U. S. Dept of Commerce, Natn’l Institute of Standards and

Technology, Gaithersburg, Maryland USA 20899.

Ott, Lyman. 1984. An introduction to statistical methods and data analysis, 2nd edition,

Duxbury Press, Boston, Massachusetts USA, pp. 280-324. 

Moffat, R. 1988. Describing the uncertainties in experimental results. Experimental Thermal

and Fluid Science. Vol. 1. pp. 3-17. 

37
Neter J., Wasserman W., and Kutner M.H., 1990. Applied linear statistical models, 

regression, analysis of variance and experimental design, 3rd edition, Irwin

publishing, Burr Ridge, Illinois, USA, pp.10. 

Taylor, B. N., and Kuyatt, C. E., 1994. “Guidelines for evaluating and expressing the 

uncertainty of NIST measurement results”, NIST Technical Note 1297, 1994 edition, 

U.S. Department of Commerce. 

38
APPENDIX A: EVAPORATOR COIL DESCRIPTIONS 

Appendix A presents design information for the nine mixed evaporators tested at NIST. It 

includes a picture, design data, and refrigerant circuitry representation in the input format of

the EVAP-COND simulation package. General information and name designation for the 

mixed evaporators is given in Table 2.1. 

Coil 1 

 

39
Coil 2 

Coil circuitry 

40
Coil 3 

Coil Circuitry (left slab) 

 

41
Coil 4 

Coil Circuitry (right slab as seen below) 

42
Coil 5 

Coil circuitry 

43
Coil 6 

Coil circuitry 

 

44
Coil 7 

Coil circuitry (left or right slab) 

 

45
Coil 8 

Coil circuitry (left slab) 

 

46
Coil 9 

Coil circuitry 

 

47
APPENDIX B: UNCERTAINTY ANALYSIS 

A. 1 General Remarks 

The uncertainty analysis was performed to gain knowledge about the uncertainty of the 

measured and calculated data. This Appendix presents the major equations used for the 

uncertainty analysis. 

A. 2 Theory

The uncertainty of a quantity R calculated from n independent measurements xi is a

function of the individual uncertainty of each measurement. 

R f x x x x (A.1) = n ( , , ,....., ) 1 2 3

When each measurement, xi , has a given uncertainty, dx , the maximum uncertainty of R is 

given by: 

i

n

n

3

3

2

2

1

1

R d d d ..... dx

x

f

x

x

f

x

x

f

x

x

f E

∂

∂

∂

∂

∂

∂

∂

∂ = + + + + . (A.2) 

However, using the maximum error to judge the uncertainty of a calculated quantity is not

common. Usually the standard deviation (root sum square) is regarded to be a much better

approach to a quantity’s uncertainty. 

2

n

n

2

3

3

2

2

2

2

1

1

R d d d ..... d 















+ + 















+ 















+ 













 = x

x

f

x

x

f

x

x

f

x

x

f E

∂

∂

∂

∂

∂

∂

∂

∂ (A.3) 

The absolute error calculated with equation (A.3) is often converted to a relative error having

the units of percent. 

100 R

R R

E

e = (A.4)

A. 3 Temperature Measurements 

Most of the temperature measurements performed for these tests were determined by 

thermocouples. Their voltage signals were measured with the data acquisition system and

then converted into a temperature. 

The equation used in the test rig’s control program to convert the voltage signals into 

temperatures was a sixth degree polynomial of the form: 

θ ( ) 32

5

9 ( ) 2 3 4 5 6 = f V = A + BV + CV + DV + EV + FV + GV + (A.5) 

48
where: 

 θ = temperature (°F) 

 V = measured voltage (μV) 

If one premises that the uncertainty of the equation itself can be neglected, only one 

derivation is needed to evaluate the uncertainty in the temperature measurements. 

( ) 2 3 4 5 2 3 4 5 6

5

9 B CV DV EV FV GV

V = + + + + +

∂

∂θ (A.6) 

According to the manufacturer of the voltmeter, the 95 % uncertainty of the voltage

measurement (VM) was: EVM = dV( ) VM = ± 0.007 % of reading + 5 μV . 

The measurement of a temperature (θ ) actually is the measurement of the difference to a

reference temperature. The data acquisition system provided temperature compensation to 

0 °C (32 °F) with a given uncertainty of: ETC = dTC = ± 0.2236 °C = ± 0.4025 °F. 

Rewriting equation A.3 for the measurement of the absolute temperature gives: 

θ = f(V) (A.7)

( )

2

2

T dVM dTC

V

E  + 

 



 = ∂

∂θ (A.8) 

In addition to the common thermocouple measurements, the dew-point temperature in the

air duct was measured to evaluate the humidity ratio of the moist air in the duct. 

The manufacturer of the dew-point hygrometer specified the 95 % uncertainty in this 

measurement to be: ETdew = dTdew = ± 0.05 % of reading . 

)

A. 4 Temperature Difference Measurements

The evaluation of the uncertainty of a temperature difference (∆θ measurement using a

thermopile is slightly more complicated than that for a normal temperature measurement.

The uncertainty evaluation is presented using the air duct temperature difference as an

example, because this shows the most complicated case. Again there are two independent

uncertainties being part of the measurement uncertainty. The first is the uncertainty caused

by the voltage signal measurement, discussed in section A.3. The cause for the second 

uncertainty influencing the measurement of a temperature difference is the nonlinear

character of the temperature/voltage function (see equation A.5). The nonlinearity requires 

temperature at one end of the thermopile used for the temperature difference measurement

to be known. 

The temperature difference across the indoor coil was calculated using both the voltage

signals of the temperature difference measurement (∆V ) and the average voltage signal 

49
(Vav.) of the entering temperature measurement of the air duct. The equation used to do so 

was: 

( ) ( av. Vav. ∆θ = f V + ∆V − f ) (A.9)

The entering temperature was measured using 25 thermocouples equally distributed over

the air duct’s cross section. The average of the 25 temperature signals was considered to 

be the entering temperature. For the uncertainty in this average entering temperature the

average voltage measurement uncertainty EVM ,av.

 of the 25 measurements was calculated. 

( ) ( ) ∑=

= =

25

x 1

av. x

,av. av 25

d d V VM EVM V VM (A.10)

All 25 thermocouples were connected to the same temperature compensation. This means 

the overall uncertainty of the air’s average entering temperature voltage signal Vav. was: 

( ) ( ) ( ) ( ) 2

av.

2

av.

2 2 dVav. = EVM,av. + ETC = dV VM + dV TC (A.11) 

To evaluate equation A.11 the uncertainty in the temperature compensation must be

rewritten to have the unit of μV

4025

. Using equation A.5 one finds that an uncertainty of

 in the temperature compensation to 0 °C (32 °F) is

equivalent to a voltage signal uncertainty of 

ETC TC C FO = d = ±0.2236° = ± 0.

dVav.(TC) = ± 8.6264 μV . As already 

mentioned, the uncertainty of the voltage signal measurement was given from manufacturer 

data. 

The nonlinearity of the voltage/temperature function (A.5) causes an uncertainty dslope in 

the temperature difference that depends on the uncertainty in the entering temperature 

voltage signal Vav.. 

( ) ( ) ( ) d Vav. dV Vav. Eslope = slope = θ + −θ

 ( ) ( ) ( ) − θ Vav. + dVav. + ∆V −θ Vav. + dVav. (A.12) 

where: 

 Vav. = entering temperature voltage signal ( ) μV

 d = uncertainty of the entering temperature voltage signal ( ) Vav. μV

 ∆V = temperature difference voltage signal ( ) μV

Remembering that an additional uncertainty in the temperature difference is caused by the 

voltage measurement of the temperature difference voltage signal (∆V ), the uncertainty of

the air duct temperature difference is given to be: 

50
1/ 2

2

2

d d d















  + 

 





∆ = ∆ = ∆V slope V

E

∂

∂θ

θ θ (A.13)

A. 5 Uncertainty of the Air Side Capacity

The air side capacity of the heat pump was evaluated using the equation: 

 (A.14) QC QS QL & & & = +

where: 

 Q = sensible capacity, kW (Btu/h) S

&

 Q = latent capacity, kW (Btu/h) L

&

The sensible capacity is the heat needed to cool or heat the moist air passing the heat 

pump’s indoor coil. The latent capacity is the heat rejected by water vapor condensing on

the air coil. Condensation does not occur in the heating mode. 

The two different capacities were calculated separately and then added (A.14). Therefore 

the uncertainty of the air-side capacity can be written as: 

( 1/ 2 2

L

2

S

1/ 2 2

L

L

C

2

S

S

C d d d d C

Q Q Q

Q

Q Q

Q

Q EQ

& & & &

& & &

&

& = + 































+ 













 = ∂

∂

∂

∂ ) (A.15) 

The equations for both the sensible and latent capacities and their uncertainties are 

presented on the following pages. 

A. 5. 1 Uncertainty of the Sensible Capacity

According to ASHRAE Standard 116-1993 the sensible capacity Q is given by: S

( )( ) ( )

1/ 2

2

C n nact

S D n av. l e 144 1

2 3600 0.24 0.444 



 





−

∆ = + − β

ρ θ θ g p Q& C A W (A.16) 

where: 

 CD = nozzle discharge coefficient (0.986) 

 An = nozzle throat area, m2 ( ) ft 2

 Wav. = (W W e l + ) / 2 average humidity ratio, kg H2O/ kg dry air 

 (lb H2O/lb dry air) 

 θl −θe = indoor coil air temperature rise, °C ( ) O

F

 gC = gravity constant (32.174 ft ⋅ lb lb ⋅s m f / 2

) 

 ∆ = static pressure drop across nozzle, kPa (psia) pn

 ρ nact = density of the moist air, kg/m3

 (lb / ft ) 3

51
144 = unit conversion factor from in ft 2 2 to 

 β = area relation factor (0.250723) 

The partial derivatives required for the uncertainty analysis of Q are: S

( )( ) ( )

1/ 2

2

C n nact

D av. l e

n

S

144 1

2 3600 0.24 0.444

A 



 





−

∆ = + − β

ρ θ θ

∂

∂ g p C W Q&

 (A.17) 

( ) ( )

1/ 2

2

C n nact

D n l e

e

S

144 1

2 1800 0.444 



 





−

∆ = − β

ρ θ θ

∂

∂ g p C A

W

Q& (A.18) 

( ) ( )

1/ 2

2

C n nact

D n l e

l

S

144 1

2 1800 0.444 



 





−

∆ = − β

ρ θ θ

∂

∂ g p C A

W

Q& (A.19) 

( ) ( ) ( )

1/ 2

2

C n nact

D n av.

l e

S

144 1

2 3600 0.24 0.444 



 





−

∆ = + − β

ρ

∂ θ θ

∂ g p C A W Q&

 (A.20) 

( )( ) ( )

1/ 2

n

2

C nact

D n av. l

n

S

144 1

2 1800 0.24 0.444 



 





− ∆ = + − ∆ p

g C A W

p

Q e βρ θ θ

∂

∂ &

 (A.21) 

 ∂

∂ρ

Q&

S

nact

= ( )( ) ( )

1/ 2

nact

2

C n

D n av. l e 144 1

2 1800 0.24 0.444

















−

∆

+ − β ρ

θ θ g p C A W (A.22) 

 ( )( ) ( )

1/ 2

3 2

C n nact

D n av. l e

S

144 1

2 3600 0.24 0.444 















−

∆ = + −

β

ρ θ θ β ∂β∂ g p C A W Q&

 (A.23) 

Using the above partial derivatives for rewriting equation A.3 gives: 

 







+ 















∆

∆

+ 















+ 















+ 













 =

2

n

n

S

2

l

l

S

2

e

e

S

2

n

n

S d d d d S p

p

Q W

W

Q W

W

Q A

A

Q EQ ∂

∂

∂

∂

∂

∂

∂

∂ & & & &

 

1/ 2

S

2

nact

nact

S

2

l e

l e

S d( ) d d

( ) 























+ 















+ 













 − − + β ∂β

∂

ρ ∂ρ

∂ θ θ

∂ θ θ

∂Q& Q& Q&

 (A.24) 

Equation A.24 can be evaluated to give the uncertainty of Q if each of the individual

uncertainties is known. However, A, 

&

S

β , We , Wl and ρnact are calculated quantities, so their 

uncertainties were not known, but had to be calculated using equation A.3. 

52
The flow in the air duct was measured using a venturi tube measurement. The nozzle throat 

area , which is part of equation A.16, was calculated from the throat diameter. Thus its 

uncertainty can be evaluated very easily. 

An

 4

2

n

n

d A π= (A.25)

n

n

n

n

n d

2

d n d d d

d

A EA

π

∂

∂

= = (A.26) 

The uncertainty of the throat diameter was given to be: Edn = ddn = ±0.254 mm = ± 0.01 in. 

The area ratio factor β was calculated using the equation: 

2

en

2

n

en

n

d

d

A

A β = = (A.27)

Again, both areas were calculated using their diameter given by the manufacturer of the

venturi tube. The partial derivatives used to evaluate the uncertainty in β were: 

2

en

n

n

2

d

d

d = ∂

∂β (A.28) 

3

en

2

n

en

2

d

d

d = − ∂

∂β (A.29) 

Using these derivatives to rewrite A.3 gives: 

1/ 2 2

3 en

en

2

n

2

2 n

en

2 n d 2 d 















































+ − 





























 = d

d

d d

d

d Eβ (A.30) 

The required uncertainty in the inlet diameter was also 

E dd 0.254 mm 0.01 in . d en en = = ± = ±

The humidity ratios We and Wl are a function of the water vapor pressure pw and the

atmospheric pressure p. 

W

w

w 0.62198

p p

p

− = (A.31)

The factor 0.62198 comes from the ratio of the mole weights of the two components, water

and air. 

53
The required partial derivatives of equation A.31 are: 

2

w

w

( )

0.62198

p p

p

p

W

− = ∂

∂ (A.32) 

2 w w ( )

0.62198

p p

p

p

W

− = ∂

∂ (A.33) 

They lead to the uncertainty in W: 

1/ 2 2

w

w

2

d d 































+ 













 = = p

p

W

p

p

W EW dW

∂

∂

∂

∂ (A.34) 

Unfortunately the water saturation pressure is a calculated quantity itself, which means its 

uncertainty had to be calculated. 

The equation that was used to calculate the saturation pressure from the dew-point

temperature, Tdew , (°R), is given below. The equation was assumed to cause no additional 

uncertainties. 





 



 = + + + + + 13 dew

3

12 dew

2

9 10 dew 11 dew

dew

8

w C C T C T C T C lnT

T

C

p EXP (A.35) 

The partial derivative of equation A.35 with respect to Tdew is: 

w

dew

2 13

2 10 11 dew 12 dew

dew

8

dew

w 2 3 p T

C C C T C T

T

C

T

p

















+ + + + − = ∂

∂ (A.36) 

The uncertainty in pW is now given by: 

dew

dew

w d w d w T

T

p Ep p ∂

∂ = = (A.37) 

As already mentioned in section A.3, the uncertainty of the dew-point temperature 

measurement was given to be: ET dTdew 0.05 % of reading dew = = ± . 

Finally, the uncertainty in the moist air's density ρnact had to be evaluated. The density was 

calculated using the ideal gas equation and the humidity ratio. 

( )

R T ( W )

p W

1 1.6078

144 1

a n

n

nact

+

+

ρ = (A.38)

The factor 1.6078 is the ratio of the molar weights of air and water. 

54
The partial derivatives of the A.38 are: 

(1 1.6078 )

144(1 )

n n

nact

RT W

W

p +

+ = ∂

∂ρ (A.39) 

(1 1.6078 )

144(1 )

2

n

n

n

nact

RT W

p W

T +

− + = ∂

∂ρ (A.40) 

2

n

nact n

(1 1.6078 )

0.6078 144

RT W

p

W +

− = ∂

∂ρ (A.41) 

Rewriting equation A.3 with the above partial derivatives gives: 























 







+ 















+ 













 =

2

nact

2

n

n

nact

2

n

n

nact d d d

p nact WW

T

T

E p ∂

∂ρ

∂

∂ρ

∂

∂ρ

ρ (A.42) 

The pressure in the nozzle throat was calculated as the difference of atmospheric 

pressure and nozzle pressure drop. The uncertainty of the nozzle pressure can be derived

as follows: 

pn

pn = patm − ∆p (A.43) 

[ ( ) ]

1/ 2 2 2 d n (d atm ) d n Ep = p = p + ∆p (A.44)

The uncertainties of the pressure measurements were given from manufacturer data:

and

. 

Ep dpatm 0.3429mmHg 0.0135 in Hg atm = = ± = ±

EDp dDpn 2.489 mmH2O 0.098 in H2O n = = ± = ±

A. 5. 2 Uncertainty of the Latent Capacity

The latent cooling capacity (ASHRAE Standard 116-1983) is given by: 

( ) ( )

1/ 2

2

C n nact

L D n e l 144 1

2 6360060 



 





−

∆ = − β

g p ρ Q& C A W W (A.44) 

where: 

 CD = nozzle discharge coefficient (0.986) 

 = nozzle throat area (f An t )

2

 We = entering humidity ratio (lb H2O/lb dry air) 

 Wl = leaving humidity ratio (lb H2O/lb dry air) 

 g = gravity constant (32.174 ) C ft lb / lb s m f

2 ⋅ ⋅

 ∆ = static pressure drop across nozzle (psia) pn

55
 ρ nact = density of the moist air (lb / ft ) 3

144 = unit conversion factor from in to ft 2 2

 β = area relation factor (0.250723) 

The partial derivatives of this equation are: 

( ) ( )

1/ 2

2

C n nact

D e l

n

L

144 1

2 6360060 



 





−

∆ = − β

ρ

∂

∂ g p C W W

A

Q& (A.45) 

( )

1/ 2

2

C n nact

D n

e

L

144 1

2 6360060 



 





−

∆ = β

ρ

∂

∂ g p C A

W

Q&

 (A.46) 

( )

1/ 2

2

C n nact

D n

l

L

144 1

2 6360060 



 





−

∆ = − β

ρ

∂

∂ g p C A

W

Q& (A.47) 

( ) ( )

1/ 2

n

2

C nact

D n e

n

L

144 1

2 3180060 



 





− ∆ = − ∆ p

g C A W W

p

Q

l β

ρ

∂

∂ & (A.48) 

( ) ( )

1/ 2

nact

2

C n

D n e l

nact

L

144 1

2 3180060

















−

∆ = − ∂ρ β ρ

∂ g p C A W W Q& (A.49) 

( ) ( )

1/ 2

3 2

C n nact

D n e l

L

144 1

2 6360060 















−

∆ = −

β

ρ β ∂β

∂ g p C A W W Q& (A.50) 

If the above derivatives are used to rewrite equation A.3, one obtains the uncertainty of the

latent capacity: 









+ 















+ 















+ 













 =

2

l

l

L

2

e

e

L

2

n

n

L d d d L W

W

Q W

W

Q A

A

Q EQ ∂

∂

∂

∂

∂

∂ & & &

 

1/ 2 2

L

2

nact

nact

L

2

n

n

L d d d 























+ 















+ 















∆

∆

+ β ∂β

∂

ρ ∂ρ

∂

∂

∂ Q Q

p

p

Q& & &

 (A.51) 

In this equation, all the needed uncertainties are known. Either because the quantities are

directly measured or their uncertainties have already been calculated in Appendix A.4.1. 

The final step was calculating the uncertainty of the air side capacity by using the now 

known uncertainties of sensible and latent capacity in equation A.15. 

56
APPENDIX C: COOLING MEASUREMENT SUMMARY SHEETS 

Coil 1 

R22, A01102, No Fan

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a031216a.dat SUMMARY FILENAME: a031216a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 35172.37 1870.22 

 Indoor Dry-Bulb : 79.847 0.35 Sensible Cap (Btu/h): 27501.92 541.05 

Indoor Inlet Dew (F): 60.414 0.55 Latent Cap (Btu/h): 7670.45 1669.75 

Indoor Exit Dry-Bulb: 57.177 0.59 EvapAir Delta T (F): 24.64 0.44 

 Indoor Exit Dew (F): 56.227 0.95 Air/Ref Cap Prcnt Diff: 3.16 7.82 

 Sensible Heat Ratio: 0.782 0.0357 

 Indoor Airflow (CFM): 995.24 7.59 SCFM per Ton: 345.94 

Indoor Airflow (SCFM): 1013.97 7.68 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011194 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009608 

 Barometric Pressure (in HG): 29.96 Nozzle Temp (F): 56.87 0.55 

 Air Chamber Nozzle Pressure Drop (in Water): 1.332 0.020 

 Evaporator Coil Air Pressure Drop (in Water): 0.200 0.007 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 258.17 3.898 Ref-side Cap (Btu/h) : 36280.23 2439.34 

 Upstream Temp (F): 106.25 0.476 Ref-side Cap (tons): 3.02 0.20 

 Refrigerant Mdot (lbm/h): 575.01 39.17 

 Coriolis Density (lbm/ft3): 82.26 0.77 

 Upstream R22 Tsat (F): 115.23 1.159 

 Average Subcooling (F): 8.98 1.231 

 

Evap Exit Pressure (psia): 94.11 1.213 

 Evap Exit Avg Temp : 57.64 4.189 

 Exit Superheat (F): 10.52 3.862 

 Evap Exit Tsat (F): 47.13 0.761 

57
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a031218a.dat SUMMARY FILENAME: a031218a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 38226.98 1139.85 

 Indoor Dry-Bulb : 80.193 0.40 Sensible Cap (Btu/h): 29108.93 735.90 

Indoor Inlet Dew (F): 60.613 0.63 Latent Cap (Btu/h): 9118.05 921.08 

Indoor Exit Dry-Bulb: 55.959 1.09 EvapAir Delta T (F): 26.11 0.66 

 Indoor Exit Dew (F): 55.653 0.55 Air/Ref Cap Prcnt Diff: 4.70 2.57 

 Sensible Heat Ratio: 0.761 0.0210 

 Indoor Airflow (CFM): 1001.86 17.80 SCFM per Ton: 317.85 

Indoor Airflow (SCFM): 1012.53 17.34 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011395 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009507 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 55.66 0.92 

 Air Chamber Nozzle Pressure Drop (in Water): 1.339 0.046 

 Evaporator Coil Air Pressure Drop (in Water): 0.211 0.006 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.72 2.680 Ref-side Cap (Btu/h) : 40021.38 1132.54 

 Upstream Temp (F): 104.33 0.781 Ref-side Cap (tons): 3.34 0.09 

 Refrigerant Mdot (lbm/h): 628.23 17.22 

 Coriolis Density (lbm/ft3): 81.73 0.52 

 Upstream R22 Tsat (F): 118.61 0.771 

 Average Subcooling (F): 14.27 0.991 

 

Evap Exit Pressure (psia): 91.05 1.456 

 Evap Exit Avg Temp : 56.59 2.244 

 Exit Superheat (F): 11.41 1.933 

 Evap Exit Tsat (F): 45.18 0.937 

58
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a031218b.dat SUMMARY FILENAME: a031218b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 28751.99 1236.15 

 Indoor Dry-Bulb : 80.040 0.64 Sensible Cap (Btu/h): 23904.52 675.89 

Indoor Inlet Dew (F): 60.201 0.85 Latent Cap (Btu/h): 4847.46 1439.20 

Indoor Exit Dry-Bulb: 60.446 0.55 EvapAir Delta T (F): 21.55 0.65 

 Indoor Exit Dew (F): 57.614 0.40 Air/Ref Cap Prcnt Diff: 1.70 10.06 

 Sensible Heat Ratio: 0.831 0.0432 

 Indoor Airflow (CFM): 1004.88 19.23 SCFM per Ton: 420.26 

Indoor Airflow (SCFM): 1006.94 18.75 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011227 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010217 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 59.90 0.78 

 Air Chamber Nozzle Pressure Drop (in Water): 1.336 0.050 

 Evaporator Coil Air Pressure Drop (in Water): 0.186 0.006 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 263.16 3.898 Ref-side Cap (Btu/h) : 29238.19 2647.34 

 Upstream Temp (F): 106.15 0.476 Ref-side Cap (tons): 2.44 0.22 

 Refrigerant Mdot (lbm/h): 463.18 41.95 

 Coriolis Density (lbm/ft3): 82.34 0.44 

 Upstream R22 Tsat (F): 116.70 1.142 

 Average Subcooling (F): 10.55 1.129 

 

Evap Exit Pressure (psia): 97.30 1.092 

 Evap Exit Avg Temp : 60.43 4.243 

 Exit Superheat (F): 11.32 4.689 

 Evap Exit Tsat (F): 49.11 0.668 

 

59
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040105a.dat SUMMARY FILENAME: a040105a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 42951.53 1660.25 

 Indoor Dry-Bulb : 80.221 0.58 Sensible Cap (Btu/h): 31907.84 1084.17 

Indoor Inlet Dew (F): 60.321 0.90 Latent Cap (Btu/h): 11043.69 1769.65 

Indoor Exit Dry-Bulb: 53.609 0.78 EvapAir Delta T (F): 28.59 0.88 

 Indoor Exit Dew (F): 54.113 0.58 Air/Ref Cap Prcnt Diff: 4.12 6.78 

 Sensible Heat Ratio: 0.743 0.0319 

 Indoor Airflow (CFM): 994.75 11.31 SCFM per Ton: 283.38 

Indoor Airflow (SCFM): 1014.32 11.62 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011218 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008935 

 Barometric Pressure (in HG): 29.80 Nozzle Temp (F): 53.84 1.11 

 Air Chamber Nozzle Pressure Drop (in Water): 1.332 0.030 

 Evaporator Coil Air Pressure Drop (in Water): 0.233 0.010 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 247.77 3.289 Ref-side Cap (Btu/h) : 44718.18 2028.31 

 Upstream Temp (F): 103.08 0.651 Ref-side Cap (tons): 3.73 0.17 

 Refrigerant Mdot (lbm/h): 697.60 32.61 

 Coriolis Density (lbm/ft3): 81.39 0.58 

 Upstream R22 Tsat (F): 112.09 1.010 

 Average Subcooling (F): 9.01 1.335 

 

Evap Exit Pressure (psia): 82.17 1.334 

 Evap Exit Avg Temp : 55.72 4.586 

 Exit Superheat (F): 16.47 4.310 

 Evap Exit Tsat (F): 39.25 0.928 

60
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040106a.dat SUMMARY FILENAME: a040106a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 29066.22 1028.82 

 Indoor Dry-Bulb : 80.127 0.53 Sensible Cap (Btu/h): 23807.89 1479.10 

Indoor Inlet Dew (F): 60.391 1.19 Latent Cap (Btu/h): 5258.33 1463.71 

Indoor Exit Dry-Bulb: 60.618 0.78 EvapAir Delta T (F): 21.40 1.30 

 Indoor Exit Dew (F): 57.586 0.55 Air/Ref Cap Prcnt Diff: -0.33 7.26 

 Sensible Heat Ratio: 0.819 0.0450 

 Indoor Airflow (CFM): 1003.02 11.71 SCFM per Ton: 417.11 

Indoor Airflow (SCFM): 1010.32 11.26 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011239 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010148 

 Barometric Pressure (in HG): 29.82 Nozzle Temp (F): 60.17 0.69 

 Air Chamber Nozzle Pressure Drop (in Water): 1.337 0.030 

 Evaporator Coil Air Pressure Drop (in Water): 0.205 0.006 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 277.93 2.680 Ref-side Cap (Btu/h) : 28969.38 2550.83 

 Upstream Temp (F): 106.41 1.016 Ref-side Cap (tons): 2.41 0.21 

 Refrigerant Mdot (lbm/h): 459.52 39.02 

 Coriolis Density (lbm/ft3): 82.58 0.25 

 Upstream R22 Tsat (F): 120.95 0.754 

 Average Subcooling (F): 14.53 1.221 

 

Evap Exit Pressure (psia): 97.68 1.092 

 Evap Exit Avg Temp : 60.34 6.253 

 Exit Superheat (F): 11.01 5.661 

 Evap Exit Tsat (F): 49.33 0.666 

61
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040106b.dat SUMMARY FILENAME: a040106b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 43160.68 1322.97 

 Indoor Dry-Bulb : 80.200 0.56 Sensible Cap (Btu/h): 31693.62 1212.47 

Indoor Inlet Dew (F): 60.615 0.79 Latent Cap (Btu/h): 11467.06 1103.23 

Indoor Exit Dry-Bulb: 53.835 0.82 EvapAir Delta T (F): 28.28 0.88 

 Indoor Exit Dew (F): 54.234 0.88 Air/Ref Cap Prcnt Diff: 3.83 7.30 

 Sensible Heat Ratio: 0.734 0.0240 

 Indoor Airflow (CFM): 998.32 8.90 SCFM per Ton: 283.18 

Indoor Airflow (SCFM): 1018.50 9.47 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011330 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008969 

 Barometric Pressure (in HG): 29.82 Nozzle Temp (F): 53.90 0.79 

 Air Chamber Nozzle Pressure Drop (in Water): 1.342 0.024 

 Evaporator Coil Air Pressure Drop (in Water): 0.227 0.006 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 256.74 6.334 Ref-side Cap (Btu/h) : 44811.32 2412.50 

 Upstream Temp (F): 105.66 1.212 Ref-side Cap (tons): 3.73 0.20 

 Refrigerant Mdot (lbm/h): 708.12 37.74 

 Coriolis Density (lbm/ft3): 82.23 0.65 

 Upstream R22 Tsat (F): 114.80 1.885 

 Average Subcooling (F): 9.14 1.941 

 

Evap Exit Pressure (psia): 83.48 1.698 

 Evap Exit Avg Temp : 55.55 6.429 

 Exit Superheat (F): 15.39 6.523 

 Evap Exit Tsat (F): 40.16 1.166 

62
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040106c.dat SUMMARY FILENAME: a040106c.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 37684.76 2294.76 

 Indoor Dry-Bulb : 80.306 0.53 Sensible Cap (Btu/h): 29012.99 1198.92 

Indoor Inlet Dew (F): 60.153 1.06 Latent Cap (Btu/h): 8671.77 1663.84 

Indoor Exit Dry-Bulb: 56.339 0.90 EvapAir Delta T (F): 25.92 0.88 

 Indoor Exit Dew (F): 55.373 0.66 Air/Ref Cap Prcnt Diff: 1.68 6.76 

 Sensible Heat Ratio: 0.770 0.0305 

 Indoor Airflow (CFM): 1001.35 10.45 SCFM per Ton: 323.93 

Indoor Airflow (SCFM): 1017.26 9.57 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011142 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009355 

 Barometric Pressure (in HG): 29.82 Nozzle Temp (F): 55.99 0.88 

 Air Chamber Nozzle Pressure Drop (in Water): 1.344 0.027 

 Evaporator Coil Air Pressure Drop (in Water): 0.217 0.005 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 261.11 2.680 Ref-side Cap (Btu/h) : 38311.76 1857.38 

 Upstream Temp (F): 105.03 1.061 Ref-side Cap (tons): 3.19 0.15 

 Refrigerant Mdot (lbm/h): 603.49 30.41 

 Coriolis Density (lbm/ft3): 82.11 0.52 

 Upstream R22 Tsat (F): 116.10 0.790 

 Average Subcooling (F): 11.07 0.938 

 

Evap Exit Pressure (psia): 89.86 1.456 

 Evap Exit Avg Temp : 57.73 3.112 

 Exit Superheat (F): 13.31 2.874 

 Evap Exit Tsat (F): 44.42 0.945 

63
Coil 2 

R22, A01070, No Fan

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040116a.dat SUMMARY FILENAME: a040116a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 20154.12 719.94 

 Indoor Dry-Bulb : 79.789 0.60 Sensible Cap (Btu/h): 17010.06 488.46 

Indoor Inlet Dew (F): 60.417 0.50 Latent Cap (Btu/h): 3144.06 761.03 

Indoor Exit Dry-Bulb: 62.508 0.74 EvapAir Delta T (F): 19.09 0.44 

 Indoor Exit Dew (F): 58.360 0.40 Air/Ref Cap Prcnt Diff: 1.37 3.74 

 Sensible Heat Ratio: 0.844 0.0335 

 Indoor Airflow (CFM): 809.55 6.98 SCFM per Ton: 481.49 

Indoor Airflow (SCFM): 808.66 7.38 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011315 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010499 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 61.60 0.91 

 Air Chamber Nozzle Pressure Drop (in Water): 0.866 0.015 

 Evaporator Coil Air Pressure Drop (in Water): 0.075 0.005 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 262.38 1.340 Ref-side Cap (Btu/h) : 20429.82 535.58 

 Upstream Temp (F): 103.41 0.677 Ref-side Cap (tons): 1.70 0.04 

 Refrigerant Mdot (lbm/h): 319.23 9.16 

 Coriolis Density (lbm/ft3): 81.95 0.16 

 Upstream R22 Tsat (F): 116.47 0.394 

 Average Subcooling (F): 13.06 0.505 

 

Evap Exit Pressure (psia): 90.62 0.485 

 Evap Exit Avg Temp : 59.63 1.905 

 Exit Superheat (F): 14.72 2.148 

 Evap Exit Tsat (F): 44.91 0.313 

64
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040116a.dat SUMMARY FILENAME: a040116a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 20154.12 719.94 

 Indoor Dry-Bulb : 79.789 0.60 Sensible Cap (Btu/h): 17010.06 488.46 

Indoor Inlet Dew (F): 60.417 0.50 Latent Cap (Btu/h): 3144.06 761.03 

Indoor Exit Dry-Bulb: 62.508 0.74 EvapAir Delta T (F): 19.09 0.44 

 Indoor Exit Dew (F): 58.360 0.40 Air/Ref Cap Prcnt Diff: 1.37 3.74 

 Sensible Heat Ratio: 0.844 0.0335 

 Indoor Airflow (CFM): 809.55 6.98 SCFM per Ton: 481.49 

Indoor Airflow (SCFM): 808.66 7.38 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011315 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010499 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 61.60 0.91 

 Air Chamber Nozzle Pressure Drop (in Water): 0.866 0.015 

 Evaporator Coil Air Pressure Drop (in Water): 0.075 0.005 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 262.38 1.340 Ref-side Cap (Btu/h) : 20429.82 535.58 

 Upstream Temp (F): 103.41 0.677 Ref-side Cap (tons): 1.70 0.04 

 Refrigerant Mdot (lbm/h): 319.23 9.16 

 Coriolis Density (lbm/ft3): 81.95 0.16 

 Upstream R22 Tsat (F): 116.47 0.394 

 Average Subcooling (F): 13.06 0.505 

 

Evap Exit Pressure (psia): 90.62 0.485 

 Evap Exit Avg Temp : 59.63 1.905 

 Exit Superheat (F): 14.72 2.148 

 Evap Exit Tsat (F): 44.91 0.313 

65
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040116b.dat SUMMARY FILENAME: a040116b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 12918.77 789.67 

 Indoor Dry-Bulb : 79.796 0.56 Sensible Cap (Btu/h): 12648.04 554.30 

Indoor Inlet Dew (F): 60.435 0.84 Latent Cap (Btu/h): 270.73 1125.53 

Indoor Exit Dry-Bulb: 67.321 0.86 EvapAir Delta T (F): 14.26 0.65 

 Indoor Exit Dew (F): 60.263 0.66 Air/Ref Cap Prcnt Diff: 1.07 6.01 

 Sensible Heat Ratio: 0.979 0.0856 

 Indoor Airflow (CFM): 813.14 9.68 SCFM per Ton: 747.34 

Indoor Airflow (SCFM): 804.56 9.01 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011322 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.011251 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 66.36 1.64 

 Air Chamber Nozzle Pressure Drop (in Water): 0.866 0.020 

 Evaporator Coil Air Pressure Drop (in Water): 0.066 0.005 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 264.15 0.731 Ref-side Cap (Btu/h) : 13054.22 511.78 

 Upstream Temp (F): 104.96 0.542 Ref-side Cap (tons): 1.09 0.04 

 Refrigerant Mdot (lbm/h): 205.56 8.43 

 Coriolis Density (lbm/ft3): 82.60 0.32 

 Upstream R22 Tsat (F): 116.99 0.214 

 Average Subcooling (F): 12.03 0.614 

 

Evap Exit Pressure (psia): 97.48 1.092 

 Evap Exit Avg Temp : 65.53 1.224 

 Exit Superheat (F): 16.32 1.741 

 Evap Exit Tsat (F): 49.21 0.666 

66
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040119a.dat SUMMARY FILENAME: a040119a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 24917.81 718.96 

 Indoor Dry-Bulb : 79.836 0.39 Sensible Cap (Btu/h): 19597.48 514.71 

Indoor Inlet Dew (F): 60.327 0.80 Latent Cap (Btu/h): 5320.33 650.76 

Indoor Exit Dry-Bulb: 59.747 0.72 EvapAir Delta T (F): 21.91 0.44 

 Indoor Exit Dew (F): 56.767 0.50 Air/Ref Cap Prcnt Diff: 2.24 3.20 

 Sensible Heat Ratio: 0.787 0.0238 

 Indoor Airflow (CFM): 808.89 8.66 SCFM per Ton: 391.26 

Indoor Airflow (SCFM): 812.44 8.25 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011277 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009905 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 58.93 0.65 

 Air Chamber Nozzle Pressure Drop (in Water): 0.869 0.018 

 Evaporator Coil Air Pressure Drop (in Water): 0.078 0.006 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 267.30 0.974 Ref-side Cap (Btu/h) : 25473.46 406.33 

 Upstream Temp (F): 105.31 0.610 Ref-side Cap (tons): 2.12 0.03 

 Refrigerant Mdot (lbm/h): 401.83 6.23 

 Coriolis Density (lbm/ft3): 82.41 0.36 

 Upstream R22 Tsat (F): 117.91 0.282 

 Average Subcooling (F): 12.60 0.661 

 

Evap Exit Pressure (psia): 83.58 0.485 

 Evap Exit Avg Temp : 54.97 2.180 

 Exit Superheat (F): 14.74 2.108 

 Evap Exit Tsat (F): 40.22 0.333 

67
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040119b.dat SUMMARY FILENAME: a040119b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 20189.62 1211.57 

 Indoor Dry-Bulb : 79.724 0.56 Sensible Cap (Btu/h): 16949.08 903.59 

Indoor Inlet Dew (F): 60.387 1.22 Latent Cap (Btu/h): 3240.53 1052.94 

Indoor Exit Dry-Bulb: 62.620 0.61 EvapAir Delta T (F): 19.01 0.87 

 Indoor Exit Dew (F): 58.265 0.66 Air/Ref Cap Prcnt Diff: 0.36 7.19 

 Sensible Heat Ratio: 0.840 0.0486 

 Indoor Airflow (CFM): 810.32 9.82 SCFM per Ton: 481.09 

Indoor Airflow (SCFM): 809.42 9.70 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011302 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010463 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 61.61 0.55 

 Air Chamber Nozzle Pressure Drop (in Water): 0.868 0.021 

 Evaporator Coil Air Pressure Drop (in Water): 0.075 0.004 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 265.97 1.462 Ref-side Cap (Btu/h) : 20258.54 775.30 

 Upstream Temp (F): 105.55 0.519 Ref-side Cap (tons): 1.69 0.06 

 Refrigerant Mdot (lbm/h): 319.95 11.72 

 Coriolis Density (lbm/ft3): 82.53 0.56 

 Upstream R22 Tsat (F): 117.52 0.425 

 Average Subcooling (F): 11.97 0.670 

 

Evap Exit Pressure (psia): 90.71 0.607 

 Evap Exit Avg Temp : 59.55 1.869 

 Exit Superheat (F): 14.58 1.791 

 Evap Exit Tsat (F): 44.97 0.391 

68
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040121a.dat SUMMARY FILENAME: a040121a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 13113.32 956.28 

 Indoor Dry-Bulb : 80.145 0.30 Sensible Cap (Btu/h): 12617.08 431.95 

Indoor Inlet Dew (F): 60.711 0.69 Latent Cap (Btu/h): 496.25 974.54 

Indoor Exit Dry-Bulb: 67.736 0.55 EvapAir Delta T (F): 14.16 0.44 

 Indoor Exit Dew (F): 60.395 0.53 Air/Ref Cap Prcnt Diff: -3.01 8.47 

 Sensible Heat Ratio: 0.963 0.0714 

 Indoor Airflow (CFM): 809.05 8.27 SCFM per Ton: 739.70 

Indoor Airflow (SCFM): 808.33 8.12 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011319 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.011190 

 Barometric Pressure (in HG): 29.95 Nozzle Temp (F): 66.56 0.72 

 Air Chamber Nozzle Pressure Drop (in Water): 0.865 0.017 

 Evaporator Coil Air Pressure Drop (in Water): 0.066 0.006 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 259.38 1.218 Ref-side Cap (Btu/h) : 12712.62 464.37 

 Upstream Temp (F): 104.33 0.435 Ref-side Cap (tons): 1.06 0.04 

 Refrigerant Mdot (lbm/h): 199.55 7.33 

 Coriolis Density (lbm/ft3): 82.36 0.16 

 Upstream R22 Tsat (F): 115.59 0.361 

 Average Subcooling (F): 11.26 0.607 

 

Evap Exit Pressure (psia): 99.70 0.607 

 Evap Exit Avg Temp : 65.65 0.892 

 Exit Superheat (F): 15.10 1.143 

 Evap Exit Tsat (F): 50.56 0.365 

 

69
Coil 3 

R22, A01148, No Fan

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040205a.dat SUMMARY FILENAME: a040205a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 41040.73 1364.36 

 Indoor Dry-Bulb : 79.463 0.23 Sensible Cap (Btu/h): 27659.16 873.81 

Indoor Inlet Dew (F): 60.632 0.44 Latent Cap (Btu/h): 13381.57 655.21 

Indoor Exit Dry-Bulb: 55.072 0.38 EvapAir Delta T (F): 26.26 0.44 

 Indoor Exit Dew (F): 52.370 0.41 Air/Ref Cap Prcnt Diff: 2.87 4.66 

 Sensible Heat Ratio: 0.674 0.0119 

 Indoor Airflow (CFM): 929.07 19.21 SCFM per Ton: 280.16 

Indoor Airflow (SCFM): 958.17 19.81 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011184 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008256 

 Barometric Pressure (in HG): 30.22 Nozzle Temp (F): 55.25 0.88 

 Air Chamber Nozzle Pressure Drop (in Water): 1.175 0.048 

 Evaporator Coil Air Pressure Drop (in Water): 0.358 0.016 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 273.51 2.193 Ref-side Cap (Btu/h) : 42213.99 650.68 

 Upstream Temp (F): 105.26 0.520 Ref-side Cap (tons): 3.52 0.05 

 Refrigerant Mdot (lbm/h): 665.74 10.62 

 Coriolis Density (lbm/ft3): 82.17 0.33 

 Upstream R22 Tsat (F): 119.69 0.625 

 Average Subcooling (F): 14.43 0.947 

 

Evap Exit Pressure (psia): 83.57 0.728 

 Evap Exit Avg Temp : 57.45 2.513 

 Exit Superheat (F): 17.24 2.347 

 Evap Exit Tsat (F): 40.22 0.498 

70
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040209a.dat SUMMARY FILENAME: a040209a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 30896.46 694.06 

 Indoor Dry-Bulb : 79.728 0.51 Sensible Cap (Btu/h): 22952.69 764.15 

Indoor Inlet Dew (F): 60.549 0.38 Latent Cap (Btu/h): 7943.77 517.21 

Indoor Exit Dry-Bulb: 59.655 0.39 EvapAir Delta T (F): 22.04 0.86 

 Indoor Exit Dew (F): 55.835 0.32 Air/Ref Cap Prcnt Diff: -1.06 2.84 

 Sensible Heat Ratio: 0.743 0.0153 

 Indoor Airflow (CFM): 925.27 13.65 SCFM per Ton: 367.48 

Indoor Airflow (SCFM): 946.16 13.96 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011135 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009375 

 Barometric Pressure (in HG): 30.26 Nozzle Temp (F): 60.01 0.28 

 Air Chamber Nozzle Pressure Drop (in Water): 1.156 0.034 

 Evaporator Coil Air Pressure Drop (in Water): 0.348 0.012 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 267.52 0.731 Ref-side Cap (Btu/h) : 30568.21 436.20 

 Upstream Temp (F): 104.48 0.480 Ref-side Cap (tons): 2.55 0.04 

 Refrigerant Mdot (lbm/h): 480.19 7.69 

 Coriolis Density (lbm/ft3): 81.94 0.38 

 Upstream R22 Tsat (F): 117.97 0.212 

 Average Subcooling (F): 13.49 0.586 

 

Evap Exit Pressure (psia): 97.44 0.485 

 Evap Exit Avg Temp : 60.39 2.736 

 Exit Superheat (F): 11.20 2.884 

 Evap Exit Tsat (F): 49.19 0.297 

71
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040209b.dat SUMMARY FILENAME: a040209b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 41393.85 883.37 

 Indoor Dry-Bulb : 80.019 0.52 Sensible Cap (Btu/h): 27938.72 683.02 

Indoor Inlet Dew (F): 60.502 0.30 Latent Cap (Btu/h): 13455.14 489.03 

Indoor Exit Dry-Bulb: 55.085 0.39 EvapAir Delta T (F): 26.72 0.44 

 Indoor Exit Dew (F): 52.064 0.34 Air/Ref Cap Prcnt Diff: -0.24 2.76 

 Sensible Heat Ratio: 0.675 0.0102 

 Indoor Airflow (CFM): 920.26 12.52 SCFM per Ton: 275.80 

Indoor Airflow (SCFM): 951.37 12.85 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011116 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008151 

 Barometric Pressure (in HG): 30.26 Nozzle Temp (F): 54.73 0.65 

 Air Chamber Nozzle Pressure Drop (in Water): 1.156 0.031 

 Evaporator Coil Air Pressure Drop (in Water): 0.349 0.014 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 274.99 1.340 Ref-side Cap (Btu/h) : 41292.35 720.00 

 Upstream Temp (F): 105.87 0.909 Ref-side Cap (tons): 3.44 0.06 

 Refrigerant Mdot (lbm/h): 653.21 10.26 

 Coriolis Density (lbm/ft3): 82.34 0.60 

 Upstream R22 Tsat (F): 120.11 0.380 

 Average Subcooling (F): 14.24 1.163 

 

Evap Exit Pressure (psia): 83.38 0.971 

 Evap Exit Avg Temp : 53.47 4.966 

 Exit Superheat (F): 13.38 4.716 

 Evap Exit Tsat (F): 40.09 0.667 

72
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040210a.dat SUMMARY FILENAME: a040210a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 35323.45 1001.75 

 Indoor Dry-Bulb : 79.862 0.41 Sensible Cap (Btu/h): 24841.59 604.71 

Indoor Inlet Dew (F): 60.568 0.68 Latent Cap (Btu/h): 10481.86 1001.13 

Indoor Exit Dry-Bulb: 57.472 0.54 EvapAir Delta T (F): 24.22 0.65 

 Indoor Exit Dew (F): 54.086 0.29 Air/Ref Cap Prcnt Diff: 3.52 4.05 

 Sensible Heat Ratio: 0.703 0.0216 

 Indoor Airflow (CFM): 906.77 6.99 SCFM per Ton: 316.85 

Indoor Airflow (SCFM): 932.67 7.17 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011150 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008794 

 Barometric Pressure (in HG): 30.24 Nozzle Temp (F): 56.84 0.75 

 Air Chamber Nozzle Pressure Drop (in Water): 1.117 0.017 

 Evaporator Coil Air Pressure Drop (in Water): 0.334 0.007 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 268.66 0.974 Ref-side Cap (Btu/h) : 36563.86 598.74 

 Upstream Temp (F): 104.33 0.498 Ref-side Cap (tons): 3.05 0.05 

 Refrigerant Mdot (lbm/h): 573.95 9.71 

 Coriolis Density (lbm/ft3): 81.89 0.36 

 Upstream R22 Tsat (F): 118.30 0.281 

 Average Subcooling (F): 13.97 0.508 

 

Evap Exit Pressure (psia): 90.59 0.485 

 Evap Exit Avg Temp : 59.09 2.837 

 Exit Superheat (F): 14.20 2.837 

 Evap Exit Tsat (F): 44.89 0.313 

73
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040211a.dat SUMMARY FILENAME: a040211a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 28797.52 635.22 

 Indoor Dry-Bulb : 79.830 0.53 Sensible Cap (Btu/h): 22212.84 940.77 

Indoor Inlet Dew (F): 60.172 0.50 Latent Cap (Btu/h): 6584.67 551.13 

Indoor Exit Dry-Bulb: 60.467 0.32 EvapAir Delta T (F): 21.15 0.86 

 Indoor Exit Dew (F): 56.318 0.29 Air/Ref Cap Prcnt Diff: 0.04 2.65 

 Sensible Heat Ratio: 0.771 0.0215 

 Indoor Airflow (CFM): 936.15 14.99 SCFM per Ton: 397.62 

Indoor Airflow (SCFM): 954.21 15.48 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011025 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009579 

 Barometric Pressure (in HG): 30.15 Nozzle Temp (F): 59.73 0.65 

 Air Chamber Nozzle Pressure Drop (in Water): 1.180 0.038 

 Evaporator Coil Air Pressure Drop (in Water): 0.340 0.010 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 266.91 0.853 Ref-side Cap (Btu/h) : 28808.32 546.01 

 Upstream Temp (F): 104.74 0.367 Ref-side Cap (tons): 2.40 0.05 

 Refrigerant Mdot (lbm/h): 453.13 8.79 

 Coriolis Density (lbm/ft3): 82.05 0.40 

 Upstream R22 Tsat (F): 117.80 0.247 

 Average Subcooling (F): 13.06 0.367 

 

Evap Exit Pressure (psia): 98.26 0.607 

 Evap Exit Avg Temp : 62.18 2.732 

 Exit Superheat (F): 12.49 2.732 

 Evap Exit Tsat (F): 49.69 0.369 

74
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040211b.dat SUMMARY FILENAME: a040211b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 36747.94 789.39 

 Indoor Dry-Bulb : 80.029 0.45 Sensible Cap (Btu/h): 25913.75 926.16 

Indoor Inlet Dew (F): 60.367 0.36 Latent Cap (Btu/h): 10834.19 457.19 

Indoor Exit Dry-Bulb: 57.210 0.23 EvapAir Delta T (F): 24.69 0.65 

 Indoor Exit Dew (F): 53.785 0.32 Air/Ref Cap Prcnt Diff: -0.41 3.06 

 Sensible Heat Ratio: 0.705 0.0118 

 Indoor Airflow (CFM): 930.35 10.67 SCFM per Ton: 311.64 

Indoor Airflow (SCFM): 954.35 12.08 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011103 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008723 

 Barometric Pressure (in HG): 30.15 Nozzle Temp (F): 56.70 0.60 

 Air Chamber Nozzle Pressure Drop (in Water): 1.172 0.028 

 Evaporator Coil Air Pressure Drop (in Water): 0.343 0.012 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.10 0.974 Ref-side Cap (Btu/h) : 36596.26 594.50 

 Upstream Temp (F): 104.40 0.520 Ref-side Cap (tons): 3.05 0.05 

 Refrigerant Mdot (lbm/h): 574.65 9.71 

 Coriolis Density (lbm/ft3): 81.89 0.19 

 Upstream R22 Tsat (F): 118.43 0.281 

 Average Subcooling (F): 14.03 0.731 

 

Evap Exit Pressure (psia): 90.35 0.728 

 Evap Exit Avg Temp : 56.66 3.573 

 Exit Superheat (F): 11.93 3.494 

 Evap Exit Tsat (F): 44.73 0.471 

75
Coil 4 

R22, A01138, No Fan

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040219x.dat SUMMARY FILENAME: a040219x.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 26783.74 1883.79 

 Indoor Dry-Bulb : 79.733 0.75 Sensible Cap (Btu/h): 18268.01 480.03 

Indoor Inlet Dew (F): 60.591 0.85 Latent Cap (Btu/h): 8515.73 1438.99 

Indoor Exit Dry-Bulb: 60.736 0.27 EvapAir Delta T (F): 20.89 0.44 

 Indoor Exit Dew (F): 54.512 0.22 Air/Ref Cap Prcnt Diff: -3.06 7.01 

 Sensible Heat Ratio: 0.682 0.0356 

 Indoor Airflow (CFM): 784.16 9.68 SCFM per Ton: 356.16 

Indoor Airflow (SCFM): 794.93 10.13 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011259 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009013 

 Barometric Pressure (in HG): 29.98 Nozzle Temp (F): 60.11 0.55 

 Air Chamber Nozzle Pressure Drop (in Water): 0.825 0.020 

 Evaporator Coil Air Pressure Drop (in Water): 0.103 0.005 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 272.62 0.974 Ref-side Cap (Btu/h) : 25954.80 364.19 

 Upstream Temp (F): 106.07 0.198 Ref-side Cap (tons): 2.16 0.03 

 Refrigerant Mdot (lbm/h): 410.99 5.50 

 Coriolis Density (lbm/ft3): 82.36 0.16 

 Upstream R22 Tsat (F): 119.44 0.278 

 Average Subcooling (F): 13.37 0.301 

 

Evap Exit Pressure (psia): 82.89 0.485 

 Evap Exit Avg Temp : 53.49 3.724 

 Exit Superheat (F): 13.74 3.640 

 Evap Exit Tsat (F): 39.75 0.335 

76
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040223a.dat SUMMARY FILENAME: a040223a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 22035.41 717.30 

 Indoor Dry-Bulb : 79.831 0.38 Sensible Cap (Btu/h): 16037.57 564.10 

Indoor Inlet Dew (F): 60.757 0.25 Latent Cap (Btu/h): 5997.85 366.03 

Indoor Exit Dry-Bulb: 63.300 0.29 EvapAir Delta T (F): 18.31 0.43 

 Indoor Exit Dew (F): 56.680 0.24 Air/Ref Cap Prcnt Diff: -1.11 3.19 

 Sensible Heat Ratio: 0.728 0.0115 

 Indoor Airflow (CFM): 797.03 14.29 SCFM per Ton: 433.12 

Indoor Airflow (SCFM): 795.33 14.25 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011454 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009873 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 62.30 0.82 

 Air Chamber Nozzle Pressure Drop (in Water): 0.839 0.030 

 Evaporator Coil Air Pressure Drop (in Water): 0.102 0.008 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 271.21 0.731 Ref-side Cap (Btu/h) : 21790.52 420.49 

 Upstream Temp (F): 104.30 0.520 Ref-side Cap (tons): 1.82 0.04 

 Refrigerant Mdot (lbm/h): 342.00 6.96 

 Coriolis Density (lbm/ft3): 82.11 0.16 

 Upstream R22 Tsat (F): 119.04 0.209 

 Average Subcooling (F): 14.73 0.614 

 

Evap Exit Pressure (psia): 90.96 0.243 

 Evap Exit Avg Temp : 56.93 4.399 

 Exit Superheat (F): 11.80 4.399 

 Evap Exit Tsat (F): 45.12 0.156 

77
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040225a.dat SUMMARY FILENAME: a040225a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 18269.45 1171.80 

 Indoor Dry-Bulb : 80.022 0.51 Sensible Cap (Btu/h): 14746.16 529.64 

Indoor Inlet Dew (F): 60.413 0.20 Latent Cap (Btu/h): 3523.29 695.37 

Indoor Exit Dry-Bulb: 64.826 0.28 EvapAir Delta T (F): 16.93 0.43 

 Indoor Exit Dew (F): 58.000 0.61 Air/Ref Cap Prcnt Diff: -3.42 5.96 

 Sensible Heat Ratio: 0.807 0.0264 

 Indoor Airflow (CFM): 782.66 8.87 SCFM per Ton: 519.44 

Indoor Airflow (SCFM): 790.82 9.75 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011122 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010188 

 Barometric Pressure (in HG): 30.15 Nozzle Temp (F): 64.41 0.64 

 Air Chamber Nozzle Pressure Drop (in Water): 0.819 0.019 

 Evaporator Coil Air Pressure Drop (in Water): 0.101 0.006 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 267.89 0.487 Ref-side Cap (Btu/h) : 17640.72 256.55 

 Upstream Temp (F): 104.71 0.520 Ref-side Cap (tons): 1.47 0.02 

 Refrigerant Mdot (lbm/h): 277.43 4.21 

 Coriolis Density (lbm/ft3): 82.22 0.16 

 Upstream R22 Tsat (F): 118.08 0.141 

 Average Subcooling (F): 13.37 0.590 

 

Evap Exit Pressure (psia): 97.83 0.243 

 Evap Exit Avg Temp : 62.27 0.682 

 Exit Superheat (F): 12.84 0.694 

 Evap Exit Tsat (F): 49.43 0.148 

78
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040226x.dat SUMMARY FILENAME: a040226x.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 22162.66 746.55 

 Indoor Dry-Bulb : 79.824 0.48 Sensible Cap (Btu/h): 16293.07 683.39 

Indoor Inlet Dew (F): 60.511 0.30 Latent Cap (Btu/h): 5869.59 264.85 

Indoor Exit Dry-Bulb: 62.849 0.23 EvapAir Delta T (F): 18.75 0.65 

 Indoor Exit Dew (F): 56.419 0.24 Air/Ref Cap Prcnt Diff: -2.32 4.07 

 Sensible Heat Ratio: 0.735 0.0134 

 Indoor Airflow (CFM): 783.74 11.71 SCFM per Ton: 427.28 

Indoor Airflow (SCFM): 789.14 11.92 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011249 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009689 

 Barometric Pressure (in HG): 29.92 Nozzle Temp (F): 62.38 0.74 

 Air Chamber Nozzle Pressure Drop (in Water): 0.819 0.024 

 Evaporator Coil Air Pressure Drop (in Water): 0.102 0.006 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.24 0.731 Ref-side Cap (Btu/h) : 21646.36 359.14 

 Upstream Temp (F): 105.78 0.649 Ref-side Cap (tons): 1.80 0.03 

 Refrigerant Mdot (lbm/h): 342.26 5.68 

 Coriolis Density (lbm/ft3): 82.45 0.22 

 Upstream R22 Tsat (F): 118.47 0.211 

 Average Subcooling (F): 12.69 0.511 

 

Evap Exit Pressure (psia): 90.58 0.243 

 Evap Exit Avg Temp : 59.46 0.975 

 Exit Superheat (F): 14.58 1.131 

 Evap Exit Tsat (F): 44.88 0.157 

79
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040225b.dat SUMMARY FILENAME: b040225b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 26781.23 822.37 

 Indoor Dry-Bulb : 80.166 0.54 Sensible Cap (Btu/h): 18704.64 613.34 

Indoor Inlet Dew (F): 60.286 0.36 Latent Cap (Btu/h): 8076.59 295.67 

Indoor Exit Dry-Bulb: 60.610 0.30 EvapAir Delta T (F): 21.40 0.44 

 Indoor Exit Dew (F): 54.447 0.26 Air/Ref Cap Prcnt Diff: -2.53 4.62 

 Sensible Heat Ratio: 0.698 0.0098 

 Indoor Airflow (CFM): 779.61 15.74 SCFM per Ton: 356.06 

Indoor Airflow (SCFM): 794.65 16.13 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011071 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008940 

 Barometric Pressure (in HG): 30.15 Nozzle Temp (F): 60.23 0.76 

 Air Chamber Nozzle Pressure Drop (in Water): 0.820 0.033 

 Evaporator Coil Air Pressure Drop (in Water): 0.105 0.009 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 270.17 0.974 Ref-side Cap (Btu/h) : 26102.18 1283.93 

 Upstream Temp (F): 106.27 0.609 Ref-side Cap (tons): 2.18 0.11 

 Refrigerant Mdot (lbm/h): 413.75 20.15 

 Coriolis Density (lbm/ft3): 82.51 0.32 

 Upstream R22 Tsat (F): 118.74 0.280 

 Average Subcooling (F): 12.47 0.542 

 

Evap Exit Pressure (psia): 83.86 0.485 

 Evap Exit Avg Temp : 54.70 3.049 

 Exit Superheat (F): 14.28 3.049 

 Evap Exit Tsat (F): 40.41 0.332 

80
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040226b.dat SUMMARY FILENAME: b040226b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 16953.69 572.29 

 Indoor Dry-Bulb : 80.011 0.45 Sensible Cap (Btu/h): 14077.80 482.68 

Indoor Inlet Dew (F): 60.711 0.16 Latent Cap (Btu/h): 2875.89 368.36 

Indoor Exit Dry-Bulb: 65.498 0.29 EvapAir Delta T (F): 16.19 0.43 

 Indoor Exit Dew (F): 58.787 0.25 Air/Ref Cap Prcnt Diff: -2.57 4.27 

 Sensible Heat Ratio: 0.830 0.0187 

 Indoor Airflow (CFM): 788.03 16.16 SCFM per Ton: 558.45 

Indoor Airflow (SCFM): 788.99 15.66 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011330 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010566 

 Barometric Pressure (in HG): 29.92 Nozzle Temp (F): 65.08 0.69 

 Air Chamber Nozzle Pressure Drop (in Water): 0.823 0.033 

 Evaporator Coil Air Pressure Drop (in Water): 0.099 0.005 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 271.82 0.487 Ref-side Cap (Btu/h) : 16516.48 372.06 

 Upstream Temp (F): 104.56 0.366 Ref-side Cap (tons): 1.38 0.03 

 Refrigerant Mdot (lbm/h): 259.56 5.68 

 Coriolis Density (lbm/ft3): 82.29 0.10 

 Upstream R22 Tsat (F): 119.21 0.139 

 Average Subcooling (F): 14.65 0.463 

 

Evap Exit Pressure (psia): 99.80 0.485 

 Evap Exit Avg Temp : 63.23 0.685 

 Exit Superheat (F): 12.61 0.938 

 Evap Exit Tsat (F): 50.62 0.291 

81
Coil 5 

R22, A01060, Fan: 273 Watts

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040302a.dat SUMMARY FILENAME: a040302a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 27580.34 853.16 

 Indoor Dry-Bulb : 80.145 0.29 Sensible Cap (Btu/h): 18827.50 513.83 

Indoor Inlet Dew (F): 60.357 0.36 Latent Cap (Btu/h): 8752.84 468.87 

Indoor Exit Dry-Bulb: 59.345 0.23 EvapAir Delta T (F): 22.72 0.44 

 Indoor Exit Dew (F): 53.644 0.22 Air/Ref Cap Prcnt Diff: -1.58 4.17 

 Sensible Heat Ratio: 0.683 0.0121 

 Indoor Airflow (CFM): 740.22 7.76 SCFM per Ton: 327.76 

Indoor Airflow (SCFM): 753.31 7.78 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011164 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008728 

 Barometric Pressure (in HG): 29.98 Nozzle Temp (F): 58.15 0.32 

 Air Chamber Nozzle Pressure Drop (in Water): 0.739 0.015 

 Evaporator Coil Air Pressure Drop (in Water): 0.124 0.028 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 268.54 0.731 Ref-side Cap (Btu/h) : 27142.87 616.61 

 Upstream Temp (F): 105.08 0.584 Ref-side Cap (tons): 2.26 0.05 

 Refrigerant Mdot (lbm/h): 427.67 9.16 

 Coriolis Density (lbm/ft3): 82.27 0.29 

 Upstream R22 Tsat (F): 118.27 0.211 

 Average Subcooling (F): 13.19 0.661 

 

Evap Exit Pressure (psia): 90.74 0.485 

 Evap Exit Avg Temp : 59.50 2.420 

 Exit Superheat (F): 14.52 2.420 

 Evap Exit Tsat (F): 44.99 0.313 

82
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040303a.dat SUMMARY FILENAME: a040303a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 32329.27 833.92 

 Indoor Dry-Bulb : 80.024 0.52 Sensible Cap (Btu/h): 20840.09 612.93 

Indoor Inlet Dew (F): 60.435 0.21 Latent Cap (Btu/h): 11489.18 334.36 

Indoor Exit Dry-Bulb: 56.983 0.27 EvapAir Delta T (F): 24.98 0.44 

 Indoor Exit Dew (F): 51.431 0.18 Air/Ref Cap Prcnt Diff: -0.37 2.91 

 Sensible Heat Ratio: 0.645 0.0055 

 Indoor Airflow (CFM): 745.45 9.82 SCFM per Ton: 281.75 

Indoor Airflow (SCFM): 759.07 9.93 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011245 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008071 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 55.80 0.42 

 Air Chamber Nozzle Pressure Drop (in Water): 0.749 0.020 

 Evaporator Coil Air Pressure Drop (in Water): 0.136 0.041 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.50 1.218 Ref-side Cap (Btu/h) : 32208.02 435.83 

 Upstream Temp (F): 104.63 0.910 Ref-side Cap (tons): 2.68 0.04 

 Refrigerant Mdot (lbm/h): 506.34 6.41 

 Coriolis Density (lbm/ft3): 81.99 0.30 

 Upstream R22 Tsat (F): 118.55 0.351 

 Average Subcooling (F): 13.91 1.170 

 

Evap Exit Pressure (psia): 83.54 0.607 

 Evap Exit Avg Temp : 52.65 6.498 

 Exit Superheat (F): 12.45 6.498 

 Evap Exit Tsat (F): 40.20 0.416 

83
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040304a.dat SUMMARY FILENAME: a040304a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 27488.36 891.82 

 Indoor Dry-Bulb : 79.846 0.71 Sensible Cap (Btu/h): 18592.08 788.83 

Indoor Inlet Dew (F): 60.399 0.31 Latent Cap (Btu/h): 8896.27 337.31 

Indoor Exit Dry-Bulb: 59.306 0.39 EvapAir Delta T (F): 22.46 0.87 

 Indoor Exit Dew (F): 53.625 0.36 Air/Ref Cap Prcnt Diff: -1.74 3.39 

 Sensible Heat Ratio: 0.676 0.0109 

 Indoor Airflow (CFM): 746.16 7.72 SCFM per Ton: 328.46 

Indoor Airflow (SCFM): 752.41 7.79 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011269 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008790 

 Barometric Pressure (in HG): 29.75 Nozzle Temp (F): 58.88 0.37 

 Air Chamber Nozzle Pressure Drop (in Water): 0.744 0.015 

 Evaporator Coil Air Pressure Drop (in Water): 0.140 0.024 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.51 1.096 Ref-side Cap (Btu/h) : 27008.54 440.01 

 Upstream Temp (F): 104.56 0.520 Ref-side Cap (tons): 2.25 0.04 

 Refrigerant Mdot (lbm/h): 424.44 6.59 

 Coriolis Density (lbm/ft3): 82.02 0.38 

 Upstream R22 Tsat (F): 118.55 0.316 

 Average Subcooling (F): 13.99 0.598 

 

Evap Exit Pressure (psia): 90.05 0.243 

 Evap Exit Avg Temp : 59.41 5.210 

 Exit Superheat (F): 14.87 5.052 

 Evap Exit Tsat (F): 44.54 0.157 

84
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040303b.dat SUMMARY FILENAME: b040303b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 23217.01 492.17 

 Indoor Dry-Bulb : 79.842 0.67 Sensible Cap (Btu/h): 16981.94 465.27 

Indoor Inlet Dew (F): 60.418 0.12 Latent Cap (Btu/h): 6235.07 176.50 

Indoor Exit Dry-Bulb: 61.269 0.35 EvapAir Delta T (F): 20.49 0.43 

 Indoor Exit Dew (F): 55.823 0.20 Air/Ref Cap Prcnt Diff: -1.71 2.83 

 Sensible Heat Ratio: 0.731 0.0106 

 Indoor Airflow (CFM): 747.39 4.97 SCFM per Ton: 389.23 

Indoor Airflow (SCFM): 753.05 5.01 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011238 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009502 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 60.81 0.64 

 Air Chamber Nozzle Pressure Drop (in Water): 0.745 0.010 

 Evaporator Coil Air Pressure Drop (in Water): 0.146 0.014 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 272.97 0.853 Ref-side Cap (Btu/h) : 22818.98 413.37 

 Upstream Temp (F): 104.56 0.416 Ref-side Cap (tons): 1.90 0.03 

 Refrigerant Mdot (lbm/h): 358.60 6.78 

 Coriolis Density (lbm/ft3): 82.08 0.37 

 Upstream R22 Tsat (F): 119.54 0.243 

 Average Subcooling (F): 14.98 0.448 

 

Evap Exit Pressure (psia): 98.39 0.485 

 Evap Exit Avg Temp : 64.17 1.260 

 Exit Superheat (F): 14.40 1.260 

 Evap Exit Tsat (F): 49.77 0.294 

85
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040305a.dat SUMMARY FILENAME: a040305a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 32479.54 1003.87 

 Indoor Dry-Bulb : 79.740 0.52 Sensible Cap (Btu/h): 20659.92 970.81 

Indoor Inlet Dew (F): 60.443 0.46 Latent Cap (Btu/h): 11819.62 344.26 

Indoor Exit Dry-Bulb: 56.551 0.39 EvapAir Delta T (F): 24.94 1.08 

 Indoor Exit Dew (F): 51.099 0.32 Air/Ref Cap Prcnt Diff: -0.93 3.45 

 Sensible Heat Ratio: 0.636 0.0130 

 Indoor Airflow (CFM): 743.16 7.82 SCFM per Ton: 278.47 

Indoor Airflow (SCFM): 753.71 7.68 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011286 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.007999 

 Barometric Pressure (in HG): 29.75 Nozzle Temp (F): 56.13 0.55 

 Air Chamber Nozzle Pressure Drop (in Water): 0.742 0.015 

 Evaporator Coil Air Pressure Drop (in Water): 0.151 0.028 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.37 0.853 Ref-side Cap (Btu/h) : 32175.10 333.48 

 Upstream Temp (F): 104.35 0.967 Ref-side Cap (tons): 2.68 0.03 

 Refrigerant Mdot (lbm/h): 505.11 5.68 

 Coriolis Density (lbm/ft3): 81.88 0.33 

 Upstream R22 Tsat (F): 118.51 0.246 

 Average Subcooling (F): 14.16 1.177 

 

Evap Exit Pressure (psia): 83.93 0.364 

 Evap Exit Avg Temp : 54.32 3.954 

 Exit Superheat (F): 13.86 3.954 

 Evap Exit Tsat (F): 40.46 0.249 

86
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040308a.dat SUMMARY FILENAME: a040308a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 22605.73 521.66 

 Indoor Dry-Bulb : 79.710 0.39 Sensible Cap (Btu/h): 16356.36 502.56 

Indoor Inlet Dew (F): 60.687 0.30 Latent Cap (Btu/h): 6249.36 290.00 

Indoor Exit Dry-Bulb: 61.590 0.11 EvapAir Delta T (F): 19.86 0.43 

 Indoor Exit Dew (F): 56.086 0.16 Air/Ref Cap Prcnt Diff: -1.31 2.36 

 Sensible Heat Ratio: 0.724 0.0103 

 Indoor Airflow (CFM): 742.04 6.90 SCFM per Ton: 397.08 

Indoor Airflow (SCFM): 748.02 6.88 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011336 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009585 

 Barometric Pressure (in HG): 29.88 Nozzle Temp (F): 61.04 0.10 

 Air Chamber Nozzle Pressure Drop (in Water): 0.735 0.013 

 Evaporator Coil Air Pressure Drop (in Water): 0.161 0.015 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 270.28 0.731 Ref-side Cap (Btu/h) : 22309.53 298.84 

 Upstream Temp (F): 105.69 0.237 Ref-side Cap (tons): 1.86 0.02 

 Refrigerant Mdot (lbm/h): 352.58 4.76 

 Coriolis Density (lbm/ft3): 82.32 0.18 

 Upstream R22 Tsat (F): 118.77 0.210 

 Average Subcooling (F): 13.08 0.386 

 

Evap Exit Pressure (psia): 98.45 0.364 

 Evap Exit Avg Temp : 63.73 0.793 

 Exit Superheat (F): 13.92 0.657 

 Evap Exit Tsat (F): 49.81 0.221 

87
Coil 6 

R22, A01125, Fan: 768 Watts

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: c040406c.dat SUMMARY FILENAME: c040406c.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 37805.35 4574.21 

 Indoor Dry-Bulb : 79.347 3.97 Sensible Cap (Btu/h): 26735.16 4315.08 

Indoor Inlet Dew (F): 60.944 0.45 Latent Cap (Btu/h): 11070.19 1947.82 

Indoor Exit Dry-Bulb: 60.804 1.28 EvapAir Delta T (F): 20.91 3.44 

 Indoor Exit Dew (F): 55.682 1.19 Air/Ref Cap Prcnt Diff: -0.44 13.23 

 Sensible Heat Ratio: 0.707 0.0418 

 Indoor Airflow (CFM): 1149.21 25.49 SCFM per Ton: 368.71 

Indoor Airflow (SCFM): 1161.61 28.57 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011438 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009440 

 Barometric Pressure (in HG): 29.89 Nozzle Temp (F): 60.06 1.13 

 Air Chamber Nozzle Pressure Drop (in Water): 0.918 0.043 

 Evaporator Coil Air Pressure Drop (in Water): 1.700 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 266.79 3.350 Ref-side Cap (Btu/h) : 37608.27 993.66 

 Upstream Temp (F): 104.78 1.051 Ref-side Cap (tons): 3.13 0.08 

 Refrigerant Mdot (lbm/h): 591.66 13.92 

 Coriolis Density (lbm/ft3): 81.51 0.28 

 Upstream R22 Tsat (F): 117.76 0.973 

 Average Subcooling (F): 12.98 1.617 

 

Evap Exit Pressure (psia): 101.49 1.638 

 Evap Exit Avg Temp : 65.58 5.368 

 Exit Superheat (F): 13.95 4.545 

 Evap Exit Tsat (F): 51.63 0.974 

88
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040407a.dat SUMMARY FILENAME: a040407a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 43850.60 5098.57 

 Indoor Dry-Bulb : 79.491 3.63 Sensible Cap (Btu/h): 29605.56 5146.04 

Indoor Inlet Dew (F): 60.528 0.70 Latent Cap (Btu/h): 14245.04 1882.32 

Indoor Exit Dry-Bulb: 58.585 1.12 EvapAir Delta T (F): 23.15 3.89 

 Indoor Exit Dew (F): 53.483 1.08 Air/Ref Cap Prcnt Diff: 0.37 13.50 

 Sensible Heat Ratio: 0.675 0.0485 

 Indoor Airflow (CFM): 1144.88 18.17 SCFM per Ton: 318.18 

Indoor Airflow (SCFM): 1162.70 18.00 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011283 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008714 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 57.15 1.38 

 Air Chamber Nozzle Pressure Drop (in Water): 0.915 0.029 

 Evaporator Coil Air Pressure Drop (in Water): 1.700 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 268.66 2.741 Ref-side Cap (Btu/h) : 43985.34 1308.50 

 Upstream Temp (F): 105.44 1.872 Ref-side Cap (tons): 3.67 0.11 

 Refrigerant Mdot (lbm/h): 694.28 21.62 

 Coriolis Density (lbm/ft3): 81.89 0.33 

 Upstream R22 Tsat (F): 118.30 0.791 

 Average Subcooling (F): 12.87 1.662 

 

Evap Exit Pressure (psia): 95.81 1.395 

 Evap Exit Avg Temp : 62.16 4.507 

 Exit Superheat (F): 13.98 3.719 

 Evap Exit Tsat (F): 48.19 0.864 

89
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: d040406d.dat SUMMARY FILENAME: d040406d.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 37704.09 1035.50 

 Indoor Dry-Bulb : 79.017 0.79 Sensible Cap (Btu/h): 26399.92 873.21 

Indoor Inlet Dew (F): 61.007 0.41 Latent Cap (Btu/h): 11304.17 631.67 

Indoor Exit Dry-Bulb: 60.679 0.43 EvapAir Delta T (F): 20.73 0.76 

 Indoor Exit Dew (F): 55.613 0.34 Air/Ref Cap Prcnt Diff: -0.30 3.53 

 Sensible Heat Ratio: 0.700 0.0088 

 Indoor Airflow (CFM): 1143.97 24.09 SCFM per Ton: 368.25 

Indoor Airflow (SCFM): 1157.04 24.16 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011464 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009416 

 Barometric Pressure (in HG): 29.89 Nozzle Temp (F): 59.74 0.64 

 Air Chamber Nozzle Pressure Drop (in Water): 0.910 0.038 

 Evaporator Coil Air Pressure Drop (in Water): 1.700 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 266.07 0.670 Ref-side Cap (Btu/h) : 37587.47 526.25 

 Upstream Temp (F): 104.36 0.401 Ref-side Cap (tons): 3.13 0.04 

 Refrigerant Mdot (lbm/h): 590.11 7.69 

 Coriolis Density (lbm/ft3): 81.47 0.27 

 Upstream R22 Tsat (F): 117.55 0.195 

 Average Subcooling (F): 13.19 0.542 

 

Evap Exit Pressure (psia): 101.34 0.485 

 Evap Exit Avg Temp : 65.33 1.689 

 Exit Superheat (F): 13.80 1.545 

 Evap Exit Tsat (F): 51.54 0.288 

90
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040402.dat SUMMARY FILENAME: a040402.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 40037.46 1134.23 

 Indoor Dry-Bulb : 79.643 0.37 Sensible Cap (Btu/h): 28653.79 899.47 

Indoor Inlet Dew (F): 60.353 0.49 Latent Cap (Btu/h): 11383.68 598.35 

Indoor Exit Dry-Bulb: 59.392 0.35 EvapAir Delta T (F): 22.52 0.55 

 Indoor Exit Dew (F): 54.835 0.37 Air/Ref Cap Prcnt Diff: 0.26 3.31 

 Sensible Heat Ratio: 0.716 0.0107 

 Indoor Airflow (CFM): 1150.15 21.70 SCFM per Ton: 346.57 

Indoor Airflow (SCFM): 1156.30 21.69 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011288 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009225 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 58.74 0.46 

 Air Chamber Nozzle Pressure Drop (in Water): 0.915 0.034 

 Evaporator Coil Air Pressure Drop (in Water): 1.715 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.74 1.157 Ref-side Cap (Btu/h) : 40140.11 525.17 

 Upstream Temp (F): 104.20 0.668 Ref-side Cap (tons): 3.35 0.04 

 Refrigerant Mdot (lbm/h): 629.67 7.24 

 Coriolis Density (lbm/ft3): 81.40 0.19 

 Upstream R22 Tsat (F): 118.61 0.333 

 Average Subcooling (F): 14.41 0.720 

 

Evap Exit Pressure (psia): 97.93 0.667 

 Evap Exit Avg Temp : 63.23 0.965 

 Exit Superheat (F): 13.74 0.708 

 Evap Exit Tsat (F): 49.49 0.406 

91
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040406a.dat SUMMARY FILENAME: a040406a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 28898.20 1928.90 

 Indoor Dry-Bulb : 79.742 0.41 Sensible Cap (Btu/h): 23756.23 986.39 

Indoor Inlet Dew (F): 60.351 0.22 Latent Cap (Btu/h): 5141.97 2225.49 

Indoor Exit Dry-Bulb: 63.430 0.22 EvapAir Delta T (F): 18.63 0.75 

 Indoor Exit Dew (F): 57.963 1.02 Air/Ref Cap Prcnt Diff: -0.64 7.75 

 Sensible Heat Ratio: 0.822 0.0644 

 Indoor Airflow (CFM): 1149.71 20.13 SCFM per Ton: 480.72 

Indoor Airflow (SCFM): 1157.67 19.85 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011195 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010264 

 Barometric Pressure (in HG): 29.89 Nozzle Temp (F): 61.80 0.46 

 Air Chamber Nozzle Pressure Drop (in Water): 0.915 0.031 

 Evaporator Coil Air Pressure Drop (in Water): 1.700 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 274.96 1.279 Ref-side Cap (Btu/h) : 28706.78 937.54 

 Upstream Temp (F): 105.07 0.511 Ref-side Cap (tons): 2.39 0.08 

 Refrigerant Mdot (lbm/h): 452.28 14.65 

 Coriolis Density (lbm/ft3): 81.89 0.38 

 Upstream R22 Tsat (F): 120.10 0.363 

 Average Subcooling (F): 15.04 0.649 

 

Evap Exit Pressure (psia): 107.81 0.303 

 Evap Exit Avg Temp : 70.32 0.946 

 Exit Superheat (F): 15.03 0.948 

 Evap Exit Tsat (F): 55.29 0.172 

92
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040402b.dat SUMMARY FILENAME: b040402b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 39504.41 778.58 

 Indoor Dry-Bulb : 79.763 0.63 Sensible Cap (Btu/h): 28482.79 688.71 

Indoor Inlet Dew (F): 60.350 0.36 Latent Cap (Btu/h): 11021.62 799.76 

Indoor Exit Dry-Bulb: 59.632 0.26 EvapAir Delta T (F): 22.39 0.43 

 Indoor Exit Dew (F): 55.021 0.24 Air/Ref Cap Prcnt Diff: 0.42 1.91 

 Sensible Heat Ratio: 0.721 0.0173 

 Indoor Airflow (CFM): 1150.36 15.38 SCFM per Ton: 351.11 

Indoor Airflow (SCFM): 1155.87 15.45 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011287 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009288 

 Barometric Pressure (in HG): 29.65 Nozzle Temp (F): 59.01 0.32 

 Air Chamber Nozzle Pressure Drop (in Water): 0.915 0.024 

 Evaporator Coil Air Pressure Drop (in Water): 1.715 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.24 0.974 Ref-side Cap (Btu/h) : 39670.12 616.85 

 Upstream Temp (F): 104.51 0.652 Ref-side Cap (tons): 3.31 0.05 

 Refrigerant Mdot (lbm/h): 623.27 9.62 

 Coriolis Density (lbm/ft3): 81.43 0.27 

 Upstream R22 Tsat (F): 118.47 0.281 

 Average Subcooling (F): 13.96 0.793 

 

Evap Exit Pressure (psia): 98.41 0.485 

 Evap Exit Avg Temp : 63.64 0.929 

 Exit Superheat (F): 13.86 0.709 

 Evap Exit Tsat (F): 49.78 0.294 

93
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040407b.dat SUMMARY FILENAME: b040407b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 29255.90 822.80 

 Indoor Dry-Bulb : 79.329 0.59 Sensible Cap (Btu/h): 22885.70 580.88 

Indoor Inlet Dew (F): 60.954 0.52 Latent Cap (Btu/h): 6370.21 425.88 

Indoor Exit Dry-Bulb: 63.454 0.37 EvapAir Delta T (F): 18.12 0.22 

 Indoor Exit Dew (F): 58.003 0.42 Air/Ref Cap Prcnt Diff: 1.42 2.38 

 Sensible Heat Ratio: 0.782 0.0113 

 Indoor Airflow (CFM): 1140.82 24.11 SCFM per Ton: 470.27 

Indoor Airflow (SCFM): 1146.51 24.02 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011457 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010293 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 62.10 0.62 

 Air Chamber Nozzle Pressure Drop (in Water): 0.900 0.038 

 Evaporator Coil Air Pressure Drop (in Water): 1.700 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 273.21 1.340 Ref-side Cap (Btu/h) : 29670.07 566.32 

 Upstream Temp (F): 104.45 0.510 Ref-side Cap (tons): 2.47 0.05 

 Refrigerant Mdot (lbm/h): 466.02 8.15 

 Coriolis Density (lbm/ft3): 81.61 0.36 

 Upstream R22 Tsat (F): 119.61 0.382 

 Average Subcooling (F): 15.15 0.739 

 

Evap Exit Pressure (psia): 108.49 0.607 

 Evap Exit Avg Temp : 67.60 1.244 

 Exit Superheat (F): 11.92 1.107 

 Evap Exit Tsat (F): 55.68 0.342 

94
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040410a.dat SUMMARY FILENAME: a040410a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 41868.75 1269.75 

 Indoor Dry-Bulb : 80.137 0.67 Sensible Cap (Btu/h): 29034.75 990.29 

Indoor Inlet Dew (F): 60.569 0.12 Latent Cap (Btu/h): 12834.01 529.88 

Indoor Exit Dry-Bulb: 59.695 0.19 EvapAir Delta T (F): 22.68 0.54 

 Indoor Exit Dew (F): 54.315 0.11 Air/Ref Cap Prcnt Diff: 0.57 5.66 

 Sensible Heat Ratio: 0.693 0.0079 

 Indoor Airflow (CFM): 1148.39 30.81 SCFM per Ton: 333.47 

Indoor Airflow (SCFM): 1163.50 31.34 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011299 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008987 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 58.29 0.44 

 Air Chamber Nozzle Pressure Drop (in Water): 0.919 0.049 

 Evaporator Coil Air Pressure Drop (in Water): 1.635 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 271.76 1.218 Ref-side Cap (Btu/h) : 42104.06 1447.15 

 Upstream Temp (F): 105.80 0.768 Ref-side Cap (tons): 3.51 0.12 

 Refrigerant Mdot (lbm/h): 665.81 23.54 

 Coriolis Density (lbm/ft3): 82.00 0.58 

 Upstream R22 Tsat (F): 119.19 0.349 

 Average Subcooling (F): 13.39 0.856 

 

Evap Exit Pressure (psia): 98.72 0.303 

 Evap Exit Avg Temp : 62.09 1.047 

 Exit Superheat (F): 12.13 1.002 

 Evap Exit Tsat (F): 49.97 0.184 

95
Coil 7 

R22, H5326, No Fan

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040506a.dat SUMMARY FILENAME: a040506a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 29842.95 280.91 

 Indoor Dry-Bulb : 80.478 0.22 Sensible Cap (Btu/h): 24549.15 294.40 

Indoor Inlet Dew (F): 60.104 0.10 Latent Cap (Btu/h): 5293.80 140.99 

Indoor Exit Dry-Bulb: 64.374 0.12 EvapAir Delta T (F): 18.49 0.11 

 Indoor Exit Dew (F): 57.725 0.07 Air/Ref Cap Prcnt Diff: -1.65 2.38 

 Sensible Heat Ratio: 0.823 0.0044 

 Indoor Airflow (CFM): 1203.06 9.21 SCFM per Ton: 484.88 

Indoor Airflow (SCFM): 1205.86 9.40 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011097 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010177 

 Barometric Pressure (in HG): 29.88 Nozzle Temp (F): 63.84 0.46 

 Air Chamber Nozzle Pressure Drop (in Water): 0.997 0.015 

 Evaporator Coil Air Pressure Drop (in Water): 0.224 0.010 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.40 0.487 Ref-side Cap (Btu/h) : 29350.36 597.02 

 Upstream Temp (F): 104.63 0.304 Ref-side Cap (tons): 2.45 0.05 

 Refrigerant Mdot (lbm/h): 461.40 8.79 

 Coriolis Density (lbm/ft3): 81.70 0.33 

 Upstream R22 Tsat (F): 118.51 0.140 

 Average Subcooling (F): 13.89 0.363 

 

Evap Exit Pressure (psia): 84.38 0.303 

 Evap Exit Avg Temp : 52.33 1.624 

 Exit Superheat (F): 11.56 1.537 

 Evap Exit Tsat (F): 40.77 0.206 

96
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040507a.dat SUMMARY FILENAME: a040507a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 25857.20 551.41 

 Indoor Dry-Bulb : 79.848 0.35 Sensible Cap (Btu/h): 22239.56 436.75 

Indoor Inlet Dew (F): 60.543 0.10 Latent Cap (Btu/h): 3617.64 217.35 

Indoor Exit Dry-Bulb: 65.465 0.23 EvapAir Delta T (F): 16.75 0.00 

 Indoor Exit Dew (F): 58.962 0.11 Air/Ref Cap Prcnt Diff: -1.85 2.08 

 Sensible Heat Ratio: 0.860 0.0073 

 Indoor Airflow (CFM): 1206.00 22.60 SCFM per Ton: 559.05 

Indoor Airflow (SCFM): 1204.62 23.63 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011289 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010659 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 64.90 0.46 

 Air Chamber Nozzle Pressure Drop (in Water): 0.999 0.038 

 Evaporator Coil Air Pressure Drop (in Water): 0.221 0.010 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 272.58 0.731 Ref-side Cap (Btu/h) : 25378.56 556.29 

 Upstream Temp (F): 105.77 0.300 Ref-side Cap (tons): 2.11 0.05 

 Refrigerant Mdot (lbm/h): 401.25 8.61 

 Coriolis Density (lbm/ft3): 82.11 0.16 

 Upstream R22 Tsat (F): 119.43 0.209 

 Average Subcooling (F): 13.66 0.282 

 

Evap Exit Pressure (psia): 90.38 0.364 

 Evap Exit Avg Temp : 56.10 0.960 

 Exit Superheat (F): 11.35 0.862 

 Evap Exit Tsat (F): 44.75 0.235 

97
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040510a.dat SUMMARY FILENAME: a040510a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 22002.44 704.07 

 Indoor Dry-Bulb : 79.966 0.46 Sensible Cap (Btu/h): 20601.59 599.35 

Indoor Inlet Dew (F): 60.200 0.06 Latent Cap (Btu/h): 1400.84 220.96 

Indoor Exit Dry-Bulb: 66.622 0.23 EvapAir Delta T (F): 15.54 0.43 

 Indoor Exit Dew (F): 59.592 0.06 Air/Ref Cap Prcnt Diff: -4.94 3.95 

 Sensible Heat Ratio: 0.936 0.0094 

 Indoor Airflow (CFM): 1210.01 17.49 SCFM per Ton: 656.15 

Indoor Airflow (SCFM): 1203.07 17.29 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011188 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010943 

 Barometric Pressure (in HG): 29.75 Nozzle Temp (F): 65.48 0.59 

 Air Chamber Nozzle Pressure Drop (in Water): 1.001 0.029 

 Evaporator Coil Air Pressure Drop (in Water): 0.215 0.008 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 266.78 2.071 Ref-side Cap (Btu/h) : 20914.67 485.59 

 Upstream Temp (F): 104.31 0.680 Ref-side Cap (tons): 1.74 0.04 

 Refrigerant Mdot (lbm/h): 328.26 7.24 

 Coriolis Density (lbm/ft3): 81.79 0.31 

 Upstream R22 Tsat (F): 117.76 0.601 

 Average Subcooling (F): 13.45 0.686 

 

Evap Exit Pressure (psia): 98.08 0.546 

 Evap Exit Avg Temp : 63.42 1.807 

 Exit Superheat (F): 13.85 1.659 

 Evap Exit Tsat (F): 49.58 0.332 

98
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040513a.dat SUMMARY FILENAME: a040513a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 29846.20 378.77 

 Indoor Dry-Bulb : 79.918 0.24 Sensible Cap (Btu/h): 24101.01 316.28 

Indoor Inlet Dew (F): 60.550 0.10 Latent Cap (Btu/h): 5745.19 232.49 

Indoor Exit Dry-Bulb: 64.014 0.17 EvapAir Delta T (F): 18.08 0.11 

 Indoor Exit Dew (F): 58.012 0.08 Air/Ref Cap Prcnt Diff: -0.50 3.91 

 Sensible Heat Ratio: 0.808 0.0063 

 Indoor Airflow (CFM): 1207.72 16.23 SCFM per Ton: 486.62 

Indoor Airflow (SCFM): 1210.32 15.90 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011291 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010296 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 63.29 0.62 

 Air Chamber Nozzle Pressure Drop (in Water): 1.005 0.027 

 Evaporator Coil Air Pressure Drop (in Water): 0.219 0.010 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 272.31 0.487 Ref-side Cap (Btu/h) : 29695.17 974.02 

 Upstream Temp (F): 104.46 0.455 Ref-side Cap (tons): 2.47 0.08 

 Refrigerant Mdot (lbm/h): 466.43 15.02 

 Coriolis Density (lbm/ft3): 81.86 1.27 

 Upstream R22 Tsat (F): 119.35 0.139 

 Average Subcooling (F): 14.89 0.525 

 

Evap Exit Pressure (psia): 83.66 0.485 

 Evap Exit Avg Temp : 55.15 1.583 

 Exit Superheat (F): 14.88 1.532 

 Evap Exit Tsat (F): 40.28 0.333 

99
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040507b.dat SUMMARY FILENAME: b040507b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 21930.45 583.25 

 Indoor Dry-Bulb : 79.714 0.18 Sensible Cap (Btu/h): 20248.31 604.31 

Indoor Inlet Dew (F): 60.607 0.15 Latent Cap (Btu/h): 1682.14 243.13 

Indoor Exit Dry-Bulb: 66.684 0.24 EvapAir Delta T (F): 15.32 0.33 

 Indoor Exit Dew (F): 59.882 0.08 Air/Ref Cap Prcnt Diff: -5.72 3.59 

 Sensible Heat Ratio: 0.923 0.0096 

 Indoor Airflow (CFM): 1206.24 18.32 SCFM per Ton: 656.24 

Indoor Airflow (SCFM): 1199.31 18.21 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011350 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.011055 

 Barometric Pressure (in HG): 29.76 Nozzle Temp (F): 65.62 0.14 

 Air Chamber Nozzle Pressure Drop (in Water): 0.995 0.030 

 Evaporator Coil Air Pressure Drop (in Water): 0.214 0.009 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 268.75 0.731 Ref-side Cap (Btu/h) : 20674.47 475.79 

 Upstream Temp (F): 105.77 0.454 Ref-side Cap (tons): 1.72 0.04 

 Refrigerant Mdot (lbm/h): 326.88 6.78 

 Coriolis Density (lbm/ft3): 82.22 0.16 

 Upstream R22 Tsat (F): 118.33 0.211 

 Average Subcooling (F): 12.56 0.584 

 

Evap Exit Pressure (psia): 98.92 0.182 

 Evap Exit Avg Temp : 63.26 0.613 

 Exit Superheat (F): 13.17 0.613 

 Evap Exit Tsat (F): 50.09 0.110 

100
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040511b.dat SUMMARY FILENAME: b040511b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 25476.71 634.85 

 Indoor Dry-Bulb : 80.144 0.24 Sensible Cap (Btu/h): 21755.04 534.33 

Indoor Inlet Dew (F): 60.483 0.06 Latent Cap (Btu/h): 3721.67 200.30 

Indoor Exit Dry-Bulb: 65.840 0.17 EvapAir Delta T (F): 16.35 0.22 

 Indoor Exit Dew (F): 58.853 0.03 Air/Ref Cap Prcnt Diff: -3.61 2.99 

 Sensible Heat Ratio: 0.854 0.0060 

 Indoor Airflow (CFM): 1207.11 13.97 SCFM per Ton: 568.77 

Indoor Airflow (SCFM): 1207.54 13.81 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011245 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010599 

 Barometric Pressure (in HG): 29.90 Nozzle Temp (F): 65.02 0.19 

 Air Chamber Nozzle Pressure Drop (in Water): 1.002 0.023 

 Evaporator Coil Air Pressure Drop (in Water): 0.213 0.009 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 271.40 0.731 Ref-side Cap (Btu/h) : 24555.06 415.26 

 Upstream Temp (F): 106.02 0.354 Ref-side Cap (tons): 2.05 0.03 

 Refrigerant Mdot (lbm/h): 388.73 6.59 

 Coriolis Density (lbm/ft3): 82.22 0.41 

 Upstream R22 Tsat (F): 119.09 0.209 

 Average Subcooling (F): 13.07 0.224 

 

Evap Exit Pressure (psia): 90.93 0.303 

 Evap Exit Avg Temp : 58.19 1.001 

 Exit Superheat (F): 13.08 1.080 

 Evap Exit Tsat (F): 45.11 0.195 

101
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040513b.dat SUMMARY FILENAME: b040513b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 29800.83 455.45 

 Indoor Dry-Bulb : 79.832 0.30 Sensible Cap (Btu/h): 24060.94 441.52 

Indoor Inlet Dew (F): 60.562 0.05 Latent Cap (Btu/h): 5739.89 112.39 

Indoor Exit Dry-Bulb: 63.937 0.19 EvapAir Delta T (F): 18.06 0.21 

 Indoor Exit Dew (F): 58.025 0.05 Air/Ref Cap Prcnt Diff: -1.08 3.85 

 Sensible Heat Ratio: 0.807 0.0048 

 Indoor Airflow (CFM): 1206.87 15.11 SCFM per Ton: 486.99 

Indoor Airflow (SCFM): 1209.38 15.22 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011296 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010301 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 63.32 0.46 

 Air Chamber Nozzle Pressure Drop (in Water): 1.003 0.025 

 Evaporator Coil Air Pressure Drop (in Water): 0.219 0.008 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 272.41 0.731 Ref-side Cap (Btu/h) : 29478.53 993.29 

 Upstream Temp (F): 104.49 0.828 Ref-side Cap (tons): 2.46 0.08 

 Refrigerant Mdot (lbm/h): 463.10 14.01 

 Coriolis Density (lbm/ft3): 81.72 1.00 

 Upstream R22 Tsat (F): 119.38 0.209 

 Average Subcooling (F): 14.89 0.849 

 

Evap Exit Pressure (psia): 83.74 0.303 

 Evap Exit Avg Temp : 54.77 1.352 

 Exit Superheat (F): 14.43 1.352 

 Evap Exit Tsat (F): 40.33 0.208 

102
Coil 8 

R22, H5321, No Fan

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040521a.dat SUMMARY FILENAME: a040521a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 34023.81 981.82 

 Indoor Dry-Bulb : 80.133 0.15 Sensible Cap (Btu/h): 29126.82 963.08 

Indoor Inlet Dew (F): 60.562 0.02 Latent Cap (Btu/h): 4896.99 115.91 

Indoor Exit Dry-Bulb: 63.116 0.15 EvapAir Delta T (F): 19.15 0.43 

 Indoor Exit Dew (F): 58.688 0.03 Air/Ref Cap Prcnt Diff: 9.58 3.56 

 Sensible Heat Ratio: 0.856 0.0036 

 Indoor Airflow (CFM): 1375.64 17.99 SCFM per Ton: 486.97 

Indoor Airflow (SCFM): 1380.73 17.33 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011300 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010557 

 Barometric Pressure (in HG): 29.84 Nozzle Temp (F): 62.11 0.60 

 Air Chamber Nozzle Pressure Drop (in Water): 1.304 0.033 

 Evaporator Coil Air Pressure Drop (in Water): 0.312 0.015 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 265.11 0.670 Ref-side Cap (Btu/h) : 37280.82 519.41 

 Upstream Temp (F): 106.24 0.313 Ref-side Cap (tons): 3.11 0.04 

 Refrigerant Mdot (lbm/h): 590.85 8.43 

 Coriolis Density (lbm/ft3): 72.75 0.43 

 Upstream R22 Tsat (F): 117.27 0.195 

 Average Subcooling (F): 11.03 0.384 

 

Evap Exit Pressure (psia): 90.52 0.243 

 Evap Exit Avg Temp : 56.58 1.512 

 Exit Superheat (F): 11.74 1.521 

 Evap Exit Tsat (F): 44.84 0.157 

103
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040525a.dat SUMMARY FILENAME: a040525a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 41587.87 912.40 

 Indoor Dry-Bulb : 80.121 0.31 Sensible Cap (Btu/h): 32532.92 869.32 

Indoor Inlet Dew (F): 60.483 0.06 Latent Cap (Btu/h): 9054.96 215.10 

Indoor Exit Dry-Bulb: 60.967 0.15 EvapAir Delta T (F): 21.33 0.43 

 Indoor Exit Dew (F): 56.923 0.05 Air/Ref Cap Prcnt Diff: 2.90 2.82 

 Sensible Heat Ratio: 0.782 0.0054 

 Indoor Airflow (CFM): 1373.54 11.26 SCFM per Ton: 399.68 

Indoor Airflow (SCFM): 1385.14 11.42 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011265 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009894 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 60.03 0.16 

 Air Chamber Nozzle Pressure Drop (in Water): 1.306 0.021 

 Evaporator Coil Air Pressure Drop (in Water): 0.316 0.008 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.25 0.853 Ref-side Cap (Btu/h) : 42791.57 751.47 

 Upstream Temp (F): 106.11 0.273 Ref-side Cap (tons): 3.57 0.06 

 Refrigerant Mdot (lbm/h): 677.74 12.09 

 Coriolis Density (lbm/ft3): 82.42 0.75 

 Upstream R22 Tsat (F): 118.47 0.246 

 Average Subcooling (F): 12.36 0.273 

 

Evap Exit Pressure (psia): 84.72 0.243 

 Evap Exit Avg Temp : 53.52 2.057 

 Exit Superheat (F): 12.52 2.016 

 Evap Exit Tsat (F): 41.00 0.165 

104
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040526a.dat SUMMARY FILENAME: a040526a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 29513.51 480.65 

 Indoor Dry-Bulb : 79.841 0.15 Sensible Cap (Btu/h): 25443.70 460.28 

Indoor Inlet Dew (F): 60.427 0.06 Latent Cap (Btu/h): 4069.81 275.45 

Indoor Exit Dry-Bulb: 65.396 0.18 EvapAir Delta T (F): 16.71 0.22 

 Indoor Exit Dew (F): 58.878 0.08 Air/Ref Cap Prcnt Diff: -3.10 2.06 

 Sensible Heat Ratio: 0.862 0.0083 

 Indoor Airflow (CFM): 1388.51 16.29 SCFM per Ton: 561.88 

Indoor Airflow (SCFM): 1381.91 16.94 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011291 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010674 

 Barometric Pressure (in HG): 29.72 Nozzle Temp (F): 64.39 0.34 

 Air Chamber Nozzle Pressure Drop (in Water): 1.317 0.031 

 Evaporator Coil Air Pressure Drop (in Water): 0.312 0.016 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 269.95 0.731 Ref-side Cap (Btu/h) : 28597.29 566.54 

 Upstream Temp (F): 105.86 0.390 Ref-side Cap (tons): 2.38 0.05 

 Refrigerant Mdot (lbm/h): 452.35 8.52 

 Coriolis Density (lbm/ft3): 82.50 0.25 

 Upstream R22 Tsat (F): 118.67 0.210 

 Average Subcooling (F): 12.82 0.390 

 

Evap Exit Pressure (psia): 97.57 0.364 

 Evap Exit Avg Temp : 64.00 1.240 

 Exit Superheat (F): 14.73 1.388 

 Evap Exit Tsat (F): 49.27 0.222 

105
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040527a.dat SUMMARY FILENAME: a040527a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 41721.31 1434.02 

 Indoor Dry-Bulb : 80.055 0.17 Sensible Cap (Btu/h): 33072.64 393.65 

Indoor Inlet Dew (F): 60.304 0.60 Latent Cap (Btu/h): 8648.66 1514.12 

Indoor Exit Dry-Bulb: 60.780 0.20 EvapAir Delta T (F): 21.55 0.22 

 Indoor Exit Dew (F): 56.914 0.09 Air/Ref Cap Prcnt Diff: 3.26 5.66 

 Sensible Heat Ratio: 0.793 0.0305 

 Indoor Airflow (CFM): 1381.48 15.68 SCFM per Ton: 400.82 

Indoor Airflow (SCFM): 1393.57 15.10 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011192 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009890 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 59.86 0.53 

 Air Chamber Nozzle Pressure Drop (in Water): 1.321 0.029 

 Evaporator Coil Air Pressure Drop (in Water): 0.318 0.014 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 267.87 0.731 Ref-side Cap (Btu/h) : 43077.28 1092.28 

 Upstream Temp (F): 105.13 0.543 Ref-side Cap (tons): 3.59 0.09 

 Refrigerant Mdot (lbm/h): 678.91 17.22 

 Coriolis Density (lbm/ft3): 82.18 0.34 

 Upstream R22 Tsat (F): 118.07 0.211 

 Average Subcooling (F): 12.94 0.684 

 

Evap Exit Pressure (psia): 84.34 0.485 

 Evap Exit Avg Temp : 55.85 1.507 

 Exit Superheat (F): 15.11 1.507 

 Evap Exit Tsat (F): 40.74 0.330 

106
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040527b.dat SUMMARY FILENAME: b040527b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 41707.19 1020.24 

 Indoor Dry-Bulb : 79.862 0.19 Sensible Cap (Btu/h): 32752.75 819.05 

Indoor Inlet Dew (F): 60.391 0.07 Latent Cap (Btu/h): 8954.44 263.78 

Indoor Exit Dry-Bulb: 60.734 0.09 EvapAir Delta T (F): 21.32 0.32 

 Indoor Exit Dew (F): 56.888 0.03 Air/Ref Cap Prcnt Diff: 3.12 3.21 

 Sensible Heat Ratio: 0.785 0.0048 

 Indoor Airflow (CFM): 1382.69 15.13 SCFM per Ton: 401.39 

Indoor Airflow (SCFM): 1395.06 15.46 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011227 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009881 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 59.77 0.14 

 Air Chamber Nozzle Pressure Drop (in Water): 1.324 0.029 

 Evaporator Coil Air Pressure Drop (in Water): 0.317 0.012 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 268.09 0.731 Ref-side Cap (Btu/h) : 43005.16 831.09 

 Upstream Temp (F): 105.41 0.294 Ref-side Cap (tons): 3.58 0.07 

 Refrigerant Mdot (lbm/h): 678.73 12.46 

 Coriolis Density (lbm/ft3): 82.29 0.47 

 Upstream R22 Tsat (F): 118.14 0.211 

 Average Subcooling (F): 12.72 0.343 

 

Evap Exit Pressure (psia): 84.17 0.243 

 Evap Exit Avg Temp : 54.43 1.860 

 Exit Superheat (F): 13.81 1.943 

 Evap Exit Tsat (F): 40.63 0.165 

107
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040603a.dat SUMMARY FILENAME: a040603a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 34980.44 729.98 

 Indoor Dry-Bulb : 80.150 0.25 Sensible Cap (Btu/h): 29184.59 705.22 

Indoor Inlet Dew (F): 60.541 0.06 Latent Cap (Btu/h): 5795.86 519.27 

Indoor Exit Dry-Bulb: 63.310 0.17 EvapAir Delta T (F): 18.99 0.32 

 Indoor Exit Dew (F): 58.331 0.24 Air/Ref Cap Prcnt Diff: 2.84 2.75 

 Sensible Heat Ratio: 0.834 0.0126 

 Indoor Airflow (CFM): 1390.38 10.12 SCFM per Ton: 478.63 

Indoor Airflow (SCFM): 1395.23 10.23 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011288 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010417 

 Barometric Pressure (in HG): 29.85 Nozzle Temp (F): 62.44 0.46 

 Air Chamber Nozzle Pressure Drop (in Water): 1.331 0.019 

 Evaporator Coil Air Pressure Drop (in Water): 0.312 0.009 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 273.51 0.792 Ref-side Cap (Btu/h) : 35974.64 595.49 

 Upstream Temp (F): 105.60 0.455 Ref-side Cap (tons): 3.00 0.05 

 Refrigerant Mdot (lbm/h): 568.32 9.62 

 Coriolis Density (lbm/ft3): 82.41 0.16 

 Upstream R22 Tsat (F): 119.69 0.225 

 Average Subcooling (F): 14.09 0.620 

 

Evap Exit Pressure (psia): 91.83 0.425 

 Evap Exit Avg Temp : 57.65 1.747 

 Exit Superheat (F): 11.96 1.747 

 Evap Exit Tsat (F): 45.69 0.271 

108
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040607a.dat SUMMARY FILENAME: a040607a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 27090.45 778.33 

 Indoor Dry-Bulb : 80.205 0.17 Sensible Cap (Btu/h): 24679.42 794.58 

Indoor Inlet Dew (F): 60.519 0.06 Latent Cap (Btu/h): 2411.02 212.56 

Indoor Exit Dry-Bulb: 66.346 0.11 EvapAir Delta T (F): 16.11 0.43 

 Indoor Exit Dew (F): 59.617 0.05 Air/Ref Cap Prcnt Diff: -1.12 3.30 

 Sensible Heat Ratio: 0.911 0.0085 

 Indoor Airflow (CFM): 1395.31 13.71 SCFM per Ton: 615.80 

Indoor Airflow (SCFM): 1390.19 13.33 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011294 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010931 

 Barometric Pressure (in HG): 29.81 Nozzle Temp (F): 65.33 0.57 

 Air Chamber Nozzle Pressure Drop (in Water): 1.331 0.026 

 Evaporator Coil Air Pressure Drop (in Water): 0.307 0.013 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 273.06 0.487 Ref-side Cap (Btu/h) : 26784.91 450.70 

 Upstream Temp (F): 105.68 0.315 Ref-side Cap (tons): 2.23 0.04 

 Refrigerant Mdot (lbm/h): 423.29 6.96 

 Coriolis Density (lbm/ft3): 82.46 0.14 

 Upstream R22 Tsat (F): 119.56 0.139 

 Average Subcooling (F): 13.89 0.315 

 

Evap Exit Pressure (psia): 99.96 0.243 

 Evap Exit Avg Temp : 64.36 1.181 

 Exit Superheat (F): 13.65 1.181 

 Evap Exit Tsat (F): 50.71 0.146 

 

109
Coil 9 

R410A, A01154, Fan

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040716a.dat SUMMARY FILENAME: a040716a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 19952.67 354.03 

 Indoor Dry-Bulb : 79.986 0.14 Sensible Cap (Btu/h): 12845.02 284.44 

Indoor Inlet Dew (F): 60.436 0.06 Latent Cap (Btu/h): 7107.65 136.91 

Indoor Exit Dry-Bulb: 58.954 0.16 EvapAir Delta T (F): 23.24 0.32 

 Indoor Exit Dew (F): 52.186 0.10 Air/Ref Cap Prcnt Diff: 0.48 2.14 

 Sensible Heat Ratio: 0.644 0.0049 

 Indoor Airflow (CFM): 501.58 5.80 SCFM per Ton: 302.28 

Indoor Airflow (SCFM): 502.60 6.20 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011330 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008365 

 Barometric Pressure (in HG): 29.63 Nozzle Temp (F): 60.37 0.82 

 Air Chamber Nozzle Pressure Drop (in Water): 0.905 0.021 

 Evaporator Coil Air Pressure Drop (in Water): 1.940 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 425.06 2.071 Ref-side Cap (Btu/h) : 20047.22 377.05 

 Upstream Temp (F): 104.08 0.289 Ref-side Cap (tons): 1.67 0.03 

 Refrigerant Mdot (lbm/h): 313.67 5.95 

 Coriolis Density (lbm/ft3): 72.80 0.16 

 Upstream R22 Tsat (F): 118.59 0.377 

 Average Subcooling (F): 14.52 0.458 

 

Evap Exit Pressure (psia): 148.69 0.728 

 Evap Exit Avg Temp : 61.26 0.676 

 Exit Superheat (F): 14.55 0.697 

 Evap Exit Tsat (F): 46.71 0.295 

110
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040728a.dat SUMMARY FILENAME: a040728a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 13018.25 438.26 

 Indoor Dry-Bulb : 80.075 0.20 Sensible Cap (Btu/h): 9855.61 293.12 

Indoor Inlet Dew (F): 60.371 0.05 Latent Cap (Btu/h): 3162.64 233.87 

Indoor Exit Dry-Bulb: 64.382 0.22 EvapAir Delta T (F): 17.85 0.43 

 Indoor Exit Dew (F): 56.937 0.26 Air/Ref Cap Prcnt Diff: 3.39 6.66 

 Sensible Heat Ratio: 0.757 0.0126 

 Indoor Airflow (CFM): 502.39 5.71 SCFM per Ton: 462.20 

Indoor Airflow (SCFM): 501.42 5.74 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011241 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009919 

 Barometric Pressure (in HG): 29.79 Nozzle Temp (F): 64.77 0.64 

 Air Chamber Nozzle Pressure Drop (in Water): 0.904 0.020 

 Evaporator Coil Air Pressure Drop (in Water): 2.000 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 425.00 1.279 Ref-side Cap (Btu/h) : 13458.06 676.75 

 Upstream Temp (F): 104.53 0.350 Ref-side Cap (tons): 1.12 0.06 

 Refrigerant Mdot (lbm/h): 211.23 10.62 

 Coriolis Density (lbm/ft3): 72.85 0.36 

 Upstream R22 Tsat (F): 118.58 0.233 

 Average Subcooling (F): 14.05 0.483 

 

Evap Exit Pressure (psia): 160.83 0.485 

 Evap Exit Avg Temp : 64.99 1.716 

 Exit Superheat (F): 13.50 1.902 

 Evap Exit Tsat (F): 51.49 0.186 

111
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040729a.dat SUMMARY FILENAME: a040729a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 20056.82 491.41 

 Indoor Dry-Bulb : 79.633 0.40 Sensible Cap (Btu/h): 12753.21 283.59 

Indoor Inlet Dew (F): 60.733 0.10 Latent Cap (Btu/h): 7303.61 246.33 

Indoor Exit Dry-Bulb: 58.829 0.13 EvapAir Delta T (F): 22.94 0.32 

 Indoor Exit Dew (F): 52.283 0.34 Air/Ref Cap Prcnt Diff: 2.06 7.48 

 Sensible Heat Ratio: 0.636 0.0039 

 Indoor Airflow (CFM): 499.63 5.05 SCFM per Ton: 302.43 

Indoor Airflow (SCFM): 505.48 4.62 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011351 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008322 

 Barometric Pressure (in HG): 29.89 Nozzle Temp (F): 59.92 0.55 

 Air Chamber Nozzle Pressure Drop (in Water): 0.906 0.017 

 Evaporator Coil Air Pressure Drop (in Water): 2.000 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 420.74 5.177 Ref-side Cap (Btu/h) : 20469.27 1264.18 

 Upstream Temp (F): 105.86 2.763 Ref-side Cap (tons): 1.71 0.11 

 Refrigerant Mdot (lbm/h): 324.24 14.01 

 Coriolis Density (lbm/ft3): 73.10 0.81 

 Upstream R22 Tsat (F): 117.80 0.947 

 Average Subcooling (F): 11.95 3.591 

 

Evap Exit Pressure (psia): 145.54 2.669 

 Evap Exit Avg Temp : 59.76 10.064 

 Exit Superheat (F): 14.34 11.159 

 Evap Exit Tsat (F): 45.42 1.095 

112
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040729b.dat SUMMARY FILENAME: b040729b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 20078.83 368.42 

 Indoor Dry-Bulb : 80.044 0.28 Sensible Cap (Btu/h): 12900.77 277.15 

Indoor Inlet Dew (F): 60.663 0.10 Latent Cap (Btu/h): 7178.06 142.28 

Indoor Exit Dry-Bulb: 59.059 0.12 EvapAir Delta T (F): 23.24 0.32 

 Indoor Exit Dew (F): 52.348 0.08 Air/Ref Cap Prcnt Diff: 2.43 3.30 

 Sensible Heat Ratio: 0.643 0.0043 

 Indoor Airflow (CFM): 499.25 5.00 SCFM per Ton: 301.73 

Indoor Airflow (SCFM): 504.86 4.90 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011322 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.008341 

 Barometric Pressure (in HG): 29.89 Nozzle Temp (F): 60.17 0.83 

 Air Chamber Nozzle Pressure Drop (in Water): 0.904 0.018 

 Evaporator Coil Air Pressure Drop (in Water): 2.000 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 422.34 0.853 Ref-side Cap (Btu/h) : 20565.08 359.86 

 Upstream Temp (F): 105.76 0.454 Ref-side Cap (tons): 1.71 0.03 

 Refrigerant Mdot (lbm/h): 325.54 6.05 

 Coriolis Density (lbm/ft3): 73.13 0.23 

 Upstream R22 Tsat (F): 118.10 0.156 

 Average Subcooling (F): 12.34 0.365 

 

Evap Exit Pressure (psia): 146.06 0.303 

 Evap Exit Avg Temp : 58.79 1.633 

 Exit Superheat (F): 13.15 1.633 

 Evap Exit Tsat (F): 45.64 0.125 

113
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040730a.dat SUMMARY FILENAME: a040730a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 23873.45 528.34 

 Indoor Dry-Bulb : 79.875 0.22 Sensible Cap (Btu/h): 14650.46 408.94 

Indoor Inlet Dew (F): 60.410 0.10 Latent Cap (Btu/h): 9222.99 136.03 

Indoor Exit Dry-Bulb: 55.759 0.09 EvapAir Delta T (F): 26.22 0.43 

 Indoor Exit Dew (F): 49.191 0.05 Air/Ref Cap Prcnt Diff: 2.59 2.58 

 Sensible Heat Ratio: 0.614 0.0054 

 Indoor Airflow (CFM): 498.81 5.64 SCFM per Ton: 255.62 

Indoor Airflow (SCFM): 508.54 5.84 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011196 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.007394 

 Barometric Pressure (in HG): 29.95 Nozzle Temp (F): 57.28 0.79 

 Air Chamber Nozzle Pressure Drop (in Water): 0.910 0.021 

 Evaporator Coil Air Pressure Drop (in Water): 2.000 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 420.09 0.975 Ref-side Cap (Btu/h) : 24489.87 230.39 

 Upstream Temp (F): 104.60 0.341 Ref-side Cap (tons): 2.04 0.02 

 Refrigerant Mdot (lbm/h): 384.57 3.21 

 Coriolis Density (lbm/ft3): 72.80 0.27 

 Upstream R22 Tsat (F): 117.68 0.179 

 Average Subcooling (F): 13.08 0.374 

 

Evap Exit Pressure (psia): 138.64 0.425 

 Evap Exit Avg Temp : 56.11 0.591 

 Exit Superheat (F): 13.59 0.581 

 Evap Exit Tsat (F): 42.53 0.181 

114
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040803a.dat SUMMARY FILENAME: a040803a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 15230.41 604.05 

 Indoor Dry-Bulb : 80.216 0.47 Sensible Cap (Btu/h): 11003.77 360.44 

Indoor Inlet Dew (F): 60.383 0.44 Latent Cap (Btu/h): 4226.64 435.63 

Indoor Exit Dry-Bulb: 62.392 0.27 EvapAir Delta T (F): 19.91 0.43 

 Indoor Exit Dew (F): 55.700 0.25 Air/Ref Cap Prcnt Diff: 3.44 7.17 

 Sensible Heat Ratio: 0.722 0.0211 

 Indoor Airflow (CFM): 500.37 5.94 SCFM per Ton: 395.56 

Indoor Airflow (SCFM): 502.05 5.68 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011227 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009462 

 Barometric Pressure (in HG): 29.84 Nozzle Temp (F): 63.02 0.70 

 Air Chamber Nozzle Pressure Drop (in Water): 0.901 0.021 

 Evaporator Coil Air Pressure Drop (in Water): 2.000 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 426.42 4.507 Ref-side Cap (Btu/h) : 15753.76 782.81 

 Upstream Temp (F): 105.37 1.638 Ref-side Cap (tons): 1.31 0.07 

 Refrigerant Mdot (lbm/h): 248.70 14.29 

 Coriolis Density (lbm/ft3): 73.10 0.60 

 Upstream R22 Tsat (F): 118.84 0.819 

 Average Subcooling (F): 13.48 1.173 

 

Evap Exit Pressure (psia): 159.78 1.213 

 Evap Exit Avg Temp : 65.49 3.001 

 Exit Superheat (F): 14.40 3.292 

 Evap Exit Tsat (F): 51.09 0.466 

115
 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: b040803b.dat SUMMARY FILENAME: b040803b.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 15328.62 177.88 

 Indoor Dry-Bulb : 80.106 0.21 Sensible Cap (Btu/h): 10983.96 159.46 

Indoor Inlet Dew (F): 60.463 0.05 Latent Cap (Btu/h): 4344.66 70.27 

Indoor Exit Dry-Bulb: 62.313 0.11 EvapAir Delta T (F): 19.86 0.22 

 Indoor Exit Dew (F): 55.656 0.03 Air/Ref Cap Prcnt Diff: 2.61 3.99 

 Sensible Heat Ratio: 0.717 0.0044 

 Indoor Airflow (CFM): 500.68 5.04 SCFM per Ton: 393.29 

Indoor Airflow (SCFM): 502.38 4.71 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011259 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.009447 

 Barometric Pressure (in HG): 29.84 Nozzle Temp (F): 63.00 0.62 

 Air Chamber Nozzle Pressure Drop (in Water): 0.903 0.017 

 Evaporator Coil Air Pressure Drop (in Water): 2.000 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 427.81 1.766 Ref-side Cap (Btu/h) : 15728.51 604.89 

 Upstream Temp (F): 105.94 0.429 Ref-side Cap (tons): 1.31 0.05 

 Refrigerant Mdot (lbm/h): 249.30 9.07 

 Coriolis Density (lbm/ft3): 73.21 0.21 

 Upstream R22 Tsat (F): 119.09 0.320 

 Average Subcooling (F): 13.15 0.518 

 

Evap Exit Pressure (psia): 159.82 0.243 

 Evap Exit Avg Temp : 65.51 1.029 

 Exit Superheat (F): 14.41 1.122 

 Evap Exit Tsat (F): 51.10 0.093 

116
117

 DOE/ARI MIX-MATCH EVAPORATOR TEST SUMMARY SHEET 

 DATA FILENAME: a040817a.dat SUMMARY FILENAME: a040817a.sum 

 Range 

 Air-Side Conditions Range Total Air-Side Capacity: 11007.81 265.30 

 Indoor Dry-Bulb : 79.944 0.34 Sensible Cap (Btu/h): 9076.99 221.25 

Indoor Inlet Dew (F): 60.380 0.15 Latent Cap (Btu/h): 1930.83 110.83 

Indoor Exit Dry-Bulb: 65.709 0.17 EvapAir Delta T (F): 16.35 0.22 

 Indoor Exit Dew (F): 58.334 0.18 Air/Ref Cap Prcnt Diff: 5.15 3.35 

 Sensible Heat Ratio: 0.825 0.0077 

 Indoor Airflow (CFM): 504.95 6.74 SCFM per Ton: 549.33 

Indoor Airflow (SCFM): 503.91 7.26 (0.075 lb/ft3 standard air) 

Evap Inlet Humidity Ratio (lbH2O/lbAir): 0.011211 

 Evap Exit Humidity Ratio (lbH2O/lbAir): 0.010407 

 Barometric Pressure (in HG): 29.88 Nozzle Temp (F): 66.27 0.55 

 Air Chamber Nozzle Pressure Drop (in Water): 0.913 0.025 

 Evaporator Coil Air Pressure Drop (in Water): 2.000 0.000 

------------------------------------------------------------------------------- 

Refrigerant Side Conditions 

 Expansion Valve 

 Upstream Pressure (psia): 432.75 1.157 Ref-side Cap (Btu/h) : 11574.22 244.37 

 Upstream Temp (F): 104.11 0.487 Ref-side Cap (tons): 0.96 0.02 

 Refrigerant Mdot (lbm/h): 181.14 3.66 

 Coriolis Density (lbm/ft3): 72.91 0.21 

 Upstream R22 Tsat (F): 119.98 0.208 

 Average Subcooling (F): 15.87 0.596 

 

Evap Exit Pressure (psia): 167.22 0.728 

 Evap Exit Avg Temp : 67.73 0.893 

 Exit Superheat (F): 13.83 0.983 

 Evap Exit Tsat (F): 53.90 0.270