FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING COILS

Certification Program for FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING OPERATIONAL MANUAL APRIL 1981 ADDENDUM Administered by AIR-CONDITIONING AND REFRIGERATION INSTITUTE 4100 North Fairfax Dr. Suite 200 Arlington VA 22203

FOREWORD This addendum to Operational Manual, OM-410, contains copies of forms needed for participation in the ARI Certification Program for Forced-Circulation Air-Cooling and Air-Heating Coils. Participants can obtain a supply of these forms by sending a request to: Director of Engineering Air-Conditioning and Refrigeration Institute 4100 NORTH FAIRFAX DRIVE, SUITE 200 Χ ARLINGTON, VIRGINIA 22203

TABLE OF CONTENTS FORM TITLE CHC-C2B...Acceptance of Certification CHC-C2...Request for Approval of Laboratory 410-1...Calculation Procedure to Determine Fin Efficiencies and Metal Thermal Resistances 410-2...Calculation of Air-Side Resistances from Steam and Water Coil Tests 410-3...Calculation of Tube-Side Pressure Drops from Steam and Water Tests 410-4...Calculation of Refrigerant-Side Thermal Resistances from Volatile Refrigerant Coils Tests 410-5...Suggested Form for Rating Calculation Procedure for Sensible Heat Air Coils 410-6...Suggested Form for Rating Calculation Procedure for Cooling and Dehumidifying Coils 410-7...Calculation of Heat Transfer Coefficient and Friction Factor for Ethylene Glycol Coils 410-8...Suggested Form for Rating Calculation Procedure for Sensible Heat Air Coils with Ethylene Glycol Solutions 410-9...Suggested Form for Rating Calculation Procedure for Cooling and Dehumidifying Coils with Ethylene Glycol Solutions CHC-CF1...Production Coil Line Certification HCC-2&3-M...Report of Manufacturer's Shipments EX-2-Q...Report of Total Export Shipments

ACCEPTANCE OF CERTIFICATION ARI CERTIFICATION PROGRAM FOR FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING PARTICIPANT DATE Data submitted with respect to coil lines listed below have been accepted and these coils lines are hereby released for certification. Data relating to these coil lines as agreed upon by the ARI Air-Heating and Air-Cooling Coils Sub Section of Air-Conditioning Heat Transfer Products Section will be published in the next issue or supplement of the Directory of Certified Applied Air-Conditioning Products and will continue in succeeding issues until the coil line is withdrawn from manufacture, or until the data is withdrawn for any reason as set forth in the License Agreement. You are authorized to apply the Certification Symbol to coils of these coil line, and to display the Certification Symbol on specification sheets or other literature pertaining to the listed coil lines, as specified in the License Agreement. Issue Coil Fluid (s) Catalog Date Type Used Number (or Code) Trade of Brand Names (s): For ARI Use Only: SIGNED Engineer Submitted: Prepared by: Typed by: Proofed by: Listed: By: REQUEST FOR APPROVAL OF LABORATORY TO TEST

FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING ARI CERTIFICATION PROGRAM FOR FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING We, the undersigned, hereby request the Air-Conditioning and Refrigeration Institute to approve our laboratory, located at for the purpose of testing Forced-Circulation Air-Cooling and Air-Heating Coils to qualify for ARI Certification. We certify that all testing will be done according to the testing codes and certified Rating Programs approved by ARI. Accompanying this request is the following information: Company By By Officer Chief Engineer or Laboratory Director Date Title Date Form CHC-C2 The above requirement for a laboratory has been met by the requesting company in regard to instruments, equipment and laboratory. This laboratory is hereby given general approval to conduct precertification check tests. AIR-CONDITIONING AND REFRIGERATION INSTITUTE By Director of Engineering

Date This laboratory has satisfactorily met the requirements of the precertification check test and is hereby approved for testing and rating air-cooled and air-heating coils in accordance with ARI Standard 410-81, subject to withdrawal if the quality of the laboratory is not maintained. AIR-CONDITIONING AND REFRIGERATION INSTITUTE By Director of Engineering Date Form CHC-C2 CALCULATION PROCEDURE TO DETERMINE FIN EFFICIENCIES AND METAL THERMAL RESISTANCES ARI CERTIFICATION PROGRAM FOR FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING COMPANY DATE ITEM NO. DESCRIPTION AND CALCULATION PROCEDURE 1 Fin Type and Thickness Profile VALUE 2 A s - Secondary Surface Area (See Par. 3.9.3, ARI sq ft [m 2 ]

3 4 Standard 410) A p - Primary Surface Area (See Par. 3.9.3, ARI Standard 410) A o - Total External Coil Surface Area ( ν2ο + ν3ο ) sq ft [m 2 ] sq ft [m 2 ] 5 D i - Tube Inside Diameter in. [mm] 6 N t - Total Number of Tubes in Coil 11 x 12 7 π x 6 L t - Fin Tube Length in. [mm] 8 A i - Total Internal Coil Surface 11 5 x6 712 5 6 7 Area 45.84 π A i 318,344 sq ft [m 2 ] 9 B - Surface Ratio ν4ο / ν8ο 10 D f - Spiral Fin Outside Diameter in. [mm] *11 *12 L f - Fin Length Perpendicular to Direction of Tubes L d - Fin Depth in Direction of Air Flow in. [mm] in. [mm] *For non-circular shaped fins only Sheet 1 of 5 Form 410-1 ITEM NO. DESCRIPTION AND CALCULATION PROCEDURE 13 x e - Outside Radius of Equivalent Annular Area of Non- Circular Fin or of Annular or Spiral Fin in. [mm] VALUE x e - for continuous

plate fin x e for individually finned tube x e ν10ο / 2 - for spiral fin 14 D o - Tube Outside Diameter in. [mm] 15 Y f - Fin Thickness for Fin of Uniform Thickness in. [mm] 16 x o - Fin Root Radius x o ν14ο + ν15ο - for plate 2 type fins with collars not touching adjacent fins in. [mm] x D ν14ο + 2 ν15ο - for plate 2 type fins with collars touching adjacent fins x o ν14ο - for plate type 2 fins without collars and spiral fins Form 410-1 ITEM NO. DESCRIPTION AND CALCULATION PROCEDURE VALUE 17 w - Height of Equivalent or of Actual Annual Fin w ν13ο - ν16ο in. [mm] 18 x e /x o - Radius Ratio of Equivalent Annular Fin ν13ο / ν16ο

19 20 k f Fin Material Thermal Conductivity (See Table 2, ARI Standard 410) k t Tube Material Thermal Conductivity (See Table 2, ARI Standard 410) Btu per (hr) (sq ft) (F) / (ft) [W mm/m 2 ΕC] Btu per (hr) (sq ft) (F) / (ft) [W mm/m 2 ΕC] 21 Y r - Fin Thickness at Root of Spiral Fins 22 23 R 1D - for Dry Surface Coils R aw c o m" - for Wet Surface Coils Note: Arbitrarily assume various values, covering application ratings f a - Air-Side Film Heat Transfer Coefficient Where: f ad 1/ ν22ο - for Dry Surface Coils f aw 1/R aw m" c p for Wet Surface Coils Fin Efficiency Parameter in. [mm] (hr) (F) (sq ft) per Btu [m 2 ΕC/W] Btu per (hr) (sq ft) (F) [W/m 2 ΕC] 24 for plate-type fins for spiral fins ITEM NO. 17 17 23 2 x 23 6 x 19 x 15 17 19 x 15 DESCRIPTION AND CALCULATION PROCEDURE preceding 23 item numbers) 2 x 23 17 6 x 19 x 21 19 x 21 25 Ø - Mean Fin Efficiency (See Figs. 10 and 11) VALUE

26 27 η 0 - Total Surface Effectiveness ( ν25ο x ν2ο ) + ν3ο ν4ο R f Thermal Resistance of Fin Based on Total Surface Effectiveness 1 26 1 26 23 (hr) (sq ft) (F) per Btu [m 2 ΕC/W] 28 R t Thermal Resistance of Tube 9 5 14 9 5 14 Ln Ln 24 20 5 2 20 5 (hr) (sq ft) (F) per Btu [m 2 ΕC/W] 29 30 31 32 R md - Total Metal Resistance of Fin and Tube ν27ο + ν28ο R a D + R m D - Combined Air Film Plus Metal Thermal Resistance for Dry Surface Coils ν22ο + ν29ο Plot (R ad + R md ) vs R ad ( ν30ο) vs ν22ο ) on rectilinear coordinates, as shown in Fig. 1 Plot R ad vs f a ( ν29ο vs ν23ο) on on rectilinear coordinates, as shown in Fig. 2 (hr) (sq ft) (F) per Btu [m 2 ΕC/W] (hr) (sq ft) (F) per Btu [m 2 ΕC/W] SIGNED TITLE NOTE: Alternate Method to Determine Mean Fin Efficiency by Fin Segmentation

A more accurate, but more involved, method of calculating and R f for non-circular shaped fins is described as Method (2), pages 313-315 in Reference A9 of ARI Standard 410. The mean values of, as determined by this alternate method, will be somewhat lower than those calculated by the simpler, equivalent annular area method given in the above procedure. For non-circular fin designs of large size, in combination with thin, low thermal conductivity fin material, this alternate method is recommended. The difference in, as calculated by the two methods, also becomes greater as the fin becomes more oblong. If this alternate method is used, it is recommended that the fin efficiency,, for each of the individual fin sectors be based on data by K. A. Gardner (Reference A8 of ARI Standard 410), rather than that given in Reference A9. Where this alternate method is used, please include all necessary information and calculations and attach them to this form.

CALCULATION OF AIR-SIDE RESISTANCES FROM STEAM AND WATER COIL TESTS ARI CERTIFICATION PROGRAM FOR FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING COMPANY DATE SOLUTION PROCEDURE STEAM WATER DRY - TED COIL LINE COIL TYPE COIL PROCEDURE 1 1 1 1 A O - Total External Coil Surface (See Form 410-1) sq ft [m 2 ] COIL PHYSICAL DATA 2 2 2 2 D i - Tube Inside Diameter (See Form 410-1) 3 3 3 3 B - Surface Ratio (See Form 410-1) - 4 4 4 N c - Number of Tube Circuits in Coil in. [mm] - 5 5 5 A ix - Total Cross-Sectional Fluid Flow Area Inside Tubes 0.00545 (ν2ο) 2 x ν4ο [A ix ] 7.85 x 10 7 (ν2ο) 2 x ν4ο] sq ft [m 2] 4 6 6 6 Nr - Coil Depth in Rows 6a 6a 6a L s - Straight Tube Length Per Tube Pass in. [mm] Sheet 1 of 12 Form 410-

SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 5 7 7 7 p S - Average Absolute Static Pressure at Test Coil IN. Hg abs [Kpa abs] - 8 8 8 t l - Entering Air Dry-Bulb Temperature F LABORATORY TEST OBSERVATION AND CALCULATIONS OBTAINED FROM ASHRAE STANDARD 33-78, FORMS 33TD-1, -2, -3-9 9 9 ' t l - Entering Air Wet-Bulb Temperature F - - 10 10 h l - Entering Air Enthalpy Btu per lb dry air [KJ/Kg] 6 9-11 t 2 - Leaving Air Dry-Bulb Temperature F - - 11 12 h 2 - Leaving Air Enthalpy Btu per lb dry air [KJ/Kg] - 10 12 13 t wl - Entering Water Temperature F - 11 13 14 t w2 - Leaving Water Temperature F - 12 14 15 w w - Rate of Water Flow lb per hr [g/s] 7 - - 16 t vm - Mean Saturated Steam Temperature in Coil Circuit 8 13-17 q s - Average Sensible Heat Capacity Btuh [W] - - 15 18 q r - Average Total Heat Capacity Btuh [W] 9 14 16 19 v a - Standard Air Face Velocity ft per min [m/s] - 15 17 20 t wm - Mean Water Temperature Inside Tubes 0.5 (ν13ο) + (ν14ο) 10 16-21 )P st - Isothermal Dry Surface Air-Side Friction at Standard Conditions - - 18 22 )P sw - Wet Surface Air-Side Friction at in. water Standard Conditions [Pa] Sheet 2 of 12 Form 410-2 F F in. water [Pa]

SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4-17 19 23 q S /q t - Sensible Heat Ratio ν17ο / ν18ο If << 0.95, coil surface is all wet or partially dry. If 0.95, coil surface is fully dry. - 18 20 24 V w - Average Standard Water Velocity 11 19 - CALCULATIONS DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS Inside ν15ο Tubes 224,500 x ν5ο 25 )t m - Logarithmic Mean Temperature Difference between Air and Heating or Cooling Fluid 11 8 16 8 In 16 11 ( 8 14 ) ( 11 8 14 In 11 13 v w - For Steam Coils 13 ) 15 1,000,000 x 5 For Thermal Counterflow Water Coils ft per sec [m/s] F If other than thermal counterflow, determine logarithm mean temperature difference from Flgs. 13, 14 or 15. Form 410-2

SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 12 20-26 R - Overall Thermal Resistance Between Air and Heating or Cooling Fluid ν1ο x ν25ο ν17ο 13 - - 27 Plot R vs V a on logarithmic coordinates as shown in Fig. 3. This curve is used in obtaining steam coil application ratings. (hr) (sq ft) (F) per Btu [m 2 ΕC/W] - 21 21 28 Btu per (hr) (sq ft) (F) * 22 22 CALCULATIONS TO DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS 29 Tube-Side Film Thermal Resistance R v ν3ο /2000 - For Steam [R v 3 /11364] R w ν3ο/28n - For Cold and Hot Water [W/m 2 ΕC] (hr) (sq ft) (F) per Btu [m 2 ΕC/W] * These items apply when steam coil tests are used to determine R ad for hot water ratings. Form 410-2

SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 21a 21a 28a C pw Specific Heat of Water at ν20ο Btu/lb Α ΕF [KJ/kg Α ΕC] 21b 21b 28b k w Thermal Conductivity of Water at ν20ο Btu? Α ft Α ΕF [w/m Α ΕC] 21c 21c 28c Φ w Absolute Viscosity of Water at ν20ο lb/? Α ft [mpa Α s] 21d 21d 28d t tw Average Tube Wall Temperature (Assumed) For chilled water coils, initially assume t tw is 5ΕF to 10ΕF greater than ν20ο 21e 21e 28e Φ tw Absolute Viscosity of Water at ν28dο lb/? ft [mpa Αs] 21f 21f 28f G w Mass Velocity of Water ν15ο/ν5ο lb/? ft 2 21g 21g 28g R aw Reynolds Number for Water ν2ο x ν28fο 12 x ν28cο 21h 21h 28h L s /D: Ratio of Tube Length to Diameter ν6aο ν2ο 21i 21i CALCULATIONS TO DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS 28i J w - Colburn Heat Transfer Factor for Water from Fig. 17 using ν28gο and ν28hο 9or calculate from equation? on Fig. 17) ΕF [g/s Α m 2 ]

SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 21j 21j 28j Pr w Prandtl Number for Water ν28aο x ν28cο ν28bο 21k 21k 28k Pr w 2/3 ν28jο 2/3 21l 21l 28l (: tw /: w ) Α 14 Viscosity Ratio (ν28eο/ν28cο) Α 14 21m 21m 28m S tw Stanton Number for Water ν28jο ν28kο x ν28lο 21n 21n 28n f w Film Heat Transfer Coefficient for Water ν28mο x ν28aο x ν28fο 23a 30a t tw Average Tube Wall Temperature (calculated) For chilled Water Coils ν20ο + ν25ο ν29ο ν29ο + ν30ο ν30aο must equal ν28dο within 10ΕF [ 5.6C], if not assume a new value for ν28dο and repeat calculations thru ν30aο 28a CALCULATIONS TO DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS 37a t tw Average Tube Wall Temperature (calculated) For chilled Water Coils ν20ο + ν29ο (ν37ο - ν20ο) ν29ο + ν34ο ν37aο must equal ν28dο within 10ΕF [ 5.6C], if not assume a new value for ν28dο and repeat calculations thru ν30aο Btu/? Α ft 2 Α ΕF [w/m 2 Α ΕC] ΕF ΕF Form 410-2

SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER PROCEDURE 23a 23a 30a C pw Specific Heat of Water at ν28ο Btu/lb Α ΕF [KJ/kg Α ΕC] 23b 23b 30b k w Thermal Conductivity of Water at ν28ο Btu h Α ft Α ΕF [w/m Α ΕC] 23c 23c 30c Φ w Absolute Viscosity of Water at ν28ο lb/h Α ft [mpa Α s] 23d 23d 30d t tw Average Tube Wall Temperature (assumed) - For chilled water coils, initially assume t tw is 5ΕF to 10ΕF greater than ν28ο - For hot water coils, initially assume t tw is 10ΕF to 20ΕF less than ν28ο 23e 23e 30e Φ tw Absolute Viscosity of Water at ν30dο 23f 23f 30f G w Mass Velosity of Water ν29ο/ν11ο 23g 23g 30g Ra w Reynolds Number for Water ν10ο x ν30fο 12 x ν30cο 23h 23h 30h L s /D: Ratio of Tube Length to Diameter ν12ο ν10ο 23i 23i WATER RATING PARAMETERS 30i J w Colburn Heat Transfer Factor for Water from Fig. 17 using ν30gο and ν30hο (or calculate from equation? on Fig. 17) ΕF lb/h Α ft [mpa Αs] lb/h ft 2 [g/s Α m 2 ]

Form 410-5 SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER PROCEDURE 23j 23j 30j P rw Prandtl Number for Water ν30aο x ν30cο ν30bο 23k 23k 30k P rw 2/3 - (ν30jο) 2/3 23l 23l 30l (Φ tw /Φ w ).14 Viscosity Ratio (ν30eο/ν30cο).14 23m 23m 30m S tw Stanton Number for Water ν30iο ν30kο x ν30lο 23n 23n 30n f w Film Heat Transfer Coefficient for Water ν30mο x ν30aο x ν30fο 24 24 35a WATER RATING PARAMETERS CALCULATIONS TO SOLVE FOR COIL CAPACITY (qs) 31 R w Water Film Thermal Resistance ν4ο/ν30nο 42a t tw Average Tube Wall Temperature (Calculated) For chilled water coils ν28ο + ν31ο x ν39ο ν33ο x ν35ο For hot water coils ν28ο - ν31ο x ν39ο ν33ο x ν35ο ν42aο must equal ν30dο within 10 ΕF [ 5.6 ΕC] for chilled water coils and 20 ΕF [ 11.1 ΕC] for hot water coils. If not, assume a new value for ν30dο and repeat calculations thru ν42aο Btu/h ft 2 - ΕF [w/m 2 Α ΕC] h Α ft 2 Α ΕF/Btu [m 2 Α Εc/w] ΕF

SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 * 23-30 R ad + R md - Combined Air Film Plus Metal Thermal Resistance CALCULATIONS TO DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS ν26ο - ν29ο Plot ν30ο vs ν19ο on logarithmic coordinates as shown in Fig. 4. This curve is used in obtaining application ratings for all sensible heat coils except steam coils. * 24 23 31 R ad Air Film Thermal Resistance for Dry Surface (From Fig. 1, knowing ν30ο ) * 25-32 Plot R ad vs V a on logarithmic coordinates as shown in Fig. 4. This curve is used in obtaining application ratings for all sensible heat coils except steam coils. - 26 24 33 f ad Air-side Heat Transfer Coefficient 1 1 for Dry Surface R ad ν31ο (hr) (sq ft) (F) per Btu [m 2 ΕC/W] (hr) (sq ft) (F) per Btu [m 2 ΕC/W] Btu per (hr) (sq ft) (F) [W/m 2 ΕC] - - 25 34 R md Total Metal Thermal Resistance of Fin and Tube (Assuming dry surface, obtain from Fig. 2 with ν33ο) (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W] * These items apply when steam coil tests are used to determine R ad for hot water ratings.

For fully-wetted coils, read value of R a D from Fig. 4 as determined from dry coil tests.

SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 - - 26 35 h m - Mean Air Enthalpy 0.5 (ν10ο + ν12ο) Btu per lb dry air [KJ/Kg] - - 27 36 C - Approximate Coil Characteristic CALCULATIONS TO DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS ν29ο + ν34ο 0.243 ν31ο 29 + C 1.018 - - 28 37 t sm - Approximate Mean Coil Surface Temperature (From Fig. 9 with ν20ο, ν35ο, and ν36ο) - - 29 38 m "/ cp -Approximate Air-Side Heat Transfer Multiplier for Wet Surface Coils (From Fig. 8 with ν7ο and ν37ο) 34 31 - - 30 39 R aw - Air Film Thermal Resistance for Wet Surface Note: Assume this value for trial and error solution. Suggest initial value be same as ν31ο. - - 31 40 f aw - Approximate Air-Side Heat Transfer Coefficient for Wet Surface ν38ο / ν39ο (lb) (F) per Btu [Kg ΕC/KJ] F (hr) (sq ft) (F) per Btu [m 2 ΕC/W] Btu per (hr) (sq ft) (F) [W/m 2 ΕC] - - 32 41 R mw - Total Metal Thermal Resistance of Fin and Tube for Wet Surface (From Fig. 2 with ν40ο) (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W]

SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 - - 33 42 ν29ο + ν41ο C - Coil Charasteric 0.243 ν39ο 29 + 41 C 1.018 39 (lb) (F) per Btu [Kg ΕC/KJ] - - 34 CALCULATIONS TO DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS 43 " t l - Entering Air Dew Point Temperature (From Psychrometric Chart with ν7ο, ν8ο, and ν9ο) Calculation of Dew Point Temperature for Nonstandard Air Pressure* p v p v p' (ps p') (t1 2830 1.44 t Where: p s Air Pressure p Saturation Vapor ' Pressure at t l from Steam Tables p v Saturation Vapor Pressure at Dew Point Temperature- ' t l ) ' (p s p') (t1 t l ) p' ' 1548.4 1.33 t l F in. Hg abs [Kpa abs] Jordon & Priester, Refrigeration and Air Conditioning. 2 nd Edition, 1956

SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 CALCULATIONS TO DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS " t l Dew Point Temperature Is Saturation Temperature Corresponding to Saturation Vapor Pressure, p v, from Stream Tables - - 35 44 t sl - Coil Surface Temperature on Entering Air Side (From Fig. 9 with ν10ο, ν14ο, and ν42ο unless ν7ο varies more than 0.3 in. Hg [ 1.014 Kpa] from 29.92 in. Hg [101.325 Kpa]. If it does, then determine t s1 by trial and error using equation: t s1 t w2 + C (h 1 - h s1 ). Correct h 2l for ν7ο and use ν10ο, ν14ο, and ν42ο. For fully wetted coil, ν43ο ν44ο. If ν43ο < ν44ο, coil is partially wet and calculation procedures may be determined from Form 410-6.) F F - - 36 45 h s1 - Saturated Air Enthalpy at ν7ο and ν44ο Btu per lb dry air [KJ/Kg]

SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER PROCEDURE 35a 50a t tw Average Tube Wall Temperature (Calculated) For chilled water coils ν28ο + ν31ο x ν44ο ν33ο x ν50ο For hot water coils ν28ο - ν31ο x ν44ο ν33ο x ν50ο ΕF CALCULATIONS TO SOLVE FOR ROWS DEEP ν50aο must equal ν30dο within 10ΕF [5.6ΕC] for chilled water coils and 20ΕF [11.1ΕC] for hot water coils. If not, assume a new value for ν30dο and repeat calculations thru ν50aο -

SOLUTION PROCEDURE COLD WATER PARTIALLY VOLATILE REFRIGERANT PARTIALLY PROCEDURE 31a 31a - - 47a C pw - Specific Heat of Water - at ν46ο Btu/lb ΕF [KJ/kg ΕC] 31b 31b - - 47b k w - Thermal Conductivity of Water at ν46ο Btu h ft ΕF [ w / m ΕC] CALCULATIONS TO SOLVE FOR ROWS DEEP 31c 31c - - 47c Φ w - Absolute Viscosity of Water at ν46ο lb/h ft [mpa s] 31d 31d - - 47d t tw - Average Tube Wall Temperature (assumed) - For chilled water coils, initially assume t tw is 5ΕF to 10ΕF greater than ν46ο 31e 31e - - 47e Φ tw - Absolute Viscosity of Water at ν47dο lb/h ft [mpa s] 31f 31f - - 47f G w - Mass Velosity of Water ν32ο/ν13ο lb/h ft 2 31g 31g - - 47g Ra w - Reynolds Number for Water ν9ο x ν47fο ν12ο x ν47cο 31h 31h - - 47h L s /D 1 Ration of Tube Length of Diameter 10 9 ΕF [g/s m 2 ] - - - - 31i 31i - - 47i j w - Colburn Heat Transfer Factor for Water from Fig. 17 using ν47gο and ν47hο (or calculate from equation above on Fig. 17) - -

SOLUTION PROCEDURE COLD WATER PARTIALLY VOLATILE REFRIGERANT PARTIALLY PROCEDURE 31j 31j - - 47j P rw - Prandtl Number for Water ν47aο x ν47cο ν47bο 31k 31k - - 47k Pr w 2/3 (ν47jο) 2/3 31l 31l - - 47l (Φ tw /Φ w ).14 - Viscosity Ratio (ν47eο/ν47cο).14 31m 31m - - 47m s tw Stanton Number for Water ν47iο ν47kο x ν47lο 31n 31n - - RATING CONDITIONS & DATA COMPUTATIONS 47n f w Film Heat Transfer Coefficient for Water ν47mο x ν47aο x ν47fο Btu/h ft 2 ΕF [ w / m 2 ΕC] 36a 36a - - 52a h m - Mean Air Enthalpy (ν26ο + ν30ο)/2 Btu/lb [KJ/Kg] 36b 36b - - 52b ts m - Mean Surface Temperature from Fig. 9 using ν52aο, ν52ο and ν46ο 36c 36c - - RATING PARAMETERS 52c t tw - Average Tube Wall Temperature (Calculated) ν46ο + ν48ο (ν52bο - ν46ο) ν48ο + ν51ο ν52cο must equal ν47dο within 10ΕF [ 5.6 ΕC], if not assume a new value for ν47dο and repeat calculations thru ν52cο ΕF ΕF

SOLUTION PROCEDURE COLD WATER PARTIALLY VOLATILE REFRIGERANT PARTIALLY PROCEDURE 32 32 42 42 RATING CONDS AND DATA COMPUTATIONS 48 Tube-Side Thermal Resistance R w R r ν4ο/ν47nο For Water Coils - From Fig. 6 with ν45ο for Volatile Refrigerant Coils (hr) (sq ft) (F) per Btu [m 2 ΕC/W] 33 33 43 43 49 R ad - Air Film Thermal Resistance for Dry Surface (From Fig. 5 or 6 with ν16ο) 34 34 44 44 50 R aw - Air Film Thermal Resistance for Wetted 35 35 45 45 RATING PARAMETERS Surface (From Fig. 5 or 6 with ν16ο) 51 R md - Metal Thermal Resistance for Dry Surface (From Fig. 2 at f a 1/ν49ο) (hr) (sq ft) (F) per Btu [m 2 ΕC/W] (hr) (sq ft) (F) per Btu [m 2 ΕC/W] (hr) (sq ft) (F) per Btu [m 2 ΕC/W]

36 36 46 46 52 Approximate Coil Characteristic ν48ο + ν51ο 0.243 x ν50ο 48 1.018 + 51 x 50 (lb) (F) per Btu [Kg ΕC/KJ] Note: This approximate coil characteristic is used to obtain R mw in ν63ο. SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 - - 41 50 Assume other values for ν39ο and repeat procedure through - - 42 CALCULATIONS TO DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS ν49ο. Plot values of ν49ο vs ν39ο as shown in Fig. 12a. Two or more points shall be plotted so that A o lies between calculated values of A c. 51 R aw - Air Film Thermal Resistance for Wet Surface The point on the curve (Fig. 12a) as plotted in ν50ο, where A c A o determines the R aw value which cor- responds to ν19ο. - - - - - - (hr) (sq ft) (F) per Btu [m 2 ΕC/W]

- - 43 52 Plot R aw vs V a (ν51ο vs ν19ο) on logarithmic coordinates as shown in Figs. 5 and 6. If the R aw curve is within 5 percent of the R ad curve, R ad may be used to obtain application ratings for the wetted surface portiono f all cooling and dehumidifying coils. - - - - SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4 - - 37 46 t s2 - Coil Surface Temperature on Leaving Air-Side - - 38 CALCULATIONS TO DETERMINE HEAT TRANSFER COEFFICIENTS FOR USE IN APPLICATION RATINGS (From Fig. 9 with ν12ο, ν13ο, and ν42ο unless ν7ο varies more than 0.3 in. Hg [ 1.014 Kpa] from 29.92 in. Hg [101.325KPa]. If it does, then determine t s2 by trial and error using equation: t s2 t w1 + C (h 2 h s2 ). Correct h s2 for ν7ο and use ν12ο, ν13ο, and ν42ο.) F 47 h s2 Saturated Air Enthalpy at ν7ο and ν46ο Btu per lb dry air [KJ/Kg]

- - 39 48 Δh m - Logarithmic Mean Enthalpy Difference between Air Stream and Coil Surface ( 10 45 ) ( 12 10 45 In 12 47 47 ) Btu per lb dry air [KJ/Kg] Note: See Typical Thermal Diagram at end of Form. - - 40 49 A c - Calculated External Surface Area 0.243 39 x 48 18 A c 1.018 39 x 48 18 sq ft [m 2 ] SOLUTION PROCEDURE WATER PROCEDURE TEST RUN NUMBER STEAM DRY - TED 1 2 3 4? 27 44 CALCULATIONS OF COIL AIR-SIDE PRESSURE DROP 53 Coil Air-Side Pressure Drop per Row Deep at Standard Conditions For dry surface: )p st ν21ο/ν6ο N r For fully-wetted surface: )p st ν22ο/ν6ο N r in. water per row deep [Pascal per row deep]

? 28 45 54 Plot ν53ο vs ν19ο on logarithmic coordinates as shown in Figs. 3, 4, 5, and 6, depending on coil type. Plot both dry and wet surface pressure drop in Figs. 5 and 6. These curves are used for application ratings. - - - - SIGNED TITLE

TYPICAL THERMAL DIAGRAMS FOR STEAM AND WATER TEMPERATURE OR ENTHALPY Sat. Steam Cond. Temp. t vm t vm t 2 t w1 t w2 t 2 t l t l

CALCULATION OF TUBE-SIDE PRESSURE DROPS FROM STEAM AND WATER TESTS ARI CERTIFICATION PROGRAM FOR FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING COMPANY DATE SOLUTION PROCEDURE STEAM WATER COIL LINE COIL TYPE COIL TEST RUN NUMBER 1 1 1 D I - Tube Inside Diameter in. [mm] 2 2 2 N t - Total Number of Tubes In Coil 3 3 3 N c - Number of Tube Circuits in Coil 4 4 4 A ix - Total Cross-Sectional Fluid Flow Area Inside Tubes 0.00545 (ν1ο) 2 x ν3ο [A ix 7.85 x 10-7 (ν1ο) 2 x ν3ο ] 5 5 5 L x - Straight Tube Length Per Pass in. [mm] 6 6 6 K b - Equivalent Length of Coil Circuit Per Return Bend 7 7 COIL PHYSICAL DATA 7 L e - Total Equivalent Length of Coil Circuit 2 2 0.0833 5 + 6 1 3 3 L e 2 2 0.001 [ 5 ) + 6 ( 1)] 3 3 sq ft [m 2 ] in. [mm] ft [m]

SOLUTION PROCEDURE PROCEDURE TEST RUN NUMBER STEAM WATER 1 2 3 4-8 8 t w1 - Entering Water Temperature F - 9 9 t w2 - Leaving Water Temperature F LABORATORY TEST OBSERVATION AND CALCULATIONS FROM ASHRAE STANDARD 33-78 FORMS 33TD-2 AND 33TD-3-10 10 t wm - Mean Water Temperature F 8-11 t vm - Mean Steam Temperature F - 11 12 w w - Water Flow Rate lb per hr [g/s] 9-13 w w - Steam Flow Rate lb per hr [g/s] 10-14 v vm - Average Saturated Steam Specific Volume cu ft per lb [m 3 /Kg] - 12 15 ( p w ) T - Water Pressure Drop Across Coil at Test Conditions ft of water [KPa] 11-16 p v - Steam Pressure Drop in Coil psi [KPa] - 13 17 V w - Average Standard Water Velocity Inside 12 - CALCUALTION AND PLOTTING Tubes 12 224,500 x 4 V 18 w v /N c - Steam Flow Rate Inside Tubes ν13ο/ν3ο w 12 1,000,000 x 4 ft per sec [m/s] lb per (hr) (circuit) [ (gram) per (second) (circuit)]

SOLUTION PROCEDURE PROCEDURE TEST RUN NUMBER STEAM WATER 1 2 3 4 13 14 CALCULATION AND PLOTTING 19 P h (for Water Coils); p h /v vm (for Steam Coils) - Header, Nozzles and Tube Entrance and Exit Losses to be established by manufacturer 20 F t - Temperature Coorection Factor for tube Circuit Tube Circuit Water Pressure Drop (From Fig. 7 with ν10ο) - 15 21 p t /L e F t - Water Pressure Drop Inside Tubes 15 19 WaterCoils 7 x 20 14-22 p tv /L e v vm - Pressure Drop Parameter for Steam Flow Inside Tubes [ν16ο / (ν7ο x ν14ο)] - ν19ο / ν7ο - 17 23 Plot p t /L e F t vs V w (ν21ο vs ν17ο) on logarithmic coordinates as shown in Fig. 4. This curve with Fig. 7 is sued for application ratings for either cold water or hot water coils. ft [KPa] (for water) (lb) 2 (In.) 2 (ft) 3 (g) 2 2 3 (mm) (m) (for steam) ft water per ft equiv. tube length [KPa/m] ( lb) 2 (in.) 2 (ft) 4 (g) 2 2 (mm) 4 (m) - - - - 15-24 Plot Δ p tv /L e v vm vs w v /N c (ν22ο vs ν18ο) on logarithmic - - - - coordinates as shown in Fig. 3. This curve is used in obtaining steam coil application ratings.

CALCULATION OF REFRIGERANT-SIDE THEREMAL RESISTANCES FROM VOLATILE REFRIGERANT COIL TESTS ARI CERTIFICATION PROGRAM FOR FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING COMPANY DATE SOLUTION PROCEDURE DRY TED COIL LINE COIL TYPE COIL 1 1 1 A o - Total External Coil Surface (From Form 410-1) sq ft [m 2 ] 2 2 2 D I - Tube Inside Diameter (From Form 410-1) in. [mm] 3 3 3 N t - Total Number of Tubes in Coil 4 4 4 L t - Coil Finned Tube Length Exposed to Air Flow in. [mm] 5 5 5 B - Surface Ration (From Form 410-1) 6 6 6 N c - Number of Tube Circuits in Coil 7 7 7 A ix - Total Cross-Section Fluid Flow Area Inside Tubes 0.00545 (ν2ο) 2 x ν6ο sq ft [m 2 ] [A ix 7.85 x 10-7 (ν2ο) 2 x ν6ο) 8 8 8 L x - Straight Tube Length Per Pass in. [mm] 9 9 9 L e - Equivalent Length of Coil Circuit Per Return Bend in. [mm] Sheet 1 of 11 Form 410-4

SOLUTION PROCEDURE PROCEDURE TEST RUN NUMBER DRY TED 1 2 3 4 10 10 10 L e - Total Equivalent Length of Coil Circuit ft COIL PHYSICAL DATA 3 3 [m] 0.0833 8 + 9 1 6 6 L e 3 3 0.001 8 + 9 1 6 6 11 11 11 P s - Average Absolute Static Pressure at Test Coil in. Hg abs [KPa abs] 12 12 12 t l - Entering Air Dry-Bulb Temperature F 13 13 13 ' t l - Entering Air Wet-Bulb Temperature F 14 14 14 h i - Entering Air Enthalpy Btu per lb dry air [KJ/Kg] 15 15 15 t 2 - Leaving Air Dry-Bulb Temperature F 16 16 16 h 2 - Leaving Air Enthalpy Btu per lb dry aid [KJ/Kg] 17 17 17 V a - Standard Air Face Velocity ft per min [m/s] 18 18 LABORATORY TEST OBSERVATIONS AND CALCULATIONS OBTAINED FROM ASHRAE STANDARD 33-78, FORMS 33TD-1 AND 33TD-4 18 P rc2 - Absolute Refrigerant Pressure Leaving Coil Circuits psia [KPa abs]

SOLUTION PROCEDURE PROCEDURE TEST RUN NUMBER DRY TED 1 2 3 4 19 19 19 )p rc - Refrigerant Pressure Drop Through Coil Circuits psi [KPa] LABORATORY TEST OBSERVATIONS AND CALCUALTIONS OBTAINED FROM ASHRAE STANDARD 33-78, FORMS 33TD-1 AND 33TD-4 20 20 20 t r1 - Saturated Refrigerant Temperature Entering Coil Circuits 21 21 21 ' t rc2 - Saturated Refrigerant Temperature Leaving Coil Circuits 22 22 22 t rc2 - Temperature of Superheated Refrigerant Leaving Coil Circuits t r2 23 23 23 w r - Refrigerant Flow Rate lb per hr [g/s] 24 24 24 q s - Average Sensible Cooling Capacity Btuh [W] F F F 25 25 25 q t - Average Total Cooling and Dehumidifying Capacity Btuh [W] 26 26 26 q s /q t - Sensible Heat Ratio ν24ο / ν25ο (If ν26ο << 0.95, coil surface is all wet or partically dry; if ν26ο 0.95 coil surface is fully dry) 27 27 27 v rc2 - Specific Volume of Saturated Refrigerant Leaving Coil Circuit (From Refrigerant Tables with ν18ο) 28 28 CALCULATIONS OF REFRIGEANT- SIDE THERMAL RESISTANCES 28 R ad + R md - Combined Air Film Plus Metal Thermal Resistance (From Fig. 4 with ν17ο ) cu ft per lb [m 3 /Kg] (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W]

FORM 410-4

SOLUTION PROCEDURE PROCEDURE TEST RUN NUMBER DRY TED 1 2 3 4 29 29 t m - Overall Logarithmic Mean Temperature Difference ( 12 20 ) 12 1n 15 ( 15 20 21 21 ) If other than thermal counterflow, determine the logarithm mean temperature difference from Figs. 13, 14 or 15. 30 30 R - Overall Thermal Resistance ν1ο x ν29ο ν25ο 31 31 R r - Film Thermal Resistance of Refrigerant ν30ο - ν28ο 32 32 f r - Refrigerant-Side Film Heat Transfer Coefficient ν5ο / ν31ο 33 33 q t /N c - Refrigerant Loading Rate Per Tube Circuit ν25ο / ν6ο 34 28 CALCULATIONS OF REFRIGERANT-SIDE THERMAL RESISTANCES 34 )p rc /L e v rc2 - Pressure Drop Parameter for Volatile Refrigerant ν19 ο ν10ο x ν27ο F (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W] (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W] Btu per (hr) (sq ft) (F) [W/m 2 Α ΕC] Btuh per circuit [watt per circuit] (lb) 2 (in.) 2 (ft) 4 2 (g) 2 (mm) (m) 4 FORM 410-4

SOLUTION PROCEDURE PROCEDURE TEST RUN NUMBER DRY TED 1 2 3 4 35 29 35 w r /N c - Volatile Refrigerant Flow Rate Per Tube Circuit ν23ο / ν6ο 36-36 Plot R r vs q t /N c (ν31ο vs ν33ο) on logarithmic coordinates as shown in Fig. 6. 37 30 37 Plot Δp c /L e v rc2 vs w r /N c (ν34ο vs ν35ο) on logarithmic coordinates as shown in Fig. 6. This curve is used for application ratings of volatile refrigerant coils. - 31 38 R aw - Air Film Thermal Resistance for Wet Surface - (From Fig. 5 with ν17ο) 32 39 f r (Assumed) - Refrigerant-Side Film Heat Surface Transfer Coefficient Note: Assume this value for trial and error solution. Suggest initial trial value of 300. - 33 40 R r - Film Thermal Resistance of Refrigerant - 34 CALCULATIONS OF REFRIGERANT-SIDE THERMAL RESISTANCES ν5ο / ν39ο 41 R mw - Approximate Total Metal Thermal Resistance (Wetted Surface) (From Fig. 2 with f aw 1/ν38ο) lb per hr per circuit gram per sec ond per circuit - - - - - - - - (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W] Btu per (hr) (sq ft) (F) [W/m 2 Α ΕC] (hr) (sq ft) (F) per Btu [m2 Α Εc/w] (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W]

SOLUTION PROCEDURE PROCEDURE FORM 410-4 TEST RUN NUMBER DRY TED 1 2 3 4-35 42 C Δ- Approximate Coil Characteristic (for Wetted Surface) 40 + 41 40 + 41 C 0.243 38 1.018 38 Note: This approximate value of C is used only to obtain the final value of R mw in ν48ο. (lb) (F) per Btu Kg C KJ - 36 43 h m - Mean Air Enthalpy 0.5 (ν14ο + ν16ο) Btu per lb dry air [KJ/Kg - 37 44 t rm - Mean Refrigerant Temperature 0.5 (ν20ο + ν21ο) - 38 45 t sm - Approximate Mean Surface Temperature - 39 CALCULATIONS OF REFRIGERANT-SIDE THERMAL RESISTANCES 46 " p (From Fig. 9 with ν42ο, ν43ο, and ν44ο) m / c -Approximate Air-Side Heat Transfer Multiplier for Wet Surface Coils (From Fig. 8 with ν11ο and ν45ο) - 40 47 f aw - Air-Side Heat Transfer Coefficient ν46ο / ν38ο Btu per (hr) (sq ft) (F) [W/m 2 Α ΕC] F F - 41 48 R mw - Total Metal Thermal Resistance of Fin and Tube for Wet Surface (From Fig.2 with 47) ((hr) (sq ft) (F) per Btu [m 2 Α ΕC] FORM 410-4

SOLUTION PROCEDURE PROCEDURE TEST RUN NUMBER DRY TED 1 2 3 4-42 49 C - Coil Charactertistic for Wetted Surface - 43 CALCULATIONS OF REFRIGERANT-SIDE THERMAL RESISTANCES 50 " t l 40 + 48 0.243 38 40 + 48 C 1.018 38 - Entering Air Dew Point Temperature (From Psychrometric Chart with ν11ο, ν12ο, and ν13ο) Calculation of Dew Point Temperature for Nonstandard Air Pressure* p v p v ' p p ' ' (p s p ) (tl tl) ' 2830 1.44 tl ' ' ' ( p p )( t t ) s l 1548.4 1.33 t l ' l Where: p s Air Pressure- ' p Saturation Vapor Pressure at ' t l from Steam Tables p v Saturation Vapor Pressure at Dew Point Temperature- (lb) (F) per Btu Kg C KJ F in. Hg abs {Kpa abs] FORM 410-4

SOLUTION PROCEDURE PROCEDURE TEST RUN NUMBER DRY TED 1 2 3 4 " t l Dew Point Temperature Is Saturation Temperature Corresponding to Saturation Vapor Pressure, p v from Steam Tables - 44 51 t sl - Coil Suface Temperature on Entering Air Side (From Fig. 9 with ν14ο, ν20ο, and ν49ο unless ν11ο varies more than 0.3 in. Hg [ 1.014 KPa] from 29.92 in Hg. [101.325 Kpa]. If it does, then determine t sl by trial and error using equation: - 45 CALCULATIONS OF REFRIGERANT-SIDE THERMAL RESISTANCES t sl t rl + C (h l - h sl ). Correct h sl for ν11ο and use ν14ο, ν20ο, and ν49ο. For fully wetted coil ν50ο ν51ο. If ν50ο < ν51ο, coil is partially wet and calculation procedures may be determined from Form 410-6) F F 52 h sl - Saturated Air Enthalpy at t sl (From Air Enthalpy Btu per lb Tables with ν11ο and ν51ο) dry air [KJ/Kg]

SOLUTION PROCEDURE PROCEDURE FORM 410-4 TEST RUN NUMBER DRY TED 1 2 3 4-46 53 t s2 - Coil Surface Temperature on Leaving Air Side (From Fig. 9 with ν16ο, ν21ο, and ν49ο unless ν11ο varies more than 0.3 in. Hg [ 1.014 Kpa] from 29.92 in. Hg [101.325 Kpa]. If it does, then determine t s2 by trial and error using equation: t s2 t r2 +C (h 2 - h s2 ). Correct h s2 for ν11ο and use ν16ο, ν21ο, and ν49ο.) - 47 54 h s2 - Saturated Air Enthalpy at t s2 (From Air Enthalpy Tables with ν11ο and ν53ο) - 48 55 h m - Logarithmic Mean Enthalpy Difference - 49 CALCULATIONS OF REFRIGERANT-SIDE THERMAL RESISTANCES ( 14 52 ) 14 ln 16 ( 16 54 ) 52 54 56 A c - Calculated External Surface Area of Coil 0.243 (ν38ο x ν25ο/ν55ο) F Btu per lb dry air [KJ/Kg] Btu per lb dry air [KJ/Kg] sq ft [m 2 ] [A c 1.018 (ν38ο x ν25ο / ν55ο)] FORM 410-4

SOLUTION PROCEDURE PROCEDURE TEST RUN NUMBER DRY TED 1 2 3 4-50 57 Assume other values for ν39ο and repeat procedure through ν56ο. Plot ν39ο vs ν56ο as in Fig. 12b. Two or more points should be plotted so that A o lies between calculated values of A c. - 51 58 f r - Refrigerant Side Film Heat Transfer Coefficient Note: The point on the curve (Fig. 12b), as PLOTS plotted in ν57ο, where A c A o determines the value of f r corresponding to the circuit loading, ν33ο. Btu per (hr) (sq ft) (F) [W/m 2 Α ΕC] - - - - - 52 59 Rr - Film Thermal Resistance of Refrigerant ν5ο/ν58ο (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W] - 53 60 Plot R r vs q t /N c (ν59ο vs ν33ο) on logarithmic coordinates as shown in Fig. 6. This curve is used to obtain application rating data. - - - - SIGNED TITLE

t l h ' l t sl h ' sl t 2 h ' 2 t rl t s h 2' s2 t rc2

SUGGESTED FORM FOR RATING CALCULATION PROCEDURE FOR SENSIBLE HEAT AIR ARI CERTIFICATION PROGRAM FOR FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING COMPANY DATE SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE 1 1 1 1 1 H - Coil Face Height in. [mm] 2 2 2 2 2 L - Coil Face Length in. [mm] 3 3 3 3 3 A f - Coil Face Area sq ft [m 2 ] COIL PHYSICAL DATA 4 4 4 4 4 B - Surface Ration (From Form 410-1) 5 5 5 5 5 N r - Number of Rows Deep 6 6 6 6 6 N t - Total Number of Tubes in Coil 7 7 7 7 7 N c - Parallel Tube Circuits in Coil 8 8 8 8 8 A o /A f N r (sq ft ) per (sq ft F.A.) (row) 9 9 9 9 9 A o ν8ο x ν3ο x ν5ο sq ft

10 10 10 10 10 D i - Tube Inside Diameter in. [mm] SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE 11 11 11 11 11 A ix - Total Cross Sectional Fluid Flow Area 12 12 12 12 12 L s Inside Tubes 0.00545 (ν10ο 2 [A ix 7.85 x 10-7 (ν10ο x ν7ο)] - Straight Tube Length Per Tube Pass 13 13 13 13 13 K b - Equivalent Length of Coil Circuit Per Return Bend in. [mm] 14 14 14 14 COIL PHYSICAL DATA x ν7ο) 14 L e - Total Equivalent Length of Coil Circuit L e 6 6 0.0833 12 + 13 1 7 7 7 6 0.001 12 + 13 1 7 7 sq ft [m 2 ] in. [mm] ft [m] 15 15 15 15 NG CON DITI 15 Q a - Air Volume Flow at Standard Conditions scfm [std Ρ/s]

16 16 16 16 16 V a - Standard Air Face Velocity, ν15ο/ν3ο V a 0.001 x ν15ο/ν3ο] ft per min [m/s] 17 17 17 17 17 t l - Entering Air Dry-Bulb Temperature F - 18-18 18 V w - Average Standard Water Velocity in Tubes ft per sec [m/s SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE - 19-19 19 18 20 18 20 20 T wl P s - Entering Water Temperature - Average Absolute Static Pressure at Coil F in. Hg abs [Kpa abs] 19-19 - 21 P v1 - Inlet Steam Gage Pressure to Coil psig [Kpa gage] 20-20 - COIL PHYSICAL DATA 22 ' t - Inlet Steam Temperature to Coil vl F 21-21 - S M PROP ERTIE 23 P vl - Coil Inlet Steam Pressure ν21ο + 0.491 ν20ο [P vl ν21ο + ν20ο] psia [Kpa abs)

22-22 - 24 t vl - Steam Saturation Temperature Entering Coil (From ν23ο and Steam Property Tables) 23-23 - 25 v vl - Steam Specific Volume Entering Coil (From ν22ο, ν23ο and Steam Property Tables) v v2 for rating convenience 24-24 - 26 h vl - Enthalpy of Steam Entering Coil (From ν22ο, ν23ο and Steam Property Tables) F cu ft per lb [m 3 /Kg] Btu per lb [KJ/Kg] SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE 25-25 - STEAM PROPERTIES 27 h f2 - Enthalpy of Steam Condensed Leaving Coil (From ν23ο and Steam Property Tables as- suming h fl h f2 for rating convenience) Btu per lb [KJ/Kg] - 21-21 WATER RATING PARAMETERS 28 t wm - Mean Water Temperature Inside Tubes - When solving for rows deep, this value is known (assume c pw 1.000 for this calculation) - When solving for capacity, this value must be approximated (Suggest t wm be 5 F [2.8ΕC to 10 F [5.6ΕC] from t wl F

- 22-22 29 w w - Water Flow Rate 224,500 x ν11ο x ν18ο [w w 1,000,000 x ν11ο x ν18ο] lb per hr [g/s] - 23-23 (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W] SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE - 24-24 31 (hr) (sq ft) (F) per Btu - 25-25 WATER RATING PARAMETERS 32 R ad + R md - Combined Air Film Plus Metal Thermal Resistance (From Fig. 4 with ν16ο [m 2 Α ΕC/W] (hr) (sq ft) (F) per Btu [m 2 Α ΕC/W]

26 26 26 26 33 R - Overall Thermal Resistance between Air and (hr) (sq ft) Tube-Side Fluid ν31ο + ν32ο for Water (F) per Btu Coils (From Fig. 3 knowing ν16ο for Steam Coils) [m 2 Α ΕC/W] SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE - - 27 27 C CU O NS TO SOLVE FOR COIL CAPACITY 34 M - Air-to-Tube Fluid-Side Heat Capacity Ratio.5 x 15 x c 29 1.2 x 15 x c M 29 4 p p

- - 28 28 35 C o - Heat Transfer Exponent 4.5 c p 9 x 15 x 33 C o 1.2c p 9 x 15 x 33 - - 29 29 36 E - Air-Side Effectiveness - at ν34ο and ν35ο 0 and Fig. 13 for Steam Coils - at ν34ο, ν35ο, and Fig. 13 for One-Row Water Coils - at ν34ο, ν35ο, and Fig. 14 for Two-Row Water Coils - at 34, 35, and Fig. 15 for Three-Row or Greater Counterflow Water Coils SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE

27 27 30 30 37 Δt o - Initial Air-to-Field Temperature Difference - - 31 31 38 q s - Coil Sensible Heat ν19ο - ν17ο - For Air-Heating Water Coils ν17ο - ν19ο - For Air-Cooling Water Coils ν24ο - ν17ο - For Steam Coils 4.5 c p x ν15ο x ν36ο x ν37ο [ q s 1.2 c p x ν15ο x ν36ο x ν37ο ] - - 32 32 39 )t a - Air Temperature Rise or Drop Across Coil 4.5 c 38 x 15 p Δt a 1.2 c - - 33 34 40 t 2 - Leaving Air Temperature at Coil - - 33 34 CALCULATIONS TO SOLVE FOR COIL CAPACITY (qs) ν17ο + ν39ο (For Air Heating) ν17ο - ν39ο (For Air Cooling) p 38 x 15 41 )t w - Water Temperature Rise or Drop Across Coil ν18ο / ν29ο F Btuh [W] F F F SOLUTION PROCEDURE COIL LINE COIL TYPE COIL PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) TO SOLVE FOR CAPACITY (q s ) GENER AL CATEG ITEM NO.

STEAM HOT OR COLD WATER STEAM HOT OR COLD WATER - - - 35 42 *t wm - Average Water Temperature Inside Tubes ν19ο - 0.5 x ν41ο - For Air-Heating Coil ν19ο + 0.5 x ν41ο - For Air-Cooling Coil F CALCULATIONS TO SOLVE FOR ROWS DEEP 28 28 - - 43 q s - Coil Sensible Heat (Known) Btuh 29 29 - - 44 )t a - Air Temperature Rise or Drop Across Coil 43 4.5 c x 15 p Δt a 1.2 c 30 30 - - 45 t 2 - Leaving Air Temperature at Coil p 43 x 15 ν17ο + ν44ο For Air-Heating Coil ν17ο - ν44ο For Air-Cooling Coil - 31 - - 46 )t w - Water Temperature Rise or Drop Across Coil ν43ο / ν29ο [W] F F F - 32 - - 47 t w2 - Leaving Water Temperature at Coil ν19ο - ν46ο - For Air-Heating Coil ν19ο + ν46ο - For Air-Cooling Coil F * ν42ο must equal ν28ο within 5 F [ 2.8]. If not, assume a new value for ν28ο and repeat calclations through ν42ο. SOLUTION PROCEDURE COIL LINE COIL TYPE COIL

PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER 31 33 - - 48 M - Air-to-Tube Fluid-Side Heat Capacity Ratio 32 34 - - 49 E - Air-Side Effectiveness CALCULATIONS TO SOLVE FOR ROWS DEEP ν46ο / ν44ο - For Water Coils 0 - For Steam Coils (for rating convenience) ν44ο / ν37ο 33 35 - - 50 C o - Heat Transfer Exponenet (Air-to-Tube Fluid) - From Fig. 13 or 14 or 15 with ν48ο and ν49ο - Fig. 13 for One-Row Coils - Fig. 14 for Two-Row Coils - Fig. 15 for Coils with three rows or more 34 36 - - 51 N rc - Calculated Row Depth Required 43 8 x x 33 3 x x 50 44 35 37 - - 52 N t - Integral Coil Row Depth Installed

SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE 36 38 34 36 53 )p st /N r - Air-Side Pressure Drop Per Row Deep at Standard Conditions (From Fig. 3 or 4 with ν16ο) CALCULATIONS TO SOLVE FOR ROWS DEEP 37 39 35 37 54 F a - Air-Side Pressure Drop Correction Factor 17 + 40 + 45 460 + 2 17.71 x 20 273.15 17 + 40 or 45 + 2 2.909 x 20 38 40 36 38 55 ()p a ) JOB - Air-Side Pressure Pressure Drop at Job Conditions F a (Constant w a ) ν52ο x ν53ο x ν54ο in. water row [pascal per row] in water [Pa] 39-37 - 56 w v - Total Steam Condensate Mass Flow Rate Through Coil ν38ο or ν43ο ν26ο or ν27ο lb per hr [g/s]

40-38 - 57 w v /N c - Steam Flow Rate Per Tube Circuit lb per (hr) ν56ο / ν7ο (circuit) [(gram) per second) (circuit) SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE 41 41 39 39 58 Obtain Header, Nozzle and Entrance and Exit Losses for Water and Steam to be determined by manufacturer )p h /F h - for Water Coils at 60ΕF Mean Water Temperature with ν18ο )p h /v vm - for Steam Coils - 42-40 59 )p t /L e F t - Tube Circuit Water Pressure Drop Parameter at 60 F [15.6ΕC] Mean Water Temperature (From Fig. 4 with ν18ο ) (F t l) - 43-41 CALCULATIONS TO SOLVE FOR ROWS DEEP 60 F h - Temperature Correction Factor for Header Water Pressure Drop (From Fig. 7 with ν28ο ft of water [kpa] (lb) 2 (in.) 2 (ft) 3 2 (g) 2 (mm) (m) ft water per ft [KPa/m] 3

- 44-42 61 F t - Temperature Correction Factor for Water Pressure Drop (From Fig. 7 with ν28ο ) - 45-43 62 )p w ) JOB - Water Pressure Drop Across Coil at Job Conditions ν58ο x ν60ο + ν14ο x ν59ο x ν61ο ft water [Kpa] SOLUTION PROCEDURE TO SOLVE FOR ROWS DEEP (N r ) STEAM HOT OR COLD WATER TO SOLVE FOR CAPACITY (q s ) STEAM HOT OR COLD WATER COIL LINE COIL TYPE COIL PROCEDURE 42-40 - 63 )p tv /L c v vm - Steam Pressure Drop Parameter (From Fig. 3 with ν57ο 43-41 - TUBE-SIDE PRESSURE DROP CALCULATIONS (lb) 2 (in.) 2 (ft) 4 2 (g) 2 (mm) (m) 64 )p v - Steam Pressure Drop Inside Tubes at Job Conditions psi [(ν63ο x ν14ο) + ν58ο ] ν25ο [Kpa] 4

Signed Title SUGGESTED FORM FOR RATING CALCULATION PROCEDURE FOR COOLING AND DEHUMIDIFYING ARI CERTIFICATION PROGRAM FOR FORCED-CIRCULATION AIR-COOLING AND AIR-HEATING SOLUTION PROCEDURE COLD WATER PARTIALLY VOLATILE REFRIGERANT STEAM COIL LINE COIL TYPE COIL PROCEDURE 1 1 1 1 1 H - Coil Face Height in. [mm] 2 2 2 2 COIL PHYSICAL DATA 2 L - Coil Face Length in. [mm]

3 3 3 3 3 A f - Coil Face Area sq ft [m 2 ] 4 4 4 4 4 B - Surface Ration (From Form 410-1) 5 5 5 5 5 N r - Number of Rows Deep (if known) 6 6 6 6 6 N t - Total Number of Tubes in Coil (if known) 7 7 7 7 7 N c - Parallel tube Circuits in Coil (if known) 8 8 8 8 8 A o /A f N r (sq ft) per (sq ft F.A.) (row) [(sq metre) per] [(sq metre-f.a.) (Row) SOLUTION PROCEDURE COLD WATER PARTICLALY VOLATILE REFRIGERANT STEAM COIL LINE COIL TYPE COIL PROCEDURE 9 9 9 9 9 D i - Tube Inside Diameter in. [mm] 10 10 10 10 COIL PHYSICAL DATA 10 L s - Straight Tube Length Per Tube Pass in. [mm]

11 11 11 11 11 K b - Equivalent Length of Coil Circuit Per Return Bend in. [mm] 12 12 12 12 12 A o - ν8ο x ν3ο x ν5ο (if known) sq ft [m 2 ] 13 13 13 13 13 A ix - Total Cross-Sectional Fluid Flow Area Inside Tubes 0.00545 (ν9 2 ο x ν7ο) [A ix 7.85 x 10-7 (ν9ο 2 x ν7ο)] 14 14 14 14 14 L e Total Equivalent Length of Coil Circuit 6 6 0.0833 10 + 11 l 7 7 L e 6 6 0.001 10 + 11 1 7 7 15 15 15 15 15 Q a - Air Volume Flow at Standard Conditions scfm [std Ρ/s] 16 16 16 16 RATING CONDITIONS AND DATA COMUPATTIONS 16 V a - Standard Air Face Velocity ν15ο/ν3ο [V a 0.001 x ν15ο/ν3ο sq ft [m 2 ] ft [m] ft per min [m/s] SOLUTION PROCEDURE COLD WATER PARTIALLY VOLATILE REFRIGERANT PARTIALLY COIL LINE COIL TYPE COIL PROCEDURE

17 17 17 17 17 t l - Entering Air Dry-Bulb Temperature F 18 18 18 18 18 ' t - Entering Air Wet-Bulb Temperature RATING CONDITIONS AND DATA COMPUTATIONS l 19 19 - - 19 V w - Average Standard Water Velocity in Tubes ft per sec [m/s] 20 20 - - 20 t wl - Entering Water Temperature F - - 19 19 21 t r2 - Saturated Suction Refrigerant Temperature at Coil Outlet Note: For rating convenience, it is assumed that there is no temperature drop from coil circuits to coil outlet. - - 20 20 22 ' t r2 - Superheated Refrigerant Temperature at Coil Outlet Note: For rating convenience, it is assumed that there is no temperature drop from coil circuits to coil outlet. 21 21 21 21 23 P s - Average Absolute Static Pressure at Coil in. Hg abs [Kpa abs] F F F - - 22 22 24 t ro - Refrigerant Temperature Entering the Coil Control Device (Equal to the refrigerant condensing temperature) F SOLUTION PROCEDURE COIL LINE COIL TYPE COIL PROCEDURE COLD WATER VOLATILE REFRIGERANT GENER AL CATEG ITEM NO.

PARTIALLY PARTIALLY - - 23 23 25 h ro - Enthalpy of Refrigerant Entering Coil Control Device (From ν24ο and Refrigerant Tables) 22 22 24 24 26 h l - Entering Air Enthalpy (From ν17ο, ν18ο, and ν23ο) 23 23 25 25 27 60w a - Standard Air Flow Rate 4.50 x ν15ο [1000w a 1.2 x ν15ο ] 24 24 26 26 28 Case I - If ν29ο is known, determine ν30ο at ν29ο saturated and ν23ο. Then calculate ν31ο ν27ο (ν26ο - ν30ο). 25 25 27 27 RATING CONDITIONS AND DATA COMPUTATIONS Case II - Case III - If ν31ο is known, determine ν30ο and then ν29ο. ν30ο ν26ο ν31ο/ν27ο. If ν5ο is known, assume ν31ο or ν29ο, find ν30ο and then ν29ο or ν31ο, respectively. 29 ' t - Leaving Air Wet-Bulb Temperature 2 Btu per lb [KJ/Kg] Btu per lb [KJ/Kg] lb per hr [g/s] F SOLUTION PROCEDURE COIL LINE COIL TYPE COIL

PROCEDURE COLD WATER PARTIALLY VOLATILE REFRIGERANT PARTIALLY SURFCE 26 26 28 28 30 H 2 - Leaving Air Enthalpy If q t is known, h 2 ν26ο - 27 27 29 29 31 q t - Total Heat Capacity of Coil ν27ο (ν26ο - ν30ο) Enter numerical value if known. q t 27 If not known, assume a numberical value for a trial and error solution. 28 28 - - 32 w w - Water Flow Rate 224,500 x ν13ο x ν19ο [w w 1,000,000 x ν13ο x ν19ο] Btu per lb [KJ/Kg] Btuh [W] lb per hr [g/s] 29 29 - - 33 t w2 - Leaving Water Temperature ν20ο + ν31ο/ν32ο F - - 30 30 34 P r2 - Absolute Pressure of Refrigerant at Coil Outlet (From Refrigerant Tables with ν21ο) - - 31 31 RATING CONDITIONS AND DATA COMPUTATIONS 35 h r2 - Enthalpy of Saturated Refrigerant Vapor at Coil Outlet Pressure (From Refrigerant Tables with ν21ο. Assumed saturated for rating convenience.) psia [KPa abs] Btu per lb [KJ/Kg]