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Shell and Tube Heat Exchanger Design SpreadsheetProject: Evaporator Project No.: Item No.: - Service: Cooling of 23% sodium chloride solution By:
Tube Side ShellR-404 Fluid Name Sodium Chloride1.132 Flow (M), Kg/s 33.2
-13 -9 No. of passes =-13 -10
Av. Density 903 1050Av. Viscosity 0.158 2.300
Av. Heat Capacity 1.250 4.36Heat Exchanged 145 Q, kW 145
Av. Thermal Conductivity 0.0376 0.5800Fouling Resistance 0.0004 0.0004
LMTD 3.5Corrected LMTD 3.5
Tube OD 0.0125 m length (can be trial and error). BWG 16
Tube ID, d = 0.00925 mTube Length, L = 2 m
Area of one tube = 0.079Cross sectional area of tube = 0.00007
page number 648 Bundle diameter = 0.417758 mShell diameter = 0.430258 m
7382Prandtl No. = 5.24Length / ID = 216
page number 665 0.0032Nusselt number = 40.80
165.86
The values in this block will keep on changing
Step 1. Input flows, conditions and properties data for shellside and tubeside Step 3. Start configuring the exchanger. Begin with the assumed overall heat transfer coefficient to this point:
Temp. in, °CTemp. out, °C
r, Kg/m3
m, mNs/m2
cp, kJ/kg°C
k, W/m°CR,m² °C/W Step 6. Shell side heat transfer
coefficient
°C°C
Step 2. Input tubing OD, BWG and
Segmental baffle cut 25% page number 673 jh =
m²m²
Step. 4 Bundle and Shell diameter
Step. 5 Tube side heat transfer coefficient
Tubeside Reynolds No., NRe =
j h
hi = W/m² °C
Shell and Tube Heat Exchanger Design Spreadsheet-
MAS Date/Time: 6-May-23 13:00 BWG/Tube Wall Thicknesses89
101000.00 11
Then the required transfer A = 41.714 12Number of tubes required = 531 13
No. of passes = 4 14Tubes per pass = 134 132.85 15
Area of tubes per pass = 0.00900 16Volumetric flow = 0.001254
Av. Velocity = 0.139284 m/s
Tube Pitch = 0.015625 mPattern = Tri.
Baffle Spacing = 0.237 mArea of Shell = 0.020363
0.008876 mVolumetric flowrate = 0.031660
Shellside velocity = 1.55 m/s6,300
Prandtl No. = 170.0070
Nusselt number = 1147,444
R1 = 0.00013R2 = 0.00040 For 2 tube passesR3 = 0.000042
R4 = 0.0087Overall heat transfer coefficient = 107.9
Step 3. Start configuring the exchanger. Begin with the assumed overall heat transfer coefficient to this point:
Ustart = W/m² °Cm2
m²m³/s
Step 6. Shell side heat transfer coefficient
m²Equivalent Diameter, de =
m³/s
Shellside Reynolds No., NRe =
Segmental baffle cut 25% page number 673 jh =
ho = W/m² °C
W/m² °C
BWG/Tube Wall Thicknesses0.1650.148 0.0170.134 0.0140.120 0.0140.109 0.0110.095 0.0140.083 0.0120.072 0.0110.065 0.007
For 2 t.p For 4 t.p For 6 t.p0.249 0.175 0.0743 page number 6492.207 2.285 2.499 page number 649
Clearance 0.0125 page number 646
k1
n1
Shell and Tube Heat Exchanger Design SpreadsheetProject: Evaporator Project No.: -Item No.: - Service: Water cooler By: MAS
Tube Side ShellR-22 Fluid Name Water168.5 Flow (M), lb/h 11,014.1
5 865 82 Reset tubes/pass (Step 3), then no. of passes =
Av. Density 0.8053 62.42Av. Viscosity 0.011 m, cP 1.903
Av. Heat Capacity 0.163 1.003Heat Exchanged 48,000 Q, Btu/h 44,188
Av. Thermal Conductivity 0.0049 0.3351Fouling Resistance 0.0040 0.004
Prandtl No. 0.87 13.78 and estimate shell diameterCorrected MTD 79.0Corrected MTD 79.0
Tube OD 0.5000 in. length (can be trial and error). BWG 16
Tube ID, d = 0.370 in.Tube Length, L = 2 ft.
0.108Effective transfer area per tube = 0.262
Tubes/pass = 66 tubes per tube pass. lb/h per tube = 3
lb/h per tube per pass = 1.3Av. velocity, fps = 1.18
4,025Tubeside Friction Factor, f = 0.027
0.00021 adjust tube length, number of tubes per pass, number of passes, and/or shellNusselt number, Nr = 7.04 baffle spacing. Remember to reset shell diameter from tube count tables, as
11 required.
Step 1. Input flows, conditions and properties data for shellside and tubeside Step 5. Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Over all heat transfer Coefficient, Uo =
Temp. in, oFTemp. out, oF
r, lb/ft3
cp, Btu/lb·oF
k, Btu/h·ft·oF R, ft2·h·oF/Btu Step 4. Select tube arrangement
cpm/koFoF
Step 2. Input tubing OD, BWG and Equivalent Diameter, de (see table) =
Flow area per tube, at = in.2
ft2
Step 3. Estimate the number of Check: % difference, Ucalc. vs Uassum. =
Tubeside Reynolds No., NRe =Step 6. Check tubeside velocity and DP, shellside DP. If too high or too low,
DP per pass, psi =
Inside Film Coefficient, hi =
Shell and Tube Heat Exchanger Design Spreadsheet-
MAS Date/Time: 6-May-23 13:00 BWG/Tube Wall Thicknesses8 0.1659 0.148 0.017
10 0.134 0.01410 11 0.120 0.0149.7 12 0.109 0.011
Then the required transfer A = 63 13 0.095 0.014Number of tubes required = 239 14 0.083 0.012
Reset tubes/pass (Step 3), then no. of passes = 2 15 0.072 0.011Total tube count = 132 16 0.065 0.007
5.802 psi Actual effective transfer area, A = 35 MTD Correction Factors
#DIV/0!Tube Pitch 0.65 in.
and estimate shell diameter Pattern Tri. 0.000Shell ID from Tube Count Tables 8 in.
Select Baffle Spacing 5 in. #DIV/0!Number of Baffles = 4 3.80
0.064 ( 1 - S ) / ( 1 - RS ) = #DIV/0!7.5 in.
171,820 #DIV/0!56,431
Shellside Friction Factor = 0.00153 #DIV/0!0.357 psi 139.7 #DIV/0!1799.7
0.0%10.5
adjust tube length, number of tubes per pass, number of passes, and/or shell baffle spacing. Remember to reset shell diameter from tube count tables, as required.
Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Ustart = Btu/h·ft2·oF
Over all heat transfer Coefficient, Uo = Btu/h·ft2·oF
ft2
Tubeside DP (incl. returns) =ft2
R = ( T1 - T2 ) / ( t2 - t1 ) = Select tube arrangement
S = ( t2 - t1 ) / ( T1 - t1 ) =
( R2 + 1 ) ½ =
Flow Area across Bundle, as = ft2
Equivalent Diameter, de (see table) =Mass Velocity, Gs = lb/h·ft2 2 - S ( R + 1 - ( R2 + 1 ) ½ ) =
Shellside Reynolds No., NRe =2 - S ( R + 1 + ( R2 + 1 ) ½ ) =
Shellside DP =Outside Transfer Factor, jh = FT =
Outside Film Coefficient, ho =Calculated Uo =
Check: % difference, Ucalc. vs Uassum. =Uclean =
Check tubeside velocity and DP, shellside DP. If too high or too low,
Shell and Tube Heat Exchanger Design SpreadsheetProject: Evaporator Project No.: -Item No.: - Service: Water cooler By: MAS
Tube Side ShellR-22 Fluid Name Water168.5 Flow (M), lb/h 11,014.1
5 865 82 Reset tubes/pass (Step 3), then no. of passes =
Av. Density 0.8053 62.42Av. Viscosity 0.011 m, cP 1.903
Av. Heat Capacity 0.163 1.003Heat Exchanged 48,000 Q, Btu/h 44,188
Av. Thermal Conductivity 0.0049 0.3351Fouling Resistance 0.0040 0.004
Prandtl No. 0.87 13.78 and estimate shell diameterCorrected MTD 79.0Corrected MTD 79.0
Tube OD 0.5000 in. length (can be trial and error). BWG 16
Tube ID, d = 0.370 in.Tube Length, L = 2 ft.
0.108Effective transfer area per tube = 0.262
Tubes/pass = 66 tubes per tube pass. lb/h per tube = 3
lb/h per tube per pass = 1.3Av. velocity, fps = 1.18
4,025Tubeside Friction Factor, f = 0.027
0.00021 adjust tube length, number of tubes per pass, number of passes, and/or shellNusselt number, Nr = 7.04 baffle spacing. Remember to reset shell diameter from tube count tables, as
11 required.
Step 1. Input flows, conditions and properties data for shellside and tubeside Step 5. Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Over all heat transfer Coefficient, Uo =
Temp. in, oFTemp. out, oF
r, lb/ft3
cp, Btu/lb·oF
k, Btu/h·ft·oF R, ft2·h·oF/Btu Step 4. Select tube arrangement
cpm/koFoF
Step 2. Input tubing OD, BWG and Equivalent Diameter, de (see table) =
Flow area per tube, at = in.2
ft2
Step 3. Estimate the number of Check: % difference, Ucalc. vs Uassum. =
Tubeside Reynolds No., NRe =Step 6. Check tubeside velocity and DP, shellside DP. If too high or too low,
DP per pass, psi =
Inside Film Coefficient, hi =
Shell and Tube Heat Exchanger Design Spreadsheet-
MAS Date/Time: 6-May-23 13:00 BWG/Tube Wall Thicknesses8 0.1659 0.148 0.017
10 0.134 0.01410 11 0.120 0.0149.7 12 0.109 0.011
Then the required transfer A = 63 13 0.095 0.014Number of tubes required = 239 14 0.083 0.012
Reset tubes/pass (Step 3), then no. of passes = 2 15 0.072 0.011Total tube count = 132 16 0.065 0.007
5.802 psi Actual effective transfer area, A = 35 MTD Correction Factors
#DIV/0!Tube Pitch 0.65 in.
and estimate shell diameter Pattern Tri. 0.000Shell ID from Tube Count Tables 8 in.
Select Baffle Spacing 5 in. #DIV/0!Number of Baffles = 4 3.80
0.064 ( 1 - S ) / ( 1 - RS ) = #DIV/0!7.5 in.
171,820 #DIV/0!56,431
Shellside Friction Factor = 0.00153 #DIV/0!0.357 psi 139.7 #DIV/0!1799.7
0.0%10.5
adjust tube length, number of tubes per pass, number of passes, and/or shell baffle spacing. Remember to reset shell diameter from tube count tables, as required.
Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Ustart = Btu/h·ft2·oF
Over all heat transfer Coefficient, Uo = Btu/h·ft2·oF
ft2
Tubeside DP (incl. returns) =ft2
R = ( T1 - T2 ) / ( t2 - t1 ) = Select tube arrangement
S = ( t2 - t1 ) / ( T1 - t1 ) =
( R2 + 1 ) ½ =
Flow Area across Bundle, as = ft2
Equivalent Diameter, de (see table) =Mass Velocity, Gs = lb/h·ft2 2 - S ( R + 1 - ( R2 + 1 ) ½ ) =
Shellside Reynolds No., NRe =2 - S ( R + 1 + ( R2 + 1 ) ½ ) =
Shellside DP =Outside Transfer Factor, jh = FT =
Outside Film Coefficient, ho =Calculated Uo =
Check: % difference, Ucalc. vs Uassum. =Uclean =
Check tubeside velocity and DP, shellside DP. If too high or too low,
Shell and Tube Heat Exchanger Design SpreadsheetProject: Evaporator Project No.: -Item No.: - Service: Water cooler By: MAS
Tube Side ShellR-22 Fluid Name Water168.5 Flow (M), lb/h 11,014.1
5 865 82 Reset tubes/pass (Step 3), then no. of passes =
Av. Density 0.8053 62.42Av. Viscosity 0.011 m, cP 1.903
Av. Heat Capacity 0.163 1.003Heat Exchanged 48,000 Q, Btu/h 44,188
Av. Thermal Conductivity 0.0049 0.3351Fouling Resistance 0.0040 0.004
Prandtl No. 0.87 13.78 and estimate shell diameterCorrected MTD 79.0Corrected MTD 79.0
Tube OD 0.5000 in. length (can be trial and error). BWG 16
Tube ID, d = 0.370 in.Tube Length, L = 2 ft.
0.108Effective transfer area per tube = 0.262
Tubes/pass = 66 tubes per tube pass. lb/h per tube = 3
lb/h per tube per pass = 1.3Av. velocity, fps = 1.18
4,025Tubeside Friction Factor, f = 0.027
0.00021 adjust tube length, number of tubes per pass, number of passes, and/or shellNusselt number, Nr = 7.04 baffle spacing. Remember to reset shell diameter from tube count tables, as
11 required.
Step 1. Input flows, conditions and properties data for shellside and tubeside Step 5. Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Over all heat transfer Coefficient, Uo =
Temp. in, oFTemp. out, oF
r, lb/ft3
cp, Btu/lb·oF
k, Btu/h·ft·oF R, ft2·h·oF/Btu Step 4. Select tube arrangement
cpm/koFoF
Step 2. Input tubing OD, BWG and Equivalent Diameter, de (see table) =
Flow area per tube, at = in.2
ft2
Step 3. Estimate the number of Check: % difference, Ucalc. vs Uassum. =
Tubeside Reynolds No., NRe =Step 6. Check tubeside velocity and DP, shellside DP. If too high or too low,
DP per pass, psi =
Inside Film Coefficient, hi =
Shell and Tube Heat Exchanger Design Spreadsheet-
MAS Date/Time: 6-May-23 13:00 BWG/Tube Wall Thicknesses8 0.1659 0.148 0.017
10 0.134 0.01410 11 0.120 0.0149.7 12 0.109 0.011
Then the required transfer A = 63 13 0.095 0.014Number of tubes required = 239 14 0.083 0.012
Reset tubes/pass (Step 3), then no. of passes = 2 15 0.072 0.011Total tube count = 132 16 0.065 0.007
5.802 psi Actual effective transfer area, A = 35 MTD Correction Factors
#DIV/0!Tube Pitch 0.65 in.
and estimate shell diameter Pattern Tri. 0.000Shell ID from Tube Count Tables 8 in.
Select Baffle Spacing 5 in. #DIV/0!Number of Baffles = 4 3.80
0.064 ( 1 - S ) / ( 1 - RS ) = #DIV/0!7.5 in.
171,820 #DIV/0!56,431
Shellside Friction Factor = 0.00153 #DIV/0!0.357 psi 139.7 #DIV/0!1799.7
0.0%10.5
adjust tube length, number of tubes per pass, number of passes, and/or shell baffle spacing. Remember to reset shell diameter from tube count tables, as required.
Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Ustart = Btu/h·ft2·oF
Over all heat transfer Coefficient, Uo = Btu/h·ft2·oF
ft2
Tubeside DP (incl. returns) =ft2
R = ( T1 - T2 ) / ( t2 - t1 ) = Select tube arrangement
S = ( t2 - t1 ) / ( T1 - t1 ) =
( R2 + 1 ) ½ =
Flow Area across Bundle, as = ft2
Equivalent Diameter, de (see table) =Mass Velocity, Gs = lb/h·ft2 2 - S ( R + 1 - ( R2 + 1 ) ½ ) =
Shellside Reynolds No., NRe =2 - S ( R + 1 + ( R2 + 1 ) ½ ) =
Shellside DP =Outside Transfer Factor, jh = FT =
Outside Film Coefficient, ho =Calculated Uo =
Check: % difference, Ucalc. vs Uassum. =Uclean =
Check tubeside velocity and DP, shellside DP. If too high or too low,
Shell and Tube Heat Exchanger Design SpreadsheetProject: Evaporator Project No.: -Item No.: - Service: Water cooler By: MAS
Tube Side ShellR-22 Fluid Name Water168.5 Flow (M), lb/h 11,014.1
5 865 82 Reset tubes/pass (Step 3), then no. of passes =
Av. Density 0.8053 62.42Av. Viscosity 0.011 m, cP 1.903
Av. Heat Capacity 0.163 1.003Heat Exchanged 48,000 Q, Btu/h 44,188
Av. Thermal Conductivity 0.0049 0.3351Fouling Resistance 0.0040 0.004
Prandtl No. 0.87 13.78 and estimate shell diameterCorrected MTD 79.0Corrected MTD 79.0
Tube OD 0.5000 in. length (can be trial and error). BWG 16
Tube ID, d = 0.370 in.Tube Length, L = 2 ft.
0.108Effective transfer area per tube = 0.262
Tubes/pass = 66 tubes per tube pass. lb/h per tube = 3
lb/h per tube per pass = 1.3Av. velocity, fps = 1.18
4,025Tubeside Friction Factor, f = 0.027
0.00021 adjust tube length, number of tubes per pass, number of passes, and/or shellNusselt number, Nr = 7.04 baffle spacing. Remember to reset shell diameter from tube count tables, as
11 required.
Step 1. Input flows, conditions and properties data for shellside and tubeside Step 5. Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Over all heat transfer Coefficient, Uo =
Temp. in, oFTemp. out, oF
r, lb/ft3
cp, Btu/lb·oF
k, Btu/h·ft·oF R, ft2·h·oF/Btu Step 4. Select tube arrangement
cpm/koFoF
Step 2. Input tubing OD, BWG and Equivalent Diameter, de (see table) =
Flow area per tube, at = in.2
ft2
Step 3. Estimate the number of Check: % difference, Ucalc. vs Uassum. =
Tubeside Reynolds No., NRe =Step 6. Check tubeside velocity and DP, shellside DP. If too high or too low,
DP per pass, psi =
Inside Film Coefficient, hi =
Shell and Tube Heat Exchanger Design Spreadsheet-
MAS Date/Time: 6-May-23 13:00 BWG/Tube Wall Thicknesses8 0.1659 0.148 0.017
10 0.134 0.01410 11 0.120 0.0149.7 12 0.109 0.011
Then the required transfer A = 63 13 0.095 0.014Number of tubes required = 239 14 0.083 0.012
Reset tubes/pass (Step 3), then no. of passes = 2 15 0.072 0.011Total tube count = 132 16 0.065 0.007
5.802 psi Actual effective transfer area, A = 35 MTD Correction Factors
#DIV/0!Tube Pitch 0.65 in.
and estimate shell diameter Pattern Tri. 0.000Shell ID from Tube Count Tables 8 in.
Select Baffle Spacing 5 in. #DIV/0!Number of Baffles = 4 3.80
0.064 ( 1 - S ) / ( 1 - RS ) = #DIV/0!7.5 in.
171,820 #DIV/0!56,431
Shellside Friction Factor = 0.00153 #DIV/0!0.357 psi 139.7 #DIV/0!1799.7
0.0%10.5
adjust tube length, number of tubes per pass, number of passes, and/or shell baffle spacing. Remember to reset shell diameter from tube count tables, as required.
Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Ustart = Btu/h·ft2·oF
Over all heat transfer Coefficient, Uo = Btu/h·ft2·oF
ft2
Tubeside DP (incl. returns) =ft2
R = ( T1 - T2 ) / ( t2 - t1 ) = Select tube arrangement
S = ( t2 - t1 ) / ( T1 - t1 ) =
( R2 + 1 ) ½ =
Flow Area across Bundle, as = ft2
Equivalent Diameter, de (see table) =Mass Velocity, Gs = lb/h·ft2 2 - S ( R + 1 - ( R2 + 1 ) ½ ) =
Shellside Reynolds No., NRe =2 - S ( R + 1 + ( R2 + 1 ) ½ ) =
Shellside DP =Outside Transfer Factor, jh = FT =
Outside Film Coefficient, ho =Calculated Uo =
Check: % difference, Ucalc. vs Uassum. =Uclean =
Check tubeside velocity and DP, shellside DP. If too high or too low,
Shell and Tube Heat Exchanger Design SpreadsheetProject: Evaporator Project No.: -Item No.: - Service: Water cooler By: MAS
Tube Side ShellR-22 Fluid Name Water168.5 Flow (M), lb/h 11,014.1
5 865 82 Reset tubes/pass (Step 3), then no. of passes =
Av. Density 0.8053 62.42Av. Viscosity 0.011 m, cP 1.903
Av. Heat Capacity 0.163 1.003Heat Exchanged 48,000 Q, Btu/h 44,188
Av. Thermal Conductivity 0.0049 0.3351Fouling Resistance 0.0040 0.004
Prandtl No. 0.87 13.78 and estimate shell diameterCorrected MTD 79.0Corrected MTD 79.0
Tube OD 0.5000 in. length (can be trial and error). BWG 16
Tube ID, d = 0.370 in.Tube Length, L = 2 ft.
0.108Effective transfer area per tube = 0.262
Tubes/pass = 66 tubes per tube pass. lb/h per tube = 3
lb/h per tube per pass = 1.3Av. velocity, fps = 1.18
4,025Tubeside Friction Factor, f = 0.027
0.00021 adjust tube length, number of tubes per pass, number of passes, and/or shellNusselt number, Nr = 7.04 baffle spacing. Remember to reset shell diameter from tube count tables, as
11 required.
Step 1. Input flows, conditions and properties data for shellside and tubeside Step 5. Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Over all heat transfer Coefficient, Uo =
Temp. in, oFTemp. out, oF
r, lb/ft3
cp, Btu/lb·oF
k, Btu/h·ft·oF R, ft2·h·oF/Btu Step 4. Select tube arrangement
cpm/koFoF
Step 2. Input tubing OD, BWG and Equivalent Diameter, de (see table) =
Flow area per tube, at = in.2
ft2
Step 3. Estimate the number of Check: % difference, Ucalc. vs Uassum. =
Tubeside Reynolds No., NRe =Step 6. Check tubeside velocity and DP, shellside DP. If too high or too low,
DP per pass, psi =
Inside Film Coefficient, hi =
Shell and Tube Heat Exchanger Design Spreadsheet-
MAS Date/Time: 6-May-23 13:00 BWG/Tube Wall Thicknesses8 0.1659 0.148 0.017
10 0.134 0.01410 11 0.120 0.0149.7 12 0.109 0.011
Then the required transfer A = 63 13 0.095 0.014Number of tubes required = 239 14 0.083 0.012
Reset tubes/pass (Step 3), then no. of passes = 2 15 0.072 0.011Total tube count = 132 16 0.065 0.007
5.802 psi Actual effective transfer area, A = 35 MTD Correction Factors
#DIV/0!Tube Pitch 0.65 in.
and estimate shell diameter Pattern Tri. 0.000Shell ID from Tube Count Tables 8 in.
Select Baffle Spacing 5 in. #DIV/0!Number of Baffles = 4 3.80
0.064 ( 1 - S ) / ( 1 - RS ) = #DIV/0!7.5 in.
171,820 #DIV/0!56,431
Shellside Friction Factor = 0.00153 #DIV/0!0.357 psi 139.7 #DIV/0!1799.7
0.0%10.5
adjust tube length, number of tubes per pass, number of passes, and/or shell baffle spacing. Remember to reset shell diameter from tube count tables, as required.
Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Ustart = Btu/h·ft2·oF
Over all heat transfer Coefficient, Uo = Btu/h·ft2·oF
ft2
Tubeside DP (incl. returns) =ft2
R = ( T1 - T2 ) / ( t2 - t1 ) = Select tube arrangement
S = ( t2 - t1 ) / ( T1 - t1 ) =
( R2 + 1 ) ½ =
Flow Area across Bundle, as = ft2
Equivalent Diameter, de (see table) =Mass Velocity, Gs = lb/h·ft2 2 - S ( R + 1 - ( R2 + 1 ) ½ ) =
Shellside Reynolds No., NRe =2 - S ( R + 1 + ( R2 + 1 ) ½ ) =
Shellside DP =Outside Transfer Factor, jh = FT =
Outside Film Coefficient, ho =Calculated Uo =
Check: % difference, Ucalc. vs Uassum. =Uclean =
Check tubeside velocity and DP, shellside DP. If too high or too low,
Shell and Tube Heat Exchanger Design SpreadsheetProject: Evaporator Project No.: -Item No.: - Service: Water cooler By: MAS
Tube Side ShellR-22 Fluid Name Water168.5 Flow (M), lb/h 11,014.1
5 865 82 Reset tubes/pass (Step 3), then no. of passes =
Av. Density 0.8053 62.42Av. Viscosity 0.011 m, cP 1.903
Av. Heat Capacity 0.163 1.003Heat Exchanged 48,000 Q, Btu/h 44,188
Av. Thermal Conductivity 0.0049 0.3351Fouling Resistance 0.0040 0.004
Prandtl No. 0.87 13.78 and estimate shell diameterCorrected MTD 79.0Corrected MTD 79.0
Tube OD 0.5000 in. length (can be trial and error). BWG 16
Tube ID, d = 0.370 in.Tube Length, L = 2 ft.
0.108Effective transfer area per tube = 0.262
Tubes/pass = 66 tubes per tube pass. lb/h per tube = 3
lb/h per tube per pass = 1.3Av. velocity, fps = 1.18
4,025Tubeside Friction Factor, f = 0.027
0.00021 adjust tube length, number of tubes per pass, number of passes, and/or shellNusselt number, Nr = 7.04 baffle spacing. Remember to reset shell diameter from tube count tables, as
11 required.
Step 1. Input flows, conditions and properties data for shellside and tubeside Step 5. Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Over all heat transfer Coefficient, Uo =
Temp. in, oFTemp. out, oF
r, lb/ft3
cp, Btu/lb·oF
k, Btu/h·ft·oF R, ft2·h·oF/Btu Step 4. Select tube arrangement
cpm/koFoF
Step 2. Input tubing OD, BWG and Equivalent Diameter, de (see table) =
Flow area per tube, at = in.2
ft2
Step 3. Estimate the number of Check: % difference, Ucalc. vs Uassum. =
Tubeside Reynolds No., NRe =Step 6. Check tubeside velocity and DP, shellside DP. If too high or too low,
DP per pass, psi =
Inside Film Coefficient, hi =
Shell and Tube Heat Exchanger Design Spreadsheet-
MAS Date/Time: 6-May-23 13:00 BWG/Tube Wall Thicknesses8 0.1659 0.148 0.017
10 0.134 0.01410 11 0.120 0.0149.7 12 0.109 0.011
Then the required transfer A = 63 13 0.095 0.014Number of tubes required = 239 14 0.083 0.012
Reset tubes/pass (Step 3), then no. of passes = 2 15 0.072 0.011Total tube count = 132 16 0.065 0.007
5.802 psi Actual effective transfer area, A = 35 MTD Correction Factors
#DIV/0!Tube Pitch 0.65 in.
and estimate shell diameter Pattern Tri. 0.000Shell ID from Tube Count Tables 8 in.
Select Baffle Spacing 5 in. #DIV/0!Number of Baffles = 4 3.80
0.064 ( 1 - S ) / ( 1 - RS ) = #DIV/0!7.5 in.
171,820 #DIV/0!56,431
Shellside Friction Factor = 0.00153 #DIV/0!0.357 psi 139.7 #DIV/0!1799.7
0.0%10.5
adjust tube length, number of tubes per pass, number of passes, and/or shell baffle spacing. Remember to reset shell diameter from tube count tables, as required.
Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Ustart = Btu/h·ft2·oF
Over all heat transfer Coefficient, Uo = Btu/h·ft2·oF
ft2
Tubeside DP (incl. returns) =ft2
R = ( T1 - T2 ) / ( t2 - t1 ) = Select tube arrangement
S = ( t2 - t1 ) / ( T1 - t1 ) =
( R2 + 1 ) ½ =
Flow Area across Bundle, as = ft2
Equivalent Diameter, de (see table) =Mass Velocity, Gs = lb/h·ft2 2 - S ( R + 1 - ( R2 + 1 ) ½ ) =
Shellside Reynolds No., NRe =2 - S ( R + 1 + ( R2 + 1 ) ½ ) =
Shellside DP =Outside Transfer Factor, jh = FT =
Outside Film Coefficient, ho =Calculated Uo =
Check: % difference, Ucalc. vs Uassum. =Uclean =
Check tubeside velocity and DP, shellside DP. If too high or too low,
Shell and Tube Heat Exchanger Design SpreadsheetProject: Evaporator Project No.: -Item No.: - Service: Water cooler By: MAS
Tube Side ShellR-22 Fluid Name Water168.5 Flow (M), lb/h 11,014.1
5 865 82 Reset tubes/pass (Step 3), then no. of passes =
Av. Density 0.8053 62.42Av. Viscosity 0.011 m, cP 1.903
Av. Heat Capacity 0.163 1.003Heat Exchanged 48,000 Q, Btu/h 44,188
Av. Thermal Conductivity 0.0049 0.3351Fouling Resistance 0.0040 0.004
Prandtl No. 0.87 13.78 and estimate shell diameterCorrected MTD 79.0Corrected MTD 79.0
Tube OD 0.5000 in. length (can be trial and error). BWG 16
Tube ID, d = 0.370 in.Tube Length, L = 2 ft.
0.108Effective transfer area per tube = 0.262
Tubes/pass = 66 tubes per tube pass. lb/h per tube = 3
lb/h per tube per pass = 1.3Av. velocity, fps = 1.18
4,025Tubeside Friction Factor, f = 0.027
0.00021 adjust tube length, number of tubes per pass, number of passes, and/or shellNusselt number, Nr = 7.04 baffle spacing. Remember to reset shell diameter from tube count tables, as
11 required.
Step 1. Input flows, conditions and properties data for shellside and tubeside Step 5. Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Over all heat transfer Coefficient, Uo =
Temp. in, oFTemp. out, oF
r, lb/ft3
cp, Btu/lb·oF
k, Btu/h·ft·oF R, ft2·h·oF/Btu Step 4. Select tube arrangement
cpm/koFoF
Step 2. Input tubing OD, BWG and Equivalent Diameter, de (see table) =
Flow area per tube, at = in.2
ft2
Step 3. Estimate the number of Check: % difference, Ucalc. vs Uassum. =
Tubeside Reynolds No., NRe =Step 6. Check tubeside velocity and DP, shellside DP. If too high or too low,
DP per pass, psi =
Inside Film Coefficient, hi =
Shell and Tube Heat Exchanger Design Spreadsheet-
MAS Date/Time: 6-May-23 13:00 BWG/Tube Wall Thicknesses8 0.1659 0.148 0.017
10 0.134 0.01410 11 0.120 0.0149.7 12 0.109 0.011
Then the required transfer A = 63 13 0.095 0.014Number of tubes required = 239 14 0.083 0.012
Reset tubes/pass (Step 3), then no. of passes = 2 15 0.072 0.011Total tube count = 132 16 0.065 0.007
5.802 psi Actual effective transfer area, A = 35 MTD Correction Factors
#DIV/0!Tube Pitch 0.65 in.
and estimate shell diameter Pattern Tri. 0.000Shell ID from Tube Count Tables 8 in.
Select Baffle Spacing 5 in. #DIV/0!Number of Baffles = 4 3.80
0.064 ( 1 - S ) / ( 1 - RS ) = #DIV/0!7.5 in.
171,820 #DIV/0!56,431
Shellside Friction Factor = 0.00153 #DIV/0!0.357 psi 139.7 #DIV/0!1799.7
0.0%10.5
adjust tube length, number of tubes per pass, number of passes, and/or shell baffle spacing. Remember to reset shell diameter from tube count tables, as required.
Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Ustart = Btu/h·ft2·oF
Over all heat transfer Coefficient, Uo = Btu/h·ft2·oF
ft2
Tubeside DP (incl. returns) =ft2
R = ( T1 - T2 ) / ( t2 - t1 ) = Select tube arrangement
S = ( t2 - t1 ) / ( T1 - t1 ) =
( R2 + 1 ) ½ =
Flow Area across Bundle, as = ft2
Equivalent Diameter, de (see table) =Mass Velocity, Gs = lb/h·ft2 2 - S ( R + 1 - ( R2 + 1 ) ½ ) =
Shellside Reynolds No., NRe =2 - S ( R + 1 + ( R2 + 1 ) ½ ) =
Shellside DP =Outside Transfer Factor, jh = FT =
Outside Film Coefficient, ho =Calculated Uo =
Check: % difference, Ucalc. vs Uassum. =Uclean =
Check tubeside velocity and DP, shellside DP. If too high or too low,
Shell and Tube Heat Exchanger Design SpreadsheetProject: Evaporator Project No.: -Item No.: - Service: Water cooler By: MAS
Tube Side ShellR-22 Fluid Name Water168.5 Flow (M), lb/h 11,014.1
5 865 82 Reset tubes/pass (Step 3), then no. of passes =
Av. Density 0.8053 62.42Av. Viscosity 0.011 m, cP 1.903
Av. Heat Capacity 0.163 1.003Heat Exchanged 48,000 Q, Btu/h 44,188
Av. Thermal Conductivity 0.0049 0.3351Fouling Resistance 0.0040 0.004
Prandtl No. 0.87 13.78 and estimate shell diameterCorrected MTD 79.0Corrected MTD 79.0
Tube OD 0.5000 in. length (can be trial and error). BWG 16
Tube ID, d = 0.370 in.Tube Length, L = 2 ft.
0.108Effective transfer area per tube = 0.262
Tubes/pass = 66 tubes per tube pass. lb/h per tube = 3
lb/h per tube per pass = 1.3Av. velocity, fps = 1.18
4,025Tubeside Friction Factor, f = 0.027
0.00021 adjust tube length, number of tubes per pass, number of passes, and/or shellNusselt number, Nr = 7.04 baffle spacing. Remember to reset shell diameter from tube count tables, as
11 required.
Step 1. Input flows, conditions and properties data for shellside and tubeside Step 5. Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Over all heat transfer Coefficient, Uo =
Temp. in, oFTemp. out, oF
r, lb/ft3
cp, Btu/lb·oF
k, Btu/h·ft·oF R, ft2·h·oF/Btu Step 4. Select tube arrangement
cpm/koFoF
Step 2. Input tubing OD, BWG and Equivalent Diameter, de (see table) =
Flow area per tube, at = in.2
ft2
Step 3. Estimate the number of Check: % difference, Ucalc. vs Uassum. =
Tubeside Reynolds No., NRe =Step 6. Check tubeside velocity and DP, shellside DP. If too high or too low,
DP per pass, psi =
Inside Film Coefficient, hi =
Shell and Tube Heat Exchanger Design Spreadsheet-
MAS Date/Time: 6-May-23 13:00 BWG/Tube Wall Thicknesses8 0.1659 0.148 0.017
10 0.134 0.01410 11 0.120 0.0149.7 12 0.109 0.011
Then the required transfer A = 63 13 0.095 0.014Number of tubes required = 239 14 0.083 0.012
Reset tubes/pass (Step 3), then no. of passes = 2 15 0.072 0.011Total tube count = 132 16 0.065 0.007
5.802 psi Actual effective transfer area, A = 35 MTD Correction Factors
#DIV/0!Tube Pitch 0.65 in.
and estimate shell diameter Pattern Tri. 0.000Shell ID from Tube Count Tables 8 in.
Select Baffle Spacing 5 in. #DIV/0!Number of Baffles = 4 3.80
0.064 ( 1 - S ) / ( 1 - RS ) = #DIV/0!7.5 in.
171,820 #DIV/0!56,431
Shellside Friction Factor = 0.00153 #DIV/0!0.357 psi 139.7 #DIV/0!1799.7
0.0%10.5
adjust tube length, number of tubes per pass, number of passes, and/or shell baffle spacing. Remember to reset shell diameter from tube count tables, as required.
Start configuring the exchanger. Begin with the total calculated transfer coefficient to this point:
Ustart = Btu/h·ft2·oF
Over all heat transfer Coefficient, Uo = Btu/h·ft2·oF
ft2
Tubeside DP (incl. returns) =ft2
R = ( T1 - T2 ) / ( t2 - t1 ) = Select tube arrangement
S = ( t2 - t1 ) / ( T1 - t1 ) =
( R2 + 1 ) ½ =
Flow Area across Bundle, as = ft2
Equivalent Diameter, de (see table) =Mass Velocity, Gs = lb/h·ft2 2 - S ( R + 1 - ( R2 + 1 ) ½ ) =
Shellside Reynolds No., NRe =2 - S ( R + 1 + ( R2 + 1 ) ½ ) =
Shellside DP =Outside Transfer Factor, jh = FT =
Outside Film Coefficient, ho =Calculated Uo =
Check: % difference, Ucalc. vs Uassum. =Uclean =
Check tubeside velocity and DP, shellside DP. If too high or too low,