Calculation Report
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Dario110C EXCHANGER
ALTERATION - CALCULATION REPORT
PROJECTO N.: DEPARTMENT: DOC NUMBER: DATE: 30-7-2019
19B-1191R Engineering 1191R-MC-001
REV.: A
ALTERATION CALCULATION REPORT
Doc. No. 1191R-MC-001
Rev.
DATE DESCRIPTION ISSUED FOR REVISADO POR APROBADO POR
No.
A 30/JUL/2019 FOR APPROVAL DXV JM DXV
Table of Contents
Cover Sheet ................................................................................................................................................ 3
Title Page................................................................................................................................................... 4
Warnings and Errors : ......................................................................................................................... 6
Input Echo : .............................................................................................................................................. 7
XY Coordinate Calculations : ....................................................................................................... 23
Flg Calc [Int P] : FRONT COVER................................................................................................. 24
Flg Calc [Int P] : Ring FLG Fro .............................................................................................. 29
Flg Calc [Int P] : RingFLGBACK................................................................................................. 36
Flg Calc [Int P] : Back Cover ................................................................................................... 43
Internal Pressure Calculations : .............................................................................................. 48
External Pressure Calculations : .............................................................................................. 56
Element and Detail Weights : ....................................................................................................... 59
Nozzle Flange MAWP : .......................................................................................................................... 63
Wind Load Calculation : ................................................................................................................... 64
Earthquake Load Calculation : ..................................................................................................... 68
Center of Gravity Calculation :................................................................................................. 69
Horizontal Vessel Analysis (Ope.) : ....................................................................................... 70
Horizontal Vessel Analysis (Test) : ....................................................................................... 86
Nozzle Calcs. : D............................................................................................................................... 102
Nozzle Calcs. : CO-1 ........................................................................................................................ 107
Nozzle Calcs. : P7 ............................................................................................................................ 116
Nozzle Calcs. : P8 ............................................................................................................................ 121
Nozzle Calcs. : SO-1 ........................................................................................................................ 126
Nozzle Calcs. : SI-1 ........................................................................................................................ 135
Nozzle Calcs. : SI-2 ........................................................................................................................ 144
Nozzle Calcs. : P1 ............................................................................................................................ 153
Nozzle Calcs. : P2 ............................................................................................................................ 158
Nozzle Calcs. : P3 ............................................................................................................................ 163
Nozzle Calcs. : P4 ............................................................................................................................ 168
Nozzle Calcs. : P5 ............................................................................................................................ 173
Nozzle Calcs. : P6 ............................................................................................................................ 178
Nozzle Calcs. : V............................................................................................................................... 183
Nozzle Calcs. : CI-1 ........................................................................................................................ 188
Nozzle Calcs. : P9 ............................................................................................................................ 197
Nozzle Calcs. : P10 .......................................................................................................................... 202
Nozzle Schedule :............................................................................................................................... 207
Nozzle Summary : ................................................................................................................................. 211
Tubesheet,............................................................................................................................................... 213
MDMT Summary : ..................................................................................................................................... 222
Vessel Design Summary : ................................................................................................................. 225
Cover Page 3
B-19-1191R
Client Name : NUTRIEN
DESIGN CALCULATION
In Accordance with ASME Section VIII Division 1
ASME Code Version : 2015
Analysis Performed by : SPLM Licensed User
Job File : C:\USERS\DARíOXAVIER\BOX SYNC\PROYECTOS IDV\PROY
Date of Analysis : Jul 31,2019 9:18am
PV Elite 2016, January 2016
Title Page 4
110 C- ALTERATION CODE CALC CALCULATION
PROJECT NUMBER: B-19-1191R
OWNER: NUTRIEN
DESING BY: DARÍO XAVIER VALLEJO
DATE:30-7-2019
Title Page 5
B-19-1191R 6
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FileName : HEAT EXCHANGER
Warnings and Errors : Step: 0 9:18am Jul 31,2019
Class From To : Basic Element Checks.
==========================================================================
Note 20 40 There is a high jump in the Joint Eff.
Note 60 80 There is a high jump in the Joint Eff.
Class From To: Check of Additional Element Data
==========================================================================
There were no geometry errors or warnings.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 7
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Input Echo : Step: 1 9:18am Jul 31,2019
PV Elite Vessel Analysis Program: Input Data
B-19-1191R
Exchanger Design Pressures and Temperatures
Shell Side Design Pressure 75.000 psig
Channel Side Design Pressure 80.000 psig
Shell Side Design Temperature 150 F
Channel Side Design Temperature 150 F
Type of Hydrotest User Entered Pressure
Hydrotest Position Horizontal
Projection of Nozzle from Vessel Top 0.0000 in
Projection of Nozzle from Vessel Bottom 0.0000 in
Type of Construction Welded
Special Service None
Degree of Radiography None
Use Higher Longitudinal Stresses (Flag) Y
Select t for Internal Pressure (Flag) N
Select t for External Pressure (Flag) N
Select t for Axial Stress (Flag) N
Select Location for Stiff. Rings (Flag) N
Consider Vortex Shedding N
Perform a Corroded Hydrotest N
Is this a Heat Exchanger Yes
User Defined Hydro. Press. (Used if > 0) 0.0000 psig
User defined MAWP 0.0000 psig
User defined MAPnc 0.0000 psig
Load Case 1 NP+EW+WI+FW+BW
Load Case 2 NP+EW+EE+FS+BS
B-19-1191R 8
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Load Case 3 NP+OW+WI+FW+BW
Load Case 4 NP+OW+EQ+FS+BS
Load Case 5 NP+HW+HI
Load Case 6 NP+HW+HE
Load Case 7 IP+OW+WI+FW+BW
Load Case 8 IP+OW+EQ+FS+BS
Load Case 9 EP+OW+WI+FW+BW
Load Case 10 EP+OW+EQ+FS+BS
Load Case 11 HP+HW+HI
Load Case 12 HP+HW+HE
Load Case 13 IP+WE+EW
Load Case 14 IP+WF+CW
Load Case 15 IP+VO+OW
Load Case 16 IP+VE+EW
Load Case 17 NP+VO+OW
Load Case 18 FS+BS+IP+OW
Load Case 19 FS+BS+EP+OW
Wind Design Code ASCE-7 93
Basic Wind Speed [V] 70.000 mile/hr
Surface Roughness Category C: Open Terrain
Importance Factor 1.0
Type of Surface Moderately Smooth
Base Elevation 0.0000 in
Percent Wind for Hydrotest 33.0
Using User defined Wind Press. Vs Elev. N
Damping Factor (Beta) for Wind (Ope) 0.0100
Damping Factor (Beta) for Wind (Empty) 0.0000
Damping Factor (Beta) for Wind (Filled) 0.0000
Seismic Design Code UBC 94
UBC Seismic Zone (1=1,2=2a,3=2b,4=3,5=4) 0.000
UBC Importance Factor 1.000
B-19-1191R 9
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UBC Soil Type S1
UBC Horizontal Force Factor 3.000
UBC Percent Seismic for Hydrotest 0.000
Design Nozzle for Des. Press. + St. Head Y
Consider MAP New and Cold in Noz. Design N
Consider External Loads for Nozzle Des. Y
Use ASME VIII-1 Appendix 1-9 N
Material Database Year 1943 to 1974
Configuration Directives:
Do not use Nozzle MDMT Interpretation VIII-1 01-37 No
Use Table G instead of exact equation for "A" Yes
Shell Head Joints are Tapered Yes
Compute "K" in corroded condition Yes
Use Code Case 2286 No
Use the MAWP to compute the MDMT Yes
Using Metric Material Databases, ASME II D No
Complete Listing of Vessel Elements and Details:
Element From Node 10
Element To Node 20
Element Type Flange
Description Cover Front
Distance "FROM" to "TO" 2.0625 in
Flange Inside Diameter 49.250 in
Element Thickness 2.0625 in
Internal Corrosion Allowance 0.0000 in
Nominal Thickness 0.0000 in
External Corrosion Allowance 0.0000 in
B-19-1191R 10
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Design Internal Pressure 80.000 psig
Design Temperature Internal Pressure 150 F
Design External Pressure 0.0000 psig
Design Temperature External Pressure 200 F
Effective Diameter Multiplier 1.2
Material Name SA-182 F304
Allowable Stress, Ambient 17500. psi
Allowable Stress, Operating 16675. psi
Allowable Stress, Hydrotest 22750. psi
Material Density 0.2900 lbm/in^3
P Number Thickness 0.0000 in
Yield Stress, Operating 26700. psi
External Pressure Chart Name HA-1
UNS Number S30400
Class / Thickness / Grade ::<=5
Product Form Forgings
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 lbf
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
--------------------------------------------------------------------
Element From Node 20
Element To Node 30
Element Type Flange
Description
Distance "FROM" to "TO" 3.5000 in
Flange Inside Diameter 44.125 in
Element Thickness 3.5000 in
Internal Corrosion Allowance 0.0000 in
Nominal Thickness 0.0000 in
External Corrosion Allowance 0.0000 in
B-19-1191R 11
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Design Internal Pressure 80.000 psig
Design Temperature Internal Pressure 150 F
Design External Pressure 0.0000 psig
Design Temperature External Pressure 200 F
Effective Diameter Multiplier 1.2
Material Name SA-182 F304
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 lbf
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
--------------------------------------------------------------------
Element From Node 30
Element To Node 40
Element Type Cylinder
Description
Distance "FROM" to "TO" 32.688 in
Inside Diameter 43.000 in
Element Thickness 0.5000 in
Internal Corrosion Allowance 0.0000 in
Nominal Thickness 0.5000 in
External Corrosion Allowance 0.0000 in
Design Internal Pressure 80.000 psig
Design Temperature Internal Pressure 150 F
Design External Pressure 0.0000 psig
Design Temperature External Pressure 200 F
Effective Diameter Multiplier 1.2
Material Name SA-240 304L
Allowable Stress, Ambient 15600. psi
Allowable Stress, Operating 15600. psi
Allowable Stress, Hydrotest 20280. psi
Material Density 0.2900 lbm/in^3
B-19-1191R 12
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FileName : HEAT EXCHANGER
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P Number Thickness 0.0000 in
Yield Stress, Operating 22700. psi
External Pressure Chart Name HA-3
UNS Number S30403
Product Form Plate
Efficiency, Longitudinal Seam 0.7
Efficiency, Circumferential Seam 0.7
Element From Node 30
Detail Type Nozzle
Detail ID D
Dist. from "FROM" Node / Offset dist 13.812 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 270.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-312 TP304
Element From Node 30
Detail Type Nozzle
Detail ID CO-1
Dist. from "FROM" Node / Offset dist 13.812 in
Nozzle Diameter 12.0 in.
Nozzle Schedule 40S
Nozzle Class 150
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 122.28 lbf
Grade of Attached Flange GR 2.3
Nozzle Matl SA-312 TP304L
B-19-1191R 13
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Element From Node 30
Detail Type Nozzle
Detail ID P7
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
Element From Node 30
Detail Type Nozzle
Detail ID P8
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 270.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
--------------------------------------------------------------------
Element From Node 40
Element To Node 60
Element Type Cylinder
Description
B-19-1191R 14
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FileName : HEAT EXCHANGER
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Distance "FROM" to "TO" 231.50 in
Inside Diameter 43.000 in
Element Thickness 0.5000 in
Internal Corrosion Allowance 0.0000 in
Nominal Thickness 0.5000 in
External Corrosion Allowance 0.0000 in
Design Internal Pressure 75.000 psig
Design Temperature Internal Pressure 150 F
Design External Pressure 0.0000 psig
Design Temperature External Pressure 200 F
Effective Diameter Multiplier 1.2
Material Name SA-240 304L
Efficiency, Longitudinal Seam 0.7
Efficiency, Circumferential Seam 0.7
Element From Node 40
Detail Type Saddle
Detail ID Lft Sdl
Dist. from "FROM" Node / Offset dist 21.000 in
Width of Saddle 8.0000 in
Height of Saddle at Bottom 28.750 in
Saddle Contact Angle 121.0
Height of Composite Ring Stiffener 0.0000 in
Width of Wear Plate 10.000 in
Thickness of Wear Plate 0.5000 in
Contact Angle, Wear Plate (degrees) 128.0
Element From Node 40
Detail Type Saddle
Detail ID New Sdl
Dist. from "FROM" Node / Offset dist 210.50 in
Width of Saddle 8.0000 in
Height of Saddle at Bottom 28.750 in
B-19-1191R 15
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FileName : HEAT EXCHANGER
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Saddle Contact Angle 121.0
Height of Composite Ring Stiffener 0.0000 in
Width of Wear Plate 10.000 in
Thickness of Wear Plate 0.5000 in
Contact Angle, Wear Plate (degrees) 128.0
Element From Node 40
Detail Type Nozzle
Detail ID SO-1
Dist. from "FROM" Node / Offset dist 115.75 in
Nozzle Diameter 18.0 in.
Nozzle Schedule 40S
Nozzle Class 150
Layout Angle 270.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 216.39 lbf
Grade of Attached Flange GR 2.1
Nozzle Matl SA-312 TP304
Element From Node 40
Detail Type Nozzle
Detail ID SI-1
Dist. from "FROM" Node / Offset dist 10.250 in
Nozzle Diameter 18.0 in.
Nozzle Schedule 40S
Nozzle Class 150
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 216.39 lbf
Grade of Attached Flange GR 2.1
Nozzle Matl SA-312 TP304
Element From Node 40
B-19-1191R 16
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FileName : HEAT EXCHANGER
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Detail Type Nozzle
Detail ID SI-2
Dist. from "FROM" Node / Offset dist 221.25 in
Nozzle Diameter 18.0 in.
Nozzle Schedule 40S
Nozzle Class 150
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 216.39 lbf
Grade of Attached Flange GR 2.1
Nozzle Matl SA-312 TP304
Element From Node 40
Detail Type Nozzle
Detail ID P1
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
Element From Node 40
Detail Type Nozzle
Detail ID P2
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 270.0
B-19-1191R 17
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FileName : HEAT EXCHANGER
Input Echo : Step: 1 9:18am Jul 31,2019
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
Element From Node 40
Detail Type Nozzle
Detail ID P3
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 270.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
Element From Node 40
Detail Type Nozzle
Detail ID P4
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
Element From Node 40
Detail Type Nozzle
B-19-1191R 18
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FileName : HEAT EXCHANGER
Input Echo : Step: 1 9:18am Jul 31,2019
Detail ID P5
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
Element From Node 40
Detail Type Nozzle
Detail ID P6
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 270.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
--------------------------------------------------------------------
Element From Node 60
Element To Node 70
Element Type Cylinder
Description
Distance "FROM" to "TO" 30.312 in
Inside Diameter 43.000 in
Element Thickness 0.5000 in
B-19-1191R 19
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Input Echo : Step: 1 9:18am Jul 31,2019
Internal Corrosion Allowance 0.0000 in
Nominal Thickness 0.5000 in
External Corrosion Allowance 0.0000 in
Design Internal Pressure 80.000 psig
Design Temperature Internal Pressure 150 F
Design External Pressure 0.0000 psig
Design Temperature External Pressure 200 F
Effective Diameter Multiplier 1.2
Material Name SA-240 304L
Efficiency, Longitudinal Seam 0.7
Efficiency, Circumferential Seam 0.7
Element From Node 60
Detail Type Nozzle
Detail ID V
Dist. from "FROM" Node / Offset dist 16.500 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
Element From Node 60
Detail Type Nozzle
Detail ID CI-1
Dist. from "FROM" Node / Offset dist 16.500 in
Nozzle Diameter 12.0 in.
Nozzle Schedule 40S
Nozzle Class 150
Layout Angle 270.0
B-19-1191R 20
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FileName : HEAT EXCHANGER
Input Echo : Step: 1 9:18am Jul 31,2019
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 122.28 lbf
Grade of Attached Flange None
Nozzle Matl SA-312 TP304L
Element From Node 60
Detail Type Nozzle
Detail ID P9
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 270.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
Element From Node 60
Detail Type Nozzle
Detail ID P10
Dist. from "FROM" Node / Offset dist 3.0000 in
Nozzle Diameter 1.75 in.
Nozzle Schedule None
Nozzle Class None
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.6696 lbf
Grade of Attached Flange None
Nozzle Matl SA-182 F304L
--------------------------------------------------------------------
B-19-1191R 21
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FileName : HEAT EXCHANGER
Input Echo : Step: 1 9:18am Jul 31,2019
Element From Node 70
Element To Node 80
Element Type Flange
Description
Distance "FROM" to "TO" 3.5000 in
Flange Inside Diameter 43.000 in
Element Thickness 3.5000 in
Internal Corrosion Allowance 0.0000 in
Nominal Thickness 0.5000 in
External Corrosion Allowance 0.0000 in
Design Internal Pressure 80.000 psig
Design Temperature Internal Pressure 150 F
Design External Pressure 0.0000 psig
Design Temperature External Pressure 200 F
Effective Diameter Multiplier 1.2
Material Name SA-182 F304
Allowable Stress, Ambient 17500. psi
Allowable Stress, Operating 16675. psi
Allowable Stress, Hydrotest 22750. psi
Material Density 0.2900 lbm/in^3
P Number Thickness 0.0000 in
Yield Stress, Operating 26700. psi
External Pressure Chart Name HA-1
UNS Number S30400
Class / Thickness / Grade ::<=5
Product Form Forgings
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 lbf
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
--------------------------------------------------------------------
B-19-1191R 22
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FileName : HEAT EXCHANGER
Input Echo : Step: 1 9:18am Jul 31,2019
Element From Node 80
Element To Node 90
Element Type Flange
Description
Distance "FROM" to "TO" 2.0625 in
Flange Inside Diameter 49.250 in
Element Thickness 2.0625 in
Internal Corrosion Allowance 0.0000 in
Nominal Thickness 0.5000 in
External Corrosion Allowance 0.0000 in
Design Internal Pressure 80.000 psig
Design Temperature Internal Pressure 150 F
Design External Pressure 0.0000 psig
Design Temperature External Pressure 200 F
Effective Diameter Multiplier 1.2
Material Name SA-182 F304
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 lbf
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 23
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FileName : HEAT EXCHANGER
XY Coordinate Calculations : Step: 2 9:18am Jul 31,2019
XY Coordinate Calculations
| | | | | |
From| To | X (Horiz.)| Y (Vert.) |DX (Horiz.)| DY (Vert.) |
| | in | in | in | in |
--------------------------------------------------------------
Cover Fron| 2.06250 | ... | 2.06250 | ... |
20| 30| 2.06250 | ... | -3.50000 | ... |
30| 40| 34.7500 | ... | 32.6875 | ... |
40| 60| 266.250 | ... | 231.500 | ... |
60| 70| 298.062 | ... | 30.3125 | ... |
70| 80| 298.062 | ... | -3.50000 | ... |
80| 90| 300.125 | ... | 2.06250 | ... |
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 24
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FileName : HEAT EXCHANGER
Flg Calc [Int P] : FRONT COVER Flng: 5 9:18am Jul 31,2019
Flange Input Data Values Description: FRONT COVER :
Cover Front
Description of Flange Geometry (Type) Blind
Design Pressure P 80.00 psig
Design Temperature 150 F
Internal Corrosion Allowance ci 0.0000 in
External Corrosion Allowance ce 0.0000 in
Use Corrosion Allowance in Thickness Calcs. Yes
Flange Outside Diameter A 49.250 in
Flange Thickness t 2.0625 in
Flange Material SA-182 F304
Flange Material UNS number S30400
Flange Allowable Stress At Temperature Sfo 16675.00 psi
Flange Allowable Stress At Ambient Sfa 17500.00 psi
Bolt Material SA-193 B8
Bolt Allowable Stress At Temperature Sb 17750.00 psi
Bolt Allowable Stress At Ambient Sa 18800.00 psi
Diameter of the Load Reaction, Long Span D 0.000 in
Diameter of the Load Reaction, Short Span d 0.000 in
Perimeter along the Center of the Bolts L 148.048 in
Diameter of Bolt Circle C 47.125 in
Nominal Bolt Diameter a 1.0000 in
Type of Threads UNC Thread Series
Number of Bolts 40
Flange Face Outside Diameter Fod 45.000 in
B-19-1191R 25
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FileName : HEAT EXCHANGER
Flg Calc [Int P] : FRONT COVER Flng: 5 9:18am Jul 31,2019
Flange Face Inside Diameter Fid 42.562 in
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 45.000 in
Gasket Inside Diameter Gi 42.562 in
Gasket Factor m 3.5000
Gasket Design Seating Stress y 6500.00 psi
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 0.1250 in
ASME Code, Section VIII, Division 1, 2015
Gasket Contact Width, N = (Go - Gi) / 2 1.219 in
Basic Gasket Width, bo = N / 2 0.609 in
Effective Gasket Width, b = sqrt(bo) / 2 0.390 in
Gasket Reaction Diameter, G = Go - 2 * b 44.219 in
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]:
= 0.785 * G2 * Peq
= 0.785 * 44.21942 * 80.000
= 122858.469 lbf
Contact Load on Gasket Surfaces [Hp]:
= 2 * b * Pi * G * m * P
= 2 * 0.3903 * 3.1416 * 44.2194 * 3.5000 * 80.00
= 30364.268 lbf
Operating Bolt Load [Wm1]:
= max( H + Hp + H'p, 0 )
= max( 122858 + 30364 + 0 , 0 )
= 153222.734 lbf
B-19-1191R 26
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FileName : HEAT EXCHANGER
Flg Calc [Int P] : FRONT COVER Flng: 5 9:18am Jul 31,2019
Gasket Seating Bolt Load [Wm2]:
= y * b * Pi * G + yPart * bPart * lp
= 6500.00*0.3903*3.141*44.219+0.00*0.0000*0.00
= 352442.438 lbf
Required Bolt Area [Am]:
= Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 153223/17750 , 352442/18800
= 18.747 in^2
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]:
= 2a + 6t/(m + 0.5)
= 2 * 1.000 + 6 * 2.062/(3.50 + 0.5)
= 5.094 in
Actual Circumferential Bolt Spacing [Bs]:
= C * sin( pi / n )
= 47.125 * sin( 3.142/40 )
= 3.697 in
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]:
= max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 3.697/( 2 * 1.000 + 2.062 )), 1 )
= 1.0000
Bolting Information for UNC Thread Series (Non Mandatory):
-----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, in^2 18.747 22.040
Radial distance bet. bolts and the edge 1.062 1.062
Circumferential spacing between bolts 2.250 3.697 5.094
-----------------------------------------------------------------------------
B-19-1191R 27
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : FRONT COVER Flng: 5 9:18am Jul 31,2019
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]:
= Ab * Sa/( y * Pi * (Go + Gi) )
= 22.040 * 18800.00/(6500.00 * 3.14 * (45.000 + 42.56 ) )
= 0.232 in
Flange Design Bolt Load, Gasket Seating [W]:
= Sa * Ab
= 18800.00 * 22.0400
= 414352.03 lbf
Gasket Load for the Operating Condition [HG]:
= Wm1
= 153222.73 lbf
Moment Arm Calculations:
Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 47.1250 - 44.2194 )/2
= 1.4528 in
Tangential Flange Stress, Flat Head (UG-34), Operating [STo]:
= 1.9 * Wm1 * hG * Bsc/(t2 * G) + C * Z * Peq * G2/t2
= 1.9*153223*1.4528*1.0000/(2.06252*44.2194)+
0.30*1.0000*80.00*44.21942/2.06252
= 13280.32 psi
Tangential Flange Stress, Flat Head (UG-34), Seating [STa]:
= 1.9 * W * hG * Bsc/ (t2 * G)
= 1.9*414352*1.4528*1.000/(2.06252*44.2194)
= 6080.40 psi
Bolt Stress, Operating [BSo]:
= ( Wm1 / Ab )
= (153223/22.0400)
= 6952.03 psi
B-19-1191R 28
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : FRONT COVER Flng: 5 9:18am Jul 31,2019
Bolt Stress, Seating [BSa]:
= ( Wm2 / Ab )
= (352442/22.0400)
= 15991.04 psi
Flange Stress Analysis Results: psi
Operating | Gasket Seating |
Actual Allowed | Actual Allowed |
-----------------------------------------------------------------
Tangential Flange 13280.| 16675.| 6080.| 17500.|
Bolting 6952.| 17750.| 15991.| 18800.|
Reqd. Blind Flange Thickness at Center 1.841 in
Reqd. Blind Flange Thickness at Gasket 1.216 in
Estimated M.A.W.P. ( Operating ) 100.4 psig
Estimated Finished Weight of Flange at given Thk. 1139.4 lbm
Estimated Unfinished Weight of Forging at given Thk 1139.4 lbm
SA-182 F304, Min Metal Temp without impact per UHA-51: -320 F
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 29
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Ring FLG Fro Flng: 6 9:18am Jul 31,2019
Flange Input Data Values Description: Ring FLG Fro :
Item: Node 20 to 30
Description of Flange Geometry (Type) Integral Ring
Design Pressure P 80.00 psig
Design Temperature 150 F
Internal Corrosion Allowance ci 0.0000 in
External Corrosion Allowance ce 0.0000 in
Use Corrosion Allowance in Thickness Calcs. Yes
Attached Shell Inside Diameter B 44.1250 in
Flange Outside Diameter A 49.250 in
Flange Thickness t 3.5000 in
Flange Material SA-182 F304
Flange Material UNS number S30400
Flange Allowable Stress At Temperature Sfo 16675.00 psi
Flange Allowable Stress At Ambient Sfa 17500.00 psi
Bolt Material SA-193 B8
Bolt Allowable Stress At Temperature Sb 17750.00 psi
Bolt Allowable Stress At Ambient Sa 18800.00 psi
Length of Weld Leg at Back of Ring tw 0.5625 in
Number of Splits in Ring Flange n 0
Diameter of Bolt Circle C 47.125 in
Nominal Bolt Diameter a 1.0000 in
Type of Threads UNC Thread Series
Number of Bolts 40
Flange Face Outside Diameter Fod 45.000 in
B-19-1191R 30
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Ring FLG Fro Flng: 6 9:18am Jul 31,2019
Flange Face Inside Diameter Fid 44.125 in
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 45.000 in
Gasket Inside Diameter Gi 44.125 in
Gasket Factor m 3.5000
Gasket Design Seating Stress y 6500.00 psi
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 0.1250 in
ASME Code, Section VIII, Division 1, 2015
Corroded Flange ID, Bcor = B+2*Fcor 44.125 in
Corroded Large Hub, g1Cor = g1-ci 0.000 in
Corroded Small Hub, g0Cor = go-ci 0.000 in
Code R Dimension, R = (C-B)/2 - g1 1.500 in
Gasket Contact Width, N = (Go - Gi) / 2 0.438 in
Basic Gasket Width, bo = N / 2 0.219 in
Effective Gasket Width, b = bo 0.219 in
Gasket Reaction Diameter, G = (Go + Gi) / 2 44.562 in
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]:
= 0.785 * G2 * Peq
= 0.785 * 44.56252 * 80.000
= 124772.531 lbf
Contact Load on Gasket Surfaces [Hp]:
= 2 * b * Pi * G * m * P
= 2 * 0.2188 * 3.1416 * 44.5625 * 3.5000 * 80.00
= 17149.660 lbf
B-19-1191R 31
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Ring FLG Fro Flng: 6 9:18am Jul 31,2019
Hydrostatic End Load at Flange ID [Hd]:
= Pi * Bcor2 * P / 4
= 3.1416 * 44.12502 *80.0000/4
= 122334.602 lbf
Pressure Force on Flange Face [Ht]:
= H - Hd
= 124773 - 122335
= 2437.930 lbf
Operating Bolt Load [Wm1]:
= max( H + Hp + H'p, 0 )
= max( 124773 + 17150 + 0 , 0 )
= 141922.188 lbf
Gasket Seating Bolt Load [Wm2]:
= y * b * Pi * G + yPart * bPart * lp
= 6500.00*0.2188*3.141*44.562+0.00*0.0000*0.00
= 199058.562 lbf
Required Bolt Area [Am]:
= Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 141922/17750 , 199059/18800
= 10.588 in^2
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]:
= 2a + 6t/(m + 0.5)
= 2 * 1.000 + 6 * 3.500/(3.50 + 0.5)
= 7.250 in
Actual Circumferential Bolt Spacing [Bs]:
= C * sin( pi / n )
= 47.125 * sin( 3.142/40 )
= 3.697 in
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]:
= max( sqrt( Bs/( 2a + t )), 1 )
B-19-1191R 32
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Ring FLG Fro Flng: 6 9:18am Jul 31,2019
= max( sqrt( 3.697/( 2 * 1.000 + 3.500 )), 1 )
= 1.0000
Bolting Information for UNC Thread Series (Non Mandatory):
Distance Across Corners for Nuts 1.796 in
Circular Wrench End Diameter a 2.562 in
-----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, in^2 10.588 22.040
Radial distance bet. hub and bolts 1.062 1.500
Radial distance bet. bolts and the edge 1.062 1.062
Circumferential spacing between bolts 2.250 3.697 7.250
-----------------------------------------------------------------------------
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]:
= Ab * Sa/( y * Pi * (Go + Gi) )
= 22.040 * 18800.00/(6500.00 * 3.14 * (45.000 + 44.12 ) )
= 0.228 in
Note: Recommended Min. Width for Sheet and Composite Gaskets per table 2-4 :
= 1.250 in[Note: Exceeds actual gasket width, 0.438 ]
Flange Design Bolt Load, Gasket Seating [W]:
= Sa * Ab
= 18800.00 * 22.0400
= 414352.03 lbf
Gasket Load for the Operating Condition [HG]:
= Wm1 - H
= 141922 - 124773
= 17149.66 lbf
Moment Arm Calculations:
B-19-1191R 33
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Ring FLG Fro Flng: 6 9:18am Jul 31,2019
Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 47.1250 - 44.5625 )/2
= 1.2812 in
Distance to Face Pressure Reaction [ht]:
= ( R + g1 + hg ) / 2
= ( 1.5000 + 0.0000 + 1.2812 )/2
= 1.3906 in
Distance to End Pressure Reaction [hd]:
= R + ( g1 / 2 )
= 1.5000 + ( 0.0000/2.0 )
= 1.5000 in
Summary of Moments for Internal Pressure:
Loading Force Distance Bolt Corr Moment
End Pressure, Md 122335. 1.5000 1.0000 183502. in-lb
Face Pressure, Mt 2438. 1.3906 1.0000 3390. in-lb
Gasket Load, Mg 17150. 1.2812 1.0000 21973. in-lb
Gasket Seating, Matm 414352. 1.2812 1.0000 530889. in-lb
Total Moment for Operation, Mop 208865. in-lb
Total Moment for Gasket seating, Matm 530889. in-lb
Effective Hub Length, ho = 0.000 in
Hub Ratio, h/h0 = Defined as 0.0 0.000
Thickness Ratio, g1/g0 = Defined as 0.0 0.000
Factors from Figure 2-7.1 K = 1.116
T = 1.871 U = 19.407
Y = 17.661 Z = 9.137
Tangential Flange Stress, Operating [Sto]:
= ( Y * Mo )/( t2 * Bcor )
= (17.6609*208865)/(3.50002*44.1250)
B-19-1191R 34
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Ring FLG Fro Flng: 6 9:18am Jul 31,2019
= 6824.28 psi
Tangential Flange Stress, Seating [STa]:
= ( Y * Matm )/( t2 * Bcor )
= (17.6609*530889)/(3.50002*44.1250)
= 17345.80 psi
Bolt Stress, Operating [BSo]:
= ( Wm1 / Ab )
= (141922/22.0400)
= 6439.30 psi
Bolt Stress, Seating [BSa]:
= ( Wm2 / Ab )
= (199059/22.0400)
= 9031.70 psi
Flange Stress Analysis Results: psi
Operating | Gasket Seating |
Actual Allowed | Actual Allowed |
-----------------------------------------------------------------
Tangential Flange 6824.| 16675.| 17346.| 17500.|
Bolting 6439.| 17750.| 9032.| 18800.|
Minimum Required Flange Thickness 3.485 in
Estimated M.A.W.P. ( Operating ) 195.5 psig
Estimated Finished Weight of Flange at given Thk. 381.5 lbm
Estimated Unfinished Weight of Forging at given Thk 381.5 lbm
Flange Rigidity Based on Required Thickness [ASME]:
No rigidity calculation possible for this geometry.
Flange Rigidity Based on Given Thickness [ASME]:
No rigidity calculation possible for this geometry.
B-19-1191R 35
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Ring FLG Fro Flng: 6 9:18am Jul 31,2019
Could not determine the MDMT for this flange, because an
adjoining cylinder was not attached. The MDMT calculation
depends on the attached cylinder, please add one.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 36
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : RingFLGBACK Flng: 7 9:18am Jul 31,2019
Flange Input Data Values Description: RingFLGBACK :
Item: Node 70 to 80
Description of Flange Geometry (Type) Integral Ring
Design Pressure P 80.00 psig
Design Temperature 150 F
Internal Corrosion Allowance ci 0.0000 in
External Corrosion Allowance ce 0.0000 in
Use Corrosion Allowance in Thickness Calcs. Yes
Attached Shell Inside Diameter B 43.0000 in
Integral Ring Inside Diameter 44.0000 in
Flange Outside Diameter A 49.250 in
Flange Thickness t 3.5000 in
Flange Material SA-182 F304
Flange Material UNS number S30400
Flange Allowable Stress At Temperature Sfo 16675.00 psi
Flange Allowable Stress At Ambient Sfa 17500.00 psi
Bolt Material SA-193 B8
Bolt Allowable Stress At Temperature Sb 17750.00 psi
Bolt Allowable Stress At Ambient Sa 18800.00 psi
Length of Weld Leg at Back of Ring tw 0.5625 in
Number of Splits in Ring Flange n 0
Diameter of Bolt Circle C 47.125 in
Nominal Bolt Diameter a 1.0000 in
Type of Threads UNC Thread Series
Number of Bolts 40
B-19-1191R 37
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : RingFLGBACK Flng: 7 9:18am Jul 31,2019
Flange Face Outside Diameter Fod 45.000 in
Flange Face Inside Diameter Fid 44.125 in
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 45.000 in
Gasket Inside Diameter Gi 44.125 in
Gasket Factor m 3.5000
Gasket Design Seating Stress y 6500.00 psi
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 0.1250 in
ASME Code, Section VIII, Division 1, 2015
Corroded Flange ID, Bcor = B+2*Fcor 43.000 in
Corroded Large Hub, g1Cor = g1-ci 0.000 in
Corroded Small Hub, g0Cor = go-ci 0.000 in
Code R Dimension, R = (C-B)/2 - g1 2.062 in
Gasket Contact Width, N = (Go - Gi) / 2 0.438 in
Basic Gasket Width, bo = N / 2 0.219 in
Effective Gasket Width, b = bo 0.219 in
Gasket Reaction Diameter, G = (Go + Gi) / 2 44.562 in
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]:
= 0.785 * G2 * Peq
= 0.785 * 44.56252 * 80.000
= 124772.531 lbf
Contact Load on Gasket Surfaces [Hp]:
= 2 * b * Pi * G * m * P
= 2 * 0.2188 * 3.1416 * 44.5625 * 3.5000 * 80.00
B-19-1191R 38
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : RingFLGBACK Flng: 7 9:18am Jul 31,2019
= 17149.660 lbf
Hydrostatic End Load at Flange ID [Hd]:
= Pi * Bcor2 * P / 4
= 3.1416 * 43.00002 *80.0000/4
= 116176.094 lbf
Pressure Force on Flange Face [Ht]:
= H - Hd
= 124773 - 116176
= 8596.438 lbf
Operating Bolt Load [Wm1]:
= max( H + Hp + H'p, 0 )
= max( 124773 + 17150 + 0 , 0 )
= 141922.188 lbf
Gasket Seating Bolt Load [Wm2]:
= y * b * Pi * G + yPart * bPart * lp
= 6500.00*0.2188*3.141*44.562+0.00*0.0000*0.00
= 199058.562 lbf
Required Bolt Area [Am]:
= Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 141922/17750 , 199059/18800
= 10.588 in^2
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]:
= 2a + 6t/(m + 0.5)
= 2 * 1.000 + 6 * 3.500/(3.50 + 0.5)
= 7.250 in
Actual Circumferential Bolt Spacing [Bs]:
= C * sin( pi / n )
= 47.125 * sin( 3.142/40 )
= 3.697 in
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]:
B-19-1191R 39
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : RingFLGBACK Flng: 7 9:18am Jul 31,2019
= max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 3.697/( 2 * 1.000 + 3.500 )), 1 )
= 1.0000
Bolting Information for UNC Thread Series (Non Mandatory):
Distance Across Corners for Nuts 1.796 in
Circular Wrench End Diameter a 2.562 in
-----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, in^2 10.588 22.040
Radial distance bet. hub and bolts 1.062 2.062
Radial distance bet. bolts and the edge 1.062 1.062
Circumferential spacing between bolts 2.250 3.697 7.250
-----------------------------------------------------------------------------
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]:
= Ab * Sa/( y * Pi * (Go + Gi) )
= 22.040 * 18800.00/(6500.00 * 3.14 * (45.000 + 44.12 ) )
= 0.228 in
Note: Recommended Min. Width for Sheet and Composite Gaskets per table 2-4 :
= 1.250 in[Note: Exceeds actual gasket width, 0.438 ]
Flange Design Bolt Load, Gasket Seating [W]:
= Sa * ( Am + Ab ) / 2
= 18800.00 * ( 10.5882 + 22.0400 )/2
= 306705.31 lbf
Gasket Load for the Operating Condition [HG]:
= Wm1 - H
= 141922 - 124773
= 17149.66 lbf
B-19-1191R 40
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : RingFLGBACK Flng: 7 9:18am Jul 31,2019
Moment Arm Calculations:
Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 47.1250 - 44.5625 )/2
= 1.2812 in
Distance to Face Pressure Reaction [ht]:
= ( R + g1 + hg ) / 2
= ( 2.0625 + 0.0000 + 1.2812 )/2
= 1.6719 in
Distance to End Pressure Reaction [hd]:
= R + ( g1 / 2 )
= 2.0625 + ( 0.0000/2.0 )
= 2.0625 in
Summary of Moments for Internal Pressure:
Loading Force Distance Bolt Corr Moment
End Pressure, Md 116176. 2.0625 1.0000 239613. in-lb
Face Pressure, Mt 8596. 1.6719 1.0000 14372. in-lb
Gasket Load, Mg 17150. 1.2812 1.0000 21973. in-lb
Gasket Seating, Matm 306705. 1.2812 1.0000 392966. in-lb
Total Moment for Operation, Mop 275958. in-lb
Total Moment for Gasket seating, Matm 392966. in-lb
Effective Hub Length, ho = 0.000 in
Hub Ratio, h/h0 = Defined as 0.0 0.000
Thickness Ratio, g1/g0 = Defined as 0.0 0.000
Factors from Figure 2-7.1 K = 1.145
T = 1.860 U = 15.771
Y = 14.351 Z = 7.414
Tangential Flange Stress, Operating [Sto]:
= ( Y * Mo )/( t2 * Bcor )
B-19-1191R 41
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : RingFLGBACK Flng: 7 9:18am Jul 31,2019
= (14.3513*275958)/(3.50002*43.0000)
= 7518.47 psi
Tangential Flange Stress, Seating [STa]:
= ( Y * Matm )/( t2 * Bcor )
= (14.3513*392966)/(3.50002*43.0000)
= 10706.35 psi
Bolt Stress, Operating [BSo]:
= ( Wm1 / Ab )
= (141922/22.0400)
= 6439.30 psi
Bolt Stress, Seating [BSa]:
= ( Wm2 / Ab )
= (199059/22.0400)
= 9031.70 psi
Flange Stress Analysis Results: psi
Operating | Gasket Seating |
Actual Allowed | Actual Allowed |
-----------------------------------------------------------------
Tangential Flange 7518.| 16675.| 10706.| 17500.|
Bolting 6439.| 17750.| 9032.| 18800.|
Minimum Required Flange Thickness 2.738 in
Estimated M.A.W.P. ( Operating ) 177.4 psig
Estimated Finished Weight of Flange at given Thk. 459.6 lbm
Estimated Unfinished Weight of Forging at given Thk 459.6 lbm
Flange Rigidity Based on Required Thickness [ASME]:
No rigidity calculation possible for this geometry.
Flange Rigidity Based on Given Thickness [ASME]:
B-19-1191R 42
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : RingFLGBACK Flng: 7 9:18am Jul 31,2019
No rigidity calculation possible for this geometry.
SA-182 F304, Min Metal Temp without impact per UHA-51: -320 F
Required Fillet Weld Leg size for Slip on Flanges:
= max( tn, ( 6 mm or 1/4 inch ) ) no hub size given
= max( 0.5000 , 0.250 )
= 0.500 in
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 43
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Back Cover Flng: 8 9:18am Jul 31,2019
Flange Input Data Values Description: Back Cover :
Item: Node 80 to 90
Description of Flange Geometry (Type) Blind
Design Pressure P 80.00 psig
Design Temperature 150 F
Internal Corrosion Allowance ci 0.0000 in
External Corrosion Allowance ce 0.0000 in
Use Corrosion Allowance in Thickness Calcs. Yes
Flange Outside Diameter A 49.250 in
Flange Thickness t 2.0625 in
Flange Material SA-182 F304
Flange Material UNS number S30400
Flange Allowable Stress At Temperature Sfo 16675.00 psi
Flange Allowable Stress At Ambient Sfa 17500.00 psi
Bolt Material SA-193 B8
Bolt Allowable Stress At Temperature Sb 17750.00 psi
Bolt Allowable Stress At Ambient Sa 18800.00 psi
Diameter of the Load Reaction, Long Span D 0.000 in
Diameter of the Load Reaction, Short Span d 0.000 in
Perimeter along the Center of the Bolts L 148.048 in
Diameter of Bolt Circle C 47.125 in
Nominal Bolt Diameter a 1.0000 in
Type of Threads UNC Thread Series
Number of Bolts 40
Flange Face Outside Diameter Fod 45.000 in
B-19-1191R 44
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Back Cover Flng: 8 9:18am Jul 31,2019
Flange Face Inside Diameter Fid 42.562 in
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 45.000 in
Gasket Inside Diameter Gi 42.562 in
Gasket Factor m 3.5000
Gasket Design Seating Stress y 6500.00 psi
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 0.1250 in
ASME Code, Section VIII, Division 1, 2015
Gasket Contact Width, N = (Go - Gi) / 2 1.219 in
Basic Gasket Width, bo = N / 2 0.609 in
Effective Gasket Width, b = sqrt(bo) / 2 0.390 in
Gasket Reaction Diameter, G = Go - 2 * b 44.219 in
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]:
= 0.785 * G2 * Peq
= 0.785 * 44.21942 * 80.000
= 122858.469 lbf
Contact Load on Gasket Surfaces [Hp]:
= 2 * b * Pi * G * m * P
= 2 * 0.3903 * 3.1416 * 44.2194 * 3.5000 * 80.00
= 30364.268 lbf
Operating Bolt Load [Wm1]:
= max( H + Hp + H'p, 0 )
= max( 122858 + 30364 + 0 , 0 )
= 153222.734 lbf
B-19-1191R 45
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Back Cover Flng: 8 9:18am Jul 31,2019
Gasket Seating Bolt Load [Wm2]:
= y * b * Pi * G + yPart * bPart * lp
= 6500.00*0.3903*3.141*44.219+0.00*0.0000*0.00
= 352442.438 lbf
Required Bolt Area [Am]:
= Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 153223/17750 , 352442/18800
= 18.747 in^2
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]:
= 2a + 6t/(m + 0.5)
= 2 * 1.000 + 6 * 2.062/(3.50 + 0.5)
= 5.094 in
Actual Circumferential Bolt Spacing [Bs]:
= C * sin( pi / n )
= 47.125 * sin( 3.142/40 )
= 3.697 in
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]:
= max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 3.697/( 2 * 1.000 + 2.062 )), 1 )
= 1.0000
Bolting Information for UNC Thread Series (Non Mandatory):
-----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, in^2 18.747 22.040
Radial distance bet. bolts and the edge 1.062 1.062
Circumferential spacing between bolts 2.250 3.697 5.094
-----------------------------------------------------------------------------
B-19-1191R 46
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Back Cover Flng: 8 9:18am Jul 31,2019
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]:
= Ab * Sa/( y * Pi * (Go + Gi) )
= 22.040 * 18800.00/(6500.00 * 3.14 * (45.000 + 42.56 ) )
= 0.232 in
Flange Design Bolt Load, Gasket Seating [W]:
= Sa * ( Am + Ab ) / 2
= 18800.00 * ( 18.7469 + 22.0400 )/2
= 383397.25 lbf
Gasket Load for the Operating Condition [HG]:
= Wm1
= 153222.73 lbf
Moment Arm Calculations:
Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 47.1250 - 44.2194 )/2
= 1.4528 in
Tangential Flange Stress, Flat Head (UG-34), Operating [STo]:
= 1.9 * Wm1 * hG * Bsc/(t2 * G) + C * Z * Peq * G2/t2
= 1.9*153223*1.4528*1.0000/(2.06252*44.2194)+
0.30*1.0000*80.00*44.21942/2.06252
= 13280.32 psi
Tangential Flange Stress, Flat Head (UG-34), Seating [STa]:
= 1.9 * W * hG * Bsc/ (t2 * G)
= 1.9*383397*1.4528*1.000/(2.06252*44.2194)
= 5626.15 psi
Bolt Stress, Operating [BSo]:
= ( Wm1 / Ab )
= (153223/22.0400)
= 6952.03 psi
B-19-1191R 47
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Flg Calc [Int P] : Back Cover Flng: 8 9:18am Jul 31,2019
Bolt Stress, Seating [BSa]:
= ( Wm2 / Ab )
= (352442/22.0400)
= 15991.04 psi
Flange Stress Analysis Results: psi
Operating | Gasket Seating |
Actual Allowed | Actual Allowed |
-----------------------------------------------------------------
Tangential Flange 13280.| 16675.| 5626.| 17500.|
Bolting 6952.| 17750.| 15991.| 18800.|
Reqd. Blind Flange Thickness at Center 1.841 in
Reqd. Blind Flange Thickness at Gasket 1.169 in
Estimated M.A.W.P. ( Operating ) 100.4 psig
Estimated Finished Weight of Flange at given Thk. 1139.4 lbm
Estimated Unfinished Weight of Forging at given Thk 1139.4 lbm
SA-182 F304, Min Metal Temp without impact per UHA-51: -320 F
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 48
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Internal Pressure Calculations : Step: 7 9:18am Jul 31,2019
Element Thickness, Pressure, Diameter and Allowable Stress :
| | Int. Press | Nominal | Total Corr| Element | Allowable |
From| To | + Liq. Hd | Thickness | Allowance | Diameter | Stress(SE)|
| | psig | in | in | in | psi |
---------------------------------------------------------------------------
Cover Fron| 80.0000 | ... | ... | 49.2500 | 16675.0 |
20| 30| 80.0000 | ... | ... | 44.1250 | 16675.0 |
30| 40| 80.0000 | 0.50000 | ... | 43.0000 | 10920.0 |
40| 60| 75.0000 | 0.50000 | ... | 43.0000 | 10920.0 |
60| 70| 80.0000 | 0.50000 | ... | 43.0000 | 10920.0 |
70| 80| 80.0000 | 0.50000 | ... | 43.0000 | 16675.0 |
80| 90| 80.0000 | 0.50000 | ... | 49.2500 | 16675.0 |
Element Required Thickness and MAWP :
| | Design | M.A.W.P. | M.A.P. | Minimum | Required |
From| To | Pressure | Corroded | New & Cold | Thickness | Thickness |
| | psig | psig | psig | in | in |
----------------------------------------------------------------------------
Cover Fron| 80.0000 | 100.440 | 105.410 | 2.06250 | 1.84062 |
20| 30| 80.0000 | 115.165 | 115.281 | 3.50000 | 3.48500 |
30| 40| 80.0000 | 250.459 | 250.459 | 0.50000 | 0.15820 |
40| 60| 75.0000 | 250.459 | 250.459 | 0.50000 | 0.14828 |
60| 70| 80.0000 | 250.459 | 250.459 | 0.50000 | 0.15820 |
70| 80| 80.0000 | 177.420 | 186.200 | 3.50000 | 2.73800 |
80| 90| 80.0000 | 100.440 | 105.410 | 2.06250 | 1.84062 |
Summary of Heat Exchanger Maximum Allowable Working Pressures :
Note:
The MAWPs and MAPs for the Exchanger elements all appear to
B-19-1191R 49
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Internal Pressure Calculations : Step: 7 9:18am Jul 31,2019
be zero or some could not be calculated. Please fill these
values in on the main tubesheet tab.
Internal Pressure Calculation Results :
ASME Code, Section VIII, Division 1, 2015
Cylindrical Shell From 30 To 40 SA-240 304L at 150 F
Longitudinal Joint: No Radiography per UW 11(c) Type 1
Circumferential Joint: No Radiography per UW 11(c) Type 1
Material UNS Number: S30403
Required Thickness due to Internal Pressure [tr]:
= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (80.000*21.5000)/(15600.00*0.70-0.6*80.000)
= 0.1582 + 0.0000 = 0.1582 in
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]:
= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (15600.00*0.70*0.5000)/(21.5000+0.6*0.5000)
= 250.459 psig
Maximum Allowable Pressure, New and Cold [MAPNC]:
= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (15600.00*0.70*0.5000)/(21.5000+0.6*0.5000)
= 250.459 psig
Actual stress at given pressure and thickness, corroded [Sact]:
= (P*(R+0.6*t))/(E*t)
= (80.000*(21.5000+0.6*0.5000))/(0.70*0.5000)
= 4982.857 psi
B-19-1191R 50
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Internal Pressure Calculations : Step: 7 9:18am Jul 31,2019
Percent Elongation per UHA-44 (50*tnom/Rf)*(1-Rf/Ro) 1.149 %
Note: Please Check Requirements of Table UHA-44 for Elongation limits.
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
Cylindrical Shell From 40 To 60 SA-240 304L at 150 F
Longitudinal Joint: No Radiography per UW 11(c) Type 1
Circumferential Joint: No Radiography per UW 11(c) Type 1
Material UNS Number: S30403
Required Thickness due to Internal Pressure [tr]:
= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (75.000*21.5000)/(15600.00*0.70-0.6*75.000)
= 0.1483 + 0.0000 = 0.1483 in
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]:
= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (15600.00*0.70*0.5000)/(21.5000+0.6*0.5000)
= 250.459 psig
Maximum Allowable Pressure, New and Cold [MAPNC]:
= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (15600.00*0.70*0.5000)/(21.5000+0.6*0.5000)
= 250.459 psig
Actual stress at given pressure and thickness, corroded [Sact]:
= (P*(R+0.6*t))/(E*t)
= (75.000*(21.5000+0.6*0.5000))/(0.70*0.5000)
= 4671.429 psi
B-19-1191R 51
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Internal Pressure Calculations : Step: 7 9:18am Jul 31,2019
Percent Elongation per UHA-44 (50*tnom/Rf)*(1-Rf/Ro) 1.149 %
Note: Please Check Requirements of Table UHA-44 for Elongation limits.
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
Cylindrical Shell From 60 To 70 SA-240 304L at 150 F
Longitudinal Joint: No Radiography per UW 11(c) Type 1
Circumferential Joint: No Radiography per UW 11(c) Type 1
Material UNS Number: S30403
Required Thickness due to Internal Pressure [tr]:
= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (80.000*21.5000)/(15600.00*0.70-0.6*80.000)
= 0.1582 + 0.0000 = 0.1582 in
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]:
= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (15600.00*0.70*0.5000)/(21.5000+0.6*0.5000)
= 250.459 psig
Maximum Allowable Pressure, New and Cold [MAPNC]:
= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (15600.00*0.70*0.5000)/(21.5000+0.6*0.5000)
= 250.459 psig
Actual stress at given pressure and thickness, corroded [Sact]:
= (P*(R+0.6*t))/(E*t)
= (80.000*(21.5000+0.6*0.5000))/(0.70*0.5000)
= 4982.857 psi
Percent Elongation per UHA-44 (50*tnom/Rf)*(1-Rf/Ro) 1.149 %
B-19-1191R 52
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Internal Pressure Calculations : Step: 7 9:18am Jul 31,2019
Note: Please Check Requirements of Table UHA-44 for Elongation limits.
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
Hydrostatic Test Pressure Results:
Exchanger Shell Side Hydrostatic Test Pressures:
Pressure per UG99b = 1.3 * M.A.W.P. * Sa/S 97.500 psig
Pressure per UG99b[36] = 1.3 * Design Pres * Sa/S 97.500 psig
Pressure per UG99c = 1.3 * M.A.P. - Head(Hyd) 0.000 psig
Pressure per UG100 = 1.1 * M.A.W.P. * Sa/S 82.500 psig
Pressure per PED = 1.43 * MAWP 107.250 psig
Pressure per App 27-4 = 1.3 * M.A.W.P. * Sa/S 97.500 psig
User defined Hydrostatic Test Pressures:
Shell Side Test Pressure at High Point 113.000 psig
Channel Side Test Pressure at High Point 120.000 psig
Exchanger Channel Side Hydrostatic Test Pressures:
Pressure per UG99b = 1.3 * M.A.W.P. * Sa/S 104.000 psig
Pressure per UG99b[36] = 1.3 * Design Pres * Sa/S 104.000 psig
Pressure per UG99c = 1.3 * M.A.P. - Head(Hyd) 0.000 psig
Pressure per UG100 = 1.1 * M.A.W.P. * Sa/S 88.000 psig
Pressure per PED = 1.43 * MAWP 114.400 psig
Pressure per App 27-4 = 1.3 * M.A.W.P. * Sa/S 104.000 psig
Horizontal Test performed per: User Hydro Pressure
Please note that Nozzle, Shell, Head, Flange, etc MAWPs are all considered
when determining the hydrotest pressure for those test types that are based
B-19-1191R 53
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FileName : HEAT EXCHANGER
Internal Pressure Calculations : Step: 7 9:18am Jul 31,2019
on the MAWP of the vessel.
Stresses on Elements due to Test Pressure:
From To Stress Allowable Ratio Pressure
----------------------------------------------------------------------
30 40 7571.0 20280.0 0.373 121.55
40 60 7135.0 20280.0 0.352 114.55
60 70 7571.0 20280.0 0.373 121.55
----------------------------------------------------------------------
Stress ratios for Nozzle and Pad Materials:
Description Pad/Nozzle Ambient Operating ratio
----------------------------------------------------------------------
D Nozzle 16000.00 15225.00 1.051
CO-1 Nozzle 17500.00 16400.00 1.067
P7 Nozzle 16250.00 16050.00 1.012
P8 Nozzle 16250.00 16050.00 1.012
SO-1 Nozzle 16000.00 15225.00 1.051
SI-1 Nozzle 16000.00 15225.00 1.051
SI-2 Nozzle 16000.00 15225.00 1.051
P1 Nozzle 16250.00 16050.00 1.012
P2 Nozzle 16250.00 16050.00 1.012
P3 Nozzle 16250.00 16050.00 1.012
P4 Nozzle 16250.00 16050.00 1.012
P5 Nozzle 16250.00 16050.00 1.012
P6 Nozzle 16250.00 16050.00 1.012
V Nozzle 15600.00 15450.00 1.010
CI-1 Nozzle 17500.00 16400.00 1.067
P9 Nozzle 15600.00 15450.00 1.010
P10 Nozzle 15600.00 15450.00 1.010
----------------------------------------------------------------------
B-19-1191R 54
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Internal Pressure Calculations : Step: 7 9:18am Jul 31,2019
Minimum 1.010
Stress ratios for Stiffening Ring Materials:
Description Ambient Operating ratio
----------------------------------------------------------------------
----------------------------------------------------------------------
Minimum ******
Stress ratios for Vessel Elements:
Description Ambient Operating ratio
----------------------------------------------------------------------
Cover Front 17500.00 16675.00 1.049
17500.00 16675.00 1.049
15600.00 15600.00 1.000
15600.00 15600.00 1.000
15600.00 15600.00 1.000
17500.00 16675.00 1.049
17500.00 16675.00 1.049
----------------------------------------------------------------------
Minimum 1.000
Stress ratios for Exchanger Materials:
Description Ambient Operating ratio
----------------------------------------------------------------------
Tube Material 20000.00 20000.00 1.000
Tubesheet Material 15600.00 15600.00 1.000
----------------------------------------------------------------------
Minimum 1.000
Elements Suitable for Internal Pressure.
B-19-1191R 55
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Internal Pressure Calculations : Step: 7 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 56
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
External Pressure Calculations : Step: 8 9:18am Jul 31,2019
External Pressure Calculation Results :
ASME Code, Section VIII, Division 1, 2015
Cylindrical Shell From 30 to 40 Ext. Chart: HA-3 at 200 F
Elastic Modulus from Chart: HA-3 at 200 F : 0.273E+08 psi
Results for Maximum Allowable External Pressure (MAEP):
Tca OD SLEN D/t L/D Factor A B
0.500 44.00 32.69 88.00 0.7429 0.0022666 9126.60
EMAP = (4*B)/(3*(D/t)) = (4*9126.5977 )/(3*88.0000 ) = 138.2818 psig
Results for Maximum Stiffened Length (Slen):
Tca OD SLEN D/t L/D Factor A B
0.500 44.00 32.69 88.00 0.7429 0.0022666 9126.60
EMAP = (4*B)/(3*(D/t)) = (4*9126.5977 )/(3*88.0000 ) = 138.2818 psig
Cylindrical Shell From 60 to 70 Ext. Chart: HA-3 at 200 F
Elastic Modulus from Chart: HA-3 at 200 F : 0.273E+08 psi
Results for Maximum Allowable External Pressure (MAEP):
Tca OD SLEN D/t L/D Factor A B
0.500 44.00 30.31 88.00 0.6889 0.0024616 9264.80
EMAP = (4*B)/(3*(D/t)) = (4*9264.8047 )/(3*88.0000 ) = 140.3758 psig
Results for Maximum Stiffened Length (Slen):
Tca OD SLEN D/t L/D Factor A B
0.500 44.00 30.31 88.00 0.6889 0.0024616 9264.80
EMAP = (4*B)/(3*(D/t)) = (4*9264.8047 )/(3*88.0000 ) = 140.3758 psig
B-19-1191R 57
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
External Pressure Calculations : Step: 8 9:18am Jul 31,2019
External Pressure Calculations
| | Section | Outside | Corroded | Factor | Factor |
From| To | Length | Diameter | Thickness | A | B |
| | in | in | in | | psi |
---------------------------------------------------------------------------
10| 20| No Calc | ... | 2.06250 | No Calc | No Calc |
20| 30| No Calc | ... | 3.50000 | No Calc | No Calc |
30| 40| 32.6875 | 44.0000 | 0.50000 | 0.0022666 | 9126.60 |
40|Tsht| 32.6875 | 44.0000 | 0.50000 | 0.0022666 | 9126.60 |
Tsht|Tsht| No Calc | ... | 0.50000 | No Calc | No Calc |
Tsht| 60| No Calc | ... | 0.50000 | No Calc | No Calc |
60| 70| 30.3133 | 44.0000 | 0.50000 | 0.0024616 | 9264.80 |
70| 80| No Calc | ... | 3.50000 | No Calc | No Calc |
80| 90| No Calc | ... | 2.06250 | No Calc | No Calc |
External Pressure Calculations
| | External | External | External | External |
From| To | Actual T. | Required T.|Des. Press. | M.A.W.P. |
| | in | in | psig | psig |
----------------------------------------------------------------
10| 20| 2.06250 | 1.25600 | ... | No Calc |
20| 30| 3.50000 | 3.48500 | ... | No Calc |
30| 40| 0.50000 | No Calc | ... | 138.282 |
40|Tsht| 0.50000 | No Calc | ... | 138.282 |
Tsht|Tsht| 0.50000 | No Calc | ... | No Calc |
Tsht| 60| 0.50000 | No Calc | ... | No Calc |
60| 70| 0.50000 | No Calc | ... | 140.376 |
70| 80| 3.50000 | 2.73800 | ... | No Calc |
80| 90| 2.06250 | 1.21200 | ... | No Calc |
Minimum 138.282
B-19-1191R 58
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
External Pressure Calculations : Step: 8 9:18am Jul 31,2019
External Pressure Calculations
| | Actual Len.| Allow. Len.| Ring Inertia | Ring Inertia |
From| To | Bet. Stiff.| Bet. Stiff.| Required | Available |
| | in | in | in**4 | in**4 |
-------------------------------------------------------------------
10| 20| No Calc | No Calc | No Calc | No Calc |
20| 30| No Calc | No Calc | No Calc | No Calc |
30| 40| 32.6875 | No Calc | No Calc | No Calc |
40|Tsht| 32.6875 | No Calc | No Calc | No Calc |
Tsht|Tsht| No Calc | No Calc | No Calc | No Calc |
Tsht| 60| No Calc | No Calc | No Calc | No Calc |
60| 70| 30.3133 | No Calc | No Calc | No Calc |
70| 80| No Calc | No Calc | No Calc | No Calc |
80| 90| No Calc | No Calc | No Calc | No Calc |
Elements Suitable for External Pressure.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 59
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Element and Detail Weights : Step: 9 9:18am Jul 31,2019
Element and Detail Weights
| | Element | Element | Corroded | Corroded | Extra due |
From| To | Metal Wgt. | ID Volume |Metal Wgt. | ID Volume | Misc % |
| | lbf | gal | lbf | gal | lbf |
---------------------------------------------------------------------------
10| 20| 1139.45 | ... | 1139.45 | ... | ... |
20| 30| 381.488 | ... | 381.488 | ... | ... |
30| 40| 647.722 | 205.493 | 647.722 | 205.493 | ... |
40| 60| 4587.31 | 1455.34 | 4587.31 | 1455.34 | ... |
60| 70| 600.660 | 190.562 | 600.660 | 190.562 | ... |
70| 80| 459.624 | ... | 459.624 | ... | ... |
80| 90| 1139.45 | ... | 1139.45 | ... | ... |
Total | 8955 | 1851.40 | 8955 | 1851.40 | 0 |
For elements specified as shell side elements, the volume(s) shown
above for those elements, reflects the displacement of the tubes.
Weight of Details
| | Weight of | X Offset, | Y Offset, |
From|Type| Detail | Dtl. Cent. |Dtl. Cent. | Description
| | lbf | in | in |
-------------------------------------------------
30|Nozl| 0.66963 | 13.8125 | 22.3750 | D
30|Nozl| 122.281 | 13.8125 | 27.5000 | CO-1
30|Nozl| 0.66963 | 3.00000 | 22.3750 | P7
30|Nozl| 0.66963 | 3.00000 | 22.3750 | P8
40|Sadl| 322.816 | 21.0000 | 24.6250 | Lft Sdl
40|Sadl| 322.816 | 210.500 | 24.6250 | New Sdl
40|Nozl| 216.390 | 115.750 | 30.1250 | SO-1
40|Nozl| 216.390 | 10.2500 | 30.1250 | SI-1
B-19-1191R 60
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FileName : HEAT EXCHANGER
Element and Detail Weights : Step: 9 9:18am Jul 31,2019
40|Nozl| 216.390 | 221.250 | 30.1250 | SI-2
40|Nozl| 0.66963 | 3.00000 | 22.3750 | P1
40|Nozl| 0.66963 | 3.00000 | 22.3750 | P2
40|Nozl| 0.66963 | 3.00000 | 22.3750 | P3
40|Nozl| 0.66963 | 3.00000 | 22.3750 | P4
40|Nozl| 0.66963 | 3.00000 | 22.3750 | P5
40|Nozl| 0.66963 | 3.00000 | 22.3750 | P6
60|Nozl| 0.66963 | 16.5000 | 22.3750 | V
60|Nozl| 122.281 | 16.5000 | 27.5000 | CI-1
60|Nozl| 0.66963 | 3.00000 | 22.3750 | P9
60|Nozl| 0.66963 | 3.00000 | 22.3750 | P10
40|FTsh| 593.101 | 0.75000 | ... | TUBESHEET
40|Tube| 812.042 | 116.500 | ... |
40|RTsh| 593.101 | 232.250 | ... |
Total Weight of Each Detail Type
Total Weight of Saddles 645.6
Total Weight of Nozzles 901.8
Total Weight of Exchanger Components 1998.2
---------------------------------------------------------------
Sum of the Detail Weights 3545.6 lbf
Weight Summation: lbf
Fabricated | Shop Test | Shipping | Erected | Empty | Operating |
------------------------------------------------------------------------------
8955.7 | 12501.3 | 8955.7 | 12501.3 | 8955.7 | 12501.3 |
645.6 | 15443.8 | 645.6 | ... | 645.6 | ... |
901.8 | ... | 901.8 | ... | ... | ... |
... | 1218.0 | ... | ... | ... | ... |
... | ... | ... | ... | ... | ... |
... | ... | ... | ... | ... | ... |
B-19-1191R 61
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Element and Detail Weights : Step: 9 9:18am Jul 31,2019
... | ... | ... | ... | 901.8 | ... |
1998.2 | ... | 1998.2 | ... | ... | ... |
... | ... | ... | ... | 1998.2 | ... |
12501.3 | 29163.1 | 12501.3 | 12501.3 | 12501.3 | 12501.3 |
Note:
The shipping total has been modified because some items have
been specified as being installed in the shop.
Weight Summary
Fabricated Wt. - Bare Weight W/O Removable Internals 12501.3 lbf
Shop Test Wt. - Fabricated Weight + Water ( Full ) 29163.1 lbf
Shipping Wt. - Fab. Wt + Rem. Intls.+ Shipping App. 12501.3 lbf
Erected Wt. - Fab. Wt + Rem. Intls.+ Insul. (etc) 12501.3 lbf
Ope. Wt. no Liq - Fab. Wt + Intls. + Details + Wghts. 12501.3 lbf
Operating Wt. - Empty Wt + Operating Liq. Uncorroded 12501.3 lbf
Oper. Wt. + CA - Corr Wt. + Operating Liquid 12501.3 lbf
Field Test Wt. - Empty Weight + Water (Full) 29163.1 lbf
Exchanger Tube Data
Volume of Exchanger tubes : 146.0 gal
Weight of Ope Liq in tubes : 0.0 lbf
Weight of Water in tubes : 1218.0 lbf
Note:
The Corroded Weight and thickness are used in the Horizontal
Vessel Analysis (Ope Case) and Earthquake Load Calculations.
Outside Surface Areas of Elements
| | Surface |
B-19-1191R 62
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Element and Detail Weights : Step: 9 9:18am Jul 31,2019
From| To | Area |
| | in^2 |
----------------------------
10| 20| 2224.15 |
20| 30| 917.382 |
30| 40| 4518.40 |
40| 60| 32000.3 |
60| 70| 4190.10 |
70| 80| 994.363 |
80| 90| 2224.15 |
Total 47068.801 in^2 [326.9 Square Feet ]
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 63
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Flange MAWP : Step: 10 9:18am Jul 31,2019
Nozzle Flange MAWP Results :
Nozzle Flange Rating
Description Operating Ambient Temperature Class Grade/Group
psig psig F
----------------------------------------------------------------------------
CO-1 212.5 230.0 150 150 GR 2.3
SO-1 252.5 275.0 150 150 GR 2.1
SI-1 252.5 275.0 150 150 GR 2.1
SI-2 252.5 275.0 150 150 GR 2.1
Shellside Flange Rating
Lowest Flange Pressure Rating was (Ope)[ShellSide]: 252.500 psig
Lowest Flange Pressure Rating was (Amb)[ShellSide]: 275.000 psig
Channelside Flange Rating
Lowest Flange Pressure Rating was (Ope)[TubeSide ]: 212.500 psig
Lowest Flange Pressure Rating was (Amb)[TubeSide ]: 230.000 psig
Note: ANSI Ratings are per ANSI/ASME B16.5 2013 Edition
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 64
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Wind Load Calculation : Step: 11 9:18am Jul 31,2019
Wind Analysis Results
User Entered Importance Factor is 1.000
Gust Factor (Gh, Gbar) Static Dynamic 1.321
Shape Factor (Cf) for the Vessel is 0.600
User Entered Basic Wind Speed 70.0 mile/hr
Exposure Category C
Table Lookup Value Alpha from Table C6 7.0000
Table Lookup Value Zg from Table C6 900.0000
Table Lookup Value Do from Table C6 0.0050
Wind Load Results per ASCE-7 93:
Sample Calculation for the First Element:
Rougness Factor = 1.000
Values [cf1] and [cf2]
Because RoughFact = 1 and DQZ > 2.5 and H/D > 7.0
Interpolating to find the final cf:
Because H / D < 25.0
CF = CF1 + (CF2-CF1) * ( H/D - 7.0 )/( 25.0 - 7.0 )
= 0.600 + (0.700 -0.600 ) * ( 7.006 - 7.0 )/( 25.0 - 7.0 )
= 0.600
Value of Alpha, Zg is taken from Table C6-2 [Alpha, Zg]
For Exposure Category C:
Alpha = 7.000 , Zg = 10800.000 in
Height of Interest for First Element [z]
= Centroid Hgt + Base Height
= 28.750 + 0.000 = 28.750 in
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FileName : HEAT EXCHANGER
Wind Load Calculation : Step: 11 9:18am Jul 31,2019
but: z = Max(180.000 , 28.750 ) = 180.000 in
Note: Because z < 15 feet, use 15 feet to compute kz.
Velocity Pressure Coefficient [kZ]:
= 2.58( z/zg )2/Alpha : z is Elevation of First Element
= 2.58( 180.000/900 )2/7.0
= 0.801
Determine if Static or Dynamic Gust Factor Applies
Height to Diameter ratio :
= Maximum Height(length)^2 / Sum of Area of the Elements
= 25.010 (^2)/89.279
= 7.006
Vibration Frequency = 33.000 Hz
Because H/D > 5 Or Freqency < 1.0: Dynamic Analysis Implemented
Element O/Dia = 3 in
Vibration Damping Factor (Operating) Beta = 0.01000
For Terrain Category C
S = 1.000 , Gamma = 0.230 , Drag Coeff. = 0.005 , Alpha = 7.000
Compute [fbar]
= 10.5 * Frequency(Hz) * Vessel Height(ft) / (S * Vr(mph))
= 10.5 * 33.000 (Hz) * 25.010 (ft)/S * 1.000 (mph)
= 123.802
Because FBAR > 40: FBAR = 40.000
Wind Pressure - (performed in Imperial Units) [qz]
Importance Factor: I = 1.000
Wind Speed = 70.000 mile/hr
B-19-1191R 66
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Wind Load Calculation : Step: 11 9:18am Jul 31,2019
qz = 0.00256 * kZ * (I * Vr)2
= 0.00256 * 0.801 *(1.000 * 70.000 )2 = 10.046 psf
Force on the First Element [Fz]
= qz * Gh * CF * Wind Area
= 10.046 * 1.321 * 0.600 * 121.894
= 6.740 lbf
Element z GH Area qz Force
in in^2 psf lbf
------------------------------------------------------------------------
Cover Front 28.8 1.321 121.9 10.0 6.7
Node 20 to 30 28.8 1.321 -185.3 10.0 -10.2
Node 30 to 40 28.8 1.321 1725.9 10.0 95.4
Node 40 to 60 28.8 1.321 12223.2 10.0 675.8
Node 60 to 70 28.8 1.321 1600.5 10.0 88.5
Node 70 to 80 28.8 1.321 -180.6 10.0 -10.0
Node 80 to 90 28.8 1.321 121.9 10.0 6.7
Wind Load Calculation
| | Wind | Wind | Wind | Wind | Element |
From| To | Height | Diameter | Area | Pressure | Wind Load |
| | in | in | in^2 | psf | lbf |
---------------------------------------------------------------------------
10| 20| 28.7500 | 59.1000 | 121.894 | 10.0464 | 6.73953 |
20| 30| 28.7500 | 52.9500 | -185.325 | 10.0464 | -10.2466 |
30| 40| 28.7500 | 52.8000 | 1725.90 | 10.0464 | 95.4253 |
40| 60| 28.7500 | 52.8000 | 12223.2 | 10.0464 | 675.823 |
60| 70| 28.7500 | 52.8000 | 1600.50 | 10.0464 | 88.4919 |
70| 80| 28.7500 | 51.6000 | -180.600 | 10.0464 | -9.98540 |
80| 90| 28.7500 | 59.1000 | 121.894 | 10.0464 | 6.73953 |
B-19-1191R 67
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Wind Load Calculation : Step: 11 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 68
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FileName : HEAT EXCHANGER
Earthquake Load Calculation : Step: 12 9:18am Jul 31,2019
Earthquake Analysis Results
The UBC Zone Factor for the Vessel is ............. 0.0000
The Importance Factor as Specified by the User is . 1.000
The UBC Frequency and Soil Factor (C) is ......... 2.750
The UBC Force Factor as Specified by the User is .. 3.000
The UBC Total Weight (W) for the Vessel is ........ 12501.3 lbf
The UBC Total Shear (V) for the Vessel is ......... 0.0 lbf
The UBC Top Shear (Ft) for the Vessel is .......... 0.0 lbf
Earthquake Load Calculation
| | Earthquake | Earthquake | Element |
From| To | Height | Weight | Ope Load |
| | in | lbf | lbf |
-------------------------------------------------
10| 20| 24.6250 | 1389.04 | ... |
20| 30| 22.0625 | 1389.04 | ... |
30| 40| 21.5000 | 1389.04 | ... |
40|Sadl| 21.5000 | 1389.04 | ... |
Sadl| 60| 21.5000 | 1389.04 | ... |
40| 60| 21.5000 | 1389.04 | ... |
60| 70| 21.5000 | 1389.04 | ... |
70| 80| 21.5000 | 1389.04 | ... |
80| 90| 24.6250 | 1389.04 | ... |
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 69
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FileName : HEAT EXCHANGER
Center of Gravity Calculation : Step: 13 9:18am Jul 31,2019
Shop/Field Installation Options :
Note : The CG is computed from the first Element From Node
Center of Gravity of Saddles 150.500 in
Center of Gravity of Nozzles 149.841 in
Center of Gravity of Tubesheet(s) 151.250 in
Center of Gravity of Tubes 151.250 in
Center of Gravity of Bare Shell New and Cold 150.801 in
Center of Gravity of Bare Shell Corroded 150.801 in
Vessel CG in the Operating Condition 150.788 in
Vessel CG in the Fabricated (Shop/Empty) Condition 150.788 in
Vessel CG in the Test Condition 150.108 in
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 70
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
ASME Horizontal Vessel Analysis: Stresses for the Left Saddle
(per ASME Sec. VIII Div. 2 based on the Zick method.)
Horizontal Vessel Stress Calculations : Operating Case
Note:
Wear Pad Bearing angle is less than saddle angle + saddle/12
degrees. The wear plate will be ignored.
Minimum Wear Plate Angle [theta1]:
= 133.0 degrees
Note:
Wear Pad Width (0.00) is less than 1.56*sqrt(rm*t)
and less than 2a. The wear plate will be ignored.
Minimum Wear Plate Width to be considered in analysis [b1]:
= min( b + 1.56*sqrt( Rm * t ), 2a )
= min( 8.000 + 1.56*sqrt( 21.7500 * 0.5000 ), 2 * 56.750 )
= 13.1445 in
Input and Calculated Values:
Vessel Mean Radius Rm 21.75 in
Stiffened Vessel Length per 4.15.6 L 231.50 in
Distance from Saddle to Vessel tangent a 56.75 in
Saddle Width b 8.00 in
Saddle Bearing Angle theta 121.00 degrees
Shell Allowable Stress used in Calculation 15600.00 psi
Head Allowable Stress used in Calculation 16675.00 psi
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
Saddle Force Q, Operating Case 7203.25 lbf
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 1610.44 15600.00 psi
Long. Stress at Bottom of Midspan 1652.06 15600.00 psi
Long. Stress at Top of Saddles 2786.08 15600.00 psi
Long. Stress at Bottom of Saddles 990.44 15600.00 psi
Tangential Shear in Shell 389.76 9360.00 psi
Circ. Stress at Horn of Saddle 2522.15 19500.00 psi
Circ. Compressive Stress in Shell 82.92 15600.00 psi
Intermediate Results: Saddle Reaction Q due to Wind or Seismic
Saddle Reaction Force due to Wind Ft [Fwt]:
= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 853.0/2 + 0 ) * 28.7500/37.8605
= 971.6 lbf
Saddle Reaction Force due to Wind Fl or Friction [Fwl]:
= max( Fl, Friction Load, Sum of X Forces) * B / Ls
= max( 127.30 , 0.00 , 0 ) * 28.7500/189.5000
= 19.3 lbf
Load Combination Results for Q + Wind or Seismic [Q]:
= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 6232 + Max( 19 , 972 , 0 , 0 )
= 7203.3 lbf
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
Summary of Loads at the base of this Saddle:
Vertical Load (including saddle weight) 7526.07 lbf
Transverse Shear Load Saddle 426.49 lbf
Longitudinal Shear Load Saddle 127.30 lbf
Formulas and Substitutions for Horizontal Vessel Analysis:
Note: Wear Plate is Welded to the Shell, k = 0.1
The Computed K values from Table 4.15.1:
K1 = 0.1082 K2 = 1.1544 K3 = 0.8626 K4 = 0.3969
K5 = 0.7565 K6 = 0.0520 K7 = 0.0520 K8 = 0.3395
K9 = 0.2696 K10 = 0.0574 K1* = 0.1950
Note: Dimension a is greater than or equal to Rm / 2.
Moment per Equation 4.15.3 [M1]:
= -Q*a [1 - (1- a/L + (R2-h22)/(2a*L))/(1+(4h2)/3L)]
= -7203*56.75[1-(1-56.75/231.50+(21.7502-0.0002)/
(2*56.75*231.50))/(1+(4*0.00)/(3*231.50))]
= -92849.8 in-lb
Moment per Equation 4.15.4 [M2]:
= Q*L/4(1+2(R2-h22)/(L2))/(1+(4h2)/( 3L))-4a/L
= 7203*231.5/4(1+2(21.7502-0.0002)/(231.502))/(1+(4*0.000)/
(3*231.500))-4*56.75/231.50
= 15463.5 in-lb
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]:
= P * Rm/(2t) - M2/(pi*Rm2t)
= 75.000 * 21.750/(2*0.500 ) - 15463.5/(pi*21.82*0.500 )
= 1610.44 psi
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:
= P * Rm/(2t) + M2/(pi * Rm2 * t)
= 75.000 * 21.750/(2 * 0.500 ) + 15463.5/(pi * 21.82 * 0.500 )
= 1652.06 psi
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:
= P * Rm/(2t) - M1/(K1*pi*Rm2t)
= 75.000*21.750/(2*0.500)--92849.8/(0.1082*pi*21.82*0.500)
= 2786.08 psi
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]:
= P * Rm/(2t) + M1/(K1* * pi * Rm2 * t)
= 75.000*21.750/(2*0.500)+-92849.8/(0.1950*pi*21.82*0.500)
= 990.44 psi
Maximum Shear Force in the Saddle (4.15.5) [T]:
= Q(L-2a)/(L+(4*h2/3))
= 7203 ( 231.50 - 2 * 56.75 )/(231.50 + ( 4 * 0.00/3))
= 3671.6 lbf
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:
= K2 * T / ( Rm * t )
= 1.1544 * 3671.64/( 21.7500 * 0.5000 )
= 389.76 psi
Decay Length (4.15.22) [x1,x2]:
= 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 21.750 * 0.500 )
= 2.572 in
Circumferential Stress in shell, no rings (4.15.23) [sigma6]:
= -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7565 * 7203 * 0.1/( 0.500 * ( 8.00 + 2.57 + 2.57 ) )
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
= -82.92 psi
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]:
= -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t2)
= -7203/(4*0.500 *(8.000 +2.572 +2.572 )) -
3*0.0520 *7203/(2*0.5002)
= -2522.15 psi
Effective reinforcing plate width (4.15.1) [B1]:
= min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 8.00 + 1.56 * sqrt( 21.750 * 0.500 ), 2 * 56.750 )
= 13.14 in
Free Un-Restrained Thermal Expansion between the Saddles [Exp]:
= Alpha * Ls * ( Design Temperature - Ambient Temperature )
= 0.890E-05 * 189.500 * ( 200.0 - 70.0 )
= 0.219 in
Results for Vessel Ribs, Web and Base:
Baseplate Length Bplen 40.0000 in
Baseplate Thickness Bpthk 0.7500 in
Baseplate Width Bpwid 8.0000 in
Number of Ribs ( inc. outside ribs ) Nribs 4
Rib Thickness Ribtk 0.5000 in
Web Thickness Webtk 0.5000 in
Web Location Webloc Side
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 0. 8. 2. 1.
Wearplate 1. 5. 4. 3.
Web 6. 5. 31. 237.
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
BasePlate 12. 6. 70. 811.
Totals 19. 24. 107. 1052.
Value C1 = Sumof(Ay)/Sumof(A) = 5. in
Value I = Sumof(Io) - C1*Sumof(Ay) = 570. in**4
Value As = Sumof(A) - Ashell = 16. in^2
K1 = (1+Cos(beta)-.5*Sin(beta)2 )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2053
Fh = K1 * Q = 0.2053 * 7203.254 = 1479.1028 lbf
Tension Stress, St = ( Fh/As ) = 91.7273 psi
Allowed Stress, Sa = 0.6 * Yield Str = 15000.0010 psi
d = B - R*Sin(theta) / theta = 15.7784 in
Bending Moment, M = Fh * d = 23337.9023 in-lb
Bending Stress, Sb = ( M * C1 / I ) = 184.4929 psi
Allowed Stress, Sa = 2/3 * Yield Str = 16666.6680 psi
Minimum Thickness of Baseplate per Moss :
= ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 2 * BasePlateLength *
AllStress )).5
= ( 3 * (7203 + 323 ) * 8.00/( 2 * 40.000 * 16666.668 )).5
= 0.368 in
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]:
= ( Bplen - Clearance ) / ( Nribs - 1)
= ( 40.0000 - 1.0 )/( 4 - 1 ) = 13.0000 in
Baseplate Pressure Area [Ap]:
B-19-1191R 76
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
= e * Bpwid / 2
= 13.0000 * 8.0000/2 = 52.0000 in^2
Axial Load [P]:
= Ap * Bp
= 52.0 * 22.51 = 1170.5 lbf
Area of the Rib and Web [Ar]:
= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 8.000 - 1.0 - 0.500 ) * 0.500 + 13.0000/2 * 0.500
= 6.500 in^2
Compressive Stress [Sc]:
= P/Ar
= 1170.5/6.5000 = 180.0814 psi
Check of Outside Ribs:
Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay2 Io
Rib 3.8 3.5 13.1 9.9 17.6
Web 0.2 3.2 0.8 10.7 0.1
Values 2.1 6.8 13.9 20.6 17.7
Bending Moment [Rm]:
= Fl /( 2 * Bplen ) * e * rl / 2
= 127.3/( 2 * 40.00 ) * 13.000 * 22.67/2
= 234.443 in-lb
KL/R < Cc ( 9.3309 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)2/(2*Cc2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr3)/(8*Cc3)
Sca = ( 1-( 9.33 )2/(2 * 151.322 )) * 25000/
( 5/3+3*(9.33 )/(8* 151.32 )-( 9.333)/(8*151.323)
Sca = 14766.86 psi
B-19-1191R 77
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
AISC Unity Check on Outside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 180.08/14766.86 + (234.44/7.772 )/16666.67
Check = 0.01
Check of Inside Ribs
Inertia of Saddle, Inner Ribs - Axial Direction
Y A AY Ay2 Io
Rib 3.8 3.2 12.2 17.7 14.3
Web 0.2 6.5 1.6 8.8 0.1
Values 1.4 9.8 13.8 26.5 14.4
KL/R < Cc ( 5.8342 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)2/(2*Cc2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr3)/(8*Cc3)
Sca = ( 1-( 5.83 )2/(2 * 151.322 )) * 25000/
( 5/3+3*(5.83 )/(8* 151.32 )-( 5.833)/(8*151.323)
Sca = 14860.00 psi
AISC Unity Check on Inside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 240.11/14860.00 + ( 247.39/11.705 )/16666.67
Check = 0.02
ASME Horizontal Vessel Analysis: Stresses for the Right Saddle
(per ASME Sec. VIII Div. 2 based on the Zick method.)
Note:
Wear Pad Bearing angle is less than saddle angle + saddle/12
degrees. The wear plate will be ignored.
B-19-1191R 78
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
Minimum Wear Plate Angle [theta1]:
= 133.0 degrees
Note:
Wear Pad Width (0.00) is less than 1.56*sqrt(rm*t)
and less than 2a. The wear plate will be ignored.
Minimum Wear Plate Width to be considered in analysis [b1]:
= min( b + 1.56*sqrt( Rm * t ), 2a )
= min( 8.000 + 1.56*sqrt( 21.7500 * 0.5000 ), 2 * 56.750 )
= 13.1445 in
Input and Calculated Values:
Vessel Mean Radius Rm 21.75 in
Stiffened Vessel Length per 4.15.6 L 231.50 in
Distance from Saddle to Vessel tangent a 56.75 in
Saddle Width b 8.00 in
Saddle Bearing Angle theta 121.00 degrees
Shell Allowable Stress used in Calculation 15600.00 psi
Head Allowable Stress used in Calculation 16675.00 psi
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
Saddle Force Q, Operating Case 7241.28 lbf
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 1610.33 15600.00 psi
Long. Stress at Bottom of Midspan 1652.17 15600.00 psi
Long. Stress at Top of Saddles 2792.18 15600.00 psi
B-19-1191R 79
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
Long. Stress at Bottom of Saddles 987.06 15600.00 psi
Tangential Shear in Shell 391.82 9360.00 psi
Circ. Stress at Horn of Saddle 2535.46 19500.00 psi
Circ. Compressive Stress in Shell 83.35 15600.00 psi
Intermediate Results: Saddle Reaction Q due to Wind or Seismic
Saddle Reaction Force due to Wind Ft [Fwt]:
= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 853.0/2 + 0 ) * 28.7500/37.8605
= 971.6 lbf
Saddle Reaction Force due to Wind Fl or Friction [Fwl]:
= max( Fl, Friction Load, Sum of X Forces) * B / Ls
= max( 127.30 , 0.00 , 0 ) * 28.7500/189.5000
= 19.3 lbf
Load Combination Results for Q + Wind or Seismic [Q]:
= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 6270 + Max( 19 , 972 , 0 , 0 )
= 7241.3 lbf
Summary of Loads at the base of this Saddle:
Vertical Load (including saddle weight) 7564.09 lbf
Transverse Shear Load Saddle 426.49 lbf
Longitudinal Shear Load Saddle 127.30 lbf
Formulas and Substitutions for Horizontal Vessel Analysis:
Note: Wear Plate is Welded to the Shell, k = 0.1
The Computed K values from Table 4.15.1:
B-19-1191R 80
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
K1 = 0.1082 K2 = 1.1544 K3 = 0.8626 K4 = 0.3969
K5 = 0.7565 K6 = 0.0520 K7 = 0.0520 K8 = 0.3395
K9 = 0.2696 K10 = 0.0574 K1* = 0.1950
Note: Dimension a is greater than or equal to Rm / 2.
Moment per Equation 4.15.3 [M1]:
= -Q*a [1 - (1- a/L + (R2-h22)/(2a*L))/(1+(4h2)/3L)]
= -7241*56.75[1-(1-56.75/231.50+(21.7502-0.0002)/
(2*56.75*231.50))/(1+(4*0.00)/(3*231.50))]
= -93339.9 in-lb
Moment per Equation 4.15.4 [M2]:
= Q*L/4(1+2(R2-h22)/(L2))/(1+(4h2)/( 3L))-4a/L
= 7241*231.5/4(1+2(21.7502-0.0002)/(231.502))/(1+(4*0.000)/
(3*231.500))-4*56.75/231.50
= 15545.1 in-lb
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]:
= P * Rm/(2t) - M2/(pi*Rm2t)
= 75.000 * 21.750/(2*0.500 ) - 15545.1/(pi*21.82*0.500 )
= 1610.33 psi
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:
= P * Rm/(2t) + M2/(pi * Rm2 * t)
= 75.000 * 21.750/(2 * 0.500 ) + 15545.1/(pi * 21.82 * 0.500 )
= 1652.17 psi
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:
= P * Rm/(2t) - M1/(K1*pi*Rm2t)
= 75.000*21.750/(2*0.500)--93339.9/(0.1082*pi*21.82*0.500)
= 2792.18 psi
B-19-1191R 81
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]:
= P * Rm/(2t) + M1/(K1* * pi * Rm2 * t)
= 75.000*21.750/(2*0.500)+-93339.9/(0.1950*pi*21.82*0.500)
= 987.06 psi
Maximum Shear Force in the Saddle (4.15.5) [T]:
= Q(L-2a)/(L+(4*h2/3))
= 7241 ( 231.50 - 2 * 56.75 )/(231.50 + ( 4 * 0.00/3))
= 3691.0 lbf
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:
= K2 * T / ( Rm * t )
= 1.1544 * 3691.02/( 21.7500 * 0.5000 )
= 391.82 psi
Decay Length (4.15.22) [x1,x2]:
= 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 21.750 * 0.500 )
= 2.572 in
Circumferential Stress in shell, no rings (4.15.23) [sigma6]:
= -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7565 * 7241 * 0.1/( 0.500 * ( 8.00 + 2.57 + 2.57 ) )
= -83.35 psi
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]:
= -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t2)
= -7241/(4*0.500 *(8.000 +2.572 +2.572 )) -
3*0.0520 *7241/(2*0.5002)
= -2535.46 psi
Effective reinforcing plate width (4.15.1) [B1]:
= min( b + 1.56 * sqrt( Rm * t ), 2a )
B-19-1191R 82
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
= min( 8.00 + 1.56 * sqrt( 21.750 * 0.500 ), 2 * 56.750 )
= 13.14 in
Results for Vessel Ribs, Web and Base
Baseplate Length Bplen 40.0000 in
Baseplate Thickness Bpthk 0.7500 in
Baseplate Width Bpwid 8.0000 in
Number of Ribs ( inc. outside ribs ) Nribs 4
Rib Thickness Ribtk 0.5000 in
Web Thickness Webtk 0.5000 in
Web Location Webloc Side
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 0. 8. 2. 1.
Wearplate 1. 5. 4. 3.
Web 6. 5. 31. 237.
BasePlate 12. 6. 70. 811.
Totals 19. 24. 107. 1052.
Value C1 = Sumof(Ay)/Sumof(A) = 5. in
Value I = Sumof(Io) - C1*Sumof(Ay) = 570. in**4
Value As = Sumof(A) - Ashell = 16. in^2
K1 = (1+Cos(beta)-.5*Sin(beta)2 )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2053
Fh = K1 * Q = 0.2053 * 7241.278 = 1486.9105 lbf
Tension Stress, St = ( Fh/As ) = 92.2115 psi
Allowed Stress, Sa = 0.6 * Yield Str = 15000.0010 psi
B-19-1191R 83
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
d = B - R*Sin(theta) / theta = 15.7784 in
Bending Moment, M = Fh * d = 23461.0957 in-lb
Bending Stress, Sb = ( M * C1 / I ) = 185.4667 psi
Allowed Stress, Sa = 2/3 * Yield Str = 16666.6680 psi
Minimum Thickness of Baseplate per Moss :
= ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 2 * BasePlateLength *
AllStress )).5
= ( 3 * (7241 + 323 ) * 8.00/( 2 * 40.000 * 16666.668 )).5
= 0.369 in
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]:
= ( Bplen - Clearance ) / ( Nribs - 1)
= ( 40.0000 - 1.0 )/( 4 - 1 ) = 13.0000 in
Baseplate Pressure Area [Ap]:
= e * Bpwid / 2
= 13.0000 * 8.0000/2 = 52.0000 in^2
Axial Load [P]:
= Ap * Bp
= 52.0 * 22.63 = 1176.7 lbf
Area of the Rib and Web [Ar]:
= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 8.000 - 1.0 - 0.500 ) * 0.500 + 13.0000/2 * 0.500
= 6.500 in^2
Compressive Stress [Sc]:
= P/Ar
B-19-1191R 84
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Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
= 1176.7/6.5000 = 181.0320 psi
Check of Outside Ribs:
Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay2 Io
Rib 3.8 3.5 13.1 9.9 17.6
Web 0.2 3.2 0.8 10.7 0.1
Values 2.1 6.8 13.9 20.6 17.7
Bending Moment [Rm]:
= Fl /( 2 * Bplen ) * e * rl / 2
= 127.3/( 2 * 40.00 ) * 13.000 * 22.67/2
= 234.443 in-lb
KL/R < Cc ( 9.3309 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)2/(2*Cc2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr3)/(8*Cc3)
Sca = ( 1-( 9.33 )2/(2 * 151.322 )) * 25000/
( 5/3+3*(9.33 )/(8* 151.32 )-( 9.333)/(8*151.323)
Sca = 14766.86 psi
AISC Unity Check on Outside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 181.03/14766.86 + (234.44/7.772 )/16666.67
Check = 0.01
Check of Inside Ribs
Inertia of Saddle, Inner Ribs - Axial Direction
Y A AY Ay2 Io
Rib 3.8 3.2 12.2 17.7 14.3
Web 0.2 6.5 1.6 8.8 0.1
Values 1.4 9.8 13.8 26.5 14.4
B-19-1191R 85
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Ope.) : Step: 14 9:18am Jul 31,2019
KL/R < Cc ( 5.8342 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)2/(2*Cc2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr3)/(8*Cc3)
Sca = ( 1-( 5.83 )2/(2 * 151.322 )) * 25000/
( 5/3+3*(5.83 )/(8* 151.32 )-( 5.833)/(8*151.323)
Sca = 14860.00 psi
AISC Unity Check on Inside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 241.38/14860.00 + ( 247.39/11.705 )/16666.67
Check = 0.02
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 86
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
ASME Horizontal Vessel Analysis: Stresses for the Left Saddle
(per ASME Sec. VIII Div. 2 based on the Zick method.)
Horizontal Vessel Stress Calculations : Test Case
Note:
Wear Pad Bearing angle is less than saddle angle + saddle/12
degrees. The wear plate will be ignored.
Minimum Wear Plate Angle [theta1]:
= 133.0 degrees
Note:
Wear Pad Width (0.00) is less than 1.56*sqrt(rm*t)
and less than 2a. The wear plate will be ignored.
Minimum Wear Plate Width to be considered in analysis [b1]:
= min( b + 1.56*sqrt( Rm * t ), 2a )
= min( 8.000 + 1.56*sqrt( 21.7500 * 0.5000 ), 2 * 56.750 )
= 13.1445 in
Input and Calculated Values:
Vessel Mean Radius Rm 21.75 in
Stiffened Vessel Length per 4.15.6 L 231.50 in
Distance from Saddle to Vessel tangent a 56.75 in
Saddle Width b 8.00 in
Saddle Bearing Angle theta 121.00 degrees
Shell Allowable Stress used in Calculation 23750.00 psi
Head Allowable Stress used in Calculation 23750.00 psi
B-19-1191R 87
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
Saddle Force Q, Test Case, no Ext. Forces 14962.55 lbf
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 2431.61 23750.00 psi
Long. Stress at Bottom of Midspan 2518.06 23750.00 psi
Long. Stress at Top of Saddles 4873.65 23750.00 psi
Long. Stress at Bottom of Saddles 1143.75 23750.00 psi
Tangential Shear in Shell 809.61 14250.00 psi
Circ. Stress at Horn of Saddle 5238.99 35625.00 psi
Circ. Compressive Stress in Shell 172.23 23750.00 psi
Intermediate Results: Saddle Reaction Q due to Wind or Seismic
Saddle Reaction Force due to Wind Ft [Fwt]:
= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 281.5/2 + 0 ) * 28.7500/37.8605
= 320.6 lbf
Saddle Reaction Force due to Wind Fl or Friction [Fwl]:
= max( Fl, Friction Load, Sum of X Forces) * B / Ls
= max( 42.01 , 0.00 , 0 ) * 28.7500/189.5000
= 6.4 lbf
Load Combination Results for Q + Wind or Seismic [Q]:
= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 14642 + Max( 6 , 321 , 0 , 0 )
= 14962.6 lbf
B-19-1191R 88
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Summary of Loads at the base of this Saddle:
Vertical Load (including saddle weight) 15285.37 lbf
Transverse Shear Load Saddle 140.74 lbf
Longitudinal Shear Load Saddle 42.01 lbf
Hydrostatic Test Pressure at center of Vessel: 113.785 psig
Formulas and Substitutions for Horizontal Vessel Analysis:
Note: Wear Plate is Welded to the Shell, k = 0.1
The Computed K values from Table 4.15.1:
K1 = 0.1082 K2 = 1.1544 K3 = 0.8626 K4 = 0.3969
K5 = 0.7565 K6 = 0.0520 K7 = 0.0520 K8 = 0.3395
K9 = 0.2696 K10 = 0.0574 K1* = 0.1950
Note: Dimension a is greater than or equal to Rm / 2.
Moment per Equation 4.15.3 [M1]:
= -Q*a [1 - (1- a/L + (R2-h22)/(2a*L))/(1+(4h2)/3L)]
= -14963*56.75[1-(1-56.75/231.50+(21.7502-0.0002)/
(2*56.75*231.50))/(1+(4*0.00)/(3*231.50))]
= -192867.0 in-lb
Moment per Equation 4.15.4 [M2]:
= Q*L/4(1+2(R2-h22)/(L2))/(1+(4h2)/( 3L))-4a/L
= 14963*231.5/4(1+2(21.7502-0.0002)/(231.502))/(1+(4*0.000)/
(3*231.500))-4*56.75/231.50
= 32120.6 in-lb
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]:
= P * Rm/(2t) - M2/(pi*Rm2t)
= 113.785 * 21.750/(2*0.500 ) - 32120.6/(pi*21.82*0.500 )
B-19-1191R 89
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
= 2431.61 psi
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:
= P * Rm/(2t) + M2/(pi * Rm2 * t)
= 113.785 * 21.750/(2 * 0.500 ) + 32120.6/(pi * 21.82 * 0.500 )
= 2518.06 psi
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:
= P * Rm/(2t) - M1/(K1*pi*Rm2t)
= 113.785*21.750/(2*0.500)--192867.0/(0.1082*pi*21.82*0.500)
= 4873.65 psi
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]:
= P * Rm/(2t) + M1/(K1* * pi * Rm2 * t)
= 113.785*21.750/(2*0.500)+-192867.0/(0.1950*pi*21.82*0.500)
= 1143.75 psi
Maximum Shear Force in the Saddle (4.15.5) [T]:
= Q(L-2a)/(L+(4*h2/3))
= 14963 ( 231.50 - 2 * 56.75 )/(231.50 + ( 4 * 0.00/3))
= 7626.7 lbf
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:
= K2 * T / ( Rm * t )
= 1.1544 * 7626.70/( 21.7500 * 0.5000 )
= 809.61 psi
Decay Length (4.15.22) [x1,x2]:
= 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 21.750 * 0.500 )
= 2.572 in
Circumferential Stress in shell, no rings (4.15.23) [sigma6]:
B-19-1191R 90
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
= -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7565 * 14963 * 0.1/( 0.500 * ( 8.00 + 2.57 + 2.57 ) )
= -172.23 psi
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]:
= -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t2)
= -14963/(4*0.500 *(8.000 +2.572 +2.572 )) -
3*0.0520 *14963/(2*0.5002)
= -5238.99 psi
Effective reinforcing plate width (4.15.1) [B1]:
= min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 8.00 + 1.56 * sqrt( 21.750 * 0.500 ), 2 * 56.750 )
= 13.14 in
Results for Vessel Ribs, Web and Base:
Baseplate Length Bplen 40.0000 in
Baseplate Thickness Bpthk 0.7500 in
Baseplate Width Bpwid 8.0000 in
Number of Ribs ( inc. outside ribs ) Nribs 4
Rib Thickness Ribtk 0.5000 in
Web Thickness Webtk 0.5000 in
Web Location Webloc Side
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 0. 8. 2. 1.
Wearplate 1. 5. 4. 3.
Web 6. 5. 31. 237.
BasePlate 12. 6. 70. 811.
Totals 19. 24. 107. 1052.
B-19-1191R 91
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Value C1 = Sumof(Ay)/Sumof(A) = 5. in
Value I = Sumof(Io) - C1*Sumof(Ay) = 570. in**4
Value As = Sumof(A) - Ashell = 16. in^2
K1 = (1+Cos(beta)-.5*Sin(beta)2 )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2053
Fh = K1 * Q = 0.2053 * 14962.553 = 3072.3826 lbf
Tension Stress, St = ( Fh/As ) = 190.5354 psi
Allowed Stress, Sa = 0.6 * Yield Str = 15000.0010 psi
d = B - R*Sin(theta) / theta = 15.7784 in
Bending Moment, M = Fh * d = 48477.3359 in-lb
Bending Stress, Sb = ( M * C1 / I ) = 383.2274 psi
Allowed Stress, Sa = 2/3 * Yield Str = 16666.6680 psi
Minimum Thickness of Baseplate per Moss :
= ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 2 * BasePlateLength *
AllStress )).5
= ( 3 * (14963 + 323 ) * 8.00/( 2 * 40.000 * 16666.668 )).5
= 0.525 in
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]:
= ( Bplen - Clearance ) / ( Nribs - 1)
= ( 40.0000 - 1.0 )/( 4 - 1 ) = 13.0000 in
Baseplate Pressure Area [Ap]:
= e * Bpwid / 2
= 13.0000 * 8.0000/2 = 52.0000 in^2
B-19-1191R 92
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Axial Load [P]:
= Ap * Bp
= 52.0 * 46.76 = 2431.4 lbf
Area of the Rib and Web [Ar]:
= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 8.000 - 1.0 - 0.500 ) * 0.500 + 13.0000/2 * 0.500
= 6.500 in^2
Compressive Stress [Sc]:
= P/Ar
= 2431.4/6.5000 = 374.0638 psi
Check of Outside Ribs:
Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay2 Io
Rib 3.8 3.5 13.1 9.9 17.6
Web 0.2 3.2 0.8 10.7 0.1
Values 2.1 6.8 13.9 20.6 17.7
Bending Moment [Rm]:
= Fl /( 2 * Bplen ) * e * rl / 2
= 42.0/( 2 * 40.00 ) * 13.000 * 22.67/2
= 77.366 in-lb
KL/R < Cc ( 9.3309 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)2/(2*Cc2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr3)/(8*Cc3)
Sca = ( 1-( 9.33 )2/(2 * 151.322 )) * 25000/
( 5/3+3*(9.33 )/(8* 151.32 )-( 9.333)/(8*151.323)
Sca = 14766.86 psi
AISC Unity Check on Outside Ribs ( must be <= 1.0 )
B-19-1191R 93
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Check = Sc/Sca + (Rm/Z)/Sba
Check = 374.06/14766.86 + (77.37/7.772 )/16666.67
Check = 0.03
Check of Inside Ribs
Inertia of Saddle, Inner Ribs - Axial Direction
Y A AY Ay2 Io
Rib 3.8 3.2 12.2 17.7 14.3
Web 0.2 6.5 1.6 8.8 0.1
Values 1.4 9.8 13.8 26.5 14.4
KL/R < Cc ( 5.8342 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)2/(2*Cc2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr3)/(8*Cc3)
Sca = ( 1-( 5.83 )2/(2 * 151.322 )) * 25000/
( 5/3+3*(5.83 )/(8* 151.32 )-( 5.833)/(8*151.323)
Sca = 14860.00 psi
AISC Unity Check on Inside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 498.75/14860.00 + ( 81.64/11.705 )/16666.67
Check = 0.03
ASME Horizontal Vessel Analysis: Stresses for the Right Saddle
(per ASME Sec. VIII Div. 2 based on the Zick method.)
Note:
Wear Pad Bearing angle is less than saddle angle + saddle/12
degrees. The wear plate will be ignored.
Minimum Wear Plate Angle [theta1]:
= 133.0 degrees
B-19-1191R 94
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Note:
Wear Pad Width (0.00) is less than 1.56*sqrt(rm*t)
and less than 2a. The wear plate will be ignored.
Minimum Wear Plate Width to be considered in analysis [b1]:
= min( b + 1.56*sqrt( Rm * t ), 2a )
= min( 8.000 + 1.56*sqrt( 21.7500 * 0.5000 ), 2 * 56.750 )
= 13.1445 in
Input and Calculated Values:
Vessel Mean Radius Rm 21.75 in
Stiffened Vessel Length per 4.15.6 L 231.50 in
Distance from Saddle to Vessel tangent a 56.75 in
Saddle Width b 8.00 in
Saddle Bearing Angle theta 121.00 degrees
Shell Allowable Stress used in Calculation 23750.00 psi
Head Allowable Stress used in Calculation 23750.00 psi
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
Saddle Force Q, Test Case, no Ext. Forces 14841.83 lbf
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 2431.96 23750.00 psi
Long. Stress at Bottom of Midspan 2517.71 23750.00 psi
Long. Stress at Top of Saddles 4854.29 23750.00 psi
Long. Stress at Bottom of Saddles 1154.49 23750.00 psi
Tangential Shear in Shell 803.08 14250.00 psi
B-19-1191R 95
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Circ. Stress at Horn of Saddle 5196.72 35625.00 psi
Circ. Compressive Stress in Shell 170.84 23750.00 psi
Intermediate Results: Saddle Reaction Q due to Wind or Seismic
Saddle Reaction Force due to Wind Ft [Fwt]:
= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 281.5/2 + 0 ) * 28.7500/37.8605
= 320.6 lbf
Saddle Reaction Force due to Wind Fl or Friction [Fwl]:
= max( Fl, Friction Load, Sum of X Forces) * B / Ls
= max( 42.01 , 0.00 , 0 ) * 28.7500/189.5000
= 6.4 lbf
Load Combination Results for Q + Wind or Seismic [Q]:
= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 14521 + Max( 6 , 321 , 0 , 0 )
= 14841.8 lbf
Summary of Loads at the base of this Saddle:
Vertical Load (including saddle weight) 15164.64 lbf
Transverse Shear Load Saddle 140.74 lbf
Longitudinal Shear Load Saddle 42.01 lbf
Hydrostatic Test Pressure at center of Vessel: 113.785 psig
Formulas and Substitutions for Horizontal Vessel Analysis:
Note: Wear Plate is Welded to the Shell, k = 0.1
The Computed K values from Table 4.15.1:
K1 = 0.1082 K2 = 1.1544 K3 = 0.8626 K4 = 0.3969
B-19-1191R 96
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
K5 = 0.7565 K6 = 0.0520 K7 = 0.0520 K8 = 0.3395
K9 = 0.2696 K10 = 0.0574 K1* = 0.1950
Note: Dimension a is greater than or equal to Rm / 2.
Moment per Equation 4.15.3 [M1]:
= -Q*a [1 - (1- a/L + (R2-h22)/(2a*L))/(1+(4h2)/3L)]
= -14842*56.75[1-(1-56.75/231.50+(21.7502-0.0002)/
(2*56.75*231.50))/(1+(4*0.00)/(3*231.50))]
= -191310.9 in-lb
Moment per Equation 4.15.4 [M2]:
= Q*L/4(1+2(R2-h22)/(L2))/(1+(4h2)/( 3L))-4a/L
= 14842*231.5/4(1+2(21.7502-0.0002)/(231.502))/(1+(4*0.000)/
(3*231.500))-4*56.75/231.50
= 31861.5 in-lb
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]:
= P * Rm/(2t) - M2/(pi*Rm2t)
= 113.785 * 21.750/(2*0.500 ) - 31861.5/(pi*21.82*0.500 )
= 2431.96 psi
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:
= P * Rm/(2t) + M2/(pi * Rm2 * t)
= 113.785 * 21.750/(2 * 0.500 ) + 31861.5/(pi * 21.82 * 0.500 )
= 2517.71 psi
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:
= P * Rm/(2t) - M1/(K1*pi*Rm2t)
= 113.785*21.750/(2*0.500)--191310.9/(0.1082*pi*21.82*0.500)
= 4854.29 psi
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]:
B-19-1191R 97
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
= P * Rm/(2t) + M1/(K1* * pi * Rm2 * t)
= 113.785*21.750/(2*0.500)+-191310.9/(0.1950*pi*21.82*0.500)
= 1154.49 psi
Maximum Shear Force in the Saddle (4.15.5) [T]:
= Q(L-2a)/(L+(4*h2/3))
= 14842 ( 231.50 - 2 * 56.75 )/(231.50 + ( 4 * 0.00/3))
= 7565.2 lbf
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:
= K2 * T / ( Rm * t )
= 1.1544 * 7565.16/( 21.7500 * 0.5000 )
= 803.08 psi
Decay Length (4.15.22) [x1,x2]:
= 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 21.750 * 0.500 )
= 2.572 in
Circumferential Stress in shell, no rings (4.15.23) [sigma6]:
= -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7565 * 14842 * 0.1/( 0.500 * ( 8.00 + 2.57 + 2.57 ) )
= -170.84 psi
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]:
= -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t2)
= -14842/(4*0.500 *(8.000 +2.572 +2.572 )) -
3*0.0520 *14842/(2*0.5002)
= -5196.72 psi
Effective reinforcing plate width (4.15.1) [B1]:
= min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 8.00 + 1.56 * sqrt( 21.750 * 0.500 ), 2 * 56.750 )
B-19-1191R 98
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
= 13.14 in
Results for Vessel Ribs, Web and Base
Baseplate Length Bplen 40.0000 in
Baseplate Thickness Bpthk 0.7500 in
Baseplate Width Bpwid 8.0000 in
Number of Ribs ( inc. outside ribs ) Nribs 4
Rib Thickness Ribtk 0.5000 in
Web Thickness Webtk 0.5000 in
Web Location Webloc Side
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 0. 8. 2. 1.
Wearplate 1. 5. 4. 3.
Web 6. 5. 31. 237.
BasePlate 12. 6. 70. 811.
Totals 19. 24. 107. 1052.
Value C1 = Sumof(Ay)/Sumof(A) = 5. in
Value I = Sumof(Io) - C1*Sumof(Ay) = 570. in**4
Value As = Sumof(A) - Ashell = 16. in^2
K1 = (1+Cos(beta)-.5*Sin(beta)2 )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2053
Fh = K1 * Q = 0.2053 * 14841.828 = 3047.5933 lbf
Tension Stress, St = ( Fh/As ) = 188.9980 psi
Allowed Stress, Sa = 0.6 * Yield Str = 15000.0010 psi
d = B - R*Sin(theta) / theta = 15.7784 in
B-19-1191R 99
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FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Bending Moment, M = Fh * d = 48086.1992 in-lb
Bending Stress, Sb = ( M * C1 / I ) = 380.1353 psi
Allowed Stress, Sa = 2/3 * Yield Str = 16666.6680 psi
Minimum Thickness of Baseplate per Moss :
= ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 2 * BasePlateLength *
AllStress )).5
= ( 3 * (14842 + 323 ) * 8.00/( 2 * 40.000 * 16666.668 )).5
= 0.522 in
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]:
= ( Bplen - Clearance ) / ( Nribs - 1)
= ( 40.0000 - 1.0 )/( 4 - 1 ) = 13.0000 in
Baseplate Pressure Area [Ap]:
= e * Bpwid / 2
= 13.0000 * 8.0000/2 = 52.0000 in^2
Axial Load [P]:
= Ap * Bp
= 52.0 * 46.38 = 2411.8 lbf
Area of the Rib and Web [Ar]:
= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 8.000 - 1.0 - 0.500 ) * 0.500 + 13.0000/2 * 0.500
= 6.500 in^2
Compressive Stress [Sc]:
= P/Ar
= 2411.8/6.5000 = 371.0457 psi
B-19-1191R 100
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Check of Outside Ribs:
Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay2 Io
Rib 3.8 3.5 13.1 9.9 17.6
Web 0.2 3.2 0.8 10.7 0.1
Values 2.1 6.8 13.9 20.6 17.7
Bending Moment [Rm]:
= Fl /( 2 * Bplen ) * e * rl / 2
= 42.0/( 2 * 40.00 ) * 13.000 * 22.67/2
= 77.366 in-lb
KL/R < Cc ( 9.3309 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)2/(2*Cc2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr3)/(8*Cc3)
Sca = ( 1-( 9.33 )2/(2 * 151.322 )) * 25000/
( 5/3+3*(9.33 )/(8* 151.32 )-( 9.333)/(8*151.323)
Sca = 14766.86 psi
AISC Unity Check on Outside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 371.05/14766.86 + (77.37/7.772 )/16666.67
Check = 0.03
Check of Inside Ribs
Inertia of Saddle, Inner Ribs - Axial Direction
Y A AY Ay2 Io
Rib 3.8 3.2 12.2 17.7 14.3
Web 0.2 6.5 1.6 8.8 0.1
Values 1.4 9.8 13.8 26.5 14.4
KL/R < Cc ( 5.8342 < 151.3192 ) per AISC E2-1
B-19-1191R 101
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Horizontal Vessel Analysis (Test) : Step: 15 9:18am Jul 31,2019
Sca = (1-(Klr)2/(2*Cc2))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr3)/(8*Cc3)
Sca = ( 1-( 5.83 )2/(2 * 151.322 )) * 25000/
( 5/3+3*(5.83 )/(8* 151.32 )-( 5.833)/(8*151.323)
Sca = 14860.00 psi
AISC Unity Check on Inside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 494.73/14860.00 + ( 81.64/11.705 )/16666.67
Check = 0.03
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 102
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : D Nozl: 18 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: D From : 30
Pressure for Reinforcement Calculations P 80.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-240 304L
Shell Allowable Stress at Temperature Sv 15600.00 psi
Shell Allowable Stress At Ambient Sva 15600.00 psi
Inside Diameter of Cylindrical Shell D 43.0000 in
Shell Finished (Minimum) Thickness t 0.5000 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
Distance from Bottom/Left Tangent 15.8750 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-312 TP304
Material UNS Number S30400
Material Specification/Type Wld. pipe
Allowable Stress at Temperature Sn 17911.76 psi
Allowable Stress At Ambient Sna 18823.53 psi
Note: The allowables above have been divided by 0.85, see UG-37 [S].
Diameter Basis (for tr calc only) OD
Layout Angle 270.00 deg
Diameter 1.7500 in.
B-19-1191R 103
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : D Nozl: 18 9:18am Jul 31,2019
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.5000 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: D
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
B-19-1191R 104
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : D Nozl: 18 9:18am Jul 31,2019
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (80.00*21.5000)/(15600*1.00-0.6*80.00)
= 0.1106 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-80.00/(17911.76*1.00)))
= 0.0039 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: D.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0039 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.1106 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.1106 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
B-19-1191R 105
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : D Nozl: 18 9:18am Jul 31,2019
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.1106 , 0.0625 ) ]
= 0.1106 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0039 , 0.1106 )
= 0.1106 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: D
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 250.459 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
B-19-1191R 106
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : D Nozl: 18 9:18am Jul 31,2019
The Drop for this Nozzle is : 0.0178 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 2.0178 in
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 107
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : CO-1 Nozl: 19 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: CO-1 From : 30
Pressure for Reinforcement Calculations P 80.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-240 304L
Shell Allowable Stress at Temperature Sv 15600.00 psi
Shell Allowable Stress At Ambient Sva 15600.00 psi
Inside Diameter of Cylindrical Shell D 43.0000 in
Shell Finished (Minimum) Thickness t 0.5000 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
Distance from Bottom/Left Tangent 15.8750 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-312 TP304L
Material UNS Number S30403
Material Specification/Type Smls. pipe
Allowable Stress at Temperature Sn 16400.00 psi
Allowable Stress At Ambient Sna 17500.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 90.00 deg
Diameter 12.0000 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
B-19-1191R 108
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : CO-1 Nozl: 19 9:18am Jul 31,2019
Flange Material SA-182 F304L
Flange Type Slip on
Corrosion Allowance can 0.0000 in
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 7.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
Class of attached Flange 150
Grade of attached Flange GR 2.3
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
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____________/| |
| \ | |
| \ | |
|____________\|__|
Insert/Set-in Nozzle No Pad, no Inside projection
B-19-1191R 109
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : CO-1 Nozl: 19 9:18am Jul 31,2019
Reinforcement CALCULATION, Description: CO-1
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 12.000 in.
Actual Thickness Used in Calculation 0.350 in.
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (80.00*21.5000)/(15600*1.00-0.6*80.00)
= 0.1106 in
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press]
= (P*Ro)/(Sn*E+0.4*P) per Appendix 1-1 (a)(1)
= (80.00*6.0000)/(16400*1.00+0.4*80.00)
= 0.0292 in
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0292 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.1106 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.1106 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.3280 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.328 , max( 0.1106 , 0.0625 ) ]
= 0.1106 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
B-19-1191R 110
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : CO-1 Nozl: 19 9:18am Jul 31,2019
= max( ta, tb )
= max( 0.0292 , 0.1106 )
= 0.1106 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
SA-312 TP304L, Min Metal Temp without impact per UHA-51: -320 F
Note:
The flange pressure ratio is less than 0.35. Impact testing in not
required due to low stress per UHA-51(g).
Design Pressure/Ambient Rating = 80.00/230.00 = 0.348
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]:
= thickness - corrosion allowance
= 0.350 - 0.000
= 0.350 in
Effective Pressure Radius [Reff]:
= Di/2 + corrosion allowance
= 43.000/2 + 0.000
= 21.500 in
Effective Length of Vessel Wall [LR]:
= 8 * t
= 8 * 0.500
= 4.000 in
B-19-1191R 111
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : CO-1 Nozl: 19 9:18am Jul 31,2019
Thickness Limit Candidate [LH1]:
= t + 0.78 * sqrt( Rn * tn )
= 0.500 + 0.78 * sqrt( 5.650 * 0.350 )
= 1.597 in
Thickness Limit Candidate [LH2]:
= Lpr1 + T
= 7.500 + 0.500
= 8.000 in
Thickness Limit Candidate [LH3]:
= 8( t + te )
= 8( 0.500 + 0.000 )
= 4.000 in
Effective Nozzle Wall Length Outside the Vessel [LH]:
= min[ LH1, LH2, LH3 ]
= min[ 1.597 , 8.000 , 4.000 )
= 1.597 in
Effective Vessel Thickness [teff]:
= t
= 0.500 in
Determine Parameter [Lamda]:
= min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (11.30 + 0.350 )/( sqrt((43.00 + 0.500 ) * 0.500 )) )
= 2.498
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]:
= t * LR * max( Lamda/4, 1 )
B-19-1191R 112
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FileName : HEAT EXCHANGER
Nozzle Calcs. : CO-1 Nozl: 19 9:18am Jul 31,2019
= 0.500 * 4.000 * max( 2.498/4, 1 )
= 2.000 in^2
Area Contributed by the Nozzle Outside the Vessel Wall [A2]:
= tn * LH
= 0.350 * 1.597
= 0.559 in^2
Area Contributed by the Outside Fillet Weld [A41]:
= 0.5 * Leg412
= 0.5 * 0.3752
= 0.070 in^2
The total area contributed by A1 through A43 [AT]:
= A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 2.000+1.000(0.559+0.000)+0.070+0.000+0.000
= 2.629 in^2
Allowable Local Primary Membrane Stress [Sallow]:
= 1.5 * S * E
= 1.5 * 15600.000 * 1.000
= 23400.0 psi
Determine Force acting on the Nozzle [fN]:
= P * Rn( LH - t )
= 80.000 * 5.650 ( 1.597 - 0.500 )
= 495.8 lbf
Determine Force acting on the Shell [fS]:
= P * Reff( LR + tn )
= 80.000 * 21.500 ( 4.000 + 0.350 )
= 7482.0 lbf
B-19-1191R 113
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : CO-1 Nozl: 19 9:18am Jul 31,2019
Discontinuity Force from Internal Pressure [fY]:
= P * Reff * Rnc
= 80.000 * 21.500 * 5.650
= 9718.0 lbf
Area Resisting Internal Pressure [Ap]:
= Rn( LH - t ) + Reff( LR + tn + Rnc )
= 5.650 ( 1.597 - 0.500 ) + 21.500 ( 4.000 + 0.350 + 5.650 )
= 221.2 in^2
Maximum Allowable Working Pressure Candidate [Pmax1]:
= Sallow /( 2 * Ap/AT - Rxs/teff )
= 23400.000/( 2 * 221.197/2.629 - 21.500/0.500 )
= 186.8 psig
Maximum Allowable Working Pressure Candidate [Pmax2]:
= S[t/Reff]
= 15600.000 [0.500/21.500 ]
= 362.8 psig
Maximum Allowable Working Pressure [Pmax]:
= min( Pmax1, Pmax2 )
= min( 186.810 , 362.791 )
= 186.810 psig
Average Primary Membrane Stress [SigmaAvg]:
= ( fN + fS + fY ) / AT
= ( 495.783 + 7482.000 + 9718.000 )/2.629
= 6730.443 psi
General Primary Membrane Stress [SigmaCirc]:
= P * Reff / teff
= 80.000 * 21.500/0.500
B-19-1191R 114
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : CO-1 Nozl: 19 9:18am Jul 31,2019
= 3440.0 psi
Maximum Local Primary Membrane Stress [PL]:
= max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 6730.443 - 3440.000 , 3440.000 )
= 10020.9 psi
Summary of Nozzle Pressure/Stress Results:
Allowed Local Primary Membrane Stress Sallow 23400.00 psi
Local Primary Membrane Stress PL 10020.89 psi
Maximum Allowable Working Pressure Pmax 186.81 psig
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]:
= ( Rnc + tn ) / Rnc
= ( 5.650 + 0.350 )/5.650
= 1.062 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]:
= pi/2 * ( Rn + tn )
= pi/2 * ( 5.650 + 0.350 )
= 9.425 in
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]:
= 0.265, 0.000, 0.000, in
Weld Load Value [fwelds]:
= min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(9718*1.06,1.5*16400.0(0.559+0.000),pi/4*80.0*5.65^2*1.06^2)
= 2261.947 lbf
Weld Stress Value [tau]:
B-19-1191R 115
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : CO-1 Nozl: 19 9:18am Jul 31,2019
= fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 2261.947/(9.425 (0.49*0.265 + 0.6*0.375 + 0.49*0.000 ) )
= 676.190 < or = to 15600.000 Weld Size is OK
Weld Size Calculations, Description: CO-1
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 186.792 psig
The Drop for this Nozzle is : 0.8542 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 8.8542 in
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 116
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : P7 Nozl: 20 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P7 Parent : CO-1
Pressure for Reinforcement Calculations P 80.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304L
Shell Allowable Stress at Temperature Sv 16400.00 psi
Shell Allowable Stress At Ambient Sva 17500.00 psi
Inside Diameter of Cylindrical Shell D 11.3000 in
Shell Finished (Minimum) Thickness t 0.3500 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30400
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 16050.00 psi
Allowable Stress At Ambient Sna 16250.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 90.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
B-19-1191R 117
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : P7 Nozl: 20 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
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____________/| |
| \ | |
| \ | |
|____________\|__|
Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P7
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
B-19-1191R 118
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : P7 Nozl: 20 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (80.00*5.6500)/(16400*1.00-0.6*80.00)
= 0.0276 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-80.00/(16050.00*1.00)))
= 0.0044 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P7.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0044 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0276 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
B-19-1191R 119
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : P7 Nozl: 20 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0044 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304L, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P7
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 979.522 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0682 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9182 in
B-19-1191R 120
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P7 Nozl: 20 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P8 Nozl: 21 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P8 Parent : CO-1
Pressure for Reinforcement Calculations P 80.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304L
Shell Allowable Stress at Temperature Sv 16400.00 psi
Shell Allowable Stress At Ambient Sva 17500.00 psi
Inside Diameter of Cylindrical Shell D 11.3000 in
Shell Finished (Minimum) Thickness t 0.3500 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30400
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 16050.00 psi
Allowable Stress At Ambient Sna 16250.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 270.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
B-19-1191R 122
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P8 Nozl: 21 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P8
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P8 Nozl: 21 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (80.00*5.6500)/(16400*1.00-0.6*80.00)
= 0.0276 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-80.00/(16050.00*1.00)))
= 0.0044 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P8.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0044 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0276 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P8 Nozl: 21 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0044 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304L, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P8
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 979.522 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0682 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9182 in
B-19-1191R 125
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P8 Nozl: 21 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 126
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FileName : HEAT EXCHANGER
Nozzle Calcs. : SO-1 Nozl: 22 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: SO-1 From : 40
Pressure for Reinforcement Calculations P 75.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-240 304L
Shell Allowable Stress at Temperature Sv 15600.00 psi
Shell Allowable Stress At Ambient Sva 15600.00 psi
Inside Diameter of Cylindrical Shell D 43.0000 in
Shell Finished (Minimum) Thickness t 0.5000 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
Distance from Bottom/Left Tangent 150.5000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-312 TP304
Material UNS Number S30400
Material Specification/Type Wld. pipe
Allowable Stress at Temperature Sn 17911.76 psi
Allowable Stress At Ambient Sna 18823.53 psi
Note: The allowables above have been divided by 0.85, see UG-37 [S].
Diameter Basis (for tr calc only) ID
Layout Angle 270.00 deg
Diameter 18.0000 in.
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FileName : HEAT EXCHANGER
Nozzle Calcs. : SO-1 Nozl: 22 9:18am Jul 31,2019
Size and Thickness Basis Nominal
Nominal Thickness tn 40S
Flange Material SA-182 F304
Flange Type Slip on
Corrosion Allowance can 0.0000 in
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 7.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.5000 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
Class of attached Flange 150
Grade of attached Flange GR 2.1
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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B-19-1191R 128
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FileName : HEAT EXCHANGER
Nozzle Calcs. : SO-1 Nozl: 22 9:18am Jul 31,2019
Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: SO-1
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 17.250 in.
Actual Thickness Used in Calculation 0.375 in.
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (75.00*21.5000)/(15600*1.00-0.6*75.00)
= 0.1037 in
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press]
= (P*R)/(Sn*E-0.6*P) per UG-27 (c)(1)
= (75.00*8.62)/(17912*1.00-0.6*75.00)
= 0.0362 in
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0362 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.1037 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.1037 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.3280 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.328 , max( 0.1037 , 0.0625 ) ]
= 0.1037 in
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Nozzle Calcs. : SO-1 Nozl: 22 9:18am Jul 31,2019
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0362 , 0.1037 )
= 0.1037 in
Available Nozzle Neck Thickness = 0.875 * 0.375 = 0.328 in --> OK
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
Note:
The flange pressure ratio is less than 0.35. Impact testing in not
required due to low stress per UHA-51(g).
Design Pressure/Ambient Rating = 75.00/275.00 = 0.273
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]:
= thickness - corrosion allowance
= 0.375 - 0.000
= 0.375 in
Effective Pressure Radius [Reff]:
= Di/2 + corrosion allowance
= 43.000/2 + 0.000
= 21.500 in
Effective Length of Vessel Wall [LR]:
= 8 * t
= 8 * 0.500
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Nozzle Calcs. : SO-1 Nozl: 22 9:18am Jul 31,2019
= 4.000 in
Thickness Limit Candidate [LH1]:
= t + 0.78 * sqrt( Rn * tn )
= 0.500 + 0.78 * sqrt( 8.625 * 0.375 )
= 1.903 in
Thickness Limit Candidate [LH2]:
= Lpr1 + T
= 7.500 + 0.500
= 8.000 in
Thickness Limit Candidate [LH3]:
= 8( t + te )
= 8( 0.500 + 0.000 )
= 4.000 in
Effective Nozzle Wall Length Outside the Vessel [LH]:
= min[ LH1, LH2, LH3 ]
= min[ 1.903 , 8.000 , 4.000 )
= 1.903 in
Effective Vessel Thickness [teff]:
= t
= 0.500 in
Determine Parameter [Lamda]:
= min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (17.25 + 0.375 )/( sqrt((43.00 + 0.500 ) * 0.500 )) )
= 3.779
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
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Nozzle Calcs. : SO-1 Nozl: 22 9:18am Jul 31,2019
Area Contributed by the Vessel Wall [A1]:
= t * LR * max( Lamda/4, 1 )
= 0.500 * 4.000 * max( 3.779/4, 1 )
= 2.000 in^2
Area Contributed by the Nozzle Outside the Vessel Wall [A2]:
= tn * LH
= 0.375 * 1.903
= 0.714 in^2
Area Contributed by the Outside Fillet Weld [A41]:
= 0.5 * Leg412
= 0.5 * 0.3752
= 0.070 in^2
The total area contributed by A1 through A43 [AT]:
= A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 2.000+1.000(0.714+0.000)+0.070+0.000+0.000
= 2.784 in^2
Allowable Local Primary Membrane Stress [Sallow]:
= 1.5 * S * E
= 1.5 * 15600.000 * 1.000
= 23400.0 psi
Determine Force acting on the Nozzle [fN]:
= P * Rn( LH - t )
= 75.000 * 8.625 ( 1.903 - 0.500 )
= 907.4 lbf
Determine Force acting on the Shell [fS]:
= P * Reff( LR + tn )
= 75.000 * 21.500 ( 4.000 + 0.375 )
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Nozzle Calcs. : SO-1 Nozl: 22 9:18am Jul 31,2019
= 7054.7 lbf
Discontinuity Force from Internal Pressure [fY]:
= P * Reff * Rnc
= 75.000 * 21.500 * 8.625
= 13907.8 lbf
Area Resisting Internal Pressure [Ap]:
= Rn( LH - t ) + Reff( LR + tn + Rnc )
= 8.625 ( 1.903 - 0.500 ) + 21.500 ( 4.000 + 0.375 + 8.625 )
= 291.6 in^2
Maximum Allowable Working Pressure Candidate [Pmax1]:
= Sallow /( 2 * Ap/AT - Rxs/teff )
= 23400.000/( 2 * 291.599/2.784 - 21.500/0.500 )
= 140.5 psig
Maximum Allowable Working Pressure Candidate [Pmax2]:
= S[t/Reff]
= 15600.000 [0.500/21.500 ]
= 362.8 psig
Maximum Allowable Working Pressure [Pmax]:
= min( Pmax1, Pmax2 )
= min( 140.547 , 362.791 )
= 140.547 psig
Average Primary Membrane Stress [SigmaAvg]:
= ( fN + fS + fY ) / AT
= ( 907.424 + 7054.688 + 13907.812 )/2.784
= 7855.984 psi
General Primary Membrane Stress [SigmaCirc]:
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Nozzle Calcs. : SO-1 Nozl: 22 9:18am Jul 31,2019
= P * Reff / teff
= 75.000 * 21.500/0.500
= 3225.0 psi
Maximum Local Primary Membrane Stress [PL]:
= max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 7855.984 - 3225.000 , 3225.000 )
= 12487.0 psi
Summary of Nozzle Pressure/Stress Results:
Allowed Local Primary Membrane Stress Sallow 23400.00 psi
Local Primary Membrane Stress PL 12486.97 psi
Maximum Allowable Working Pressure Pmax 140.55 psig
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]:
= ( Rnc + tn ) / Rnc
= ( 8.625 + 0.375 )/8.625
= 1.043 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]:
= pi/2 * ( Rn + tn )
= pi/2 * ( 8.625 + 0.375 )
= 14.137 in
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]:
= 0.265, 0.000, 0.000, in
Weld Load Value [fwelds]:
= min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(13908*1.04,1.5*17911.8(0.714+0.000),pi/4*75.0*8.62^2*1.04^2)
= 4771.294 lbf
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Nozzle Calcs. : SO-1 Nozl: 22 9:18am Jul 31,2019
Weld Stress Value [tau]:
= fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 4771.294/(14.137 (0.49*0.265 + 0.6*0.500 + 0.49*0.000 ) )
= 785.012 < or = to 15600.000 Weld Size is OK
Weld Size Calculations, Description: SO-1
Intermediate Calc. for nozzle/shell Welds Tmin 0.3750 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2500 = Min per Code 0.2651 = 0.7 * Wo in
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 140.526 psig
The Drop for this Nozzle is : 1.9744 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 9.9744 in
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 135
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FileName : HEAT EXCHANGER
Nozzle Calcs. : SI-1 Nozl: 23 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: SI-1 From : 40
Pressure for Reinforcement Calculations P 75.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-240 304L
Shell Allowable Stress at Temperature Sv 15600.00 psi
Shell Allowable Stress At Ambient Sva 15600.00 psi
Inside Diameter of Cylindrical Shell D 43.0000 in
Shell Finished (Minimum) Thickness t 0.5000 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
Distance from Bottom/Left Tangent 45.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-312 TP304
Material UNS Number S30400
Material Specification/Type Wld. pipe
Allowable Stress at Temperature Sn 17911.76 psi
Allowable Stress At Ambient Sna 18823.53 psi
Note: The allowables above have been divided by 0.85, see UG-37 [S].
Diameter Basis (for tr calc only) ID
Layout Angle 90.00 deg
Diameter 18.0000 in.
B-19-1191R 136
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FileName : HEAT EXCHANGER
Nozzle Calcs. : SI-1 Nozl: 23 9:18am Jul 31,2019
Size and Thickness Basis Nominal
Nominal Thickness tn 40S
Flange Material SA-182 F304
Flange Type Slip on
Corrosion Allowance can 0.0000 in
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 7.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.5000 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
Class of attached Flange 150
Grade of attached Flange GR 2.1
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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B-19-1191R 137
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : SI-1 Nozl: 23 9:18am Jul 31,2019
Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: SI-1
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 17.250 in.
Actual Thickness Used in Calculation 0.375 in.
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (75.00*21.5000)/(15600*1.00-0.6*75.00)
= 0.1037 in
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press]
= (P*R)/(Sn*E-0.6*P) per UG-27 (c)(1)
= (75.00*8.62)/(17912*1.00-0.6*75.00)
= 0.0362 in
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0362 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.1037 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.1037 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.3280 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.328 , max( 0.1037 , 0.0625 ) ]
= 0.1037 in
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FileName : HEAT EXCHANGER
Nozzle Calcs. : SI-1 Nozl: 23 9:18am Jul 31,2019
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0362 , 0.1037 )
= 0.1037 in
Available Nozzle Neck Thickness = 0.875 * 0.375 = 0.328 in --> OK
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
Note:
The flange pressure ratio is less than 0.35. Impact testing in not
required due to low stress per UHA-51(g).
Design Pressure/Ambient Rating = 75.00/275.00 = 0.273
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]:
= thickness - corrosion allowance
= 0.375 - 0.000
= 0.375 in
Effective Pressure Radius [Reff]:
= Di/2 + corrosion allowance
= 43.000/2 + 0.000
= 21.500 in
Effective Length of Vessel Wall [LR]:
= 8 * t
= 8 * 0.500
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FileName : HEAT EXCHANGER
Nozzle Calcs. : SI-1 Nozl: 23 9:18am Jul 31,2019
= 4.000 in
Thickness Limit Candidate [LH1]:
= t + 0.78 * sqrt( Rn * tn )
= 0.500 + 0.78 * sqrt( 8.625 * 0.375 )
= 1.903 in
Thickness Limit Candidate [LH2]:
= Lpr1 + T
= 7.500 + 0.500
= 8.000 in
Thickness Limit Candidate [LH3]:
= 8( t + te )
= 8( 0.500 + 0.000 )
= 4.000 in
Effective Nozzle Wall Length Outside the Vessel [LH]:
= min[ LH1, LH2, LH3 ]
= min[ 1.903 , 8.000 , 4.000 )
= 1.903 in
Effective Vessel Thickness [teff]:
= t
= 0.500 in
Determine Parameter [Lamda]:
= min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (17.25 + 0.375 )/( sqrt((43.00 + 0.500 ) * 0.500 )) )
= 3.779
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
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Nozzle Calcs. : SI-1 Nozl: 23 9:18am Jul 31,2019
Area Contributed by the Vessel Wall [A1]:
= t * LR * max( Lamda/4, 1 )
= 0.500 * 4.000 * max( 3.779/4, 1 )
= 2.000 in^2
Area Contributed by the Nozzle Outside the Vessel Wall [A2]:
= tn * LH
= 0.375 * 1.903
= 0.714 in^2
Area Contributed by the Outside Fillet Weld [A41]:
= 0.5 * Leg412
= 0.5 * 0.3752
= 0.070 in^2
The total area contributed by A1 through A43 [AT]:
= A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 2.000+1.000(0.714+0.000)+0.070+0.000+0.000
= 2.784 in^2
Allowable Local Primary Membrane Stress [Sallow]:
= 1.5 * S * E
= 1.5 * 15600.000 * 1.000
= 23400.0 psi
Determine Force acting on the Nozzle [fN]:
= P * Rn( LH - t )
= 75.000 * 8.625 ( 1.903 - 0.500 )
= 907.4 lbf
Determine Force acting on the Shell [fS]:
= P * Reff( LR + tn )
= 75.000 * 21.500 ( 4.000 + 0.375 )
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FileName : HEAT EXCHANGER
Nozzle Calcs. : SI-1 Nozl: 23 9:18am Jul 31,2019
= 7054.7 lbf
Discontinuity Force from Internal Pressure [fY]:
= P * Reff * Rnc
= 75.000 * 21.500 * 8.625
= 13907.8 lbf
Area Resisting Internal Pressure [Ap]:
= Rn( LH - t ) + Reff( LR + tn + Rnc )
= 8.625 ( 1.903 - 0.500 ) + 21.500 ( 4.000 + 0.375 + 8.625 )
= 291.6 in^2
Maximum Allowable Working Pressure Candidate [Pmax1]:
= Sallow /( 2 * Ap/AT - Rxs/teff )
= 23400.000/( 2 * 291.599/2.784 - 21.500/0.500 )
= 140.5 psig
Maximum Allowable Working Pressure Candidate [Pmax2]:
= S[t/Reff]
= 15600.000 [0.500/21.500 ]
= 362.8 psig
Maximum Allowable Working Pressure [Pmax]:
= min( Pmax1, Pmax2 )
= min( 140.547 , 362.791 )
= 140.547 psig
Average Primary Membrane Stress [SigmaAvg]:
= ( fN + fS + fY ) / AT
= ( 907.424 + 7054.688 + 13907.812 )/2.784
= 7855.984 psi
General Primary Membrane Stress [SigmaCirc]:
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= P * Reff / teff
= 75.000 * 21.500/0.500
= 3225.0 psi
Maximum Local Primary Membrane Stress [PL]:
= max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 7855.984 - 3225.000 , 3225.000 )
= 12487.0 psi
Summary of Nozzle Pressure/Stress Results:
Allowed Local Primary Membrane Stress Sallow 23400.00 psi
Local Primary Membrane Stress PL 12486.97 psi
Maximum Allowable Working Pressure Pmax 140.55 psig
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]:
= ( Rnc + tn ) / Rnc
= ( 8.625 + 0.375 )/8.625
= 1.043 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]:
= pi/2 * ( Rn + tn )
= pi/2 * ( 8.625 + 0.375 )
= 14.137 in
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]:
= 0.265, 0.000, 0.000, in
Weld Load Value [fwelds]:
= min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(13908*1.04,1.5*17911.8(0.714+0.000),pi/4*75.0*8.62^2*1.04^2)
= 4771.294 lbf
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Nozzle Calcs. : SI-1 Nozl: 23 9:18am Jul 31,2019
Weld Stress Value [tau]:
= fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 4771.294/(14.137 (0.49*0.265 + 0.6*0.500 + 0.49*0.000 ) )
= 785.012 < or = to 15600.000 Weld Size is OK
Weld Size Calculations, Description: SI-1
Intermediate Calc. for nozzle/shell Welds Tmin 0.3750 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2500 = Min per Code 0.2651 = 0.7 * Wo in
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 140.526 psig
The Drop for this Nozzle is : 1.9744 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 9.9744 in
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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Nozzle Calcs. : SI-2 Nozl: 24 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: SI-2 From : 40
Pressure for Reinforcement Calculations P 75.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-240 304L
Shell Allowable Stress at Temperature Sv 15600.00 psi
Shell Allowable Stress At Ambient Sva 15600.00 psi
Inside Diameter of Cylindrical Shell D 43.0000 in
Shell Finished (Minimum) Thickness t 0.5000 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
Distance from Bottom/Left Tangent 256.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-312 TP304
Material UNS Number S30400
Material Specification/Type Wld. pipe
Allowable Stress at Temperature Sn 17911.76 psi
Allowable Stress At Ambient Sna 18823.53 psi
Note: The allowables above have been divided by 0.85, see UG-37 [S].
Diameter Basis (for tr calc only) ID
Layout Angle 90.00 deg
Diameter 18.0000 in.
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Size and Thickness Basis Nominal
Nominal Thickness tn 40S
Flange Material SA-182 F304
Flange Type Slip on
Corrosion Allowance can 0.0000 in
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 7.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.5000 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
Class of attached Flange 150
Grade of attached Flange GR 2.1
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: SI-2
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 17.250 in.
Actual Thickness Used in Calculation 0.375 in.
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (75.00*21.5000)/(15600*1.00-0.6*75.00)
= 0.1037 in
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press]
= (P*R)/(Sn*E-0.6*P) per UG-27 (c)(1)
= (75.00*8.62)/(17912*1.00-0.6*75.00)
= 0.0362 in
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0362 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.1037 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.1037 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.3280 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.328 , max( 0.1037 , 0.0625 ) ]
= 0.1037 in
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Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0362 , 0.1037 )
= 0.1037 in
Available Nozzle Neck Thickness = 0.875 * 0.375 = 0.328 in --> OK
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
Note:
The flange pressure ratio is less than 0.35. Impact testing in not
required due to low stress per UHA-51(g).
Design Pressure/Ambient Rating = 75.00/275.00 = 0.273
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]:
= thickness - corrosion allowance
= 0.375 - 0.000
= 0.375 in
Effective Pressure Radius [Reff]:
= Di/2 + corrosion allowance
= 43.000/2 + 0.000
= 21.500 in
Effective Length of Vessel Wall [LR]:
= 8 * t
= 8 * 0.500
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= 4.000 in
Thickness Limit Candidate [LH1]:
= t + 0.78 * sqrt( Rn * tn )
= 0.500 + 0.78 * sqrt( 8.625 * 0.375 )
= 1.903 in
Thickness Limit Candidate [LH2]:
= Lpr1 + T
= 7.500 + 0.500
= 8.000 in
Thickness Limit Candidate [LH3]:
= 8( t + te )
= 8( 0.500 + 0.000 )
= 4.000 in
Effective Nozzle Wall Length Outside the Vessel [LH]:
= min[ LH1, LH2, LH3 ]
= min[ 1.903 , 8.000 , 4.000 )
= 1.903 in
Effective Vessel Thickness [teff]:
= t
= 0.500 in
Determine Parameter [Lamda]:
= min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (17.25 + 0.375 )/( sqrt((43.00 + 0.500 ) * 0.500 )) )
= 3.779
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
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Area Contributed by the Vessel Wall [A1]:
= t * LR * max( Lamda/4, 1 )
= 0.500 * 4.000 * max( 3.779/4, 1 )
= 2.000 in^2
Area Contributed by the Nozzle Outside the Vessel Wall [A2]:
= tn * LH
= 0.375 * 1.903
= 0.714 in^2
Area Contributed by the Outside Fillet Weld [A41]:
= 0.5 * Leg412
= 0.5 * 0.3752
= 0.070 in^2
The total area contributed by A1 through A43 [AT]:
= A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 2.000+1.000(0.714+0.000)+0.070+0.000+0.000
= 2.784 in^2
Allowable Local Primary Membrane Stress [Sallow]:
= 1.5 * S * E
= 1.5 * 15600.000 * 1.000
= 23400.0 psi
Determine Force acting on the Nozzle [fN]:
= P * Rn( LH - t )
= 75.000 * 8.625 ( 1.903 - 0.500 )
= 907.4 lbf
Determine Force acting on the Shell [fS]:
= P * Reff( LR + tn )
= 75.000 * 21.500 ( 4.000 + 0.375 )
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Nozzle Calcs. : SI-2 Nozl: 24 9:18am Jul 31,2019
= 7054.7 lbf
Discontinuity Force from Internal Pressure [fY]:
= P * Reff * Rnc
= 75.000 * 21.500 * 8.625
= 13907.8 lbf
Area Resisting Internal Pressure [Ap]:
= Rn( LH - t ) + Reff( LR + tn + Rnc )
= 8.625 ( 1.903 - 0.500 ) + 21.500 ( 4.000 + 0.375 + 8.625 )
= 291.6 in^2
Maximum Allowable Working Pressure Candidate [Pmax1]:
= Sallow /( 2 * Ap/AT - Rxs/teff )
= 23400.000/( 2 * 291.599/2.784 - 21.500/0.500 )
= 140.5 psig
Maximum Allowable Working Pressure Candidate [Pmax2]:
= S[t/Reff]
= 15600.000 [0.500/21.500 ]
= 362.8 psig
Maximum Allowable Working Pressure [Pmax]:
= min( Pmax1, Pmax2 )
= min( 140.547 , 362.791 )
= 140.547 psig
Average Primary Membrane Stress [SigmaAvg]:
= ( fN + fS + fY ) / AT
= ( 907.424 + 7054.688 + 13907.812 )/2.784
= 7855.984 psi
General Primary Membrane Stress [SigmaCirc]:
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Nozzle Calcs. : SI-2 Nozl: 24 9:18am Jul 31,2019
= P * Reff / teff
= 75.000 * 21.500/0.500
= 3225.0 psi
Maximum Local Primary Membrane Stress [PL]:
= max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 7855.984 - 3225.000 , 3225.000 )
= 12487.0 psi
Summary of Nozzle Pressure/Stress Results:
Allowed Local Primary Membrane Stress Sallow 23400.00 psi
Local Primary Membrane Stress PL 12486.97 psi
Maximum Allowable Working Pressure Pmax 140.55 psig
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]:
= ( Rnc + tn ) / Rnc
= ( 8.625 + 0.375 )/8.625
= 1.043 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]:
= pi/2 * ( Rn + tn )
= pi/2 * ( 8.625 + 0.375 )
= 14.137 in
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]:
= 0.265, 0.000, 0.000, in
Weld Load Value [fwelds]:
= min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(13908*1.04,1.5*17911.8(0.714+0.000),pi/4*75.0*8.62^2*1.04^2)
= 4771.294 lbf
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Nozzle Calcs. : SI-2 Nozl: 24 9:18am Jul 31,2019
Weld Stress Value [tau]:
= fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 4771.294/(14.137 (0.49*0.265 + 0.6*0.500 + 0.49*0.000 ) )
= 785.012 < or = to 15600.000 Weld Size is OK
Weld Size Calculations, Description: SI-2
Intermediate Calc. for nozzle/shell Welds Tmin 0.3750 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2500 = Min per Code 0.2651 = 0.7 * Wo in
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 140.526 psig
The Drop for this Nozzle is : 1.9744 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 9.9744 in
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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Nozzle Calcs. : P1 Nozl: 25 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P1 Parent : SO-1
Pressure for Reinforcement Calculations P 75.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304
Shell Allowable Stress at Temperature Sv 15225.00 psi
Shell Allowable Stress At Ambient Sva 16000.00 psi
Inside Diameter of Cylindrical Shell D 17.2500 in
Shell Finished (Minimum) Thickness t 0.3750 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30400
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 16050.00 psi
Allowable Stress At Ambient Sna 16250.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 90.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
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Nozzle Calcs. : P1 Nozl: 25 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P1
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
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Nozzle Calcs. : P1 Nozl: 25 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (75.00*8.6250)/(15225*1.00-0.6*75.00)
= 0.0426 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-75.00/(16050.00*1.00)))
= 0.0041 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P1.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0041 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0426 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
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Nozzle Calcs. : P1 Nozl: 25 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0041 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P1
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 645.127 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0445 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9195 in
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Nozzle Calcs. : P1 Nozl: 25 9:18am Jul 31,2019
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Nozzle Calcs. : P2 Nozl: 26 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P2 Parent : SO-1
Pressure for Reinforcement Calculations P 75.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304
Shell Allowable Stress at Temperature Sv 15225.00 psi
Shell Allowable Stress At Ambient Sva 16000.00 psi
Inside Diameter of Cylindrical Shell D 17.2500 in
Shell Finished (Minimum) Thickness t 0.3750 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30400
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 16050.00 psi
Allowable Stress At Ambient Sna 16250.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 270.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
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Nozzle Calcs. : P2 Nozl: 26 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P2
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
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Nozzle Calcs. : P2 Nozl: 26 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (75.00*8.6250)/(15225*1.00-0.6*75.00)
= 0.0426 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-75.00/(16050.00*1.00)))
= 0.0041 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P2.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0041 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0426 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
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Nozzle Calcs. : P2 Nozl: 26 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0041 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P2
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 645.127 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0445 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9195 in
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Nozzle Calcs. : P2 Nozl: 26 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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Nozzle Calcs. : P3 Nozl: 27 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P3 Parent : SI-1
Pressure for Reinforcement Calculations P 75.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304
Shell Allowable Stress at Temperature Sv 15225.00 psi
Shell Allowable Stress At Ambient Sva 16000.00 psi
Inside Diameter of Cylindrical Shell D 17.2500 in
Shell Finished (Minimum) Thickness t 0.3750 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30400
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 16050.00 psi
Allowable Stress At Ambient Sna 16250.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 270.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P3 Nozl: 27 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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____________/| |
| \ | |
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Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P3
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
B-19-1191R 165
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P3 Nozl: 27 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (75.00*8.6250)/(15225*1.00-0.6*75.00)
= 0.0426 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-75.00/(16050.00*1.00)))
= 0.0041 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P3.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0041 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0426 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
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Nozzle Calcs. : P3 Nozl: 27 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0041 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P3
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 645.127 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0445 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9195 in
B-19-1191R 167
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P3 Nozl: 27 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 168
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P4 Nozl: 28 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P4 Parent : SI-1
Pressure for Reinforcement Calculations P 75.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304
Shell Allowable Stress at Temperature Sv 15225.00 psi
Shell Allowable Stress At Ambient Sva 16000.00 psi
Inside Diameter of Cylindrical Shell D 17.2500 in
Shell Finished (Minimum) Thickness t 0.3750 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30400
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 16050.00 psi
Allowable Stress At Ambient Sna 16250.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 90.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
B-19-1191R 169
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P4 Nozl: 28 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
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____________/| |
| \ | |
| \ | |
|____________\|__|
Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P4
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
B-19-1191R 170
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P4 Nozl: 28 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (75.00*8.6250)/(15225*1.00-0.6*75.00)
= 0.0426 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-75.00/(16050.00*1.00)))
= 0.0041 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P4.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0041 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0426 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
B-19-1191R 171
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P4 Nozl: 28 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0041 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P4
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 645.127 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0445 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9195 in
B-19-1191R 172
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P4 Nozl: 28 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 173
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P5 Nozl: 29 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P5 Parent : SI-2
Pressure for Reinforcement Calculations P 75.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304
Shell Allowable Stress at Temperature Sv 15225.00 psi
Shell Allowable Stress At Ambient Sva 16000.00 psi
Inside Diameter of Cylindrical Shell D 17.2500 in
Shell Finished (Minimum) Thickness t 0.3750 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30400
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 16050.00 psi
Allowable Stress At Ambient Sna 16250.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 90.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
B-19-1191R 174
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P5 Nozl: 29 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
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____________/| |
| \ | |
| \ | |
|____________\|__|
Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P5
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
B-19-1191R 175
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P5 Nozl: 29 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (75.00*8.6250)/(15225*1.00-0.6*75.00)
= 0.0426 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-75.00/(16050.00*1.00)))
= 0.0041 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P5.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0041 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0426 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
B-19-1191R 176
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P5 Nozl: 29 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0041 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P5
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 645.127 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0445 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9195 in
B-19-1191R 177
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P5 Nozl: 29 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 178
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P6 Nozl: 30 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P6 Parent : SI-2
Pressure for Reinforcement Calculations P 75.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304
Shell Allowable Stress at Temperature Sv 15225.00 psi
Shell Allowable Stress At Ambient Sva 16000.00 psi
Inside Diameter of Cylindrical Shell D 17.2500 in
Shell Finished (Minimum) Thickness t 0.3750 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30400
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 16050.00 psi
Allowable Stress At Ambient Sna 16250.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 270.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
B-19-1191R 179
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P6 Nozl: 30 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
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| |
____________/| |
| \ | |
| \ | |
|____________\|__|
Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P6
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
B-19-1191R 180
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P6 Nozl: 30 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (75.00*8.6250)/(15225*1.00-0.6*75.00)
= 0.0426 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-75.00/(16050.00*1.00)))
= 0.0041 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P6.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0041 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0426 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P6 Nozl: 30 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0041 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P6
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 645.127 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0445 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9195 in
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P6 Nozl: 30 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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FileName : HEAT EXCHANGER
Nozzle Calcs. : V Nozl: 31 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: V From : 60
Pressure for Reinforcement Calculations P 80.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-240 304L
Shell Allowable Stress at Temperature Sv 15600.00 psi
Shell Allowable Stress At Ambient Sva 15600.00 psi
Inside Diameter of Cylindrical Shell D 43.0000 in
Shell Finished (Minimum) Thickness t 0.5000 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
Distance from Bottom/Left Tangent 282.7500 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30403
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 15450.00 psi
Allowable Stress At Ambient Sna 15600.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 90.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
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FileName : HEAT EXCHANGER
Nozzle Calcs. : V Nozl: 31 9:18am Jul 31,2019
Corrosion Allowance can 0.0000 in
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.5000 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
| |
| |
| |
____________/| |
| \ | |
| \ | |
|____________\|__|
Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: V
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
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FileName : HEAT EXCHANGER
Nozzle Calcs. : V Nozl: 31 9:18am Jul 31,2019
Actual Thickness Used in Calculation 0.350 in.
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (80.00*21.5000)/(15600*1.00-0.6*80.00)
= 0.1106 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-80.00/(15450.00*1.00)))
= 0.0045 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: V.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0045 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.1106 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.1106 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
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FileName : HEAT EXCHANGER
Nozzle Calcs. : V Nozl: 31 9:18am Jul 31,2019
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.1106 , 0.0625 ) ]
= 0.1106 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0045 , 0.1106 )
= 0.1106 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: V
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 250.459 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0178 in
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FileName : HEAT EXCHANGER
Nozzle Calcs. : V Nozl: 31 9:18am Jul 31,2019
The Cut Length for this Nozzle is, Drop + Ho + H + T : 2.0178 in
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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FileName : HEAT EXCHANGER
Nozzle Calcs. : CI-1 Nozl: 32 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: CI-1 From : 60
Pressure for Reinforcement Calculations P 80.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-240 304L
Shell Allowable Stress at Temperature Sv 15600.00 psi
Shell Allowable Stress At Ambient Sva 15600.00 psi
Inside Diameter of Cylindrical Shell D 43.0000 in
Shell Finished (Minimum) Thickness t 0.5000 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
Distance from Bottom/Left Tangent 282.7500 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-312 TP304L
Material UNS Number S30403
Material Specification/Type Smls. pipe
Allowable Stress at Temperature Sn 16400.00 psi
Allowable Stress At Ambient Sna 17500.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 270.00 deg
Diameter 12.0000 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
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FileName : HEAT EXCHANGER
Nozzle Calcs. : CI-1 Nozl: 32 9:18am Jul 31,2019
Flange Material SA-182 F304L
Flange Type Slip on
Corrosion Allowance can 0.0000 in
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 7.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: CI-1
B-19-1191R 190
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FileName : HEAT EXCHANGER
Nozzle Calcs. : CI-1 Nozl: 32 9:18am Jul 31,2019
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 12.000 in.
Actual Thickness Used in Calculation 0.350 in.
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (80.00*21.5000)/(15600*1.00-0.6*80.00)
= 0.1106 in
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press]
= (P*Ro)/(Sn*E+0.4*P) per Appendix 1-1 (a)(1)
= (80.00*6.0000)/(16400*1.00+0.4*80.00)
= 0.0292 in
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0292 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.1106 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.1106 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.3280 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.328 , max( 0.1106 , 0.0625 ) ]
= 0.1106 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0292 , 0.1106 )
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FileName : HEAT EXCHANGER
Nozzle Calcs. : CI-1 Nozl: 32 9:18am Jul 31,2019
= 0.1106 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-240 304L, Min Metal Temp without impact per UHA-51: -320 F
SA-312 TP304L, Min Metal Temp without impact per UHA-51: -320 F
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]:
= thickness - corrosion allowance
= 0.350 - 0.000
= 0.350 in
Effective Pressure Radius [Reff]:
= Di/2 + corrosion allowance
= 43.000/2 + 0.000
= 21.500 in
Effective Length of Vessel Wall [LR]:
= 8 * t
= 8 * 0.500
= 4.000 in
Thickness Limit Candidate [LH1]:
= t + 0.78 * sqrt( Rn * tn )
= 0.500 + 0.78 * sqrt( 5.650 * 0.350 )
= 1.597 in
Thickness Limit Candidate [LH2]:
= Lpr1 + T
= 7.500 + 0.500
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FileName : HEAT EXCHANGER
Nozzle Calcs. : CI-1 Nozl: 32 9:18am Jul 31,2019
= 8.000 in
Thickness Limit Candidate [LH3]:
= 8( t + te )
= 8( 0.500 + 0.000 )
= 4.000 in
Effective Nozzle Wall Length Outside the Vessel [LH]:
= min[ LH1, LH2, LH3 ]
= min[ 1.597 , 8.000 , 4.000 )
= 1.597 in
Effective Vessel Thickness [teff]:
= t
= 0.500 in
Determine Parameter [Lamda]:
= min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (11.30 + 0.350 )/( sqrt((43.00 + 0.500 ) * 0.500 )) )
= 2.498
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]:
= t * LR * max( Lamda/4, 1 )
= 0.500 * 4.000 * max( 2.498/4, 1 )
= 2.000 in^2
Area Contributed by the Nozzle Outside the Vessel Wall [A2]:
= tn * LH
= 0.350 * 1.597
= 0.559 in^2
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FileName : HEAT EXCHANGER
Nozzle Calcs. : CI-1 Nozl: 32 9:18am Jul 31,2019
Area Contributed by the Outside Fillet Weld [A41]:
= 0.5 * Leg412
= 0.5 * 0.3752
= 0.070 in^2
The total area contributed by A1 through A43 [AT]:
= A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 2.000+1.000(0.559+0.000)+0.070+0.000+0.000
= 2.629 in^2
Allowable Local Primary Membrane Stress [Sallow]:
= 1.5 * S * E
= 1.5 * 15600.000 * 1.000
= 23400.0 psi
Determine Force acting on the Nozzle [fN]:
= P * Rn( LH - t )
= 80.000 * 5.650 ( 1.597 - 0.500 )
= 495.8 lbf
Determine Force acting on the Shell [fS]:
= P * Reff( LR + tn )
= 80.000 * 21.500 ( 4.000 + 0.350 )
= 7482.0 lbf
Discontinuity Force from Internal Pressure [fY]:
= P * Reff * Rnc
= 80.000 * 21.500 * 5.650
= 9718.0 lbf
Area Resisting Internal Pressure [Ap]:
= Rn( LH - t ) + Reff( LR + tn + Rnc )
= 5.650 ( 1.597 - 0.500 ) + 21.500 ( 4.000 + 0.350 + 5.650 )
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Nozzle Calcs. : CI-1 Nozl: 32 9:18am Jul 31,2019
= 221.2 in^2
Maximum Allowable Working Pressure Candidate [Pmax1]:
= Sallow /( 2 * Ap/AT - Rxs/teff )
= 23400.000/( 2 * 221.197/2.629 - 21.500/0.500 )
= 186.8 psig
Maximum Allowable Working Pressure Candidate [Pmax2]:
= S[t/Reff]
= 15600.000 [0.500/21.500 ]
= 362.8 psig
Maximum Allowable Working Pressure [Pmax]:
= min( Pmax1, Pmax2 )
= min( 186.810 , 362.791 )
= 186.810 psig
Average Primary Membrane Stress [SigmaAvg]:
= ( fN + fS + fY ) / AT
= ( 495.783 + 7482.000 + 9718.000 )/2.629
= 6730.443 psi
General Primary Membrane Stress [SigmaCirc]:
= P * Reff / teff
= 80.000 * 21.500/0.500
= 3440.0 psi
Maximum Local Primary Membrane Stress [PL]:
= max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 6730.443 - 3440.000 , 3440.000 )
= 10020.9 psi
Summary of Nozzle Pressure/Stress Results:
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FileName : HEAT EXCHANGER
Nozzle Calcs. : CI-1 Nozl: 32 9:18am Jul 31,2019
Allowed Local Primary Membrane Stress Sallow 23400.00 psi
Local Primary Membrane Stress PL 10020.89 psi
Maximum Allowable Working Pressure Pmax 186.81 psig
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]:
= ( Rnc + tn ) / Rnc
= ( 5.650 + 0.350 )/5.650
= 1.062 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]:
= pi/2 * ( Rn + tn )
= pi/2 * ( 5.650 + 0.350 )
= 9.425 in
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]:
= 0.265, 0.000, 0.000, in
Weld Load Value [fwelds]:
= min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(9718*1.06,1.5*16400.0(0.559+0.000),pi/4*80.0*5.65^2*1.06^2)
= 2261.947 lbf
Weld Stress Value [tau]:
= fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 2261.947/(9.425 (0.49*0.265 + 0.6*0.375 + 0.49*0.000 ) )
= 676.190 < or = to 15600.000 Weld Size is OK
Weld Size Calculations, Description: CI-1
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
B-19-1191R 196
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FileName : HEAT EXCHANGER
Nozzle Calcs. : CI-1 Nozl: 32 9:18am Jul 31,2019
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 186.792 psig
The Drop for this Nozzle is : 0.8542 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 8.8542 in
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 197
PV Elite 2016 Licensee: SPLM Licensed User
FileName : HEAT EXCHANGER
Nozzle Calcs. : P9 Nozl: 33 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P9 Parent : CI-1
Pressure for Reinforcement Calculations P 80.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304L
Shell Allowable Stress at Temperature Sv 16400.00 psi
Shell Allowable Stress At Ambient Sva 17500.00 psi
Inside Diameter of Cylindrical Shell D 11.3000 in
Shell Finished (Minimum) Thickness t 0.3500 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30403
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 15450.00 psi
Allowable Stress At Ambient Sna 15600.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 270.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
B-19-1191R 198
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P9 Nozl: 33 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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| \ | |
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Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P9
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
B-19-1191R 199
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P9 Nozl: 33 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (80.00*5.6500)/(16400*1.00-0.6*80.00)
= 0.0276 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-80.00/(15450.00*1.00)))
= 0.0045 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P9.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0045 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0276 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
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Nozzle Calcs. : P9 Nozl: 33 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0045 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304L, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P9
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 979.522 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0682 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9182 in
B-19-1191R 201
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P9 Nozl: 33 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 202
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P10 Nozl: 34 9:18am Jul 31,2019
INPUT VALUES, Nozzle Description: P10 Parent : CI-1
Pressure for Reinforcement Calculations P 80.000 psig
Temperature for Internal Pressure Temp 150 F
Shell Material SA-312 TP304L
Shell Allowable Stress at Temperature Sv 16400.00 psi
Shell Allowable Stress At Ambient Sva 17500.00 psi
Inside Diameter of Cylindrical Shell D 11.3000 in
Shell Finished (Minimum) Thickness t 0.3500 in
Shell Internal Corrosion Allowance c 0.0000 in
Shell External Corrosion Allowance co 0.0000 in
User Entered Minimum Design Metal Temperature -20.00 F
Type of Element Connected to the Shell : Nozzle
Material SA-182 F304L
Material UNS Number S30403
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 15450.00 psi
Allowable Stress At Ambient Sna 15600.00 psi
Diameter Basis (for tr calc only) OD
Layout Angle 90.00 deg
Diameter 1.7500 in.
Size and Thickness Basis Actual
Actual Thickness tn 0.3500 in
Corrosion Allowance can 0.0000 in
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P10 Nozl: 34 9:18am Jul 31,2019
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 1.5000 in
Weld leg size between Nozzle and Pad/Shell Wo 0.3750 in
Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in
Inside Projection h 0.0000 in
Weld leg size, Inside Element to Shell Wi 0.0000 in
ASME Code Weld Type per UW-16 None
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
| |
| |
| |
____________/| |
| \ | |
| \ | |
|____________\|__|
Insert/Set-in Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: P10
ASME Code, Section VIII, Div. 1, 2015, UG-37 to UG-45
Actual Outside Diameter Used in Calculation 1.750 in.
Actual Thickness Used in Calculation 0.350 in.
B-19-1191R 204
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P10 Nozl: 34 9:18am Jul 31,2019
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press]
= (P*R)/(Sv*E-0.6*P) per UG-27 (c)(1)
= (80.00*5.6500)/(16400*1.00-0.6*80.00)
= 0.0276 in
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= Ro(1 - exp( -P/( Sn*E ))) per Appendix 1-2 (a)(1)
= 0.875(1-exp(-80.00/(15450.00*1.00)))
= 0.0045 in
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: P10.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.0045 in
Wall Thickness per UG16(b), tr16b = 0.0625 in
Wall Thickness, shell/head, internal pressure trb1 = 0.0276 in
Wall Thickness tb1 = max(trb1, tr16b) = 0.0625 in
Wall Thickness tb2 = max(trb2, tr16b) = 0.0625 in
Wall Thickness per table UG-45 tb3 = 0.1268 in
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 0.127 , max( 0.0625 , 0.0625 ) ]
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Nozzle Calcs. : P10 Nozl: 34 9:18am Jul 31,2019
= 0.0625 in
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.0045 , 0.0625 )
= 0.0625 in
Available Nozzle Neck Thickness = 0.3500 in --> OK
SA-312 TP304L, Min Metal Temp without impact per UHA-51: -320 F
SA-182 F304L, Min Metal Temp without impact per UHA-51: -320 F
Weld Size Calculations, Description: P10
Intermediate Calc. for nozzle/shell Welds Tmin 0.3500 in
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 0.2450 = 0.7 * tmin. 0.2651 = 0.7 * Wo in
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 979.522 psig
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 0.0682 in
The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.9182 in
B-19-1191R 206
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FileName : HEAT EXCHANGER
Nozzle Calcs. : P10 Nozl: 34 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
B-19-1191R 207
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FileName : HEAT EXCHANGER
Nozzle Schedule : Step: 33 9:18am Jul 31,2019
Nozzle Schedule:
Nominal Flange Noz. Wall Re-Pad Cut
Description Size Sch/Type O/Dia Thk ODia Thick Length
in. Cls in. in in in in
------------------------------------------------------------------------------
D 1.750 - None 1.750 0.350 - - 2.02
P7 1.750 - None 1.750 0.350 - - 1.92
P8 1.750 - None 1.750 0.350 - - 1.92
P1 1.750 - None 1.750 0.350 - - 1.92
P2 1.750 - None 1.750 0.350 - - 1.92
P3 1.750 - None 1.750 0.350 - - 1.92
P4 1.750 - None 1.750 0.350 - - 1.92
P5 1.750 - None 1.750 0.350 - - 1.92
P6 1.750 - None 1.750 0.350 - - 1.92
V 1.750 - None 1.750 0.350 - - 2.02
P9 1.750 - None 1.750 0.350 - - 1.92
P10 1.750 - None 1.750 0.350 - - 1.92
CO-1 12.000 150 SlipOn 12.000 0.350 - - 8.85
CI-1 12.000 - SlipOn 12.000 0.350 - - 8.85
SO-1 18.000 40S SlipOn 18.000 0.375 - - 9.97
SI-1 18.000 40S SlipOn 18.000 0.375 - - 9.97
SI-2 18.000 40S SlipOn 18.000 0.375 - - 9.97
General Notes for the above table:
The Cut Length is the Outside Projection + Inside Projection + Drop +
In Plane Shell Thickness. This value does not include weld gaps,
nor does it account for shrinkage.
In the case of Oblique Nozzles, the Outside Diameter must
be increased. The Re-Pad WIDTH around the nozzle is calculated as follows:
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Nozzle Schedule : Step: 33 9:18am Jul 31,2019
Width of Pad = (Pad Outside Dia. (per above) - Nozzle Outside Dia.)/2
For hub nozzles, the thickness and diameter shown are those of the smaller
and thinner section.
Nozzle Material and Weld Fillet Leg Size Details:
Shl Grve Noz Shl/Pad Pad OD Pad Grve Inside
Nozzle Material Weld Weld Weld Weld Weld
in in in in in
------------------------------------------------------------------------------
D SA-312 TP304 0.500 0.375 - - -
P7 SA-182 F304L 0.375 0.375 - - -
P8 SA-182 F304L 0.375 0.375 - - -
P1 SA-182 F304L 0.375 0.375 - - -
P2 SA-182 F304L 0.375 0.375 - - -
P3 SA-182 F304L 0.375 0.375 - - -
P4 SA-182 F304L 0.375 0.375 - - -
P5 SA-182 F304L 0.375 0.375 - - -
P6 SA-182 F304L 0.375 0.375 - - -
V SA-182 F304L 0.500 0.375 - - -
P9 SA-182 F304L 0.375 0.375 - - -
P10 SA-182 F304L 0.375 0.375 - - -
CO-1 SA-312 TP304L 0.375 0.375 - - -
CI-1 SA-312 TP304L 0.375 0.375 - - -
SO-1 SA-312 TP304 0.500 0.375 - - -
SI-1 SA-312 TP304 0.500 0.375 - - -
SI-2 SA-312 TP304 0.500 0.375 - - -
Note: The Outside projections below do not include the flange thickness.
Nozzle Miscellaneous Data:
Elevation/Distance Layout Projection Installed In
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FileName : HEAT EXCHANGER
Nozzle Schedule : Step: 33 9:18am Jul 31,2019
Nozzle From Datum Angle Outside Inside Component
in deg. in in
----------------------------------------------------------------------------
D 15.875 270.00 1.50 0.00 Node: 30
P7 5.062 90.00 1.50 0.00 CO-1
P8 5.062 270.00 1.50 0.00 CO-1
P1 37.750 90.00 1.50 0.00 SO-1
P2 37.750 270.00 1.50 0.00 SO-1
P3 37.750 270.00 1.50 0.00 SI-1
P4 37.750 90.00 1.50 0.00 SI-1
P5 37.750 90.00 1.50 0.00 SI-2
P6 37.750 270.00 1.50 0.00 SI-2
V 284.250 90.00 1.50 0.00 Node: 60
P9 270.750 270.00 1.50 0.00 CI-1
P10 270.750 90.00 1.50 0.00 CI-1
CO-1 15.875 90.00 7.50 0.00 Node: 30
CI-1 284.250 270.00 7.50 0.00 Node: 60
SO-1 150.500 270.00 7.50 0.00 Node: 40
SI-1 45.000 90.00 7.50 0.00 Node: 40
SI-2 256.000 90.00 7.50 0.00 Node: 40
Weld Sizes for Slip On/Socket Weld Nozzle Flanges per UW-21:
Nozzle to Flange Fillet Weld Leg dimension [xmin]:
= min( 1.4 * tn, Hub Thickness )
The Nozzle Wall thicknesses shown below are in the corroded condition. Hubs
are considered to be straight.
Nominal Flange Noz. Wall Hub Throat xmin
Description Size Sch/Type O/Dia Thk - - - - Thickness
in. Cls in. in in in in
------------------------------------------------------------------------------
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FileName : HEAT EXCHANGER
Nozzle Schedule : Step: 33 9:18am Jul 31,2019
CO-1 12.000 150 SlipOn 12.000 0.350 0.750 0.343 0.490
CI-1 12.000 - SlipOn 12.000 0.350 0.750 0.343 0.490
SO-1 18.000 40S SlipOn 18.000 0.375 0.850 0.367 0.525
SI-1 18.000 40S SlipOn 18.000 0.375 0.850 0.367 0.525
SI-2 18.000 40S SlipOn 18.000 0.375 0.850 0.367 0.525
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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FileName : HEAT EXCHANGER
Nozzle Summary : Step: 34 9:18am Jul 31,2019
Nozzle Calculation Summary:
Description MAWP Ext MAPNC UG45 [tr] Weld Areas or
psig psig Path Stresses
---------------------------------------------------------------------------
D 250.46 ... ... OK 0.111 OK NoCalc[*]
CO-1 186.79 ... 0.00 OK 0.111 OK Passed
P7 979.52 ... ... OK 0.062 OK NoCalc[*]
P8 979.52 ... ... OK 0.062 OK NoCalc[*]
SO-1 140.53 ... 0.00 OK 0.104 OK Passed
SI-1 140.53 ... 0.00 OK 0.104 OK Passed
SI-2 140.53 ... 0.00 OK 0.104 OK Passed
P1 645.13 ... ... OK 0.062 OK NoCalc[*]
P2 645.13 ... ... OK 0.062 OK NoCalc[*]
P3 645.13 ... ... OK 0.062 OK NoCalc[*]
P4 645.13 ... ... OK 0.062 OK NoCalc[*]
P5 645.13 ... ... OK 0.062 OK NoCalc[*]
P6 645.13 ... ... OK 0.062 OK NoCalc[*]
V 250.46 ... ... OK 0.111 OK NoCalc[*]
CI-1 186.79 ... 0.00 OK 0.111 OK Passed
P9 979.52 ... ... OK 0.062 OK NoCalc[*]
P10 979.52 ... ... OK 0.062 OK NoCalc[*]
---------------------------------------------------------------------------
Min. - Nozzles 140.53 SI-2 0.00 CI-1
[*] - This was a small opening and the areas were not computed or
the MAWP of this connection could not be computed because
the longitudinal bending stress was greater than the hoop stress.
Note: MAWPs (Internal Case) shown above are at the High Point.
Check the Spatial Relationship between the Nozzles
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FileName : HEAT EXCHANGER
Nozzle Summary : Step: 34 9:18am Jul 31,2019
From Node Nozzle Description X Coordinate, Layout Angle, Dia. Limit
30 D 15.875 270.000 2.750
30 CO-1 15.875 90.000 22.600
30 P7 0.000 90.000 2.450
30 P8 0.000 270.000 2.450
40 SO-1 150.500 270.000 34.500
40 SI-1 45.000 90.000 34.500
40 SI-2 256.000 90.000 34.500
40 P1 0.000 90.000 2.500
40 P2 0.000 270.000 2.500
40 P3 0.000 270.000 2.500
40 P4 0.000 90.000 2.500
40 P5 0.000 90.000 2.500
40 P6 0.000 270.000 2.500
60 V 282.750 90.000 2.750
60 CI-1 282.750 270.000 22.600
60 P9 0.000 270.000 2.450
60 P10 0.000 90.000 2.450
The nozzle spacing is computed by the following:
= Sqrt( ll2 + lc2 ) where
ll - Arc length along the inside vessel surface in the long. direction.
lc - Arc length along the inside vessel surface in the circ. direction
If any interferences/violations are found, they will be noted below.
No interference violations have been detected !
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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TEMA TS Calc : Case: 1 9:18a Jul 31,2019
Input Echo, TubeSheet Item 1, Description: TUBESHEET
Tubesheet Design Code TEMA
Shell Desc. From Node 40 to 60
Shell Design Pressure Ps 75.00 psig
Shell Temperature for Internal Pressure TEMPS 230.00 F
Shell Material SA-240 304L
Shell Material UNS Number S30403
Shell Allowable Stress at Temperature Sos 15510.00 psi
Shell Allowable Stress at Ambient Sas 15600.00 psi
Shell Thickness Ts 0.5000 in
Shell Internal Corrosion Allowance Cas 0.0000 in
Inside Diameter of Shell Ds 43.000 in
Mean Metal Temperature for Shell Tm 0.00 F
Channel Desc. From Node 30 to 40
Channel Design Pressure Pc 80.00 psig
Channel Temperature for Internal Pressure TEMPC 150.00 F
Channel Material SA-240 304L
Channel Material UNS Number S30403
Channel Allowable Stress at Temperature Soc 15600.00 psi
Channel Allowable Stress at Ambient Sac 15600.00 psi
Channel Thickness Tc 0.5000 in
Channel Corrosion Allowance Cac 0.0000 in
Inside Diameter of Channel Dc 43.000 in
Mean Metal Temperature for Tubes tm 0.00 F
Tube Design Temperature Tubtmp 150.00 F
Tube Material SA-214
Is This a Welded Tube No
Tube Material Specification used
Tube Allowable Stress at Temperature Sot 20000.00 psi
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TEMA TS Calc : Case: 1 9:18a Jul 31,2019
Tube Allowable Stress At Ambient Sat 20000.00 psi
Tube Yield Stress At Operating Temperature Syt 26000.00 psi
Tube Wall Thickness Tt 0.0200 in
Tube Corrosion Allowance Catt 0.0000 in
Number of Tubes Holes Ntubs 200
Tube Layout Pattern Triangular
Tube Outside Diameter do 1.0000 in
Tube Pitch (Center to Center Spacing) PTube 1.2500 in
Fillet Weld Leg af 0.0625 in
Groove Weld Leg ag 0.0625 in
Design Strength of Weld Fd 0.0000 lbf
Tube-Tubesheet Joint Weld Type Seal/No Weld
Is Tube-Tubesheet Joint Tested No
Tube-Tubesheet Joint Classification i
Tube Joint Reliability Factor fr 0.7000
Interface Pressure, after tube expansion Po 0.00 psig
Interface Pressure, due to diff. thermal exp. Pt 0.00 psig
Total Straight Tube Length Lt 233.000 in
Straight Tube Length, bet. inner tubsht faces RL 230.000 in
Unsupported Tube Length for max. (k*SL) SL 0.0000 in
Tube end condition corres. to span (SL) k 0.0000
Length of Expanded Portion of Tube l 0.2500 in
Tubesheet type: Fixed Tubesheet Exchanger
Tubesheet Design Metal Temperature TEMPTS 150.00 F
Tubesheet Material SA-240 304L
Tubesheet Material UNS Number S30403
Tubesheet Allowable Stress at Temperature Sots 15600.00 psi
Tubesheet Allowable Stress at Ambient Sats 15600.00 psi
Thickness of Tubesheet Tts 1.5000 in
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TEMA TS Calc : Case: 1 9:18a Jul 31,2019
Tubesheet Corr. Allowance (Shell side) Cats 0.0000 in
Tubesheet Corr. Allowance (Channel side) Catc 0.0000 in
Depth of Groove in Tube Sheet hg 0.0000 in
TEMA Tubesheet class R
Additional Data for Fixed Tubesheet Exchangers
Mean Metal Temperature for Tubesheet Tshm 70.00 F
Run Multiple Load Cases for Fixed Tubesheets No
Is this a Kettle-type configuration No
Error/Warning/Notes for Tubesheet Number 1
Warning - Tube end condition k should be between 0 - 1 (0.00 ).
Note - Tube-Tubesheet Joint Interface pressures are 0, its effect will be
ignored [App. A(2)].
Tubesheet Analysis, Tubesheet number 1,Description:TUBESHEET
TEMA Standards, Ninth Edition, 2007, Appendix A, Tubesheets
TEMA R-7.131/A.131 Minimum Tubesheet Thickness for R-type:
TMIN = MAX( do, CONST - ( CATS + CATC ) )
TMIN = MAX( 1.000 , 0.750 - ( 0.000 + 0.000 ) )
TMIN = 1.0000 in
Min. Thickness + CATS + CATC
TREQMIN = 1.0000 in
Shellside Fixity Factor, F, per RCB 7.132 FS 1.0000
Shellside Effective Diameter, per RCB 7.132 GS 43.000 in
Tubeside Fixity Factor, F, per RCB 7.132 FC 1.0000
Tubeside Effective Diameter, per RCB 7.132 GC 43.000 in
TEMA Eta factor used in calculation ETA 0.4195
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TEMA TS Calc : Case: 1 9:18a Jul 31,2019
Material Properties for Thermal Expansion Analysis:
Shell - TE-1 Austenitic Group 3 Steels
Shell - TM-1 Material Group G
-----------------------------------------------------------------
Th. Exp. Coeff. Metal Temperature 0.0 F 0.0000085000 / F
Elastic Mod. at Metal Temperature 0.0 F 0.28671E+08 psi
Tubes - TE-1 Carbon & Low Alloy Steels, Group 1
Tubes - TM-1 Carbon Steels with C<= 0.3%
-----------------------------------------------------------------
Th. Exp. Coeff. Metal Temperature 0.0 F 0.0000060891 / F
Elastic Mod. at Metal Temperature 0.0 F 0.29771E+08 psi
TubeSheet - TE-1 Austenitic Group 3 Steels
TubeSheet - TM-1 Material Group G
-----------------------------------------------------------------
Th. Exp. Coeff. Metal Temperature 70.0 F 0.0000085000 / F
Elastic Mod. at Metal Temperature 70.0 F 0.28300E+08 psi
Note: Iterating to compute the required Tubesheet Thickness
TEMA RCB-7.132/A.131 Required Thickness for Shellside Pressure [Trs]:
= FS * GS * SQRT ( PSU / ( ETA * SOTS ) ) / 3.0
= 1.0000 * 43.0000 * SQRT( 14.56 / ( 0.4195 * 15600 ) ) / 3.0
= 0.6761 in
TEMA RCB-7.132/A.131 Required Thickness for Tubeside Pressure [Trc]:
= FC * GC * SQRT ( PTU / ( ETA * SOTS ) ) / 3.0
= 1.0000 * 43.0000 * SQRT( 16.67 / ( 0.4195 * 15600 ) ) / 3.0
= 0.7233 in
TEMA RCB-7.132/A.131 Reqd Thickness for Bending + Cats + MAX(Catc,hg) [Treq]:
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FileName : HEAT EXCHANGER
TEMA TS Calc : Case: 1 9:18a Jul 31,2019
= 0.7233 in
Note: Recomputing Eff. pressures (PTU, PSU) at given Tubesheet thickness.
TEMA RCB-7.161/A.151 J Factor for Thermal Expansion = 1.0 (No Exp. Jt.)
TEMA RCB-7.161/A.151 K Factor for Thermal Exp. 5.3435
TEMA RCB-7.161/A.151 Fq Factor for Thermal Exp. 3.1886
TEMA RCB-7.161/A.151 Differential Exp. / Length -0.17E-03
TEMA RCB-7.161/A.151 Equivalent Differential Thermal Exp. Pressure:
PD = 4 * J * ES * TS * DLL /
( DOS - 3.0*TS ) * ( 1.0 + J * RK * FQ )
PD = 4 * 1.0000 * 28670588 * 0.5000 * -0.0002 /
( 44.0000 - 3.0 * 0.5000 ) * ( 1.0 + 1.0000 * 5.3435 * 3.1886 )
PD = -12.623 psig
TEMA RCB 7.163/A.153 Effective Shellside Design Pressure:
TEMA RCB-7.163/A.153 FFs Factor for Shellside Design 0.8918
PSP1 = 0.4 * J * ( 1.5 + K * (1.5 + FFS ) )
= 0.4 * 1.0000 * ( 1.5 + 5.3435 * (1.5 + 0.8918 ) )
PSP2 = ( ( 0.5 - J / 2.0 ) * ( DJ2 / G2 - 1.0 )
2 2
= ( ( 0.5 - 1.0000 / 2.0 ) * ( 43.0000 /43.0000 - 1.0 )
PSP3 = 1.0 + J * K * FQ
= 1.0 + 1.0000 * 5.3435 * 3.1886
PSP = PS * ( ( PSP1 - PSP2 ) / PSP3 )
= 75.00 * ( ( 5.7123 - 0.0000 ) / 18.0382 )
PSP = 23.751 psig
TEMA RCB-7.163/A.153 Effective Shell Side Design Pressure:
PSU = Max (absolute) of PSP : 23.75
or PBS : 0.00
or ( PSP - PD ) / 2 : ( 23.75 - -12.62 ) / 2.0
or ( PSP - PD - PBS ) / 2 : ( 23.75 --12.62 -0.00 ) / 2.0
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TEMA TS Calc : Case: 1 9:18a Jul 31,2019
or ( PBS + PD ) / 2 : ( 0.00 + -12.62 ) / 2.0
or ( PSP - PBS ) : ( 23.75 - 0.00 )
PSU = : 23.751 psig
TEMA RCB 7.163/A.153 Shellside Shear Design Pressure, PBS=0:
PSS = : 23.751 psig
TEMA RCB 7.164/A.154 Effective Tubeside Design Pressure:
TEMA RCB-7.164/A.154, FFt Factor for Tubeside Design 0.9003
PTP1 = 1.0 + 0.4 * J * K * ( 1.5 + FFT )
= 1.0 + 0.4 * 1.0000 * 5.3435 * ( 1.5 + 0.9003 )
PTP2 = 1.0 + J * K * FQ
= 1.0 + 1.0000 * 5.3435 * 3.1886
PTP = PT * PTP1 / PTP2
= 80.00 * 6.1304 / 18.0382
PTP = 27.189 psig
TEMA RCB-7.164/A.154 Effective Tube Side Design Pressure:
PTU = Max (absolute) of :
( PTP + PBT + PD ) / 2 : ( 27.19 +0.00 +-12.62 ) / 2.0
or ( PTP + PBT ) : ( 27.19 + 0.00 )
PTU = : 27.189 psig
TEMA RCB 7.164/A.154 Tubeside Shear Design Pressure (PBT=0):
PTS = : 27.189 psig
No Shear Calculation, since Pressure is less than 998.3999 psig
TEMA RCB-7.22/A.22 Shell Longitudinal Stress :
Max. Effective Pressure for Longitudinal Stress, 76.562 psig
TEMA RCB-7.22/A.22 Maximum Shell Longitudinal Stress :
STSMAX = PSSMAX * CS * ( DOS - TS )/( 4 * TS )
STSMAX = 76.56 * 1.00 * ( 44.0000 - 0.5000 ) / ( 4 * 0.5000 )
STSMAX = 1665. psi
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TEMA TS Calc : Case: 1 9:18a Jul 31,2019
TEMA RCB-7.22/A.22 Allowable Shell Longitudinal Stress :
STSALL = 15510. psi
TEMA RCB-7.23/A.23 Tube Longitudinal Stress Results :
Max. Effective Pressure for Longitudinal Stress, 4.600 psig
Min. Effective Pressure for Longitudinal Stress, -15.397 psig
TEMA RCB-7.23/A.23 Maximum Tube Long. Stress (Tension):
STTMAX = PTTMAX*CT*FQ*G*G /(4*NTUBS*TT*(do-TT))
STTMAX = 4.60 *1.00 *3.19 *43.0000 *43.0000
/ ( 4*200 *0.0200 *(1.0000 -0.0200 ) )
STTMAX = 1729.70 psi
TEMA RCB-7.23/A.23 Allowable Tube Long. Stress (Tension):
STTALL = 20000.00 psi
TEMA RCB-7.23/A.23 Minimum Tube Comp. Longitudinal Stress :
STTMIN = PTTMIN*CT*FQ*G*G/(4*NTUBS*TT*(do-TT))
STTMIN = -15.40 *1.00 *3.19 *43.0000 *43.0000
/ ( 4*200 *0.0200 *(1.0000 -0.0200 ) )
STTMIN = -5789.16 psi
TEMA RCB-7.24/A.23 Allowable Tube Compressive Stress :
STTCOM = -SYT*(1-RKLR/(2*CC))/FSAF
STTCOM = -26000 * ( 1.0 -0.0000 / ( 2.0 *150.3391 ) ) / 1.66
STTCOM = -15703.33 psi
TEMA RCB-7.25/A.25 Tube-To-Tubesheet Joint Load :
Effective Pressure for Tube-to-Tubesheet Load : 4.600 psig
TEMA RCB-7.25/A.25 Actual Tube-To-Tubesheet Load :
WJ = PI * FQ * PTLOAD * G * G / ( 4.0 * NTUBS )
WJ = 3.14 * 3.19 * 4.600 * 43.00 * 43.00 / ( 4.0 * 200 )
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TEMA TS Calc : Case: 1 9:18a Jul 31,2019
WJ = 106.51 lbf
Allowable Tube-To-Tubesheet Load per ASME App. A [Lmax]:
= (PI/4)*(DT^2-(DT-2*TT)^2)*SOT*fr*fe*fy*ft
= .785*(1.000^2-(1.000-2*0.0200)^2)*20000*0.70*1.00*0.87*1.00
= 752.64 lbf
Summary of Tubesheet Results:
------------------------------------------------------------------------
Condition Req Thk Actual Thk Actual Allow Result
(+CA) (in) Stress (psi)
------------------------------------------------------------------------
Bending 0.723 1.500 8876.39 23400.00 Ok
Min. Per code 1.000 1.500 ------ ------ Ok
Tube Fillet Leg 0.000 0.063 ------ ------ Ok
Tube Groove Leg 0.000 0.063 ------ ------ Ok
------------------------------------------------------------------------
Longitudinal stresses:
--------------------------------------------------------------------
Compressive Tensile
Condition Actual Allow Actual Allow Result
--------------------------------------------------------------------
Shell 0.000 0.000 1665.228 15510.000 Ok
Long Tubes -5789.164 15703.334 1729.703 20000.000 Ok
Tube Load 106.507 752.639 Ok
--------------------------------------------------------------------
Equivalent Differential Ther. Expansion Pressure -12.6229 psig
Shellside Prime Pressure 23.7508 psig
Tubeside Prime Pressure 27.1885 psig
Maximum Axial Differential Thermal Expansion between Shell and Tubes:
Tube has higher Thermal growth (Exp. Jt. Extension) : +0.0388 in
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FileName : HEAT EXCHANGER
TEMA TS Calc : Case: 1 9:18a Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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FileName : HEAT EXCHANGER
MDMT Summary : Step: 35 9:18am Jul 31,2019
Minimum Design Metal Temperature Results Summary :
Curve Basic Reduced UG-20(f) Thickness Gov E*
Description MDMT MDMT MDMT ratio Thk
Notes F F F in
----------------------------------------------------------------------------
[16] -320
SO-1 [15] -320
SI-1 [15] -320
SI-2 [15] -320
P1 [15] -320
P2 [15] -320
P3 [15] -320
P4 [15] -320
P5 [15] -320
P6 [15] -320
----------------------------------------------------------------------------
Cover Front [11] -320
[11] -320
[11] -320
[16] -320
[16] -320
D [15] -320
CO-1 [15] -320
P7 [15] -320
P8 [15] -320
V [15] -320
CI-1 [15] -320
P9 [15] -320
P10 [15] -320
----------------------------------------------------------------------------
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MDMT Summary : Step: 35 9:18am Jul 31,2019
Exchanger Side Computed MDMT Required MDMT Pass/Fail
F F
----------------------------------------------------------------------------
Shell -320 -20 Pass
Channel/Tube -320 -20 Pass
Notes:
[ ! ] - This was an impact tested material.
[ 1] - Governing Nozzle Weld.
[ 4] - ANSI Flange MDMT Calcs; Thickness ratio per UCS-66(b)(1)(c).
[ 5] - ANSI Flange MDMT Calcs; Thickness ratio per UCS-66(b)(1)(b).
[ 6] - MDMT Calculations at the Shell/Head Joint.
[ 7] - MDMT Calculations for the Straight Flange.
[ 8] - Cylinder/Cone/Flange Junction MDMT.
[ 9] - Calculations in the Spherical Portion of the Head.
[10] - Calculations in the Knuckle Portion of the Head.
[11] - Calculated (Body Flange) Flange MDMT.
[12] - Calculated Flat Head MDMT per UCS-66.3
[13] - Tubesheet MDMT, shell side, if applicable
[14] - Tubesheet MDMT, tube side, if applicable
[15] - Nozzle Material
[16] - Shell or Head Material
[17] - Impact Testing required
UG-84(b)(2) was not considered.
UCS-66(g) was not considered.
UCS-66(i) was not considered.
Notes:
Impact test temps were not entered in and not considered in the analysis.
UCS-66(i) applies to impact tested materials not by specification and
UCS-66(g) applies to materials impact tested per UG-84.1 General Note (c).
The Basic MDMT includes the (30F) PWHT credit if applicable.
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MDMT Summary : Step: 35 9:18am Jul 31,2019
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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FileName : HEAT EXCHANGER
Vessel Design Summary : Step: 36 9:18am Jul 31,2019
ASME Code, Section VIII, Division 1, 2015
Diameter Spec : 43.000 in ID
Vessel Design Length, Tangent to Tangent 300.12 in
Specified Datum Line Distance 0.00 in
Shell Material SA-240 304L
Nozzle Material SA-312 TP304
Nozzle Material SA-312 TP304L
Nozzle Material SA-182 F304L
Shell Side Design Temperature 150 F
Channel Side Design Temperature 150 F
Shell Side Design Pressure 75.000 psig
Channel Side Design Pressure 80.000 psig
Shell Side Hydrostatic Test Pressure 113.000 psig
Channel Side Hydrostatic Test Pressure 120.000 psig
Wind Design Code ASCE-93
Earthquake Design Code UBC-94
Element Pressures and MAWP: psig
Element Desc | Design Pres. | External | M.A.W.P | Corrosion |
| + Stat. head | Pressure | | Allowance |
-----------------------------------------------------------------------
Cover Front | 80.000| 0.000| 100.440| 0.0000|
Body Flg | 80.000| 0.000| 115.165| 0.0000|
Cylinder | 80.000| 0.000| 250.459| 0.0000|
Cylinder | 75.000| 0.000| 250.459| 0.0000|
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Vessel Design Summary : Step: 36 9:18am Jul 31,2019
Cylinder | 80.000| 0.000| 250.459| 0.0000|
Body Flg | 80.000| 0.000| 177.420| 0.0000|
Body Flg | 80.000| 0.000| 100.440| 0.0000|
Element "To" Elev Length Element Thk R e q d T h k Joint Eff
Type in in in Int. Ext. Long Circ
-----------------------------------------------------------------------
Body Flg 2.06 2.062 2.062 1.841 ... 1.00 1.00
Body Flg 2.06 3.500 3.500 3.485 ... 1.00 1.00
Cylinder 34.75 32.688 0.500 0.158 ... 0.70 0.70
Cylinder 266.25 231.500 0.500 0.148 ... 0.70 0.70
Cylinder 298.06 30.312 0.500 0.158 ... 0.70 0.70
Body Flg 298.06 3.500 3.500 2.738 ... 1.00 1.00
Body Flg 300.12 2.062 2.062 1.841 ... 1.00 1.00
Element thicknesses are shown as Nominal if specified, otherwise are Minimum
Saddle Parameters:
Saddle Width 8.000 in
Saddle Bearing Angle 121.000 deg.
Centerline Dimension 28.750 in
Wear Pad Width 10.000 in
Wear Pad Thickness 0.500 in
Wear Pad Bearing Angle 128.000 deg.
Distance from Saddle to Tangent 56.750 in
Baseplate Length 40.000 in
Baseplate Thickness 0.750 in
Baseplate Width 8.000 in
Number of Ribs (including outside ribs) 4
Rib Thickness 0.500 in
Web Thickness 0.500 in
Height of Center Web 12.000 in
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Vessel Design Summary : Step: 36 9:18am Jul 31,2019
Baseplate Sketch
|------------------- 40.000 in ----------------------|
------------------------------------------------------ ---
| |
| | 8.000 in
| |
------------------------------------------------------ ---
Baseplate Plan View
------------------------------------------------------ ---
| | 0.750 in
------------------------------------------------------ ---
Baseplate Side View
Summary of Maximum Saddle Loads, Operating Case :
Maximum Vertical Saddle Load 7564.09 lbf
Maximum Transverse Saddle Shear Load 426.49 lbf
Maximum Longitudinal Saddle Shear Load 127.30 lbf
Summary of Maximum Saddle Loads, Hydrotest Case :
Maximum Vertical Saddle Load 15285.37 lbf
Maximum Transverse Saddle Shear Load 140.74 lbf
Maximum Longitudinal Saddle Shear Load 42.01 lbf
Weights:
Fabricated - Bare W/O Removable Internals 12501.3 lbm
Shop Test - Fabricated + Water ( Full ) 29163.1 lbm
Shipping - Fab. + Rem. Intls.+ Shipping App. 12501.3 lbm
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FileName : HEAT EXCHANGER
Vessel Design Summary : Step: 36 9:18am Jul 31,2019
Erected - Fab. + Rem. Intls.+ Insul. (etc) 12501.3 lbm
Empty - Fab. + Intls. + Details + Wghts. 12501.3 lbm
Operating - Empty + Operating Liquid (No CA) 12501.3 lbm
Field Test - Empty Weight + Water (Full) 29163.1 lbm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2016
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