Sample2-PVElite

Table of Contents

Cover Sheet...................................................................................................................................2 Input Echo .....................................................................................................................................3 Internal Pressure Calculations.......................................................................................................8 External Pressure Calculations....................................................................................................11 Element and Detail Weights ........................................................................................................13 Nozzle Flange MAWP..................................................................................................................14 Center of Gravity Calculation.......................................................................................................15 Horizontal Vessel Analysis (Ope.) ...............................................................................................16 Horizontal Vessel Analysis (Test) ................................................................................................24 Nozzle Calcs. N2 - 2 in. ...............................................................................................................32 Nozzle Calcs. N4 - 1/2 in. ............................................................................................................34 Nozzle Calcs. N1 - 4 in. ...............................................................................................................36 Nozzle Calcs. N3 - 2 in. ...............................................................................................................39 Nozzle Schedule..........................................................................................................................41 Nozzle Summary .........................................................................................................................42 Vessel Design Summary .............................................................................................................43 Problems/Failures Summary .......................................................................................................45

Cover Page

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Pressure Vesel Engineering Sample Job 2 DESIGN CALCULATION In Accordance with : ASME Section VIII Division 1 ASME Code Version : 2004, Addenda A-06 Analysis Performed by : PRESSURE VESSEL ENGINEERING Job File : L:\SAMPLES\SAMPLE 2\SAMPLE 2-CALCULATIONS 2007 E Date of Analysis : Sep 9,2008 PV Elite 2007, January 2007

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Input Echo STEP: 1 11:20a Sep 9,2008

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PV Elite Vessel Analysis Program: Input Data Pressure Vesel Engineering Sample Job 2 Design Internal Pressure (for Hydrotest) 200.00 psig Design Internal Temperature 300 F Type of Hydrotest UG99-b Hydrotest Position Horizontal Projection of Nozzle from Vessel Top 0.0000 in. Projection of Nozzle from Vessel Bottom 0.0000 in. Minimum Design Metal Temperature -20 F Type of Construction Welded Special Service None Degree of Radiography None Miscellaneous Weight Percent 15. 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 Use Hydrotest Allowable Unmodified Y Consider Vortex Shedding N Perform a Corroded Hydrotest N Is this a Heat Exchanger No 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 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 NP+EW+WI+FW+BW Load Case 14 NP+EW+EE+FS+BS Load Case 15 NP+OW+WI+FW+BW Load Case 16 NP+OW+EQ+FS+BS Load Case 17 NP+HW+HI Load Case 18 NP+HW+HE Load Case 19 IP+OW+WI+FW+BW Load Case 20 IP+OW+EQ+FS+BS Wind Design Code No Wind Loads Design Wind Speed 70.000 mile/hr Exposure Constant C Importance Factor Roughness Factor Base Elevation 0.0000 ft. Percent Wind for Hydrotest 33. Use Wind Profile (Y/N) 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


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Seismic Design Code No Seismic Design Nozzle for Des. Press. + St. Head Y Consider MAP New and Cold in Noz. Design N Consider External Loads for Nozzle Des. Y Consider Code Case 2168 for Nozzle Des. N Material Database Year Current w/Addenda or Code Year Complete Listing of Vessel Elements and Details: Element From Node 10 Element To Node 20 Element Type Elliptical Description Left Head Distance "FROM" to "TO" 0.2500 ft. Element Outside Diameter 12.750 in. Element Thickness 0.3281 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.3750 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 200.00 psig Design Temperature Internal Pressure 300 F Design External Pressure 0.0000 psig Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA-234 WPB Allowable Stress, Ambient 20000. psi Allowable Stress, Operating 20000. psi Allowable Stress, Hydrotest 26000. psi Material Density 0.2830 lb./cu.in. P Number Thickness 1.2500 in. Yield Stress, Operating 33600. psi UCS-66 Chart Curve Designation B External Pressure Chart Name CS-2 UNS Number K03006 Efficiency, Longitudinal Seam 0.85 Efficiency, Circumferential Seam 0.7 Elliptical Head Factor 2. Element From Node 10 Detail Type Liquid Detail ID WATER Dist. from "FROM" Node / Offset dist 0.0000 ft. Height/Length of Liquid 1.0625 ft. Density of Liquid 62.400 lb./cu.ft. Element From Node 10 Detail Type Nozzle Detail ID N2 - 2" Dist. from "FROM" Node / Offset dist 0.0000 in. Nozzle Diameter 3. in. Nozzle Schedule None Nozzle Class 0 Layout Angle 0. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange None Nozzle Matl SA-105 Element From Node 20 Element To Node 30 Element Type Cylinder


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Description Shell Distance "FROM" to "TO" 3.0000 ft. Element Outside Diameter 12.750 in. Element Thickness 0.3281 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.3750 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 200.00 psig Design Temperature Internal Pressure 300 F Design External Pressure 0.0000 psig Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA-106 B Allowable Stress, Ambient 17100. psi Allowable Stress, Operating 17100. psi Allowable Stress, Hydrotest 22230. psi Material Density 0.2830 lb./cu.in. P Number Thickness 1.2500 in. Yield Stress, Operating 31000. psi UCS-66 Chart Curve Designation B External Pressure Chart Name CS-2 UNS Number K03006 Efficiency, Longitudinal Seam 0.85 Efficiency, Circumferential Seam 0.7 Element From Node 20 Detail Type Saddle Detail ID Rigth Sdl Dist. from "FROM" Node / Offset dist 2.8125 ft. Width of Saddle 0.3750 in. Height of Saddle at Bottom 12.000 in. Saddle Contact Angle 120. Height of Composite Ring Stiffener 0.0000 in. Width of Wear Plate 0.0000 in. Thickness of Wear Plate 0.0000 in. Contact Angle, Wear Plate (degrees) 0. Element From Node 20 Detail Type Saddle Detail ID Left Sdl Dist. from "FROM" Node / Offset dist 0.1875 ft. Width of Saddle 3.0000 in. Height of Saddle at Bottom 12.000 in. Saddle Contact Angle 120. Height of Composite Ring Stiffener 0.0000 in. Width of Wear Plate 0.0000 in. Thickness of Wear Plate 0.0000 in. Contact Angle, Wear Plate (degrees) 0. Element From Node 20 Detail Type Liquid Detail ID WATER Dist. from "FROM" Node / Offset dist 0.0000 ft. Height/Length of Liquid 1.0625 ft. Density of Liquid 62.400 lb./cu.ft. Element From Node 20 Detail Type Nozzle Detail ID N4 - 1/2" Dist. from "FROM" Node / Offset dist 1.5000 ft. Nozzle Diameter 1.125 in. Nozzle Schedule None Nozzle Class 0


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Layout Angle 180. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange None Nozzle Matl SA-105 Element From Node 20 Detail Type Nozzle Detail ID N1 - 4" Dist. from "FROM" Node / Offset dist 1.5000 ft. Nozzle Diameter 4. in. Nozzle Schedule 40 Nozzle Class 150 Layout Angle 0. Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange GR 1.1 Nozzle Matl SA-106 B Element From Node 30 Element To Node 40 Element Type Elliptical Description Right Head Distance "FROM" to "TO" 0.2500 ft. Element Outside Diameter 12.750 in. Element Thickness 0.3281 in. Internal Corrosion Allowance 0.0000 in. Nominal Thickness 0.3750 in. External Corrosion Allowance 0.0000 in. Design Internal Pressure 200.00 psig Design Temperature Internal Pressure 300 F Design External Pressure 0.0000 psig Design Temperature External Pressure 0 F Effective Diameter Multiplier 1.2 Material Name SA-234 WPB Allowable Stress, Ambient 17100. psi Allowable Stress, Operating 17100. psi Allowable Stress, Hydrotest 22230. psi Material Density 0.2830 lb./cu.in. P Number Thickness 1.2500 in. Yield Stress, Operating 31000. psi UCS-66 Chart Curve Designation B External Pressure Chart Name CS-2 UNS Number K03006 Efficiency, Longitudinal Seam 0.85 Efficiency, Circumferential Seam 0.7 Elliptical Head Factor 2. Element From Node 30 Detail Type Liquid Detail ID WATER Dist. from "FROM" Node / Offset dist 0.0000 ft. Height/Length of Liquid 1.0625 ft. Density of Liquid 62.400 lb./cu.ft. Element From Node 30 Detail Type Nozzle Detail ID N3 - 2" Dist. from "FROM" Node / Offset dist 0.0000 in. Nozzle Diameter 3. in. Nozzle Schedule None Nozzle Class 0 Layout Angle 0.


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Blind Flange (Y/N) N Weight of Nozzle ( Used if > 0 ) 0.0000 lb. Grade of Attached Flange None Nozzle Matl SA-105 PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Internal Pressure Calculations STEP: 3 11:20a Sep 9,2008

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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 | Left Head| 200.460 | 0.37500 | 0.00000 | 12.7500 | 17000.0 | Shell| 200.460 | 0.37500 | 0.00000 | 12.7500 | 14535.0 | Right Head| 200.460 | 0.37500 | 0.00000 | 12.7500 | 14535.0 | Element Required Thickness and MAWP : | | Design | M.A.W.P. | M.A.P. | Actual | Required | From| To | Pressure | Corroded | New & Cold | Thickness | Thickness | | | psig | psig | psig | in. | in. | Left Head| 200.000 | 917.042 | 917.502 | 0.32812 | 0.074383 | Shell| 200.000 | 763.391 | 763.851 | 0.32812 | 0.087439 | Right Head| 200.000 | 784.004 | 784.464 | 0.32812 | 0.086843 | Minimum 229.540 285.000 Note : The M.A.W.P is Governed by an Flange ! Flange MAWP including Static Pressure: 229.540 = 230.000 - 0.460 psig Note : The M.A.P.(NC) is Governed by a Flange ! Internal Pressure Calculation Results : ASME Code, Section VIII, Division 1, 2004 A-06 Elliptical Head From 10 To 20 SA-234 WPB , UCS-66 Crv. B at 300 F Left Head Thickness Due to Internal Pressure [Tr]: = (P*D*K)/(2*S*E+2*P*(K-0.1)) per Appendix 1-4 (c) = (200.460*12.7500*1.00)/(2*20000.00*0.85+2*200.460*(1.00-0.1)) = 0.0744 + 0.0000 = 0.0744 in. Max. All. Working Pressure at Given Thickness [MAWP]: Less Operating Hydrostatic Head Pressure of 0.460 psig = (2*S*E*(T-CA))/(K*D-2*(T-CA)*(K-0.1)) per Appendix 1-4 (c) = (2*20000.00*0.85*(0.3281))/(1.00*12.7500-2*(0.3281)*(1.00-0.1)) = 917.502 - 0.460 = 917.042 psig Maximum Allowable Pressure, New and Cold [MAPNC]: = (2*SA*E*T)/(K*D-2*T*(K-0.1)) per Appendix 1-4 (c) = (2*20000.00*0.85*0.3281)/(1.00*12.7500-2*0.3281*(1.00-0.1)) = 917.502 psig Actual stress at given pressure and thickness [Sact]: = (P*(K*D-2*(T-Ca)*(K-0.1)))/(2*E*(T-Ca)) = (200.460*(1.00*12.7500-2*(0.3281)*(1.00-0.1)))/(2*0.85*(0.3281)) = 4369.700 psi Required Thickness of Straight Flange = 0.075 in. Percent Elongation per UCS-79 (75*tnom/Rf)*(1-Rf/Ro) 13.369 % Min Metal Temp. w/o impact per UCS-66 -20 F Min Metal Temp. at Rqd thickness (UCS 66.1)[rat 0.19] -155 F Cylindrical Shell From 20 To 30 SA-106 B , UCS-66 Crv. B at 300 F


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Shell Thickness Due to Internal Pressure [Tr]: = (P*D/2)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (200.460*12.7500/2)/(17100.00*0.85+0.4*200.460) = 0.0874 + 0.0000 = 0.0874 in. Max. All. Working Pressure at Given Thickness [MAWP]: Less Operating Hydrostatic Head Pressure of 0.460 psig = (S*E*(T-Ca))/(D/2-0.4*(T-Ca)) per Appendix 1-1 (a)(1) = (17100.00*0.85*(0.3281))/(12.7500/2-0.4*0.3281) = 763.851 - 0.460 = 763.391 psig Maximum Allowable Pressure, New and Cold [MAPNC]: = (SA*E*T)/(D/2-0.4*T) per Appendix 1-1 (a)(1) = (17100.00*0.85*0.3281)/(12.7500/2-0.4*0.3281) = 763.851 psig Actual stress at given pressure and thickness [Sact]: = (P*(D/2-0.4*(T-Ca)))/(E*(T-Ca)) = (200.460*((12.7500/2-0.4*(0.3281)))/(0.85*(0.3281)) = 4487.618 psi Percent Elongation per UCS-79 (50*tnom/Rf)*(1-Rf/Ro) 3.030 % Min Metal Temp. w/o impact per UCS-66 -20 F Min Metal Temp. at Rqd thickness (UCS 66.1)[rat 0.23] -155 F Elliptical Head From 30 To 40 SA-234 WPB , UCS-66 Crv. B at 300 F Right Head Thickness Due to Internal Pressure [Tr]: = (P*D*K)/(2*S*E+2*P*(K-0.1)) per Appendix 1-4 (c) = (200.460*12.7500*1.00)/(2*17100.00*0.85+2*200.460*(1.00-0.1)) = 0.0868 + 0.0000 = 0.0868 in. Max. All. Working Pressure at Given Thickness [MAWP]: Less Operating Hydrostatic Head Pressure of 0.460 psig = (2*S*E*(T-CA))/(K*D-2*(T-CA)*(K-0.1)) per Appendix 1-4 (c) = (2*17100.00*0.85*(0.3281))/(1.00*12.7500-2*(0.3281)*(1.00-0.1)) = 784.464 - 0.460 = 784.004 psig Maximum Allowable Pressure, New and Cold [MAPNC]: = (2*SA*E*T)/(K*D-2*T*(K-0.1)) per Appendix 1-4 (c) = (2*17100.00*0.85*0.3281)/(1.00*12.7500-2*0.3281*(1.00-0.1)) = 784.464 psig Actual stress at given pressure and thickness [Sact]: = (P*(K*D-2*(T-Ca)*(K-0.1)))/(2*E*(T-Ca)) = (200.460*(1.00*12.7500-2*(0.3281)*(1.00-0.1)))/(2*0.85*(0.3281)) = 4369.700 psi Required Thickness of Straight Flange = 0.087 in. Percent Elongation per UCS-79 (75*tnom/Rf)*(1-Rf/Ro) 13.369 % Min Metal Temp. w/o impact per UCS-66 -20 F Min Metal Temp. at Rqd thickness (UCS 66.1)[rat 0.22] -155 F MINIMUM METAL DESIGN TEMPERATURE RESULTS :


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Minimum Metal Temp. w/o impact per UCS-66 -20. F Minimum Metal Temp. at Required thickness -155. F Note: Heads and Shells Exempted to -20F (-29C) by paragraph UG-20F Minimum Design Metal Temperature ( Entered by User ) -20. F Hydrostatic Test Pressure Results: Pressure per UG99b = 1.3 * M.A.W.P. * Sa/S 298.401 psig Pressure per UG99b[33] = 1.3 * Design Pres * Sa/S 260.000 psig Pressure per UG99c = 1.3 * M.A.P. - Head(Hyd) 370.500 psig Pressure per UG100 = 1.1 * M.A.W.P. * Sa/S 252.494 psig Horizontal Hydrotest performed in accordance with: UG-99b Stresses on Elements due to Hydrostatic Test Pressure: From To Stress Allowable Ratio Pressure Left Head 6514.7 26000.0 0.251 298.86 Shell 6690.5 22230.0 0.301 298.86 Right Head 6514.7 22230.0 0.293 298.86 Elements Suitable for Internal Pressure. PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ External Pressure Calculations STEP: 4 11:20a Sep 9,2008

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External Pressure Calculation Results : ASME Code, Section VIII, Division 1, 2004 A-06 Elliptical Head From 10 to 20 Ext. Chart: CS-2 at 0 F Left Head Results for Maximum Allowable Pressure (EMAP): Tca OD D/t Factor A B 0.328 12.75 38.86 0.0035743 16652.99 EMAP = B/(K0*D/t) = 16652.9883/(0.9000 *38.8571 ) = 476.1884 psig Cylindrical Shell From 20 to 30 Ext. Chart: CS-2 at 0 F Shell Results for Maximum Allowable Pressure (EMAP): Tca OD SLEN D/t L/D Factor A B 0.328 12.75 44.02 38.86 3.4522 0.0015879 14248.89 EMAP = (4*B)/(3*(D/t)) = (4*14248.8945)/(3*38.8571 ) = 488.9326 psig Results for Maximum Stiffened Length (SLEN): Tca OD SLEN D/t L/D Factor A B 0.328 12.75 0.11E+33 38.86 .5000E+02 0.0007285 10563.77 EMAP = (4*B)/(3*(D/t)) = (4*10563.7705)/(3*38.8571 ) = 362.4823 psig Elliptical Head From 30 to 40 Ext. Chart: CS-2 at 0 F Right Head Results for Maximum Allowable Pressure (EMAP): Tca OD D/t Factor A B 0.328 12.75 38.86 0.0035743 16652.99 EMAP = B/(K0*D/t) = 16652.9883/(0.9000 *38.8571 ) = 476.1884 psig External Pressure Calculations | | Section | Outside | Corroded | Factor | Factor | From| To | Length | Diameter | Thickness | A | B | | | ft. | in. | in. | | psi | 10| 20| No Calc | 12.7500 | 0.32812 | 0.0035743 | 16653.0 | 20| 30| 3.66797 | 12.7500 | 0.32812 | 0.0015879 | 14248.9 | 30| 40| No Calc | 12.7500 | 0.32812 | 0.0035743 | 16653.0 | 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| 0.32812 | No Calc | 0.00000 | 476.188 | 20| 30| 0.32812 | No Calc | 0.00000 | 488.933 | 30| 40| 0.32812 | No Calc | 0.00000 | 476.188 | Minimum 476.188 External Pressure Calculations | | Actual Len.| Allow. Len.| Ring Inertia | Ring Inertia | From| To | Bet. Stiff.| Bet. Stiff.| Required | Available | | | ft. | ft. | in**4 | in**4 | 10| 20| No Calc | No Calc | No Calc | No Calc | 20| 30| 3.66797 | 9.299E+30 | No Calc | No Calc |

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ External Pressure Calculations STEP: 4 11:20a Sep 9,2008

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30| 40| No Calc | No Calc | No Calc | No Calc | Elements Suitable for External Pressure. PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Element and Detail Weights STEP: 5 11:20a Sep 9,2008

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Element and Detail Weights | | Element | Element | Corroded | Corroded | Extra due | From| To | Metal Wgt. | ID Volume |Metal Wgt. | ID Volume | Misc % | | | lb. | in3 | lb. | in3 | lb. | 10| 20| 32.2184 | 576.152 | 32.2184 | 576.152 | 4.83277 | 20| 30| 149.656 | 4135.37 | 149.656 | 4135.37 | 22.4483 | 30| 40| 32.2184 | 576.152 | 32.2184 | 576.152 | 4.83277 | --------------------------------------------------------------------------- Total 214 5287 214 5287 32 Weight of Details | | Weight of | X Offset, | Y Offset, | From|Type| Detail | Dtl. Cent. |Dtl. Cent. | Description | | lb. | ft. | ft. | 10|Liqd| 20.6150 | -0.083984 | -0.027344 | WATER 10|Nozl| 0.85868 | -0.020996 | 0.00000 | N2 - 2" 20|Sadl| 14.8507 | 2.81250 | 0.73828 | Rigth Sdl 20|Sadl| 19.6637 | 0.18750 | 0.73828 | Left Sdl 20|Liqd| 149.333 | 1.50000 | -0.027344 | WATER 20|Nozl| 0.080520 | 1.50000 | 0.55078 | N4 - 1/2" 20|Nozl| 21.6929 | 1.50000 | 0.67057 | N1 - 4" 30|Liqd| 20.6150 | 0.33398 | -0.027344 | WATER 30|Nozl| 0.85868 | 0.27100 | 0.00000 | N3 - 2" Total Weight of Each Detail Type Total Weight of Saddles 34.5 Total Weight of Liquid 190.6 Total Weight of Nozzles 23.5 --------------------------------------------------------------- Sum of the Detail Weights 248.6 lb. Fabricated Wt. - Bare Weight W/O Removable Internals 304.2 lb. Shop Test Wt. - Fabricated Weight + Water ( Full ) 495.2 lb. Shipping Wt. - Fab. Wt + Rem. Intls.+ Shipping App. 304.2 lb. Erected Wt. - Fab. Wt + Rem. Intls.+ Insul. (etc) 304.2 lb. Empty Wt. - Fab. Wt + Intls. + Details + Wghts. 304.2 lb. Operating Wt. - Empty Wt. + Operating Liquid (No CA) 494.8 lb. Oper. Wt. + CA - Corr Wt. + Operating Liquid 494.8 lb. Field Test Wt. - Empty Weight + Water (Full) 495.2 lb. 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 | From| To | Area | | | sq.in. | 10| 20| 299.866 | 20| 30| 1452.59 | 30| 40| 299.866 | --------------------------------------------------- Total 2052.325 sq.in. [14.3 Square Feet ] PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Nozzle Flange MAWP STEP: 6 11:20a Sep 9,2008

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Nozzle Flange MAWP Results : ANSI Flange Pressure Rating for: N1 - 4" : Class 150 : Grade GR 1.1 Pressure Rating for B16.5 Flange at : 300 F is : 230.000 psig Pressure Rating for B16.5 Flange at : 70 F is : 285.000 psig Note: ANSI Ratings are per ANSI/ASME B16.5 2003 Edition Lowest Flange Pressure Rating was (ope) : 230.000 psig Lowest Flange Pressure Rating was (Amb) : 285.000 psig PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Center of Gravity Calculation STEP: 7 11:20a Sep 9,2008

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Shop/Field Installation Options : Note : The CG is computed from the first Element From Node Center of Gravity of Saddles 1.6 ft. Center of Gravity of Liquid 1.7 ft. Center of Gravity of Nozzles 1.8 ft. Center of Gravity of Bare Shell New and Cold 1.7 ft. Center of Gravity of Bare Shell Corroded 1.7 ft. Vessel CG in the Operating Condition 1.7 ft. Vessel CG in the Fabricated (Shop/Empty) Condition 1.7 ft. PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Horizontal Vessel Analysis (Ope.) STEP: 8 11:20a Sep 9,2008

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Zick Analysis: Stresses for the Left Saddle Horizontal Vessel Stress Calculations : Operating Case Shell Allowable Stress used in Calculation 17100.00 psi Shell Comp. Yield Stress used in Calculation 31000.00 psi Head Allowable Stress used in Calculation 20000.00 psi Saddle Force Q, Operating Case 230.13 lb. Stress Results for Zick Stresses: Actual Allowable Long. Stress at Top of Saddles 1803.38 11970.00 psi Long. Stress at Bottom of Saddles 1806.48 11970.00 psi Long. Stress at Top of Midspan 1756.28 11970.00 psi Long. Stress at Bottom of Midspan 1853.58 11970.00 psi Tangential Shear in Shell 102.06 13680.00 psi Tangential Shear in Head 102.06 16000.00 psi Circ. Stress at Horn of Saddle -81.74 -25650.00 psi Addl. Stress in Head as Stiffener 46.52 5000.00 psi Circ. Compressive Stress in Shell -102.59 -15500.00 psi Note: The Longitudinal Stress from the Zick Analysis is combined with the Longitudinal Pressure Stress to get the total stress. Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst ) = 230 + Max( 0 , 0 , 0 , 0 ) = 230.1 lb. Summary of Loads on this Saddle Support: Vertical Load on this Saddle 230.13 lb. Transverse Shear Load on this Saddle 0.00 lb. Longitudinal Shear Load on this Saddle 0.00 lb. Formulas and Substitutions for Zick Analysis Results: Longitudinal Bending (+-) at Midspan = ( 3 * Q * L * K.2 / ( pi * R² * ( Ts - Ca ))) = ( 3 * 230 * 3.50 * 0.7265 ) / ( 3.141 * 6.0469 * 6.0469 * ( 0.3281 - 0.0000 ))) = 46.57 psi Compute the area ratio [K]: = Pi * (Sin(Delta)/Delta - Cos(Delta) ) / (Delta + Sin(Delta) * Cos(Delta) - (Delta + Sin(Delta) * Cos(Delta) - 2 * Sin(Delta) * Sin(Delta)/Delta) = Pi * (Sin(1.396 ) / 1.396 - Cos(1.396 )) / ( 1.396 + Sin(1.396 ) * Cos(1.396 ) - 2 * Sin(1.396 ) * Sin(1.396 )/ 1.396 ) = 9.3799 Compute the moment fraction [X]: = 1 - (1 - A/L + ( R² - H² )/(2 * A*L ) )/(1 + (4*H )/( 3 * L ) ) = 1 - (1 - 0.188 /3.500 + (6.047² - 0.252²)/( 2 * 0.188 * 3.500 ) ) / (1 + (4 * 0.252 )/(3 * 3.500 ) ) = 0.0041 Intermediate Product [K.1]: = K * X * 4 * A / L = 9.380 * 0.004 * 4 * 0.188 / 3.500 = 0.0082 Longitudinal Bending (+-) at Saddle = ( 3 * Q * L * K.1 / ( pi * R² * ( Ts - Ca )))


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= ( 3 * 230 * 3.50 * 0.0082 ) / ( 3.141 * 6.0469 * 6.0469 * ( 0.3281 - 0.0000 ))) = 0.52 psi Tangential Shear in Shell near Saddle = Q * K.5 / ( R * ( Ts - Ca ))) = 230 * 0.8799 / ( 6.0469 * ( 0.3281 - 0.0000 ) = 102.06 psi Tangential Shear in Head used as Stiffener = Q * K.5 / ( R * ( Th - Ca ))) = 230 * 0.8799 / ( 6.05 * ( 0.3281 - 0.0000 ) = 102.06 psi Circumferential Stress at Horn of Saddle = -Q/(4*TEM*(SADWTH+1.56*Sqrt(R*TCA)))-12*Q*R*K.7/(L*TEB) = -230 /( 4 * 0.3281 * (3.00 + 1.56 * Sqrt(6.0469 *0.3281 ))) -12.0 * 230 * 0.50 * 0.0130 / ( 3.5000 * 0.1077 ) = -81.74 psi Additional Tension in Head used as Stiffener = (Q/(R*(Hdthk-Ca)))*(3/8)*(sin(AL)²/(pi-AL+sin(AL*cos(AL))) = (230 / ( 6.0469 * ( 0.3281 - 0.0000 )))*(3/8)*( sin( 114.00 )²)/ ( pi - 114.00 + sin( 114.00 ) * cos( 114.00 ))) = 46.52 psi Circumferential Compression at Bottom of Shell = (Q*( K.9/( TEM9*( B+1.56 * Sqrt( R * TEM9 )))) = (230 *(0.7603 /(0.3281 *(3.00 +1.56*Sqrt(6.05 *0.3281 )))) = -102.59 psi Free Un-Restrained Thermal Expansion between the Saddles [Exp]: = Alpha * Ls * ( Design Temperature - Ambient Temperature ) = 0.643E-05 * 31.500 * ( 300.0 - 70.0 ) = 0.047 in. Results for Vessel Ribs, Web and Base: Baseplate Length Bplen 11.0400 in. Baseplate Thickness Bpthk 0.3750 in. Baseplate Width Bpwid 3.0000 in. Number of Ribs ( inc. outside ribs ) Nribs 2 Rib Thickness Ribtk 0.3750 in. Web Thickness Webtk 0.3750 in. Web Location Webloc Side Moment of Inertia of Saddle - Lateral Direction Y A AY Ay² Io Shell 0.1641 0.7210 0.1183 0.0194 0.0065 Wearplate 0.3281 0.0000 0.0000 0.0000 0.0000 Web 2.9766 1.9863 5.9124 17.5987 4.6442 BasePlate 5.8125 1.1250 6.5391 38.0083 0.0132 Totals 9.2812 3.8324 12.5698 55.6264 4.6638 Value C1 = Sumof(Ay)/Sumof(A) = 3.2799 in. Value I = Sumof(Ay²) + Sumof(Io) - C1*Sumof(Ay) = 19.0624 in**4 Value As = Sumof(A) - Ashell = 3.1113 sq.in. K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035 Fh = ( K1 * Q ) = 46.8365 lb. Tension Stress, St = ( Fh/As ) = 15.0535 psi


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Allowed Stress, Sa = 0.6 * Yield Str = 22800.0000 psi d = B - R*Sin(theta) / theta = 7.0461 in. Bending Moment, M = Fh * d = 27.5014 ft.lb. Bending Stress, Sb = ( M * C1 / I ) = 56.7832 psi Allowed Stress, Sa = 2/3 * Yield Str = 25333.3340 psi Minimum Thickness of Baseplate per Moss : = ( 3 * Q * BasePlateWidth / ( 2 * BasePlateLength * AllStress ))½ = ( 3 * 230 * 3.00 / ( 2 * 11.040 * 25333.334 ))½ = 0.06 in. Calc. of Axial Load, Inter. Values and Comp. Stress Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1) = ( 11.0400 - 1.0 ) / ( 2 - 1 ) = 10.0400 in. Baseplate Pressure Area [Ap]: = e * Bpwid / 2 = 10.0400 * 3.0000 / 2 = 15.0600 sq.in. Axial Load [P]: = Ap * Bp = 15.1 * 6.95 = 104.6 lb. Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk = ( 3.000 - 1.0 - 0.375 ) * 0.375 + 10.0400 /2 * 0.375 = 2.492 sq.in. Compressive Stress [Sc]: = P/Ar = 104.6 / 2.4919 = 41.9935 psi Check of Outside Ribs: Inertia of Saddle, Outer Ribs - Longitudinal Direction Y A AY Ay² Io Rib 1.1875 0.7969 0.9463 0.3934 0.4883 Web 0.1875 1.8825 0.3530 0.1665 0.0441 Values 0.4849 2.6794 1.2993 0.5599 0.5324 Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2 = 0.0 /( 2 * 11.04 ) * 10.040 * 8.86 / 2 = 0.000 ft.lb. KL/R < Cc ( 13.3813 < 122.7360 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 13.38 )²/(2 * 122.74² )) * 38000 / ( 5/3+3*(13.38 )/(8* 122.74 )-( 13.38³)/(8*122.74³) Sca = 22123.93 psi AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 41.99 / 22123.93 + (0.00 /0.721 ) / 25333.33 Check = 0.00 Input Data for BasePlate Bolting Calculations: Total Number of Bolts per BasePlate Nbolts 4


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Total Number of Bolts in Tension/Baseplate Nbt 2 Bolt Material Specification SA-193 B7 Bolt Allowable Stress Stba 25000.00 psi Bolt Corrosion Allowance Bca 0.0000 in. Distance from Bolts to Edge Edgedis 1.2500 in. Nominal Bolt Diameter Bnd 0.5000 in. Thread Series Series UNC BasePlate Allowable Stress S 17100.00 psi Area Available in a Single Bolt BltArea 0.1260 sq.in. Saddle Load QO (Weight) QO 230.1 lb. Saddle Load QL (Wind/Seismic contribution) QL 0.0 lb. Maximum Transverse Force Ft 0.0 lb. Maximum Longitudinal Force Fl 0.0 lb. Bolt Area Calculation per Dennis R. Moss Bolt Area Requirement Due to Longitudinal Load [Bltarearl]: = 0.0 (QO > QL --> No Uplift in Longitudinal direction) Bolt Area due to Shear Load [Bltarears]: = Fl / (Stba * Nbolts) = 0.00 / (25000.00 * 4.00 ) = 0.0000 sq.in. Bolt Area due to Transverse Load Moment on Baseplate Due to Transverse Load [Rmom]: = B * Ft + Sum of X Moments = 1.00 * 0.00 + 0.00 = 0.00 ft.lb. Eccentricity (e): = Rmom / QO = 0.00 / 230.13 = 0.00 in. < Bplen/6 --> No Uplift in Transverse direction Bolt Area due to Transverse Load [Bltareart]: = 0 (No Uplift) Required of a Single Bolt [Bltarear] = max[Bltarearl, Bltarears, Bltareart] = max[0.0000 , 0.0000 , 0.0000 ] = 0.0000 sq.in. Zick Analysis: Stresses for the Right Saddle Shell Allowable Stress used in Calculation 17100.00 psi Shell Comp. Yield Stress used in Calculation 31000.00 psi Head Allowable Stress used in Calculation 17100.00 psi Saddle Force Q, Operating Case 230.13 lb. Stress Results for Zick Stresses: Actual Allowable Long. Stress at Top of Saddles 1803.38 11970.00 psi Long. Stress at Bottom of Saddles 1806.48 11970.00 psi Long. Stress at Top of Midspan 1756.28 11970.00 psi Long. Stress at Bottom of Midspan 1853.58 11970.00 psi Tangential Shear in Shell 102.06 13680.00 psi Tangential Shear in Head 102.06 13680.00 psi Circ. Stress at Horn of Saddle -116.17 -25650.00 psi


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Addl. Stress in Head as Stiffener 46.52 4275.00 psi Circ. Compressive Stress in Shell -207.28 -15500.00 psi Note: The Longitudinal Stress from the Zick Analysis is combined with the Longitudinal Pressure Stress to get the total stress. Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst ) = 230 + Max( 0 , 0 , 0 , 0 ) = 230.1 lb. Summary of Loads on this Saddle Support: Vertical Load on this Saddle 230.13 lb. Transverse Shear Load on this Saddle 0.00 lb. Longitudinal Shear Load on this Saddle 0.00 lb. Formulas and Substitutions for Zick Analysis Results: Longitudinal Bending (+-) at Midspan = ( 3 * Q * L * K.2 / ( pi * R² * ( Ts - Ca ))) = ( 3 * 230 * 3.50 * 0.7265 ) / ( 3.141 * 6.0469 * 6.0469 * ( 0.3281 - 0.0000 ))) = 46.57 psi Compute the area ratio [K]: = Pi * (Sin(Delta)/Delta - Cos(Delta) ) / (Delta + Sin(Delta) * Cos(Delta) - (Delta + Sin(Delta) * Cos(Delta) - 2 * Sin(Delta) * Sin(Delta)/Delta) = Pi * (Sin(1.396 ) / 1.396 - Cos(1.396 )) / ( 1.396 + Sin(1.396 ) * Cos(1.396 ) - 2 * Sin(1.396 ) * Sin(1.396 )/ 1.396 ) = 9.3799 Compute the moment fraction [X]: = 1 - (1 - A/L + ( R² - H² )/(2 * A*L ) )/(1 + (4*H )/( 3 * L ) ) = 1 - (1 - 0.188 /3.500 + (6.047² - 0.252²)/( 2 * 0.188 * 3.500 ) ) / (1 + (4 * 0.252 )/(3 * 3.500 ) ) = 0.0041 Intermediate Product [K.1]: = K * X * 4 * A / L = 9.380 * 0.004 * 4 * 0.188 / 3.500 = 0.0082 Longitudinal Bending (+-) at Saddle = ( 3 * Q * L * K.1 / ( pi * R² * ( Ts - Ca ))) = ( 3 * 230 * 3.50 * 0.0082 ) / ( 3.141 * 6.0469 * 6.0469 * ( 0.3281 - 0.0000 ))) = 0.52 psi Tangential Shear in Shell near Saddle = Q * K.5 / ( R * ( Ts - Ca ))) = 230 * 0.8799 / ( 6.0469 * ( 0.3281 - 0.0000 ) = 102.06 psi Tangential Shear in Head used as Stiffener = Q * K.5 / ( R * ( Th - Ca ))) = 230 * 0.8799 / ( 6.05 * ( 0.3281 - 0.0000 ) = 102.06 psi Circumferential Stress at Horn of Saddle = -Q/(4*TEM*(SADWTH+1.56*Sqrt(R*TCA)))-12*Q*R*K.7/(L*TEB) = -230 /( 4 * 0.3281 * (0.38 + 1.56 * Sqrt(6.0469 *0.3281 ))) -12.0 * 230 * 0.50 * 0.0130 / ( 3.5000 * 0.1077 ) = -116.17 psi


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Additional Tension in Head used as Stiffener = (Q/(R*(Hdthk-Ca)))*(3/8)*(sin(AL)²/(pi-AL+sin(AL*cos(AL))) = (230 / ( 6.0469 * ( 0.3281 - 0.0000 )))*(3/8)*( sin( 114.00 )²)/ ( pi - 114.00 + sin( 114.00 ) * cos( 114.00 ))) = 46.52 psi Circumferential Compression at Bottom of Shell = (Q*( K.9/( TEM9*( B+1.56 * Sqrt( R * TEM9 )))) = (230 *(0.7603 /(0.3281 *(0.38 +1.56*Sqrt(6.05 *0.3281 )))) = -207.28 psi Results for Vessel Ribs, Web and Base Baseplate Length Bplen 11.0400 in. Baseplate Thickness Bpthk 0.3750 in. Baseplate Width Bpwid 3.0000 in. Number of Ribs ( inc. outside ribs ) Nribs 2 Rib Thickness Ribtk 0.3750 in. Web Thickness Webtk 0.3750 in. Web Location Webloc Side Moment of Inertia of Saddle - Lateral Direction Y A AY Ay² Io Shell 0.1641 0.7210 0.1183 0.0194 0.0065 Wearplate 0.3281 0.0000 0.0000 0.0000 0.0000 Web 2.9766 1.9863 5.9124 17.5987 4.6442 BasePlate 5.8125 1.1250 6.5391 38.0083 0.0132 Totals 9.2812 3.8324 12.5698 55.6264 4.6638 Value C1 = Sumof(Ay)/Sumof(A) = 3.2799 in. Value I = Sumof(Ay²) + Sumof(Io) - C1*Sumof(Ay) = 19.0624 in**4 Value As = Sumof(A) - Ashell = 3.1113 sq.in. K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035 Fh = ( K1 * Q ) = 46.8365 lb. Tension Stress, St = ( Fh/As ) = 15.0535 psi Allowed Stress, Sa = 0.6 * Yield Str = 22800.0000 psi d = B - R*Sin(theta) / theta = 7.0461 in. Bending Moment, M = Fh * d = 27.5014 ft.lb. Bending Stress, Sb = ( M * C1 / I ) = 56.7832 psi Allowed Stress, Sa = 2/3 * Yield Str = 25333.3340 psi Minimum Thickness of Baseplate per Moss : = ( 3 * Q * BasePlateWidth / ( 2 * BasePlateLength * AllStress ))½ = ( 3 * 230 * 3.00 / ( 2 * 11.040 * 25333.334 ))½ = 0.06 in. Calc. of Axial Load, Inter. Values and Comp. Stress Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1) = ( 11.0400 - 1.0 ) / ( 2 - 1 ) = 10.0400 in. Baseplate Pressure Area [Ap]: = e * Bpwid / 2 = 10.0400 * 3.0000 / 2 = 15.0600 sq.in. Axial Load [P]:


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= Ap * Bp = 15.1 * 6.95 = 104.6 lb. Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk = ( 3.000 - 1.0 - 0.375 ) * 0.375 + 10.0400 /2 * 0.375 = 2.492 sq.in. Compressive Stress [Sc]: = P/Ar = 104.6 / 2.4919 = 41.9935 psi Check of Outside Ribs: Inertia of Saddle, Outer Ribs - Longitudinal Direction Y A AY Ay² Io Rib 1.1875 0.3047 0.3618 0.2257 0.0523 Web 0.1875 1.8825 0.3530 0.0365 0.0441 Values 0.3268 2.1872 0.7148 0.2622 0.0965 Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2 = 0.0 /( 2 * 11.04 ) * 10.040 * 8.86 / 2 = 0.000 ft.lb. KL/R < Cc ( 23.3509 < 122.7360 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 23.35 )²/(2 * 122.74² )) * 38000 / ( 5/3+3*(23.35 )/(8* 122.74 )-( 23.35³)/(8*122.74³) Sca = 21479.00 psi AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 41.99 / 21479.00 + (0.00 /0.214 ) / 25333.33 Check = 0.00 Input Data for BasePlate Bolting Calculations: Total Number of Bolts per BasePlate Nbolts 4 Total Number of Bolts in Tension/Baseplate Nbt 2 Bolt Material Specification SA-193 B7 Bolt Allowable Stress Stba 25000.00 psi Bolt Corrosion Allowance Bca 0.0000 in. Distance from Bolts to Edge Edgedis 1.2500 in. Nominal Bolt Diameter Bnd 0.5000 in. Thread Series Series UNC BasePlate Allowable Stress S 17100.00 psi Area Available in a Single Bolt BltArea 0.1260 sq.in. Saddle Load QO (Weight) QO 230.1 lb. Saddle Load QL (Wind/Seismic contribution) QL 0.0 lb. Maximum Transverse Force Ft 0.0 lb. Maximum Longitudinal Force Fl 0.0 lb. Bolt Area Calculation per Dennis R. Moss Bolt Area Requirement Due to Longitudinal Load [Bltarearl]: = 0.0 (QO > QL --> No Uplift in Longitudinal direction) Bolt Area due to Shear Load [Bltarears]: = Fl / (Stba * Nbolts) = 0.00 / (25000.00 * 4.00 ) = 0.0000 sq.in.


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Bolt Area due to Transverse Load Moment on Baseplate Due to Transverse Load [Rmom]: = B * Ft + Sum of X Moments = 1.00 * 0.00 + 0.00 = 0.00 ft.lb. Eccentricity (e): = Rmom / QO = 0.00 / 230.13 = 0.00 in. < Bplen/6 --> No Uplift in Transverse direction Bolt Area due to Transverse Load [Bltareart]: = 0 (No Uplift) Required of a Single Bolt [Bltarear] = max[Bltarearl, Bltarears, Bltareart] = max[0.0000 , 0.0000 , 0.0000 ] = 0.0000 sq.in. PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Horizontal Vessel Analysis (Test) STEP: 9 11:20a Sep 9,2008

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Zick Analysis: Stresses for the Left Saddle Horizontal Vessel Stress Calculations : Filled w/Water Shell Allowable Stress used in Calculation 17100.00 psi Shell Comp. Yield Stress used in Calculation 35000.00 psi Head Allowable Stress used in Calculation 17100.00 psi Saddle Force Q, Test Case, no Ext. Forces 230.32 lb. Stress Results for Zick Stresses: Actual Allowable Long. Stress at Top of Saddles 2690.40 11970.00 psi Long. Stress at Bottom of Saddles 2689.35 11970.00 psi Long. Stress at Top of Midspan 2643.26 11970.00 psi Long. Stress at Bottom of Midspan 2736.49 11970.00 psi Tangential Shear in Shell 102.14 13680.00 psi Tangential Shear in Head 102.14 13680.00 psi Circ. Stress at Horn of Saddle -81.81 -25650.00 psi Addl. Stress in Head as Stiffener 46.55 4275.00 psi Circ. Compressive Stress in Shell -102.67 -17500.00 psi Hydrostatic Test Pressure at top of Vessel 298.401 psig Note: The Longitudinal Stress from the Zick Analysis is combined with the Longitudinal Pressure Stress to get the total stress. Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst ) = 230 + Max( 0 , 0 , 0 , 0 ) = 230.3 lb. Summary of Loads on this Saddle Support: Vertical Load on this Saddle 230.32 lb. Transverse Shear Load on this Saddle 0.00 lb. Longitudinal Shear Load on this Saddle 0.00 lb. Formulas and Substitutions for Zick Analysis Results: Longitudinal Bending (+-) at Midspan = ( 3 * Q * L * K.2 / ( pi * R² * ( Ts - Ca ))) = ( 3 * 230 * 3.50 * 0.7265 ) / ( 3.141 * 6.0469 * 6.0469 * ( 0.3281 - 0.0000 ))) = 46.61 psi Compute the area ratio [K]: = Pi * (Sin(Delta)/Delta - Cos(Delta) ) / (Delta + Sin(Delta) * Cos(Delta) - (Delta + Sin(Delta) * Cos(Delta) - 2 * Sin(Delta) * Sin(Delta)/Delta) = Pi * (Sin(1.396 ) / 1.396 - Cos(1.396 )) / ( 1.396 + Sin(1.396 ) * Cos(1.396 ) - 2 * Sin(1.396 ) * Sin(1.396 )/ 1.396 ) = 9.3799 Compute the moment fraction [X]: = 1 - (1 - A/L + ( R² - H² )/(2 * A*L ) )/(1 + (4*H )/( 3 * L ) ) = 1 - (1 - 0.188 /3.500 + (6.047² - 0.252²)/( 2 * 0.188 * 3.500 ) ) / (1 + (4 * 0.252 )/(3 * 3.500 ) ) = 0.0041 Intermediate Product [K.1]: = K * X * 4 * A / L = 9.380 * 0.004 * 4 * 0.188 / 3.500 = 0.0082


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Longitudinal Bending (+-) at Saddle = ( 3 * Q * L * K.1 / ( pi * R² * ( Ts - Ca ))) = ( 3 * 230 * 3.50 * 0.0082 ) / ( 3.141 * 6.0469 * 6.0469 * ( 0.3281 - 0.0000 ))) = 0.52 psi Tangential Shear in Shell near Saddle = Q * K.5 / ( R * ( Ts - Ca ))) = 230 * 0.8799 / ( 6.0469 * ( 0.3281 - 0.0000 ) = 102.14 psi Tangential Shear in Head used as Stiffener = Q * K.5 / ( R * ( Th - Ca ))) = 230 * 0.8799 / ( 6.05 * ( 0.3281 - 0.0000 ) = 102.14 psi Circumferential Stress at Horn of Saddle = -Q/(4*TEM*(SADWTH+1.56*Sqrt(R*TCA)))-12*Q*R*K.7/(L*TEB) = -230 /( 4 * 0.3281 * (3.00 + 1.56 * Sqrt(6.0469 *0.3281 ))) -12.0 * 230 * 0.50 * 0.0130 / ( 3.5000 * 0.1077 ) = -81.81 psi Additional Tension in Head used as Stiffener = (Q/(R*(Hdthk-Ca)))*(3/8)*(sin(AL)²/(pi-AL+sin(AL*cos(AL))) = (230 / ( 6.0469 * ( 0.3281 - 0.0000 )))*(3/8)*( sin( 114.00 )²)/ ( pi - 114.00 + sin( 114.00 ) * cos( 114.00 ))) = 46.55 psi Circumferential Compression at Bottom of Shell = (Q*( K.9/( TEM9*( B+1.56 * Sqrt( R * TEM9 )))) = (230 *(0.7603 /(0.3281 *(3.00 +1.56*Sqrt(6.05 *0.3281 )))) = -102.67 psi Results for Vessel Ribs, Web and Base: Baseplate Length Bplen 11.0400 in. Baseplate Thickness Bpthk 0.3750 in. Baseplate Width Bpwid 3.0000 in. Number of Ribs ( inc. outside ribs ) Nribs 2 Rib Thickness Ribtk 0.3750 in. Web Thickness Webtk 0.3750 in. Web Location Webloc Side Moment of Inertia of Saddle - Lateral Direction Y A AY Ay² Io Shell 0.1641 0.7210 0.1183 0.0194 0.0065 Wearplate 0.3281 0.0000 0.0000 0.0000 0.0000 Web 2.9766 1.9863 5.9124 17.5987 4.6442 BasePlate 5.8125 1.1250 6.5391 38.0083 0.0132 Totals 9.2812 3.8324 12.5698 55.6264 4.6638 Value C1 = Sumof(Ay)/Sumof(A) = 3.2799 in. Value I = Sumof(Ay²) + Sumof(Io) - C1*Sumof(Ay) = 19.0624 in**4 Value As = Sumof(A) - Ashell = 3.1113 sq.in. K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035 Fh = ( K1 * Q ) = 46.8746 lb. Tension Stress, St = ( Fh/As ) = 15.0658 psi Allowed Stress, Sa = 0.6 * Yield Str = 22800.0000 psi d = B - R*Sin(theta) / theta = 7.0461 in.


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Bending Moment, M = Fh * d = 27.5238 ft.lb. Bending Stress, Sb = ( M * C1 / I ) = 56.8295 psi Allowed Stress, Sa = 2/3 * Yield Str = 25333.3340 psi Minimum Thickness of Baseplate per Moss : = ( 3 * Q * BasePlateWidth / ( 2 * BasePlateLength * AllStress ))½ = ( 3 * 230 * 3.00 / ( 2 * 11.040 * 25333.334 ))½ = 0.06 in. Calc. of Axial Load, Inter. Values and Comp. Stress Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1) = ( 11.0400 - 1.0 ) / ( 2 - 1 ) = 10.0400 in. Baseplate Pressure Area [Ap]: = e * Bpwid / 2 = 10.0400 * 3.0000 / 2 = 15.0600 sq.in. Axial Load [P]: = Ap * Bp = 15.1 * 6.95 = 104.7 lb. Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk = ( 3.000 - 1.0 - 0.375 ) * 0.375 + 10.0400 /2 * 0.375 = 2.492 sq.in. Compressive Stress [Sc]: = P/Ar = 104.7 / 2.4919 = 42.0277 psi Check of Outside Ribs: Inertia of Saddle, Outer Ribs - Longitudinal Direction Y A AY Ay² Io Rib 1.1875 0.7969 0.9463 0.3934 0.4883 Web 0.1875 1.8825 0.3530 0.1665 0.0441 Values 0.4849 2.6794 1.2993 0.5599 0.5324 Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2 = 0.0 /( 2 * 11.04 ) * 10.040 * 8.86 / 2 = 0.000 ft.lb. KL/R < Cc ( 13.3813 < 122.7360 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 13.38 )²/(2 * 122.74² )) * 38000 / ( 5/3+3*(13.38 )/(8* 122.74 )-( 13.38³)/(8*122.74³) Sca = 22123.93 psi AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 42.03 / 22123.93 + (0.00 /0.721 ) / 25333.33 Check = 0.00 Input Data for BasePlate Bolting Calculations: Total Number of Bolts per BasePlate Nbolts 4 Total Number of Bolts in Tension/Baseplate Nbt 2 Bolt Material Specification SA-193 B7 Bolt Allowable Stress Stba 25000.00 psi


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Bolt Corrosion Allowance Bca 0.0000 in. Distance from Bolts to Edge Edgedis 1.2500 in. Nominal Bolt Diameter Bnd 0.5000 in. Thread Series Series UNC BasePlate Allowable Stress S 17100.00 psi Area Available in a Single Bolt BltArea 0.1260 sq.in. Saddle Load QO (Weight) QO 230.3 lb. Saddle Load QL (Wind/Seismic contribution) QL 0.0 lb. Maximum Transverse Force Ft 0.0 lb. Maximum Longitudinal Force Fl 0.0 lb. Bolt Area Calculation per Dennis R. Moss Bolt Area Requirement Due to Longitudinal Load [Bltarearl]: = 0.0 (QO > QL --> No Uplift in Longitudinal direction) Bolt Area due to Shear Load [Bltarears]: = Fl / (Stba * Nbolts) = 0.00 / (25000.00 * 4.00 ) = 0.0000 sq.in. Bolt Area due to Transverse Load Moment on Baseplate Due to Transverse Load [Rmom]: = B * Ft + Sum of X Moments = 1.00 * 0.00 + 0.00 = 0.00 ft.lb. Eccentricity (e): = Rmom / QO = 0.00 / 230.32 = 0.00 in. < Bplen/6 --> No Uplift in Transverse direction Bolt Area due to Transverse Load [Bltareart]: = 0 (No Uplift) Required of a Single Bolt [Bltarear] = max[Bltarearl, Bltarears, Bltareart] = max[0.0000 , 0.0000 , 0.0000 ] = 0.0000 sq.in. Zick Analysis: Stresses for the Right Saddle Shell Allowable Stress used in Calculation 17100.00 psi Shell Comp. Yield Stress used in Calculation 35000.00 psi Head Allowable Stress used in Calculation 17100.00 psi Saddle Force Q, Test Case, no Ext. Forces 230.32 lb. Stress Results for Zick Stresses: Actual Allowable Long. Stress at Top of Saddles 2690.40 11970.00 psi Long. Stress at Bottom of Saddles 2689.35 11970.00 psi Long. Stress at Top of Midspan 2643.26 11970.00 psi Long. Stress at Bottom of Midspan 2736.49 11970.00 psi Tangential Shear in Shell 102.14 13680.00 psi Tangential Shear in Head 102.14 13680.00 psi Circ. Stress at Horn of Saddle -116.26 -25650.00 psi Addl. Stress in Head as Stiffener 46.55 4275.00 psi Circ. Compressive Stress in Shell -207.45 -17500.00 psi


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Hydrostatic Test Pressure at top of Vessel 298.401 psig Note: The Longitudinal Stress from the Zick Analysis is combined with the Longitudinal Pressure Stress to get the total stress. Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst ) = 230 + Max( 0 , 0 , 0 , 0 ) = 230.3 lb. Summary of Loads on this Saddle Support: Vertical Load on this Saddle 230.32 lb. Transverse Shear Load on this Saddle 0.00 lb. Longitudinal Shear Load on this Saddle 0.00 lb. Formulas and Substitutions for Zick Analysis Results: Longitudinal Bending (+-) at Midspan = ( 3 * Q * L * K.2 / ( pi * R² * ( Ts - Ca ))) = ( 3 * 230 * 3.50 * 0.7265 ) / ( 3.141 * 6.0469 * 6.0469 * ( 0.3281 - 0.0000 ))) = 46.61 psi Compute the area ratio [K]: = Pi * (Sin(Delta)/Delta - Cos(Delta) ) / (Delta + Sin(Delta) * Cos(Delta) - (Delta + Sin(Delta) * Cos(Delta) - 2 * Sin(Delta) * Sin(Delta)/Delta) = Pi * (Sin(1.396 ) / 1.396 - Cos(1.396 )) / ( 1.396 + Sin(1.396 ) * Cos(1.396 ) - 2 * Sin(1.396 ) * Sin(1.396 )/ 1.396 ) = 9.3799 Compute the moment fraction [X]: = 1 - (1 - A/L + ( R² - H² )/(2 * A*L ) )/(1 + (4*H )/( 3 * L ) ) = 1 - (1 - 0.188 /3.500 + (6.047² - 0.252²)/( 2 * 0.188 * 3.500 ) ) / (1 + (4 * 0.252 )/(3 * 3.500 ) ) = 0.0041 Intermediate Product [K.1]: = K * X * 4 * A / L = 9.380 * 0.004 * 4 * 0.188 / 3.500 = 0.0082 Longitudinal Bending (+-) at Saddle = ( 3 * Q * L * K.1 / ( pi * R² * ( Ts - Ca ))) = ( 3 * 230 * 3.50 * 0.0082 ) / ( 3.141 * 6.0469 * 6.0469 * ( 0.3281 - 0.0000 ))) = 0.52 psi Tangential Shear in Shell near Saddle = Q * K.5 / ( R * ( Ts - Ca ))) = 230 * 0.8799 / ( 6.0469 * ( 0.3281 - 0.0000 ) = 102.14 psi Tangential Shear in Head used as Stiffener = Q * K.5 / ( R * ( Th - Ca ))) = 230 * 0.8799 / ( 6.05 * ( 0.3281 - 0.0000 ) = 102.14 psi Circumferential Stress at Horn of Saddle = -Q/(4*TEM*(SADWTH+1.56*Sqrt(R*TCA)))-12*Q*R*K.7/(L*TEB) = -230 /( 4 * 0.3281 * (0.38 + 1.56 * Sqrt(6.0469 *0.3281 ))) -12.0 * 230 * 0.50 * 0.0130 / ( 3.5000 * 0.1077 ) = -116.26 psi Additional Tension in Head used as Stiffener


29

= (Q/(R*(Hdthk-Ca)))*(3/8)*(sin(AL)²/(pi-AL+sin(AL*cos(AL))) = (230 / ( 6.0469 * ( 0.3281 - 0.0000 )))*(3/8)*( sin( 114.00 )²)/ ( pi - 114.00 + sin( 114.00 ) * cos( 114.00 ))) = 46.55 psi Circumferential Compression at Bottom of Shell = (Q*( K.9/( TEM9*( B+1.56 * Sqrt( R * TEM9 )))) = (230 *(0.7603 /(0.3281 *(0.38 +1.56*Sqrt(6.05 *0.3281 )))) = -207.45 psi Results for Vessel Ribs, Web and Base Baseplate Length Bplen 11.0400 in. Baseplate Thickness Bpthk 0.3750 in. Baseplate Width Bpwid 3.0000 in. Number of Ribs ( inc. outside ribs ) Nribs 2 Rib Thickness Ribtk 0.3750 in. Web Thickness Webtk 0.3750 in. Web Location Webloc Side Moment of Inertia of Saddle - Lateral Direction Y A AY Ay² Io Shell 0.1641 0.7210 0.1183 0.0194 0.0065 Wearplate 0.3281 0.0000 0.0000 0.0000 0.0000 Web 2.9766 1.9863 5.9124 17.5987 4.6442 BasePlate 5.8125 1.1250 6.5391 38.0083 0.0132 Totals 9.2812 3.8324 12.5698 55.6264 4.6638 Value C1 = Sumof(Ay)/Sumof(A) = 3.2799 in. Value I = Sumof(Ay²) + Sumof(Io) - C1*Sumof(Ay) = 19.0624 in**4 Value As = Sumof(A) - Ashell = 3.1113 sq.in. K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035 Fh = ( K1 * Q ) = 46.8746 lb. Tension Stress, St = ( Fh/As ) = 15.0658 psi Allowed Stress, Sa = 0.6 * Yield Str = 22800.0000 psi d = B - R*Sin(theta) / theta = 7.0461 in. Bending Moment, M = Fh * d = 27.5238 ft.lb. Bending Stress, Sb = ( M * C1 / I ) = 56.8295 psi Allowed Stress, Sa = 2/3 * Yield Str = 25333.3340 psi Minimum Thickness of Baseplate per Moss : = ( 3 * Q * BasePlateWidth / ( 2 * BasePlateLength * AllStress ))½ = ( 3 * 230 * 3.00 / ( 2 * 11.040 * 25333.334 ))½ = 0.06 in. Calc. of Axial Load, Inter. Values and Comp. Stress Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1) = ( 11.0400 - 1.0 ) / ( 2 - 1 ) = 10.0400 in. Baseplate Pressure Area [Ap]: = e * Bpwid / 2 = 10.0400 * 3.0000 / 2 = 15.0600 sq.in. Axial Load [P]: = Ap * Bp


30

= 15.1 * 6.95 = 104.7 lb. Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk = ( 3.000 - 1.0 - 0.375 ) * 0.375 + 10.0400 /2 * 0.375 = 2.492 sq.in. Compressive Stress [Sc]: = P/Ar = 104.7 / 2.4919 = 42.0277 psi Check of Outside Ribs: Inertia of Saddle, Outer Ribs - Longitudinal Direction Y A AY Ay² Io Rib 1.1875 0.3047 0.3618 0.2257 0.0523 Web 0.1875 1.8825 0.3530 0.0365 0.0441 Values 0.3268 2.1872 0.7148 0.2622 0.0965 Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2 = 0.0 /( 2 * 11.04 ) * 10.040 * 8.86 / 2 = 0.000 ft.lb. KL/R < Cc ( 23.3509 < 122.7360 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 23.35 )²/(2 * 122.74² )) * 38000 / ( 5/3+3*(23.35 )/(8* 122.74 )-( 23.35³)/(8*122.74³) Sca = 21479.00 psi AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 42.03 / 21479.00 + (0.00 /0.214 ) / 25333.33 Check = 0.00 Input Data for BasePlate Bolting Calculations: Total Number of Bolts per BasePlate Nbolts 4 Total Number of Bolts in Tension/Baseplate Nbt 2 Bolt Material Specification SA-193 B7 Bolt Allowable Stress Stba 25000.00 psi Bolt Corrosion Allowance Bca 0.0000 in. Distance from Bolts to Edge Edgedis 1.2500 in. Nominal Bolt Diameter Bnd 0.5000 in. Thread Series Series UNC BasePlate Allowable Stress S 17100.00 psi Area Available in a Single Bolt BltArea 0.1260 sq.in. Saddle Load QO (Weight) QO 230.1 lb. Saddle Load QL (Wind/Seismic contribution) QL 0.0 lb. Maximum Transverse Force Ft 0.0 lb. Maximum Longitudinal Force Fl 0.0 lb. Bolt Area Calculation per Dennis R. Moss Bolt Area Requirement Due to Longitudinal Load [Bltarearl]: = 0.0 (QO > QL --> No Uplift in Longitudinal direction) Bolt Area due to Shear Load [Bltarears]: = Fl / (Stba * Nbolts) = 0.00 / (25000.00 * 4.00 ) = 0.0000 sq.in. Bolt Area due to Transverse Load


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Moment on Baseplate Due to Transverse Load [Rmom]: = B * Ft + Sum of X Moments = 1.00 * 0.00 + 0.00 = 0.00 ft.lb. Eccentricity (e): = Rmom / QO = 0.00 / 230.13 = 0.00 in. < Bplen/6 --> No Uplift in Transverse direction Bolt Area due to Transverse Load [Bltareart]: = 0 (No Uplift) Required of a Single Bolt [Bltarear] = max[Bltarearl, Bltarears, Bltareart] = max[0.0000 , 0.0000 , 0.0000 ] = 0.0000 sq.in. PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Nozzle Calcs. N2 - 2" NOZL: 1 11:20a Sep 9,2008

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INPUT VALUES, Nozzle Description: N2 - 2" From : 10 Pressure for Nozzle Reinforcement Calculations P 200.242 psig Temperature for Internal Pressure Temp 300 F Shell Material SA-234 WPB Shell Allowable Stress at Temperature S 20000.00 psi Shell Allowable Stress At Ambient Sa 20000.00 psi Inside Diameter of Elliptical Head D 12.0938 in. Aspect Ratio of Elliptical Head Ar 2.00 Head Actual Thickness T 0.3281 in. Head Internal Corrosion Allowance Cas 0.0000 in. Head External Corrosion Allowance Caext 0.0000 in. User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-105 Nozzle Allowable Stress at Temperature Sn 20000.00 psi Nozzle Allowable Stress At Ambient Sna 20000.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 0.00 deg Nozzle Diameter Dia 3.0000 in. Nozzle Size and Thickness Basis Idbn Actual Actual Thickness of Nozzle Thk 0.3125 in. Nozzle Corrosion Allowance Can 0.0000 in. Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 1.0000 in. Weld leg size between Nozzle and Pad/Shell Wo 0.3125 in. Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in. Nozzle Inside Projection H 0.0000 in. Weld leg size, Inside Nozzle to Shell Wi 0.0000 in. ASME Code Weld Type per UW-16 C The Pressure Design option was Design Pressure + static head NOZZLE CALCULATION, Description: N2 - 2" ASME Code, Section VIII, Division 1, 2004 A-06, UG-37 to UG-45 Actual Nozzle Outside Diameter Used in Calculation 3.000 in. Actual Nozzle Thickness Used in Calculation 0.312 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Elliptical Head, Tr [Int. Press] = (P*(K*(D+2*CA)))/(2*S*E-0.2*P) per UG-37(a)(3) = (200.24*(0.90*(12.0938+2*0.0000)))/(2 *20000*1.00-0.2*200.24) = 0.0545 in. Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*D/2)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (200.24*3.0000/2.0)/(20000*1.00+0.4*200.24) = 0.0150 in. UG-40, Thickness and Diameter Limit Results : [Int. Press]


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Effective material diameter limit, Dl 4.7500 in. Effective material thickness limit, no pad Tlnp 0.7812 in. Note: Taking a UG-36(c)(3)(a) exemption for N2 - 2" . 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. It may be necessary to force the program to print the areas per UG-37. UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] = Max( Min(Max(Max(UG45B1,UG16B),Max(UG45B2,UG16B)),UG45B4), UG45A ) = Max(Min(Max(Max(0.0606,0.0625),Max(0.0000,0.0625)),0.1890),0.0150) = 0.0625 < Minimum Nozzle Thickness 0.3125 in. OK Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F Weld Size Calculations, Description: N2 - 2" Intermediate Calc. for nozzle/shell Welds Tmin 0.3125 in. Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.2188 = 0.7 * TMIN 0.2209 = 0.7 * Wo in. The Drop for this Nozzle is : 0.1014 in. The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.4295 in. PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Nozzle Calcs. N4 - 1/2" NOZL: 2 11:20a Sep 9,2008

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INPUT VALUES, Nozzle Description: N4 - 1/2" From : 20 Pressure for Nozzle Reinforcement Calculations P 200.460 psig Temperature for Internal Pressure Temp 300 F Shell Material SA-106 B Shell Allowable Stress at Temperature S 17100.00 psi Shell Allowable Stress At Ambient Sa 17100.00 psi Inside Diameter of Cylindrical Shell D 12.0938 in. Shell Actual Thickness T 0.3281 in. Shell Internal Corrosion Allowance Cas 0.0000 in. Shell External Corrosion Allowance Caext 0.0000 in. Distance from Bottom/Left Tangent 1.7500 ft. User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-105 Nozzle Allowable Stress at Temperature Sn 20000.00 psi Nozzle Allowable Stress At Ambient Sna 20000.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 180.00 deg Nozzle Diameter Dia 1.1250 in. Nozzle Size and Thickness Basis Idbn Actual Actual Thickness of Nozzle Thk 0.1425 in. Nozzle Corrosion Allowance Can 0.0000 in. Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 0.5625 in. Weld leg size between Nozzle and Pad/Shell Wo 0.2500 in. Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in. Nozzle Inside Projection H 0.0000 in. Weld leg size, Inside Nozzle to Shell Wi 0.0000 in. ASME Code Weld Type per UW-16 C The Pressure Design option was Design Pressure + static head NOZZLE CALCULATION, Description: N4 - 1/2" ASME Code, Section VIII, Division 1, 2004 A-06, UG-37 to UG-45 Actual Nozzle Outside Diameter Used in Calculation 1.125 in. Actual Nozzle Thickness Used in Calculation 0.142 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*(D/2+CA))/(S*E-0.6*P) per UG-27 (c)(1) = (200.46*(12.0938/2+0.0000))/(17100*1.00-0.6*200.46) = 0.0714 in. Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*D/2)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (200.46*1.1250/2.0)/(20000*1.00+0.4*200.46) = 0.0056 in.

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Nozzle Calcs. N4 - 1/2" NOZL: 2 11:20a Sep 9,2008

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UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 1.7812 in. Effective material thickness limit, no pad Tlnp 0.3562 in. Note: Taking a UG-36(c)(3)(a) exemption for N4 - 1/2" . 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. It may be necessary to force the program to print the areas per UG-37. UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] = Max( Min(Max(Max(UG45B1,UG16B),Max(UG45B2,UG16B)),UG45B4), UG45A ) = Max(Min(Max(Max(0.0714,0.0625),Max(0.0000,0.0625)),0.1164),0.0056) = 0.0714 < Minimum Nozzle Thickness 0.1425 in. OK Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F Weld Size Calculations, Description: N4 - 1/2" Intermediate Calc. for nozzle/shell Welds Tmin 0.1425 in. Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.0997 = 0.7 * TMIN 0.1768 = 0.7 * Wo in. The Drop for this Nozzle is : 0.0262 in. The Cut Length for this Nozzle is, Drop + Ho + H + T : 0.9168 in. PV Elite 2007 ©1993-2007 by COADE Engineering Software


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INPUT VALUES, Nozzle Description: N1 - 4" From : 20 Pressure for Nozzle Reinforcement Calculations P 200.024 psig Temperature for Internal Pressure Temp 300 F Shell Material SA-106 B Shell Allowable Stress at Temperature S 17100.00 psi Shell Allowable Stress At Ambient Sa 17100.00 psi Inside Diameter of Cylindrical Shell D 12.0938 in. Shell Actual Thickness T 0.3281 in. Shell Internal Corrosion Allowance Cas 0.0000 in. Shell External Corrosion Allowance Caext 0.0000 in. Distance from Bottom/Left Tangent 1.7500 ft. User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-106 B Nozzle Allowable Stress at Temperature Sn 17100.00 psi Nozzle Allowable Stress At Ambient Sna 17100.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 0.00 deg Nozzle Diameter Dia 4.0000 in. Nozzle Size and Thickness Basis Idbn Nominal Nominal Thickness of Nozzle Thknom 40 Nozzle Flange Material SA-105 Nozzle Flange Type Slip on Nozzle Corrosion Allowance Can 0.0000 in. Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 8.0000 in. Weld leg size between Nozzle and Pad/Shell Wo 0.2500 in. Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in. Nozzle Inside Projection H 1.0000 in. Weld leg size, Inside Nozzle to Shell Wi 0.2500 in. ASME Code Weld Type per UW-16 C Class of attached Flange 150 Grade of attached Flange GR 1.1 The Pressure Design option was Design Pressure + static head NOZZLE CALCULATION, Description: N1 - 4" ASME Code, Section VIII, Division 1, 2004 A-06, UG-37 to UG-45 Actual Nozzle Outside Diameter Used in Calculation 4.500 in. Actual Nozzle Thickness Used in Calculation 0.237 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*(D/2+CA))/(S*E-0.6*P) per UG-27 (c)(1) = (200.02*(12.0938/2+0.0000))/(17100*1.00-0.6*200.02) = 0.0712 in.


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Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*D/2)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (200.02*4.5000/2.0)/(17100*1.00+0.4*200.02) = 0.0262 in. UG-40, Thickness and Diameter Limit Results : [Int. Press] Effective material diameter limit, Dl 8.0520 in. Effective material thickness limit, no pad Tlnp 0.5925 in. Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc Area Required Ar 0.287 NA NA sq.in. Area in Shell A1 1.034 NA NA sq.in. Area in Nozzle Wall A2 0.250 NA NA sq.in. Area in Inward Nozzle A3 0.281 NA NA sq.in. Area in Welds A4 0.125 NA NA sq.in. Area in Pad A5 0.000 NA NA sq.in. TOTAL AREA AVAILABLE Atot 1.690 NA NA sq.in. The Internal Pressure Case Governs the Analysis. Nozzle Angle Used in Area Calculations 90.00 Degs. The area available without a pad is Sufficient. Reinforcement Area Required for Nozzle [Ar]: = (Dlr*Tr+2*Thk*Tr*(1-fr1)) UG-37(c) = (4.0260*0.0712+2*(0.2370-0.0000)*0.0712*(1-1.0000)) = 0.287 sq.in. Areas per UG-37.1 but with DL = Diameter Limit, DLR = Corroded ID: Area Available in Shell [A1]: = (DL-Dlr)*(ES*(T-Cas)-Tr)-2*(Thk-Can)*(ES*(T-Cas)-Tr)*(1-fr1) = (8.052-4.026)*(1.00*(0.3281-0.000)-0.071)-2*(0.237-0.000) *(1.00*(0.3281-0.0000)-0.0712)*(1-1.0000) = 1.034 sq.in. Area Available in Nozzle Wall, no Pad [A2np]: = ( 2 * min(Tlnp,ho) ) * ( Thk - Can - Trn ) * fr2 = ( 2 * min(0.593 ,8.000 ) ) * ( 0.2370 - 0.0000 - 0.0262 ) * 1.0000 ) = 0.250 sq.in. Area Available in Nozzle Penetration [A3]: = 2*(Tn-Can-Can)*(min(H-Can,Tl, 2.5*Tn-Can-Can))*fr2 = 2 * ( 0.2370 ) * ( 0.5925 ) * 1.0000 = 0.281 sq.in. Area Available in Welds, no Pad [A4np]: = Wo² * fr2 + ( Wi-Can/0.707 )² * fr2 = 0.2500² * 1.0000 + ( 0.2500 )² * 1.0000 = 0.125 sq.in. UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] = Max( Min(Max(Max(UG45B1,UG16B),Max(UG45B2,UG16B)),UG45B4), UG45A ) = Max(Min(Max(Max(0.0712,0.0625),Max(0.0000,0.0625)),0.2074),0.0262) = 0.0712 < Minimum Nozzle Thickness 0.2074 in. OK M.A.W.P. Results for this Nozzle (Based on Areas) at this Location Approximate M.A.W.P. for given geometry 664.224 psig Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F


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Minimum Temp. at required thickness -155 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F Weld Size Calculations, Description: N1 - 4" Intermediate Calc. for nozzle/shell Welds Tmin 0.2370 in. Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.1659 = 0.7 * TMIN 0.1768 = 0.7 * Wo in. The Drop for this Nozzle is : 0.4342 in. The Cut Length for this Nozzle is, Drop + Ho + H + T : 9.3281 in. PV Elite 2007 ©1993-2007 by COADE Engineering Software


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INPUT VALUES, Nozzle Description: N3 - 2" From : 30 Pressure for Nozzle Reinforcement Calculations P 200.242 psig Temperature for Internal Pressure Temp 300 F Shell Material SA-234 WPB Shell Allowable Stress at Temperature S 17100.00 psi Shell Allowable Stress At Ambient Sa 17100.00 psi Inside Diameter of Elliptical Head D 12.0938 in. Aspect Ratio of Elliptical Head Ar 2.00 Head Actual Thickness T 0.3281 in. Head Internal Corrosion Allowance Cas 0.0000 in. Head External Corrosion Allowance Caext 0.0000 in. User Entered Minimum Design Metal Temperature -20.00 F Nozzle Material SA-105 Nozzle Allowable Stress at Temperature Sn 20000.00 psi Nozzle Allowable Stress At Ambient Sna 20000.00 psi Nozzle Diameter Basis (for tr calc only) Inbase OD Layout Angle 0.00 deg Nozzle Diameter Dia 3.0000 in. Nozzle Size and Thickness Basis Idbn Actual Actual Thickness of Nozzle Thk 0.3125 in. Nozzle Corrosion Allowance Can 0.0000 in. Joint Efficiency of Shell Seam at Nozzle Es 1.00 Joint Efficiency of Nozzle Neck En 1.00 Nozzle Outside Projection Ho 1.0000 in. Weld leg size between Nozzle and Pad/Shell Wo 0.3125 in. Groove weld depth between Nozzle and Vessel Wgnv 0.3750 in. Nozzle Inside Projection H 0.0000 in. Weld leg size, Inside Nozzle to Shell Wi 0.0000 in. ASME Code Weld Type per UW-16 C The Pressure Design option was Design Pressure + static head NOZZLE CALCULATION, Description: N3 - 2" ASME Code, Section VIII, Division 1, 2004 A-06, UG-37 to UG-45 Actual Nozzle Outside Diameter Used in Calculation 3.000 in. Actual Nozzle Thickness Used in Calculation 0.312 in. Nozzle input data check completed without errors. Reqd thk per UG-37(a)of Elliptical Head, Tr [Int. Press] = (P*(K*(D+2*CA)))/(2*S*E-0.2*P) per UG-37(a)(3) = (200.24*(0.90*(12.0938+2*0.0000)))/(2 *17100*1.00-0.2*200.24) = 0.0638 in. Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*D/2)/(S*E+0.4*P) per Appendix 1-1 (a)(1) = (200.24*3.0000/2.0)/(20000*1.00+0.4*200.24) = 0.0150 in. UG-40, Thickness and Diameter Limit Results : [Int. Press]


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Effective material diameter limit, Dl 4.7500 in. Effective material thickness limit, no pad Tlnp 0.7812 in. Note: Taking a UG-36(c)(3)(a) exemption for N3 - 2" . 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. It may be necessary to force the program to print the areas per UG-37. UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] = Max( Min(Max(Max(UG45B1,UG16B),Max(UG45B2,UG16B)),UG45B4), UG45A ) = Max(Min(Max(Max(0.0709,0.0625),Max(0.0000,0.0625)),0.1890),0.0150) = 0.0709 < Minimum Nozzle Thickness 0.3125 in. OK Minimum Design Metal Temperature (Nozzle Neck), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Nozzle MDMT Thickness Calc. per UCS-66 (a)1(b), MIN(tn,t,te), Curve: B Minimum Temp. w/o impact per UCS-66 -20 F Minimum Temp. at required thickness -155 F Minimum Temp. w/o impact per UG-20(f) -20 F Weld Size Calculations, Description: N3 - 2" Intermediate Calc. for nozzle/shell Welds Tmin 0.3125 in. Results Per UW-16.1: Required Thickness Actual Thickness Nozzle Weld 0.2188 = 0.7 * TMIN 0.2209 = 0.7 * Wo in. The Drop for this Nozzle is : 0.1014 in. The Cut Length for this Nozzle is, Drop + Ho + H + T : 1.4295 in. PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Nozzle Schedule STEP: 14 11:20a Sep 9,2008

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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. ------------------------------------------------------------------------------ N4 - 1/2" 1.125 - None 1.125 0.142 - - 0.92 N2 - 2" 3.000 - None 3.000 0.312 - - 1.43 N3 - 2" 3.000 - None 3.000 0.312 - - 1.43 N1 - 4" 4.000 40 SlipOn 4.500 0.237 - - 9.33 Note on the Cut Length Calculation: 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. Please Note: In the case of Oblique Nozzles, the Outside Diameter must be increased. The Re-Pad WIDTH around the nozzle is calculated as follows: Width of Pad = (Pad Outside Dia. (per above) - Nozzle Outside Dia.)/2 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. ------------------------------------------------------------------------------ N4 - 1/ SA-105 0.375 0.250 - - - N2 - 2" SA-105 0.375 0.312 - - - N3 - 2" SA-105 0.375 0.312 - - - N1 - 4" SA-106 B 0.375 0.250 - - 0.250 Nozzle Miscellaneous Data: Elevation/Distance Layout Projection Installed In Nozzle From Datum Angle Outside Inside Component ft. deg. in. in. ---------------------------------------------------------------------------- N4 - 1/2" 1.750 180.00 0.56 0.00 Shell N2 - 2" 0.252 0.00 1.00 0.00 Left Head N3 - 2" 2.998 0.00 1.00 0.00 Right Head N1 - 4" 1.750 0.00 8.00 1.00 Shell PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Nozzle Summary STEP: 15 11:20a Sep 9,2008

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Nozzle Calculation Summary Description Internal Ext MAPNC UG45 [tr] Weld Areas psig psig Path --------------------------------------------------------------------------- N2 - 2" ... ... OK 0.063 OK NoCalc[*] N4 - 1/2" ... ... OK 0.071 OK NoCalc[*] N1 - 4" 664.20 ... ... OK 0.071 OK Passed N3 - 2" ... ... OK 0.071 OK NoCalc[*] --------------------------------------------------------------------------- Min. - Nozzles 664.20 N1 - 4" Min. Shell&Flgs 229.54 Computed Vessel M.A.W.P. 229.54 psig [*] - This was a small opening and the areas were not computed. Note: MAWPs (Internal Case) shown above are at the High Point. Check the Spatial Relationship between the Nozzles From Node Nozzle Description X Coordinate, Layout Angle, Dia. Limit 10 N2 - 2" 0.000 0.000 4.750 20 N4 - 1/2" 21.000 180.000 1.781 20 N1 - 4" 21.000 0.000 8.052 30 N3 - 2" 0.000 0.000 4.750 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 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Vessel Design Summary STEP: 16 11:20a Sep 9,2008

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Design Code: ASME Code Section VIII Division 1, 2004 A-06 Diameter Spec : 12.750 in. OD Vessel Design Length, Tangent to Tangent 3.50 ft. Specified Datum Line Distance 0.00 ft. Shell/Head Matl SA-234 WPB Shell/Head Matl SA-106 B Nozzle Material SA-105 Internal Design Temperature 300 F Internal Design Pressure 200.00 psig External Design Temperature 0 F Maximum Allowable Working Pressure 229.54 psig External Max. Allowable Working Pressure 476.19 psig Hydrostatic Test Pressure 298.40 psig Required Minimum Design Metal Temperature -20 F Warmest Computed Minimum Design Metal Temperature -155 F Wind Design Code No Wind Loads Earthquake Design Code No Seismic Element Pressures and MAWP: psig Element Desc Internal External M.A.W.P Corr. All. Left Head 200.460 0.000 917.042 0.0000 Shell 200.460 0.000 763.391 0.0000 Right Head 200.460 0.000 784.004 0.0000 Liquid Level: 1.06 ft. Dens.: 62.400 lb./cu.ft. Sp. Gr.: 1.0 Element "To" Elev Length Element Thk R e q d T h k Joint Eff Type ft. ft. in. Int. Ext. Long Circ Ellipse 0.25 0.250 0.375 0.074 No Calc 0.85 0.70 Cylinder 3.25 3.000 0.375 0.087 No Calc 0.85 0.70 Ellipse 3.50 0.250 0.375 0.087 No Calc 0.85 0.70 Element thicknesses are shown as Nominal if specified, otherwise are Minimum Saddle Parameters: Saddle Width 0.375 in. Saddle Bearing Angle 120.000 deg. Centerline Dimension 12.000 in. Wear Pad Width 0.000 in. Wear Pad Thickness 0.000 in. Wear Pad Bearing Angle 0.000 deg. Distance from Saddle to Tangent 2.250 in. Baseplate Length 11.040 in. Baseplate Thickness 0.375 in. Baseplate Width 3.000 in. Number of Ribs (including outside ribs) 2 Rib Thickness 0.375 in. Web Thickness 0.375 in. Height of Center Web 6.000 in. Summary of Maximum Saddle Loads, Operating Case : Maximum Vertical Saddle Load 230.13 lb. Maximum Transverse Saddle Shear Load 0.00 lb.

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Vessel Design Summary STEP: 16 11:20a Sep 9,2008

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Maximum Longitudinal Saddle Shear Load 0.00 lb. Summary of Maximum Saddle Loads, Hydrotest Case : Maximum Vertical Saddle Load 230.32 lb. Maximum Transverse Saddle Shear Load 0.00 lb. Maximum Longitudinal Saddle Shear Load 0.00 lb. Weights: Fabricated - Bare W/O Removable Internals 304.2 lbm Shop Test - Fabricated + Water ( Full ) 495.2 lbm Shipping - Fab. + Rem. Intls.+ Shipping App. 304.2 lbm Erected - Fab. + Rem. Intls.+ Insul. (etc) 304.2 lbm Empty - Fab. + Intls. + Details + Wghts. 304.2 lbm Operating - Empty + Operating Liquid (No CA) 494.8 lbm Field Test - Empty Weight + Water (Full) 495.2 lbm PV Elite 2007 ©1993-2007 by COADE Engineering Software

Pressure Vesel Engineering Sample Job 2 PV Elite 2007 Licensee: PRESSURE VESSEL ENGINEERING FileName : Sample 2-Calculations 2007 Edition ------------ Problems/Failures Summary STEP: 17 11:20a Sep 9,2008

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Listed below are the known problem areas for the current design. If one or more of the design flags are turned on, please re-run the analysis. Some of these issues may be resolved when using updated input values. ** Warning: An ANSI Flange is limiting the MAWP and this may affect the pressure used in the Nozzle Reinforcement Calculations. Please review all reports carefully! PV Elite 2007 ©1993-2007 by COADE Engineering Software

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