calc. reheater

7/21/2019 Calc. Reheater

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Table of Contents

Input Echo :..........................................................................................................................................

Internal Pressure Calculations :..........................................................................................

External Pressure Calculations :..........................................................................................

Tubesheet Calc....................................................................................................................................

Wind Load Calculation : ...............................................................................................................

Earthquake Load Calculation : .................................................................................................

Center of Gravity Calculation : ............................................................................................

Horizontal Vessel Analysis (Ope.) :...................................................................................

Horizontal Vessel Analysis (Test) :...................................................................................

Nozzle Calcs. : Manhole ...............................................................................................................

Nozzle Calcs. : T1 ...........................................................................................................................

Nozzle Calcs. : T2 ...........................................................................................................................Nozzle Calcs. : S1 ...........................................................................................................................

Nozzle Calcs. : S2 ...........................................................................................................................

Nozzle Schedule :..............................................................................................................................

Nozzle Summary : ................................................................................................................................

Nozzle Flange MAWP :.......................................................................................................................

Element and Detail Weights : ...................................................................................................


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PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------Input Echo : Step: 1 3:11p Jan 11,2012

PV Elite Vessel Analysis Program: Input Data

Exchanger Design Pressures and Temperatures

Shell Side Design Pressure 20.000 barsChannel Side Design Pressure 25.000 barsShell Side Design Temperature 400 CChannel Side Design Temperature 400 C

Type of Hydrotest UG99-bHydrotest Position HorizontalProjection of Nozzle from Vessel Top 0.0000 mm.Projection of Nozzle from Vessel Bottom 0.0000 mm.Minimum Design Metal Temperature 0 CType of Construction WeldedSpecial Service NoneDegree of Radiography RT 1Miscellaneous Weight Percent 10.Use Higher Longitudinal Stresses (Flag) Y

Select t for Internal Pressure (Flag) NSelect t for External Pressure (Flag) NSelect t for Axial Stress (Flag) NSelect Location for Stiff. Rings (Flag) N

User Spectrum Data points specified for increments of Time Period

Time Period Sa/g----------------------0.010 0.1100.030 0.1100.050 0.1280.100 0.3200.150 0.4260.230 0.432

0.390 0.3221.000 0.1401.260 0.0882.000 0.0502.500 0.0373.000 0.0254.000 0.0125.000 0.0126.000 0.0120.000 0.000

Consider Vortex Shedding NPerform a Corroded Hydrotest YIs this a Heat Exchanger YesUser Defined Hydro. Press. (Used if > 0) 0.0000 bars

User defined MAWP 0.0000 barsUser defined MAPnc 0.0000 bars

Load Case 1 NP+EW+WI+FW+BWLoad Case 2 NP+EW+EE+FS+BSLoad Case 3 NP+OW+WI+FW+BWLoad Case 4 NP+OW+EQ+FS+BSLoad Case 5 NP+HW+HILoad Case 6 NP+HW+HELoad Case 7 IP+OW+WI+FW+BWLoad Case 8 IP+OW+EQ+FS+BSLoad Case 9 EP+OW+WI+FW+BWLoad Case 10 EP+OW+EQ+FS+BSLoad Case 11 HP+HW+HI


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Load Case 12 HP+HW+HELoad Case 13 IP+WE+EWLoad Case 14 IP+WF+CWLoad Case 15 IP+VO+OWLoad Case 16 IP+VE+EWLoad Case 17 NP+VO+OW

Load Case 18 FS+BS+IP+OWLoad Case 19 FS+BS+EP+OW

Wind Design Code IS-875Basic Wind Speed for IS-875 175.00 Km/hrWind Zone Number 6Base Elevation 0.0000 mm.Percent Wind for Hydrotest 60.Risk Factor 1.Terrain Category 2Equipment Class 1Topography Factor 1.Damping Factor (Beta) for Wind (Ope) 0.0100Damping Factor (Beta) for Wind (Empty) 0.0000Damping Factor (Beta) for Wind (Filled) 0.0000

Seismic Design Code IS-1893-RSMImportance Factor for IS-1893 1.000Soil Factor 1.000Zone Number 3.000Percent Seismic for Hydrotest 33.000Period of Vibration ( User defined ) Sec 0.000Damping Factor 2.000


Time Period Sa/g----------------------0.010 0.1100.030 0.110

0.050 0.1280.100 0.3200.150 0.4260.230 0.4320.390 0.3221.000 0.1401.260 0.0882.000 0.0502.500 0.0373.000 0.0254.000 0.0125.000 0.0126.000 0.0120.000 0.000

Design Nozzle for Des. Press. + St. Head YConsider MAP New and Cold in Noz. Design NConsider External Loads for Nozzle Des. YUse ASME VIII-1 Appendix 1-9 N

Material Database Year Current w/Addenda or Code Year

Configuration Directives:

Do not use Nozzle MDMT Interpretation VIII-1 01-37 NoUse Table G instead of exact equation for "A" YesShell Head Joints are Tapered YesCompute "K" in corroded condition Yes


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Use Code Case 2286 NoUse Flange Bolt Stress ratio for Hydrotest ratio YesUse the MAWP to compute the MDMT Yes

Complete Listing of Vessel Elements and Details:

Element From Node 10Element To Node 20Element Type EllipticalDescription CHANNEL BONNETDistance "FROM" to "TO" 50.000 mm.Inside Diameter 1200.0 mm.Element Thickness 19.000 mm.Internal Corrosion Allowance 3.2000 mm.Nominal Thickness 22.000 mm.External Corrosion Allowance 0.0000 mm.Design Internal Pressure 25.000 barsDesign Temperature Internal Pressure 400 CDesign External Pressure 1.0500 barsDesign Temperature External Pressure 400 CEffective Diameter Multiplier 1.2

Material Name [Normalized] SA-516 70Allowable Stress, Ambient 137.90 N./mmAllowable Stress, Operating 101.30 N./mmAllowable Stress, Hydrotest 235.81 N./mmMaterial Density 0.007833 kg./cmP Number Thickness 31.750 mm.Yield Stress, Operating 181.12 N./mmUCS-66 Chart Curve Designation DExternal Pressure Chart Name CS-2UNS Number K02700Product Form Plate

Efficiency, Longitudinal Seam 1.Efficiency, Circumferential Seam 1.Elliptical Head Factor 2.

Element From Node 10Detail Type LiquidDetail ID STEAMDist. from "FROM" Node / Offset dist 0.0000 mm.Height/Length of Liquid 1200.0 mm.Liquid Density 0.0008497 kg./cm

Element From Node 10Detail Type NozzleDetail ID ManholeDist. from "FROM" Node / Offset dist 0.0000 mm.Nozzle Diameter 24. in.Nozzle Schedule NoneNozzle Class 0Layout Angle 0.

Blind Flange (Y/N) NWeight of Nozzle ( Used if > 0 ) 0.0000 KgfGrade of Attached Flange NoneNozzle Matl SA-266 2

--------------------------------------------------------------------

Element From Node 20Element To Node 30Element Type CylinderDescription CHANNELDistance "FROM" to "TO" 580.00 mm.Inside Diameter 1200.0 mm.Element Thickness 20.000 mm.


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Internal Corrosion Allowance 3.2000 mm.Nominal Thickness 20.000 mm.External Corrosion Allowance 0.0000 mm.Design Internal Pressure 25.000 barsDesign Temperature Internal Pressure 400 CDesign External Pressure 1.0500 bars

Design Temperature External Pressure 400 CEffective Diameter Multiplier 1.2Material Name [Normalized] SA-516 70Efficiency, Longitudinal Seam 1.Efficiency, Circumferential Seam 1.

Element From Node 20Detail Type LiquidDetail ID STEAMDist. from "FROM" Node / Offset dist 0.0000 mm.Height/Length of Liquid 1200.0 mm.Liquid Density 0.0008497 kg./cm

Element From Node 20Detail Type Nozzle

Detail ID T1Dist. from "FROM" Node / Offset dist 300.00 mm.Nozzle Diameter 12. in.Nozzle Schedule NoneNozzle Class 0Layout Angle 0.Blind Flange (Y/N) NWeight of Nozzle ( Used if > 0 ) 0.0000 KgfGrade of Attached Flange NoneNozzle Matl [Normalized] SA-516 70

Element From Node 20Detail Type NozzleDetail ID T2Dist. from "FROM" Node / Offset dist 300.00 mm.

Nozzle Diameter 12. in.Nozzle Schedule NoneNozzle Class 0Layout Angle 180.Blind Flange (Y/N) NWeight of Nozzle ( Used if > 0 ) 0.0000 KgfGrade of Attached Flange NoneNozzle Matl [Normalized] SA-516 70

--------------------------------------------------------------------

Element From Node 30Element To Node 40Element Type CylinderDescription SHELL

Distance "FROM" to "TO" 10180. mm.Inside Diameter 1200.0 mm.Element Thickness 16.000 mm.Internal Corrosion Allowance 3.2000 mm.Nominal Thickness 16.000 mm.External Corrosion Allowance 0.0000 mm.Design Internal Pressure 20.000 barsDesign Temperature Internal Pressure 400 CDesign External Pressure 1.0500 barsDesign Temperature External Pressure 400 CEffective Diameter Multiplier 1.2Material Name [Normalized] SA-516 70Efficiency, Longitudinal Seam 1.Efficiency, Circumferential Seam 1.


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Element From Node 30Detail Type SaddleDetail ID Fixed SaddleDist. from "FROM" Node / Offset dist 1030.0 mm.Width of Saddle 184.00 mm.

Height of Saddle at Bottom 900.00 mm.Saddle Contact Angle 120.Height of Composite Ring Stiffener 0.0000 mm.Width of Wear Plate 200.00 mm.Thickness of Wear Plate 16.000 mm.Contact Angle, Wear Plate (degrees) 132.

Element From Node 30Detail Type SaddleDetail ID Sliding EndDist. from "FROM" Node / Offset dist 8530.0 mm.Width of Saddle 184.00 mm.Height of Saddle at Bottom 900.00 mm.Saddle Contact Angle 120.Height of Composite Ring Stiffener 0.0000 mm.

Width of Wear Plate 200.00 mm.Thickness of Wear Plate 16.000 mm.Contact Angle, Wear Plate (degrees) 132.

Element From Node 30Detail Type LiquidDetail ID HTFDist. from "FROM" Node / Offset dist 0.0000 mm.Height/Length of Liquid 1200.0 mm.Liquid Density 0.0008797 kg./cm

Element From Node 30Detail Type NozzleDetail ID S1Dist. from "FROM" Node / Offset dist 370.00 mm.

Nozzle Diameter 10. in.Nozzle Schedule 80Nozzle Class 0Layout Angle 180.Blind Flange (Y/N) NWeight of Nozzle ( Used if > 0 ) 0.0000 KgfGrade of Attached Flange NoneNozzle Matl SA-106 B

Element From Node 30Detail Type NozzleDetail ID S2Dist. from "FROM" Node / Offset dist 370.00 mm.Nozzle Diameter 10. in.Nozzle Schedule 80

Nozzle Class 0Layout Angle 0.Blind Flange (Y/N) NWeight of Nozzle ( Used if > 0 ) 0.0000 KgfGrade of Attached Flange NoneNozzle Matl SA-106 B

--------------------------------------------------------------------

Element From Node 40Element To Node 50Element Type EllipticalDescription SHELL BONNETDistance "FROM" to "TO" 5.0000 mm.


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Inside Diameter 1200.0 mm.Element Thickness 16.000 mm.Internal Corrosion Allowance 3.2000 mm.Nominal Thickness 20.000 mm.External Corrosion Allowance 0.0000 mm.Design Internal Pressure 20.000 bars

Design Temperature Internal Pressure 400 CDesign External Pressure 1.0500 barsDesign Temperature External Pressure 400 CEffective Diameter Multiplier 1.2Material Name [Normalized] SA-516 70Efficiency, Longitudinal Seam 1.Efficiency, Circumferential Seam 1.Elliptical Head Factor 2.

Element From Node 40Detail Type LiquidDetail ID HTFDist. from "FROM" Node / Offset dist 0.0000 mm.Height/Length of Liquid 1200.0 mm.Liquid Density 0.0008797 kg./cm

PVElite is a registered trademark of COADE, Inc. [2010]


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PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------Internal Pressure Calculations : Step: 3 3:11p Jan 11,2012

Element Thickness, Pressure, Diameter and Allowable Stress :

| | Int. Press | Nominal | Total Corr| Element | Allowable |From| To | + Liq. Hd | Thickness | Allowance | Diameter | Stress(SE)|

| | bars | mm. | mm. | mm. | N./mm |

---------------------------------------------------------------------------CHANNEL BO| 25.1002 | 22.0000 | 3.20000 | 1200.00 | 101.297 |

CHANNEL| 25.1002 | 20.0000 | 3.20000 | 1200.00 | 101.297 |SHELL| 20.1038 | 16.0000 | 3.20000 | 1200.00 | 101.297 |

SHELL BONN| 20.1038 | 20.0000 | 3.20000 | 1200.00 | 101.297 |

Element Required Thickness and MAWP :

| | Design | M.A.W.P. | M.A.P. | Minimum | Required |From| To | Pressure | Corroded | New & Cold | Thickness | Thickness |

| | bars | bars | bars | mm. | mm. |----------------------------------------------------------------------------CHANNEL BO| 25.0000 | 26.5488 | 43.5280 | 19.0000 | 18.0795 |

CHANNEL| 25.0000 | 27.6471 | 45.0627 | 20.0000 | 18.3731 |SHELL| 20.0000 | 21.1201 | 36.1921 | 16.0000 | 15.3163 |

SHELL BONN| 20.0000 | 21.4961 | 36.6734 | 16.0000 | 15.1117 |

Summary of Heat Exchanger Maximum Allowable Working Pressures :

Note: For ASME UHX designs, the following values include MAWPs thatconsider the tubesheet, tubes, tube/tubesheet joint etc. Thesevalues were determined by iteration. Review the tubesheet analysisreport for more information.

Shell Side MAWP = 21.120 barsShell Side MAPnc = 36.192 barsChannel Side MAWP = 26.549 barsChannel Side MAPnc = 43.528 bars

Internal Pressure Calculation Results :

ASME Code, Section VIII, Division 1, 2007 A-09

Elliptical Head From 10 To 20 SA-516 70 , UCS-66 Crv. D at 400 C

CHANNEL BONNET

Required Thickness due to Internal Pressure [tr]:= (P*D*Kcor)/(2*S*E-0.2*P) Appendix 1-4(c)= (25.100*1206.4000*0.993)/(2*101.30*1.00-0.2*25.100)= 14.8795 + 3.2000 = 18.0795 mm.

Max. Allowable Working Pressure at given Thickness, corroded [MAWP]:Less Operating Hydrostatic Head Pressure of 0.100 bars= (2*S*E*t)/(Kcor*D+0.2*t) per Appendix 1-4 (c)= (2*101.30*1.00*15.8000)/(0.993*1206.4000+0.2*15.8000)= 26.649 - 0.100 = 26.549 bars

Maximum Allowable Pressure, New and Cold [MAPNC]:= (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c)= (2*137.90*1.00*19.0000)/(1.000*1200.0000+0.2*19.0000)= 43.528 bars

Actual stress at given pressure and thickness, corroded [Sact]:= (P*(Kcor*D+0.2*t))/(2*E*t)= (25.100*(0.993*1206.4000+0.2*15.8000))/(2*1.00*15.8000)= 95.410 N./mm

Straight Flange Required Thickness:


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= (P*R)/(S*E-0.6*P) + c per UG-27 (c)(1)= (25.100*603.2000)/(101.30*1.00-0.6*25.100)+3.200= 18.373 mm.

Straight Flange Maximum Allowable Working Pressure:

Less Operating Hydrostatic Head Pressure of 0.100 bars

= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)= (101.30 * 1.00 * 18.8000 ) / (603.2000 + 0.6 * 18.8000 )= 30.990 - 0.100 = 30.890 bars

Factor K, corroded condition [Kcor]:= ( 2 + ( Inside Diameter/( 2 * Inside Head Depth ))2)/6= ( 2 + ( 1206.400 /( 2 * 303.200 ))2)/6= 0.992983

Percent Elong. per UCS-79, VIII-1-01-57 (75*tnom/Rf)*(1-Rf/Ro) 7.674 %

Note: Please Check Requirements of UCS-79 as Elongation is > 5%.

MDMT Calculations in the Knuckle Portion:

Govrn. thk, tg = 19.000 , tr = 11.554 , c = 3.2000 mm. , E* = 1.00

Stress Ratio = tr * (E*) / (tg - c) = 0.731 , Temp. Reduction = 15 C

Min Metal Temp. w/o impact per UCS-66 -41 CMin Metal Temp. at Required thickness (UCS 66.1) -48 C

MDMT Calculations in the Head Straight Flange:

Govrn. thk, tg = 22.000 , tr = 9.325 , c = 3.2000 mm. , E* = 1.00Stress Ratio = tr * (E*) / (tg - c) = 0.496 , Temp. Reduction = 34 C


Cylindrical Shell From 20 To 30 SA-516 70 , UCS-66 Crv. D at 400 C

CHANNEL

Required Thickness due to Internal Pressure [tr]:= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)= (25.100*603.2000)/(101.30*1.00-0.6*25.100)= 15.1731 + 3.2000 = 18.3731 mm.

Max. Allowable Working Pressure at given Thickness, corroded [MAWP]:Less Operating Hydrostatic Head Pressure of 0.100 bars= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)= (101.30*1.00*16.8000)/(603.2000+0.6*16.8000)= 27.747 - 0.100 = 27.647 bars

Maximum Allowable Pressure, New and Cold [MAPNC]:= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)= (137.90*1.00*20.0000)/(600.0000+0.6*20.0000)= 45.063 bars

Actual stress at given pressure and thickness, corroded [Sact]:= (P*(R+0.6*t))/(E*t)= (25.100*(603.2000+0.6*16.8000))/(1.00*16.8000)= 91.633 N./mm

Percent Elongation per UCS-79 (50*tnom/Rf)*(1-Rf/Ro) 1.639 %

Minimum Design Metal Temperature Results:



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Cylindrical ShellFrom 30 To 40 SA-516 70 , UCS-66 Crv. D at 400 C

SHELL

Required Thickness due to Internal Pressure [tr]:= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)= (20.104*603.2000)/(101.30*1.00-0.6*20.104)= 12.1163 + 3.2000 = 15.3163 mm.

Max. Allowable Working Pressure at given Thickness, corroded [MAWP]:Less Operating Hydrostatic Head Pressure of 0.104 bars= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)= (101.30*1.00*12.8000)/(603.2000+0.6*12.8000)= 21.224 - 0.104 = 21.120 bars

Maximum Allowable Pressure, New and Cold [MAPNC]:= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)

= (137.90*1.00*16.0000)/(600.0000+0.6*16.0000)= 36.192 bars

Actual stress at given pressure and thickness, corroded [Sact]:= (P*(R+0.6*t))/(E*t)= (20.104*(603.2000+0.6*12.8000))/(1.00*12.8000)= 95.951 N./mm

Percent Elongation per UCS-79 (50*tnom/Rf)*(1-Rf/Ro) 1.316 %

Minimum Design Metal Temperature Results:



Elliptical Head From 40 To 50 SA-516 70 , UCS-66 Crv. D at 400 C

SHELL BONNET

Required Thickness due to Internal Pressure [tr]:= (P*D*Kcor)/(2*S*E-0.2*P) Appendix 1-4(c)= (20.104*1206.4000*0.993)/(2*101.30*1.00-0.2*20.104)= 11.9117 + 3.2000 = 15.1117 mm.

Max. Allowable Working Pressure at given Thickness, corroded [MAWP]:Less Operating Hydrostatic Head Pressure of 0.104 bars= (2*S*E*t)/(Kcor*D+0.2*t) per Appendix 1-4 (c)= (2*101.30*1.00*12.8000)/(0.993*1206.4000+0.2*12.8000)= 21.600 - 0.104 = 21.496 bars

Maximum Allowable Pressure, New and Cold [MAPNC]:= (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c)= (2*137.90*1.00*16.0000)/(1.000*1200.0000+0.2*16.0000)= 36.673 bars

Actual stress at given pressure and thickness, corroded [Sact]:= (P*(Kcor*D+0.2*t))/(2*E*t)= (20.104*(0.993*1206.4000+0.2*12.8000))/(2*1.00*12.8000)= 94.281 N./mm

Straight Flange Required Thickness:


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= (P*R)/(S*E-0.6*P) + c per UG-27 (c)(1)= (20.104*603.2000)/(101.30*1.00-0.6*20.104)+3.200= 15.316 mm.

Straight Flange Maximum Allowable Working Pressure:

Less Operating Hydrostatic Head Pressure of 0.104 bars

= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)= (101.30 * 1.00 * 16.8000 ) / (603.2000 + 0.6 * 16.8000 )= 27.747 - 0.104 = 27.644 bars

Factor K, corroded condition [Kcor]:= ( 2 + ( Inside Diameter/( 2 * Inside Head Depth ))2)/6= ( 2 + ( 1206.400 /( 2 * 303.200 ))2)/6= 0.992983

Percent Elong. per UCS-79, VIII-1-01-57 (75*tnom/Rf)*(1-Rf/Ro) 7.009 %

Note: Please Check Requirements of UCS-79 as Elongation is > 5%.

MDMT Calculations in the Knuckle Portion:

Govrn. thk, tg = 16.000 , tr = 9.188 , c = 3.2000 mm. , E* = 1.00

Stress Ratio = tr * (E*) / (tg - c) = 0.718 , Temp. Reduction = 16 C


MDMT Calculations in the Head Straight Flange:



Hydrostatic Test Pressure Results:

Exchanger Shell Side Hydrostatic Test Pressures:

Pressure per UG99b = 1.3 * M.A.W.P. * Sa/S 34.572 barsPressure per UG99b[34] = 1.3 * Design Pres * Sa/S 32.739 barsPressure per UG99c = 1.3 * M.A.P. - Head(Hyd) 47.050 barsPressure per UG100 = 1.1 * M.A.W.P. * Sa/S 29.254 barsPressure per PED = 1.43 * MAWP 30.202 bars

Exchanger Channel Side Hydrostatic Test Pressures:

Pressure per UG99b = 1.3 * M.A.W.P. * Sa/S 43.459 barsPressure per UG99b[34] = 1.3 * Design Pres * Sa/S 40.924 barsPressure per UG99c = 1.3 * M.A.P. - Head(Hyd) 56.586 barsPressure per UG100 = 1.1 * M.A.W.P. * Sa/S 36.773 barsPressure per PED = 1.43 * MAWP 37.965 bars

Horizontal Test performed per: UG-99b

Stresses on Elements due to Hydrostatic Test Pressure:

From To Stress Allowable Ratio PressureCHANNEL BONNET 165.6 235.8 0.702 43.58CHANNEL 159.1 235.8 0.675 43.58SHELL 165.6 235.8 0.702 34.69SHELL BONNET 162.7 235.8 0.690 34.69

Elements Suitable for Internal Pressure.



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PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------External Pressure Calculations : Step: 4 3:11p Jan 11,2012

External Pressure Calculation Results :

ASME Code, Section VIII, Division 1, 2007 A-09

Elliptical Head From 10 to 20 Ext. Chart: CS-2 at 400 C

CHANNEL BONNET

Elastic Modulus from Chart: CS-2 at 400 C : 0.16283E+09 KPa.

Results for Maximum Allowable External Pressure (MAEP):Tca OD D/t Factor A B

15.800 1238.00 78.35 0.0017726 59.21EMAP = B/(K0*D/t) = 59.2099 /(0.9000 *78.3544 ) = 8.3958 bars

Results for Required Thickness (Tca):Tca OD D/t Factor A B

3.579 1238.00 345.90 0.0004015 32.69EMAP = B/(K0*D/t) = 32.6922 /(0.9000 *345.9015 ) = 1.0501 bars

Cylindrical Shell From 20 to 30 Ext. Chart: CS-2 at 400 C

CHANNEL


Results for Maximum Allowable External Pressure (MAEP):Tca OD SLEN D/t L/D Factor A B

16.800 1240.00 11015.00 73.81 8.8831 0.0002325 18.93EMAP = (4*B)/(3*(D/t)) = (4*18.9304 )/(3*73.8095 ) = 3.4195 bars

Results for Required Thickness (Tca):Tca OD SLEN D/t L/D Factor A B

10.943 1240.00 11015.00 113.31 8.8831 0.0001096 8.92EMAP = (4*B)/(3*(D/t)) = (4*8.9243 )/(3*113.3124 ) = 1.0500 bars

Results for Maximum Stiffened Length (Slen):Tca OD SLEN D/t L/D Factor A B

16.800 1240.00 0.32E+22 73.81 .5000E+02 0.0002078 16.92EMAP = (4*B)/(3*(D/t)) = (4*16.9181 )/(3*73.8095 ) = 3.0560 bars

Cylindrical ShellFrom 30 to 40 Ext. Chart: CS-2 at 400 C

SHELL


Results for Maximum Allowable External Pressure (MAEP):Tca OD SLEN D/t L/D Factor A B

12.800 1232.00 11015.00 96.25 8.9407 0.0001431 11.65

EMAP = (4*B)/(3*(D/t)) = (4*11.6538 )/(3*96.2500 ) = 1.6143 bars

Results for Required Thickness (Tca):Tca OD SLEN D/t L/D Factor A B

10.895 1232.00 11015.00 113.08 8.9407 0.0001094 8.91EMAP = (4*B)/(3*(D/t)) = (4*8.9061 )/(3*113.0808 ) = 1.0501 bars

Results for Maximum Stiffened Length (Slen):Tca OD SLEN D/t L/D Factor A B

12.800 1232.00 0.23E+10 96.25 .5000E+02 0.0001202 9.79EMAP = (4*B)/(3*(D/t)) = (4*9.7858 )/(3*96.2500 ) = 1.3555 bars

Elliptical Head From 40 to 50 Ext. Chart: CS-2 at 400 C


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PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------External Pressure Calculations : Step: 4 3:11p Jan 11,2012

SHELL BONNET


Results for Maximum Allowable External Pressure (MAEP):Tca OD D/t Factor A B

12.800 1232.00 96.25 0.0014430 56.63EMAP = B/(K0*D/t) = 56.6350 /(0.9000 *96.2500 ) = 6.5376 bars

Results for Required Thickness (Tca):Tca OD D/t Factor A B

3.562 1232.00 345.91 0.0004015 32.69EMAP = B/(K0*D/t) = 32.6919 /(0.9000 *345.9053 ) = 1.0501 bars

External Pressure Calculations

| | Section | Outside | Corroded | Factor | Factor |From| To | Length | Diameter | Thickness | A | B |

| | mm. | mm. | mm. | | N./mm |---------------------------------------------------------------------------

10| 20| No Calc | 1238.00 | 15.8000 | 0.0017726 | 59.2099 |

20| 30| 11015.0 | 1240.00 | 16.8000 | 0.00023250 | 18.9304 |30| 40| 11015.0 | 1232.00 | 12.8000 | 0.00014313 | 11.6538 |40| 50| No Calc | 1232.00 | 12.8000 | 0.0014430 | 56.6350 |


| | External | External | External | External |From| To | Actual T. | Required T.|Des. Press. | M.A.W.P. |

| | mm. | mm. | bars | bars |----------------------------------------------------------------

10| 20| 19.0000 | 6.77905 | 1.05000 | 8.39582 |20| 30| 20.0000 | 14.1432 | 1.05000 | 3.41949 |30| 40| 16.0000 | 14.0949 | 1.05000 | 1.61429 |40| 50| 16.0000 | 6.76167 | 1.05000 | 6.53757 |Minimum 1.614


| | Actual Len.| Allow. Len.| Ring Inertia | Ring Inertia |From| To | Bet. Stiff.| Bet. Stiff.| Required | Available |

| | mm. | mm. | cm**4 | cm**4 |-------------------------------------------------------------------

10| 20| No Calc | No Calc | No Calc | No Calc |20| 30| 11015.0 | 3.214E+21 | No Calc | No Calc |30| 40| 11015.0 | 2.296E+09 | No Calc | No Calc |40| 50| No Calc | No Calc | No Calc | No Calc |

Elements Suitable for External Pressure.



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PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------

ASME TS Calc : Case: 1 3:11p Jan 11,2012

Input Echo, Tubesheet Number 1, Description: FIXED T/S

Main Shell Description: SHELLShell Design Pressure Ps 20.00 barsShell Thickness ts 16.0000 mm.

Shell Corrosion Allowance cas 3.2000 mm.Inside Diameter of Shell Ds 1200.000 mm.Shell Temperature for Internal Pressure Ts 400.00 CShell Material SA-516 70

Note: Using 2 * Yield for Discontinuity Stress Allowable (UG-23(e)), Sps.Make sure that material properties at this temperature are nottime-dependent for: SA-516 70

Shell Material UNS Number K02700Shell Allowable Stress at Temperature Ss 101.30 N./mmShell Allowable Stress at Ambient 137.90 N./mm

Channel Description: CHANNELChannel Type: Cylinder

Channel Design Pressure Pt 25.00 barsChannel Thickness tc 20.0000 mm.Channel Corrosion Allowance cac 3.2000 mm.Inside Diameter of Channel Dc 1200.000 mm.Channel Design Temperature TEMPC 400.00 CChannel Material SA-516 70

Note: Using 2Sy for Discontinuity Stress Allowable (UG-23(e)). Make surethat material properties at this temperature are not time-dependentfor : SA-516 70

Channel Material UNS Number K02700Channel Allowable Stress at Temperature Sc 101.30 N./mmChannel Allowable Stress at Ambient 137.90 N./mm

Number of Tubes Holes Nt 780Tube Wall Thickness et 2.1100 mm.Tube Outside Diameter D 25.4000 mm.Straight Tube Length (bet. inner tubsht faces) L 9865.00 mm.Design Temperature of the Tubes 400.00 CTube Material SA-179Tube Material UNS Number K01200Is this a Welded Tube NoTube Material Specification used Smls. tubeTube Allowable Stress at Temperature 73.38 N./mmTube Allowable Stress At Ambient 92.39 N./mmTube Yield Stress At Operating Temperature Syt 123.95 N./mmTube Pitch (Center to Center Spacing) P 33.0000 mm.Tube Layout Pattern Triangular

Fillet Weld Leg af 2.1100 mm.Groove Weld Leg ag 2.1100 mm.Tube-Tubesheet Joint Weld Type Full StrengthMethod for Tube-Tubesheet Jt. Allow. UW-20Tube-Tubesheet Joint Classification c

Radius to Outermost Tube Hole Center ro 507.000 mm.Largest Center-to-Center Tube Distance Ul 80.0000 mm.Length of Expanded Portion of Tube ltx 125.0000 mm.Tube-side pass partition groove depth hg 0.0000 mm.

Tubesheet TYPE: U-tube, Integral both sides, Conf. a

Tubesheet Design Metal Temperature T 400.00 C


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Tubesheet Material Specification SA-266 2

Note: Using 2 * Yield for Discontinuity Stress Allowable (UG-23(e)), Sps.Make sure that material properties at this temperature are nottime-dependent for Material: SA-266 2

Tubesheet Material UNS Number K03506Tubesheet Allowable Stress at Temperature S 101.30 N./mmTubesheet Allowable Stress at Ambient Tt 137.90 N./mmThickness of Tubesheet h 140.0000 mm.Tubesheet Corr. Allowance (Shell side) Cats 3.2000 mm.Tubesheet Corr. Allowance (Channel side) Catc 3.2000 mm.Tubesheet Outside Diameter A 1240.000 mm.Area of the Untubed Lanes AL 800.0 cmIs Exchanger in Creep range (skip EP, Use 3S for Sps) NO

Stress Reduction Option Perform Elastic-Plastic CalculationPerform Differential Pressure Design NORun Multiple Load Cases YESShell Side Vacuum Pressure Pexts 1.0500 barsChannel Side Vacuum Pressure Pextc 1.0500 bars

Tubesheet Integral with BothTubesheet Extended as Flange No

ASME TubeSheet Results per Part UHX, 2007 A-09

Elasticity/Expansion Material Properties :

Shell - TM-1 Carbon Steels with C


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EMAWP = (4*B)/(3*(D/T)) = ( 4 *62.5014 )/( 3 *12.0379 ) = 69.2232 bars

Results for Reqd Thickness for Ext. Pressure (Tca):TCA ODCA SLEN D/T L/D Factor A B

0.8863 25.40 10372.00 28.66 50.0000 0.0013393 45.25EMAWP = (4*B)/(3*(D/T)) = ( 4 *45.2517 )/( 3 *28.6587 ) = 21.0519 bars

Summary of Tube Required Thickness Results:Total Required Thickness including Corrosion all. 0.8863 mm.Allowable Internal Pressure at Corroded thickness 130.58 barsRequired Internal Design Pressure 26.05 barsAllowable External Pressure at Corroded thickness 69.22 barsRequired External Design Pressure 21.05 bars

-----------------------------------------------------------------

Detailed Tubesheet Results for load Case 3 un-corr. (Ps + Pt)-----------------------------------------------------------------

Results for ASME U-tube Tubesheet Calculations for Configuration a,Per Edition 2007 A-09, Original Thickness :

Minimum Required Thickness for Shear [HreqS]:= 1/(4 * Mu) * (Do/(0.8 * S)) * |Ps - Pt| + Cats + Catc= 1/(4 * 0.230 ) * (1039.40 /(0.8 * 101.30 )) * |20.00 - 25.00 | + 0.000= 6.9620 mm.

UHX-12.5.1 Step 1:

Compute the Equivalent Outer Tube Limit Circle Diameter [Do]:= 2 * ro + dt= 2 * 507.0000 + 25.4000 = 1039.400 mm.

Determine the Basic Ligament Efficiency for Shear [mu]:= (p - dt) / p= (33.000 - 25.400 ) / 33.000 = 0.230

UHX-12.5.2 Step 2 :

Compute the Ratio [Rhos]:= Ds / Do (Configurations a, b, c)= 1200.0000 / 1039.4000 = 1.1545

Compute the Ratio [Rhoc]:= Dc / Do (Configurations a, e, f)= 1200.0000 / 1039.4000 = 1.1545

Moment on Tubesheet due to Pressures (Ps, Pt) [Mts]:= Do/16 * [(Rhos-1)*(Rhos+1)* Ps - (Rhoc-1) * (Rhoc+1) * Pt ]= 1039.400/16 * [ (1.155 - 1) * (1.155 + 1) * 20.000 -(1.155 - 1) * (1.155 + 1) * 25.000 ]

= -121695.3125 bars*mm.

UHX-12.5.3 Step 3, Determination of Effective Elastic Properties :

Compute the Ratio [rho]:= ltx / h = 125.0000 / 140.0000 = 0.8929 ( must be 0


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= 33.0000 / sqrt( 1 - 4 * min( 800.00 *100.000 , 4*1039.400 *33.000 )(3.141* 1039.400) )

= 34.6751 mm.

Compute the Effective Ligament Efficiency for Bending [mu*]:= (p* - d*) / p* = (34.6751 - 22.6486 ) / 34.6751 = 0.34684

E*/E and nu* for Triangular pattern from Fig. UHX-11.3.h/p = 4.242424 ; mu* = 0.346835E*/E = 0.342977 ; nu* = 0.327877 ; E* = 58230020. KPa.

Note: As h/p (4.242) is > 2, data values for h/p = 2 were used.

UHX-12.5.4 Step 4:

Compute Shell Coefficient [betaS]:= (( 12 * (1-nus))^0.25 )/((Ds + ts) * ts )= (( 12 * (1 - 0.30) )^0.25 ) / (( 1200.0000 + 16.0000 ) * 16.0000 )= 0.0130 1/mm.

Determine Shell Coefficient [ks]:

= betaS * Es * ts / ( 6 * (1 - rnus) )= 0.013 * .17116E+07 * 16.000 / ( 6 * (1 - 0.300) )= 16733650.0000 bars*mm.

Determine Shell Coefficient [Lambdas]:= (6*Ds*ks)/h * (1 + h*betaS + *(h*betaS)/2 )= 6* 1200.000 * .16734E+08/140.000 * ( 1 + 140.000 *0.013 + 1.665 )= 197103.3281 bars

Determine Shell Coefficient [deltaS]:= Ds/(4 * Es * Ts) * ( 1 - nus/2 )= 1200.000/( 4 * .17116E+09 * 16.000 ) * ( 1 - 0.3 /2 )= 1.0957472324

Calculate Parameter [OmegaS]:

= rhos * ks * betaS * deltaS( 1 + h * betaS )= 1.1545 * .16734E+08 * 0.0130 * 1.095747 ( 1 + 140.0000 * 0.0130 )= 7946.4849 mm.

Determine Channel Coefficient [betac]:= (( 12 * (1 - nuc) )^0.25 )/((Dc + tc) * tc )^0.5= (( 12 * (1 - 0.30) )^0.25 )/((1200.0000 + 20.0000 ) * 20.0000 )^0.5= 0.0116 1/mm.

Determine Channel Coefficient [kc]:= betac * Ec * tc / ( 6 * (1 - rnus) )= 0.012 * .17116E+07 * 20.000 / ( 6 * (1 - 0.300) )= 29184520.0000 bars*mm.

Determine Channel Coefficient [Lambdac]:

= (6*Dc*kc)/h * (1 + h*betac + (h*betac)/2)= 6*1200.000 *.29185E+08/(140.000) * ( 1 + 140.000 *0.012 + 1.327 )= 302977.8125 bars

Determine Channel Coefficient [deltaC]:= Dc/(4 * Ec * Tc) * ( 1 - nuc/2 )= 1200.000/( 4 * .17116E+09 * 20.000 ) * ( 1 - 0.3 /2 )= 0.8765977621

Calculate Parameter [OmegaC]:= rhoc * kc * Betac * deltaC( 1 + h * betac )= 1.1545 * .29185E+08 * 0.0116 * 0.876598 ( 1 + 140.0000 * 0.0116 )= 9215.9766 mm.


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UHX-12.5.5 Step 5:

Diameter ratio [K]:= A / Do = 1240.0000 / 1039.4000 = 1.1930

Determine Coefficient [F]:

= (1 - nu*)/E* * ( Lambdas + Lambdac + E * ln(K) )= (1 - 0.33 )/.58230E+08 * ( 197103.33 + 302977.81 += .16978E+09 * ln(1.19 ) )= 0.9230

UHX-12.5.6 Step 6:

Moment Acting on Unperforated Tubesheet Rim [M*]= Mts + OmegaC * Pt - OmegaS * Ps= -0.1E+06 + 131648.297 * 25.000 - 97877.453 * 20.000= -50225.6211 bars*mm.

UHX-12.5.7 Step 7:

Maximum Bending Moment acting on Periphery of Tubesheet [Mp]:

= ((M*) - Do/32 * F * (Ps - Pt) ) / (1 + F)= ((-50225.62 ) - 1039.400/32 * 0.923 * (20.00 - 25.00 ) ) / (1 + 0.92 )= 54906.8750 bars*mm.

Maximum Bending Moment acting on Center of Tubesheet [Mo]:= Mp + Do/64 * (3 + rnu*)(Ps - Pt)= 54906.88 + 1039.400/64 * (3 + 0.328 )(20.00 - 25.00 )= -225974.2969 bars*mm.

Maximum Bending Moment acting on Tubesheet [M]:= Max( |Mp|, |Mo| )= Max( |54906.875 |, | -0.2E+06| )= 225974.2969 bars*mm.

UHX-12.5.8 Results for Step 8:

Tubesheet Bending Stress at Original Thickness:= 6 * M / ( (mu*) * ( h - hg') )= 6 * 225974.297 / ( (0.3468 ) * ( 140.0000 - 0.0000 ) )= 19.9460 N./mm

The Allowable Tubesheet Bending Stress [SigmaAll]:= 2 * S = 2 * 101.30 = 202.59 N./mm

Tubesheet Bending Stress at Final Thickness [Sigma]:= 6 * M / ( (mu*) * ( h - hg')= 6 * 150155.375 / ( (0.3564 ) * ( 35.3304 - 0.0000 )= 202.5509 N./mm

Required Tubesheet Thickness, for Bending Stress [HreqB]:

= H + CATS + CATC = 35.3304 + 0.0000 + 0.0000 = 35.3304 mm.

Required Tubesheet Thickness for Given Loadings (includes CA) [Hreq]:= Max( HreqB, HreqS ) = Max( 35.3304 , 6.9620 ) = 35.3304 mm.

UHX-12.5.9 Step 9:

|Ps - Pt| = |20.00 - 25.00 | = 5.000 bars

Shear Stress check [Tau_limit]:= 3.2 * S * MU * h / Do= 3.2 * 14691.37 * 0.230 * 140.000 / 1039.40 = 100.55 bars

Average Shear Stress at the Outer Edge of Perforated Region [Tau]:


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= 1/(4* Mu) * (Do/h) * |Ps - Pt|= 1/(4*0.230)*(1039.40/140.00)*|20.00-25.00|N./mm= 4.03 N./mm

UHX-12.5.10 Results for Step 10:

Note: For a given Shell thickness of: 16.000 mm.Min. Shell len. adjacent to the tubesheet is: 249.415 mm.

Axial Shell Membrane Stress [Sigmasm]:= Ds / (4 * ts * (Ds + ts) ) * Ps= 1200.0000 / (4 * 16.0000 * (1200.0000 + 16.0000 ) ) * 20.000= 37.009 N./mm

Axial Shell Bending Stress [Sigmasb]:= 6*ks/ts * ( betaS * P's + 6*(1 - rnu*) / (E*) *Do/h * (1 + h * betaS/2) * (Mp + Do / 32 * (Ps - Pt) ))

= 6*376196.03 /16.000 * [ 0.013 *0.22 + 6*(1 - 0.328 )/.58230E+08 *1039.400 /140.000 * (1 + 140.000 * 0.013 /2) *(54906.88 + 1039.400/32 *(20.00 - 25.00 )) ]

= 91.823 N./mm

Shell Membrane + Bending Stress [Sigmas]:= |Sigma_sm| + |Sigma_sb| (Should be


20/86



Required Tubesheet Thk., for Bending Stress after Elas-Plas iteration [HreqB]:= H + CATS + CATC = 35.3304 + 0.0000 + 0.0000 = 35.3304 mm.

Required Tubesheet Thk. after Elas-Plas iteration (includes CA) [Hreq]:= Max( HreqB, HreqS ) = Max( 35.3304 , 6.9620 ) = 35.3304 mm.

Tube Weld Size Results per UW-20:Tube Strength [Ft]:= 3.1415 * t * ( do - t ) * Sa= 3.1415 * 2.110 * ( 25.400 - 2.110 ) * 73.38 = 1155.108 Kgf

Fillet Weld Strength [Ff]:= .55 * 3.1415 * af * (do + 0.67*af) * Sw (but not > Ft)= .55 * 3.1415 * 2.110 * (25.400 + 0.67*2.110 ) * 73.38= 731.4294 Kgf

Groove Weld Strength [Fg]:= .85 * 3.1415 * ag * (do + 0.67*ag) * Sw (but not > Ft)= .85 * 3.1415 * 2.110 * (25.400 + 0.67*2.110 ) * 73.38= 1130.3909 Kgf

Max. Allow. Tube-Tubesheet Joint load, Lmax= Ft = 1155.1075 Kgf

Design Strength Ratio [fd]:= 1.0000

Weld Strength Factor [fw]:= Sot / ( Min(Sot, S) ) = 1.0000

Min Weld Length [ar]:= 2 *( ( (0.75 * do) + 1.07*t*(do - t)* fw * fd ) ) - .75 * do)= 2.6669 mm.

Minimum Required Fillet Weld Leg afr 1.3334 mm.

Minimum Required Groove Weld Leg agr 1.3334 mm.

Tube-Tubesheet Jt allowable, 1155.11 is >= tube strength 1155.11 Kgf

Note: This tube-tubesheet joint is a Full Strength joint

Stress/Force summary for loadcase 3 un-corr. (Ps + Pt):------------------------------------------------------------------------

Stress Description Actual Allowable Pass/Fail------------------------------------------------------------------------Tubesheet bend. stress 20.1


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Case# Tbsht Extnsn Bend Allwd Shear Allwd Type Fail----------------------------------------------------------------------------1uc 98.440 ... 113 203 21 81 Fvs+Pt Ok2uc 85.189 ... 91 203 17 81 Ps+Fvt Ok3uc 35.330 ... 20 203 4 81 Ps+Pt Ok1c 111.041 ... 132 203 22 81 Fvs+Pt-Ca Ok

2c 97.892 ... 107 203 18 81 Ps+Fvt-Ca Ok3c 40.835 ... 23 203 4 81 Ps+Pt-Ca Ok----------------------------------------------------------------------------Max: 111.0410 ... mm. 0.653 0.271 (Str. Ratio)

Load Case Definitions:Fvs,Fvt - User-defined Shell-side and Tube-side vacuum pressures or 0.0.Ps, Pt - Shell-side and Tube-side Design Pressures.Ca - With or Without Corrosion Allowance.

Shell and Channel Stress Summary:-- Integral Cyl. Reqd. Thk. Shell Stress Channel Stress PassCase# Shell Channel Stress Allwd Stress Allwd Fail----------------------------------------------------------------------------

1uc ... ... 138 152 289 362 Ok2uc ... ... 259 362 121 152 Ok3uc ... ... 129 152 174 362 Ok1c ... ... 165 362 347 362 Ok2c ... ... 319 362 145 152 Ok3c ... ... 164 362 210 362 Ok----------------------------------------------------------------------------Max ... ... 0.911 0.959

Summary of Thickness Comparisons for 6 Load Cases:----------------------------------------------------------------------------

Thickness (mm.) Required Actual P/F----------------------------------------------------------------------------Tubesheet Thickness : 111.041 140.000 OkTube Thickness : 0.886 2.110 Ok

Tube-Tubesheet Fillet Weld Leg : 1.333 2.110 OkTube-Tubesheet Groove Weld Leg : 1.333 2.110 Ok----------------------------------------------------------------------------

Given Shell Thickness: 16.0000 mm.Given Channel Thickness: 20.0000 mm.

Min Shell length of thk, (16.000) adj. to tubesheet: 249.415 mm.Min Channel length of thk, (20.000) adj. to tubesheet: 278.855 mm.

Note: This is a full strength Tube to Tubesheet Joint.

Tubesheet MAWP used to Compute Hydrotest Pressure:

Stress / Force | Tubeside (0 shellside) | Shellside (0 tubeside) |Condition | MAWP |Stress Rat.| MAWP |Stress Rat.|

------------------------------------------------------------------------------Tubesheet Bending Stress | 41.20 | 1.000 | 40.61 | 1.000 |Tubesheet Shear Stress | 95.95 | 1.000 | 95.95 | 1.000 |Shell Stress (Axial, Junc) | 31.98 | 0.526 | 23.16 | 1.000 |Tubesheet-Channel Junction | 26.60 | 1.000 | 23.16 | 0.581 |Tube Pressure Stress | 130.58 | 1.000 | 69.22 | 1.000 |------------------------------------------------------------------------------Minimum MAWP | 26.60 | | 23.16 | |

Tubesheet MAPnc used to Compute Hydrotest Pressure:

Stress / Force | Tubeside (0 shellside) | Shellside (0 tubeside) |


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Condition | MAPnc |Stress Rat.| MAPnc |Stress Rat.|------------------------------------------------------------------------------Tubesheet Bending Stress | 64.43 | 1.000 | 63.56 | 1.000 |Tubesheet Shear Stress | 136.88 | 1.000 | 136.88 | 1.000 |Shell Stress (Axial, Junc) | 64.43 | 0.621 | 41.12 | 1.000 |Tubesheet-Channel Junction | 46.06 | 1.000 | 41.12 | 0.666 |

Tube Pressure Stress | 164.42 | 1.000 | 106.12 | 1.000 |------------------------------------------------------------------------------Minimum MAPnc | 46.06 | | 41.12 | |



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Wind Load Calculation : Step: 7 3:11p Jan 11,2012

Wind Load Calculations per India Std. IS-875 (Part-3) - 1987, Amd. 1&2 (2003):

Actual Vessel Height to Diameter ratio 0.000Force Coefficient per IS:875 Table 23, Cf 0.700User Entered Basic Wind Speed 175.0 Km/hr

Base Elevation 0.00 mm.Wind Zone Number 6Risk Factor (k1) 1.0000Terrain Category 2Equipment Class ATopography Factor (k3) 1.0000Use Gust Response Factor (Dynamic Analysis) NoUser entered Beta Value ( Operating Case ) 0.0100

Vessel Operating Natural Frequency 33.000 HzVessel Height to Diameter ratio 0.000

Note: The computation of the Gust Response factor G is not required

because the height to diameter ratio is less than or equal to 5and the natural frequency is greater than 1.0 hertz.

From fo` FO E S G(ope) G(emp) G(tst)------------------------------------------------------------------10 891.69 9.12 0.0057 0.0631 1.0000 1.0000 1.000020 891.69 9.12 0.0057 0.0631 1.0000 1.0000 1.000030 891.69 9.12 0.0057 0.0631 1.0000 1.0000 1.000040 891.69 9.12 0.0057 0.0631 1.0000 1.0000 1.0000

Design Wind Speed (Vz):= Basic Wind Speed * k1 * k2 * k3

Height Factor := 0.6 * Vz

Element Wind Load := Wind Area * Cf * Height Factor

From Height k1 k2 k3 Vz Cfmm. m/sec

------------------------------------------------------------10 900.00 1.0000 1.0071 1.0000 48.95 0.700020 900.00 1.0000 1.0071 1.0000 48.95 0.700030 900.00 1.0000 1.0071 1.0000 48.95 0.700040 900.00 1.0000 1.0071 1.0000 48.95 0.7000

Wind Load Calculation

| | Wind | Wind | Wind | Height | Element |

From| To | Height | Diameter | Area | Factor | Wind Load || | mm. | mm. | cm | Kgs/m | Kgf |

---------------------------------------------------------------------------10| 20| 900.000 | 1485.60 | 3844.51 | 146.670 | 39.4571 |20| 30| 900.000 | 1488.00 | 8630.40 | 146.670 | 88.5757 |30| 40| 900.000 | 1478.40 | 150501. | 146.670 | 1544.63 |40| 50| 900.000 | 1478.40 | 3131.57 | 146.670 | 32.1400 |



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PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------Earthquake Load Calculation : Step: 8 3:11p Jan 11,2012

Seismic Analysis Results per IS 1893 (Part 1): 2002.

Importance Factor as Entered by User I 1.0000Zone Number 3Soil Type Soft SoilForce Factor R 3.0000

Time Period of Vibration ( program or user ) 0.1000 SecondsValue of Sa/g from user Spectrum Data 0.3200Percent Damping 2.0000 %

Horizontal Seismic Coefficient Ah:= Z * min( I/R, 1.0 ) * Sa/g * DampVal / 2= 0.1600 * min( 0.3333 , 1.0 ) * 0.3200 * 1.0000 / 2= 0.080


Time Period Sa/g----------------------0.010 0.110

0.030 0.1100.050 0.1280.100 0.3200.150 0.4260.230 0.4320.390 0.3221.000 0.1401.260 0.0882.000 0.0502.500 0.0373.000 0.0254.000 0.0125.000 0.0126.000 0.0120.000 0.000

Actual Time Period = 0.100 secsComputed Sa/g = 0.320

Note: It was indicated to ignore the damping factor, assuming that the SiteSpectrum specified is per the actual damping value of this vessel.The value of "DampVal" has been set to 1 (not used).

Determine the Seismic Base Shear per 7.5.3 [Vb]:= Ah * W= 0.0800 * 31391= 2511.3 Kgf

The sum of the Weight Wi * hi[SumWh2]:= 11300919296.0 Kgf mm.

Element Load Sample for the First Element per 7.7.1 [Q1]:= ( Vb * W1 * h1 / SumWh2 ) * Scalar= ( 2511.3 * 5231.9 * 600.0 / .11301E+11 ) * 1.000= 418.553 Kgf

Earthquake Load Calculation

| | Earthquake | Earthquake | Element |From| To | Height | Weight | Ope Load |

| | mm. | Kgf | Kgf |-------------------------------------------------

10| 20| 600.000 | 5231.91 | 418.553 |20| 30| 600.000 | 5231.91 | 418.553 |


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PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------Earthquake Load Calculation : Step: 8 3:11p Jan 11,2012

30|Sadl| 600.000 | 5231.91 | 418.553 |Sadl| 40| 600.000 | 5231.91 | 418.553 |30| 40| 600.000 | 5231.91 | 418.553 |40| 50| 600.000 | 5231.91 | 418.553 |



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PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------Center of Gravity Calculation : Step: 9 3:11p Jan 11,2012

Shop/Field Installation Options :

Note : The CG is computed from the first Element From Node

Center of Gravity of Saddles 5410.0 mm.Center of Gravity of Liquid 5420.1 mm.Center of Gravity of Nozzles 51.6 mm.

Center of Gravity of Bare Shell New and Cold 5311.68 mm.Center of Gravity of Bare Shell Corroded 5289.22 mm.

Vessel CG in the Operating Condition 5235.60 mm.Vessel CG in the Fabricated (Shop/Empty) Condition 4979.10 mm.



27/86


28/86

PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------Horizontal Vessel Analysis (Ope.) : Step: 10 3:11p Jan 11,2012

= 18285.1 Kgf

Summary of Loads at the base of this Saddle:Vertical Load (including saddle weight) 18433.56 KgfTransverse Shear Load Saddle 1255.66 KgfLongitudinal Shear Load Saddle 2511.32 Kgf

Formulas and Substitutions for Horizontal Vessel Analysis:

Note: Wear Plates are assumed to be Welded k = 0.1

The Computed K values from Table 4.15.1:K1 = 0.1066 K2 = 1.1707 K3 = 0.8799 K4 = 0.4011K5 = 0.7603 K6 = 0.0529 K7 = 0.0529 K8 = 0.3405K9 = 0.2711 K10 = 0.0581 K1* = 0.1923

Note: Dimension a is greater than or equal to Rm / 2.

Moment per Equation 4.15.3 [M1]:= -Q*a [1 - (1- a/L + (R-h2)/(2a*L))/(1+(4h2)/3L)]= -18285*1030.00[1-(1-1030.00/10815.00+(609.600-303.200)/

(2*1030.00*10815.00))/(1+(4*303.20)/(3*10815.00))]= -2179.8 Kg-m.

Moment per Equation 4.15.4 [M2]:= Q*L/4(1+2(R-h2)/(L))/(1+(4h2)/( 3L))-4a/L= 18285*10815/4(1+2(609-303)/(10815))/(1+(4*303)/(3*10815))-4*1030/10815

= 29051.7 Kg-m.

Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]:= P * Rm/(2t) - M2/(pi*Rmt)= 20.0 * 609.600 /(2*12.80 ) - 29051.7 /(pi*609.6*12.80 )= 28.56 N./mm

Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:

= P * Rm/(2t) + M2/(pi * Rm * t)= 20.1 * 609.600 /(2 * 12.80 ) + 29051.7 /(pi * 609.6 * 12.80 )= 66.94 N./mm

Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:= P * Rm/(2t) - M1/(K1*pi*Rmt)= 20.0 * 609.600 /(2*12.80 ) - -2179.8 /(0.1066 *pi*609.6*12.80 )= 61.05 N./mm

Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]:= P * Rm/(2t) + M1/(K1*pi*Rmt)= 20.0 * 609.600 /(2*12.80 ) + -2179.8 /(0.1066 *pi*609.6*12.80 )= 40.19 N./mm

Maximum Shear Force in the Saddle (4.15.5) [T]:

= Q(L-2a)/(L+(4*h2/3))= 18285 ( 10815.00 - 2 * 1030.00 )/(10815.00 + ( 4 * 303.20 /3))= 14268.8 Kgf

Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:= K2 * T / ( Rm * t )= 1.1707 * 14268.82 / ( 609.6000 * 12.8000 )= 20.99 N./mm

Decay Length (4.15.22) [x1,x2]:= 0.78 * sqrt( Rm * t )= 0.78 * sqrt( 609.600 * 12.800 )= 68.900 mm.


29/86


Circumferential Stress in shell, no rings (4.15.23) [sigma6]:= -K5 * Q * k / ( t * ( b + X1 + X2 ) )= -0.7603 * 18285 * 0.1 / ( 12.800 * ( 184.00 + 68.90 + 68.90 ) )= -3.31 N./mm

Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]:

= -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t)= -18285 /(4*12.800 *(184.000 +68.900 +68.900 )) -3*0.0529 *18285 /(2*12.800)

= -97.65 N./mm

Effective reinforcing plate width (4.15.1) [B1]:= min( b + 1.56 * sqrt( Rm * t ), 2a )= min( 184.00 + 1.56 * sqrt( 609.600 * 12.800 ), 2 * 1030.000 )= 321.80 mm.

Free Un-Restrained Thermal Expansion between the Saddles [Exp]:= Alpha * Ls * ( Design Temperature - Ambient Temperature )= 0.139E-04 * 7500.000 * ( 400.0 - 21.1 )= 39.402 mm.

Results for Vessel Ribs, Web and Base:Baseplate Length Bplen 1150.0000 mm.Baseplate Thickness Bpthk 20.0000 mm.Baseplate Width Bpwid 200.0000 mm.Number of Ribs ( inc. outside ribs ) Nribs 3Rib Thickness Ribtk 12.0000 mm.Web Thickness Webtk 12.0000 mm.Web Location Webloc Side

Moment of Inertia of Saddle - Lateral Direction

Y A AY Ay IoShell 6. 43. 27613. 18. 6.Wearplate 21. 32. 66560. 138. 7.Web 128. 24. 306927. 3941. 790.

BasePlate 238. 40. 952000. 22658. 13.Totals 394. 139. 1353100. 26755. 816.

Value C1 = Sumof(Ay)/Sumof(A) = 97. mm.Value I = Sumof(Ay ) + Sumof(Io) - C1*Sumof(Ay) = 14404. cm**4Value As = Sumof(A) - Ashell = 96. cm

K1 = (1+Cos(beta)-.5*Sin(beta) )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035

Fh = K1 * Q = 0.2035 * 18285.057 = 3721.4060 Kgf

Tension Stress, St = ( Fh/As ) = 3.8054 N./mmAllowed Stress, Sa = 0.6 * Yield Str = 157.2060 N./mm

d = B - R*Sin(theta) / theta = 352.3576 mm.

Bending Moment, M = Fh * d = 1311.2916 Kg-m.

Bending Stress, Sb = ( M * C1 / I ) = 8.6875 N./mmAllowed Stress, Sa = 2/3 * Yield Str = 174.6733 N./mm

Minimum Thickness of Baseplate per Moss := ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 2 * BasePlateLength *AllStress ))

= ( 3 * (18285 + 148 ) * 200.00 / ( 2 * 1150.000 * 174.673 ))= 16.431 mm.

Calculation of Axial Load, Intermediate Values and Compressive Stress

Effective Baseplate Length [e]:


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= ( Bplen - Clearance ) / ( Nribs - 1)= ( 1150.0000 - 25.4 ) / ( 3 - 1 ) = 562.3000 mm.

Baseplate Pressure Area [Ap]:= e * Bpwid / 2= 562.3000 * 200.0000 / 2 = 562.3000 cm

Axial Load [P]:= Ap * Bp= 562.3 * 7.95 = 4470.3 Kgf

Area of the Rib and Web [Ar]:= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk= ( 200.000 - 25.4 - 12.000 ) * 12.000 + 562.3000 /2 * 12.000= 53.250 cm

Compressive Stress [Sc]:= P/Ar= 4470.3 / 53.2500 = 8.2328 N./mm

Check of Outside Ribs:

Inertia of Saddle, Outer Ribs - Longitudinal DirectionY A AY Ay Io

Rib 93.3 20.1 187309.1 601.4 576.4Web 6.0 33.7 20242.8 357.9 8.1Values 38.6 53.8 207551.9 959.2 584.5

Bending Moment [Rm]:= Fl /( 2 * Bplen ) * e * rl / 2= 2511.3 /( 2 * 1150.00 ) * 562.300 * 543.20 / 2= 166.755 Kg-m.

KL/R < Cc ( 10.0886 < 122.7359 ) per AISC E2-1Sca = (1-(Klr)/(2*Cc))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr)/(8*Cc)Sca = ( 1-( 10.09 )/(2 * 122.74 )) * 262 /

( 5/3+3*(10.09 )/(8* 122.74 )-( 10.09)/(8*122.74)

Sca = 153.84 N./mm

AISC Unity Check on Outside Ribs ( must be


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Total Number of Bolts per BasePlate Nbolts 2Total Number of Bolts in Tension/Baseplate Nbt 2Bolt Material Specification IS 2062 BBolt Allowable Stress Stba 120.00 N./mmBolt Corrosion Allowance Bca 0.0000 mm.Distance from Bolts to Edge Edgedis 75.0062 mm.

Nominal Bolt Diameter Bnd 24.0000 mm.Thread Series Series TEMA MetricBasePlate Allowable Stress S 137.90 N./mmArea Available in a Single Bolt BltArea 3.1275 cmSaddle Load QO (Weight) QO 15222.6 KgfSaddle Load QL (Wind/Seismic contribution) QL 301.4 KgfMaximum Transverse Force Ft 1255.7 KgfMaximum Longitudinal Force Fl 4054.9 KgfSaddle Bolted to Steel Foundation No

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)= 4054.89 / (120.00 * 2.00 )= 1.6569 cm

Bolt Area due to Transverse Load

Moment on Baseplate Due to Transverse Load [Rmom]:= B * Ft + Sum of X Moments= 900.00 * 1255.66 + 0.00= 1130.11 Kg-m.

Eccentricity (e):= Rmom / QO= 1130.11 / 15222.64

= 74.24 mm. < 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 , 1.6569 , 0.0000 ]= 1.6569 cm

ASME Horizontal Vessel Analysis: Stresses for the Right Saddle

Warning: Wear Pad Width is less than 1.56*sqrt(rm*t) and less than 2a.The wear plate will be ignored.

Minimum Saddle Width [b1]:= min( b + 1.56*sqrt( Rm * t ), 2a )= min( 184.000 + 1.56*sqrt( 609.6000 * 12.8000 ), 2 * 3400.000 )= 321.8009 mm.

Input and Calculated Values:

Vessel Mean Radius Rm 609.60 mm.Tangent to Tangent Length L 10815.00 mm.Distance from Saddle to Vessel tangent a 1700.00 mm.

Saddle Width b 184.00 mm.Saddle Bearing Angle theta 120.00 degrees


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Inside Depth of Head h2 303.20 mm.

Shell Allowable Stress used in Calculation 101.30 N./mmHead Allowable Stress used in Calculation 101.30 N./mm

Saddle Force Q, Operating Case 16727.23 Kgf

Horizontal Vessel Analysis Results: Actual Allowable-------------------------------------------------------------------Long. Stress at Top of Midspan 37.54 101.30 N./mmLong. Stress at Bottom of Midspan 57.96 101.30 N./mmLong. Stress at Top of Saddles 79.18 101.30 N./mmLong. Stress at Bottom of Saddles 30.14 101.30 N./mm

Tangential Shear in Shell 16.27 81.04 N./mmCirc. Stress at Horn of Saddle 89.33 126.62 N./mmCirc. Compressive Stress in Shell 3.03 101.30 N./mm

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 * ( 1704.8 /2 + 0 ) * 900.0000 / 1055.8582= 2179.7 Kgf

Saddle Reaction Force due to Wind Fl or Friction [Fwl]:= Max( Fl, Friction Load, Sum of X Forces) * B / Ls= Max( 209.81 , 4054.89 , 0 ) * 900.0000 / 7500.0000= 486.6 Kgf

Saddle Reaction Force due to Earthquake Fl or Friction [Fsl]:= Max( Fl, Friction Force, Sum of X Forces ) * B / Ls= Max( 2511.32 , 4054.89 , 0 ) * 900.0000 / 7500.0000= 486.6 Kgf

Saddle Reaction Force due to Earthquake Ft [Fst]:= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E= 3.00 * ( 2511 /2 + 0 ) * 900.0000 / 1055.8582= 3210.9 Kgf

Load Combination Results for Q + Wind or Seismic [Q]:= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )= 13516 + Max( 486 , 2179 , 486 , 3210 )= 16727.2 Kgf






Moment per Equation 4.15.3 [M1]:= -Q*a [1 - (1- a/L + (R-h2)/(2a*L))/(1+(4h2)/3L)]= -16727*1700.00[1-(1-1700.00/10815.00+(609.600-303.200)/


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(2*1700.00*10815.00))/(1+(4*303.20)/(3*10815.00))]= -5125.1 Kg-m.

Moment per Equation 4.15.4 [M2]:= Q*L/4(1+2(R-h2)/(L))/(1+(4h2)/( 3L))-4a/L= 16727*10815/4(1+2(609-303)/(10815))/(1+(4*303)/

(3*10815))-4*1700/10815= 15369.1 Kg-m.


Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:= P * Rm/(2t) + M2/(pi * Rm * t)= 20.1 * 609.600 /(2 * 12.80 ) + 15369.1 /(pi * 609.6 * 12.80 )= 57.96 N./mm

Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:= P * Rm/(2t) - M1/(K1*pi*Rmt)

= 20.0 * 609.600 /(2*12.80 ) - -5125.1 /(0.1066 *pi*609.6*12.80 )= 79.18 N./mm


Maximum Shear Force in the Saddle (4.15.5) [T]:= Q(L-2a)/(L+(4*h2/3))= 16727 ( 10815.00 - 2 * 1700.00 )/(10815.00 + ( 4 * 303.20 /3))= 11055.3 Kgf

Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:= K2 * T / ( Rm * t )

= 1.1707 * 11055.30 / ( 609.6000 * 12.8000 )= 16.27 N./mm



Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]:= -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t)

= -16727 /(4*12.800 *(184.000 +68.900 +68.900 )) -3*0.0529 *16727 /(2*12.800)

= -89.33 N./mm


Results for Vessel Ribs, Web and Base

Baseplate Length Bplen 1150.0000 mm.Baseplate Thickness Bpthk 20.0000 mm.Baseplate Width Bpwid 200.0000 mm.


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Number of Ribs ( inc. outside ribs ) Nribs 3Rib Thickness Ribtk 12.0000 mm.Web Thickness Webtk 12.0000 mm.Web Location Webloc Side


Y A AY Ay IoShell 6. 43. 27613. 18. 6.Wearplate 21. 32. 66560. 138. 7.Web 128. 24. 306927. 3941. 790.BasePlate 238. 40. 952000. 22658. 13.Totals 394. 139. 1353100. 26755. 816.



Fh = K1 * Q = 0.2035 * 16727.230 = 3404.3545 Kgf


d = B - R*Sin(theta) / theta = 352.3576 mm.Bending Moment, M = Fh * d = 1199.5739 Kg-m.



= ( 3 * (16727 + 148 ) * 200.00 / ( 2 * 1150.000 * 174.673 ))= 15.722 mm.


Effective Baseplate Length [e]:= ( Bplen - Clearance ) / ( Nribs - 1)= ( 1150.0000 - 25.4 ) / ( 3 - 1 ) = 562.3000 mm.





Check of Outside Ribs:Inertia of Saddle, Outer Ribs - Longitudinal Direction

Y A AY Ay IoRib 93.3 20.1 187309.1 601.4 576.4Web 6.0 33.7 20242.8 357.9 8.1


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Values 38.6 53.8 207551.9 959.2 584.5



( 5/3+3*(10.09 )/(8* 122.74 )-( 10.09)/(8*122.74)Sca = 153.84 N./mm

AISC Unity Check on Outside Ribs ( must be No Uplift in Longitudinal direction)



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Moment on Baseplate Due to Transverse Load [Rmom]:= B * Ft + Sum of X Moments= 900.00 * 1255.66 + 0.00

= 1130.11 Kg-m.

Eccentricity (e):= Rmom / QO= 1130.11 / 13664.81= 82.70 mm. < Bplen/6 --> No Uplift in Transverse direction





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PV Elite 2010 Licensee: OHL TECHNOLOGIES GMBHFileName : STG-HX-004AB Reheater-----------------------------Horizontal Vessel Analysis (Test) : Step: 11 3:11p Jan 11,2012

ASME Horizontal Vessel Analysis: Stresses for the Left Saddle

Horizontal Vessel Stress Calculations : Test Case

Warning: Wear Pad Width is less than 1.56*sqrt(rm*t) and less than 2a.

The wear plate will be ignored.







Saddle Force Q, Test Case, no Ext. Forces 17791.34 Kgf

Horizontal Vessel Analysis Results: Actual Allowable-------------------------------------------------------------------Long. Stress at Top of Midspan 63.78 137.90 N./mmLong. Stress at Bottom of Midspan 100.88 137.90 N./mmLong. Stress at Top of Saddles 95.39 137.90 N./mmLong. Stress at Bottom of Saddles 75.09 137.90 N./mm



Saddle Reaction Force due to Wind Ft [Fwt]:= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E= 3.00 * ( 1022.9 /2 + 0 ) * 900.0000 / 1055.8582= 1307.8 Kgf



Saddle Reaction Force due to Earthquake Ft [Fst]:= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E= 3.00 * ( 828 /2 + 0 ) * 900.0000 / 1055.8582= 1059.6 Kgf

Load Combination Results for Q + Wind or Seismic [Q]:= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )= 16483 + Max( 15 , 1307 , 99 , 1059 )


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= 17791.3 Kgf


Hydrostatic Test Pressure at top of Vessel 34.572 bars





Moment per Equation 4.15.3 [M1]:

= -Q*a [1 - (1- a/L + (R-h2)/(2a*L))/(1+(4h2)/3L)]= -17791*1030.00[1-(1-1030.00/10815.00+(609.600-303.200)/(2*1030.00*10815.00))/(1+(4*303.20)/(3*10815.00))]

= -2121.0 Kg-m.


= 28267.3 Kg-m.



Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:= P * Rm/(2t) - M1/(K1*pi*Rmt)= 34.6 * 609.600 /(2*12.80 ) - -2121.0 /(0.1066 *pi*609.6*12.80 )= 95.39 N./mm



Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:= K2 * T / ( Rm * t )= 1.1707 * 13883.54 / ( 609.6000 * 12.8000 )= 20.43 N./mm

Decay Length (4.15.22) [x1,x2]:= 0.78 * sqrt( Rm * t )= 0.78 * sqrt( 609.600 * 12.800 )


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= 68.900 mm.


Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]:= -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t)= -17791 /(4*12.800 *(184.000 +68.900 +68.900 )) -

3*0.0529 *17791 /(2*12.800)= -95.01 N./mm


Results for Vessel Ribs, Web and Base:Baseplate Length Bplen 1150.0000 mm.Baseplate Thickness Bpthk 20.0000 mm.

Baseplate Width Bpwid 200.0000 mm.Number of Ribs ( inc. outside ribs ) Nribs 3Rib Thickness Ribtk 12.0000 mm.Web Thickness Webtk 12.0000 mm.Web Location Webloc Side





Fh = K1 * Q = 0.2035 * 17791.342 = 3620.9243 Kgf



Bending Stress, Sb = ( M * C1 / I ) = 8.4529 N./mm

Allowed Stress, Sa = 2/3 * Yield Str = 174.6733 N./mm


= ( 3 * (17791 + 148 ) * 200.00 / ( 2 * 1150.000 * 174.673 ))= 16.210 mm.




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Axial Load [P]:= Ap * Bp

= 562.3 * 7.74 = 4349.6 Kgf




Y A AY Ay IoRib 93.3 20.1 187309.1 601.4 576.4

Web 6.0 33.7 20242.8 357.9 8.1Values 38.6 53.8 207551.9 959.2 584.5



( 5/3+3*(10.09 )/(8* 122.74 )-( 10.09)/(8*122.74)Sca = 153.84 N./mm

AISC Unity Check on Outside Ribs ( must be


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Bolt Allowable Stress Stba 120.00 N./mmBolt Corrosion Allowance Bca 0.0000 mm.Distance from Bolts to Edge Edgedis 75.0062 mm.Nominal Bolt Diameter Bnd 24.0000 mm.Thread Series Series TEMA MetricBasePlate Allowable Stress S 137.90 N./mm

Area Available in a Single Bolt BltArea 3.1275 cmSaddle Load QO (Weight) QO 16632.0 KgfSaddle Load QL (Wind/Seismic contribution) QL 99.4 KgfMaximum Transverse Force Ft 511.4 KgfMaximum Longitudinal Force Fl 828.7 KgfSaddle Bolted to Steel Foundation No

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)= 828.73 / (120.00 * 2.00 )

= 0.3386 cm


Moment on Baseplate Due to Transverse Load [Rmom]:= B * Ft + Sum of X Moments= 900.00 * 511.44 + 0.00= 460.31 Kg-m.

Eccentricity (e):= Rmom / QO= 460.31 / 16632.01= 27.68 mm. < Bplen/6 --> No Uplift in Transverse direction



ASME Horizontal Vessel Analysis: Stresses for the Right Saddle

Warning: Wear Pad Width is less than 1.56*sqrt(rm*t) and less than 2a.The wear plate will be ignored.







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Saddle Force Q, Test Case, no Ext. Forces 16190.06 Kgf

Horizontal Vessel Analysis Results: Actual Allowable

-------------------------------------------------------------------Long. Stress at Top of Midspan 72.57 137.90 N./mmLong. Stress at Bottom of Midspan 92.09 137.90 N./mmLong. Stress at Top of Saddles 112.86 137.90 N./mmLong. Stress at Bottom of Saddles 65.41 137.90 N./mm



Saddle Reaction Force due to Wind Ft [Fwt]:= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E= 3.00 * ( 1022.9 /2 + 0 ) * 900.0000 / 1055.8582

= 1307.8 Kgf



Saddle Reaction Force due to Earthquake Ft [Fst]:= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E= 3.00 * ( 828 /2 + 0 ) * 900.0000 / 1055.8582

= 1059.6 Kgf

Load Combination Results for Q + Wind or Seismic [Q]:= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )= 14882 + Max( 15 , 1307 , 99 , 1059 )= 16190.1 Kgf


Hydrostatic Test Pressure at top of Vessel 34.572 bars





Moment per Equation 4.15.3 [M1]:= -Q*a [1 - (1- a/L + (R-h2)/(2a*L))/(1+(4h2)/3L)]= -16190*1700.00[1-(1-1700.00/10815.00+(609.600-303.200)/(2*1700.00*10815.00))/(1+(4*303.20)/(3*10815.00))]


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= -4960.5 Kg-m.


= 14875.6 Kg-m.



Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:= P * Rm/(2t) - M1/(K1*pi*Rmt)= 34.6 * 609.600 /(2*12.80 ) - -4960.5 /(0.1066 *pi*609.6*12.80 )

= 112.86 N./mm



Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:= K2 * T / ( Rm * t )= 1.1707 * 10700.28 / ( 609.6000 * 12.8000 )

= 15.74 N./mm



Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]:= -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t)= -16190 /(4*12.800 *(184.000 +68.900 +68.900 )) -

3*0.0529 *16190 /(2*12.800)= -86.46 N./mm


Results for Vessel Ribs, Web and Base

Baseplate Length Bplen 1150.0000 mm.Baseplate Thickness Bpthk 20.0000 mm.Baseplate Width Bpwid 200.0000 mm.Number of Ribs ( inc. outside ribs ) Nribs 3


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Rib Thickness Ribtk 12.0000 mm.Web Thickness Webtk 12.0000 mm.Web Location Webloc Side





Fh = K1 * Q = 0.2035 * 16190.062 = 3295.0293 Kgf





= ( 3 * (16190 + 148 ) * 200.00 / ( 2 * 1150.000 * 174.673 ))= 15.469 mm.





Area of the Rib and Web [Ar]:

= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk= ( 200.000 - 25.4 - 12.000 ) * 12.000 + 562.3000 /2 * 12.000= 53.250 cm



Y A AY Ay IoRib 93.3 20.1 187309.1 601.4 576.4Web 6.0 33.7 20242.8 357.9 8.1Values 38.6 53.8 207551.9 959.2 584.5


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( 5/3+3*(10.09 )/(8* 122.74 )-( 10.09)/(8*122.74)Sca = 153.84 N./mm

AISC Unity Check on Outside Ribs ( must be No Uplift in Longitudinal direction)



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Nozzle Calcs. : Manhole Nozl: 6 3:11p Jan 11,2012

INPUT VALUES, Nozzle Description: Manhole From : 10

Pressure for Reinforcement Calculations P 25.050 barsTemperature for Internal Pressure Temp 400 CDesign External Pressure Pext 1.05 bars

Temperature for External Pressure Tempex 400 C

Shell Material [Normalized] SA-516 70Shell Allowable Stress at Temperature S 101.30 N./mmShell Allowable Stress At Ambient Sa 137.90 N./mm

Inside Diameter of Elliptical Head D 1200.00 mm.Aspect Ratio of Elliptical Head Ar 2.00Head Finished (Minimum) Thickness t 19.0000 mm.Head Internal Corrosion Allowance c 3.2000 mm.Head External Corrosion Allowance co 0.0000 mm.

Distance from Head Centerline L1 0.0000 mm.

User Entered Minimum Design Metal Temperature 0.00 C

Type of Element Connected to the Shell : Nozzle

Material SA-266 2Material UNS Number K03506Material Specification/Type ForgingsAllowable Stress at Temperature Sn 101.30 N./mmAllowable Stress At Ambient Sna 137.90 N./mm

Diameter Basis (for tr calc only) ODLayout Angle 0.00 degDiameter 24.0000 in.

Size and Thickness Basis ActualActual Thickness tn 80.0000 mm.

Corrosion Allowance can 3.2000 mm.Joint Efficiency of Shell Seam at Nozzle E1 1.00Joint Efficiency of Nozzle Neck En 1.00

Outside Projection ho 250.0000 mm.Weld leg size between Nozzle and Pad/Shell Wo 9.0000 mm.Groove weld depth between Nozzle and Vessel Wgnv 19.0000 mm.Inside Projection h 0.0000 mm.Weld leg size, Inside Element to Shell Wi 0.0000 mm.ASME Code Weld Type per UW-16 C

The Pressure Design option was Design Pressure + static head.

Nozzle Sketch (may not represent actual weld type/configuration)

| || || || |

____________/| || \ | || \ | ||____________\|__|

Insert Nozzle No Pad, no Inside projection

Reinforcement CALCULATION, Description: Manhole


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ASME Code, Section VIII, Division 1, 2007, A-09 UG-37 to UG-45

Actual Outside Diameter Used in Calculation 24.000 in.Actual Thickness Used in Calculation 3.150 in.

Note: Post Weld Heat Treating is required for this Nozzle Geometry!

Nozzle input data check completed without errors.

Reqd thk per UG-37(a)of Elliptical Head, Tr [Int. Press]= (P*K1*D))/(2*S*E-0.2*P) per UG-37(a)(3)= (25.05*0.895*1206.4000)/(2 *101.30*1.00-0.2*25.05)= 13.3913 mm.

Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press]= (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1)= (25.05*304.8000)/(101*1.00+0.4*25.05)= 7.4641 mm.

Required Nozzle thickness under External Pressure per UG-28 : 1.4752 mm.

UG-40, Limits of Reinforcement : [Int. Press]Parallel to Vessel Wall (Diameter Limit) Dl 912.0001 mm.Parallel to Vessel Wall, opening length d 456.0000 mm.Normal to Vessel Wall (Thickness Limit), no pad Tlnp 39.5000 mm.

Weld Strength Reduction Factor [fr1]:= min( 1, Sn/S )= min( 1, 101.3 /101.3 )= 1.000

Weld Strength Reduction Factor [fr2]:= min( 1, Sn/S )= min( 1, 101.3 /101.3 )= 1.000

Weld Strength Reduction Factor [fr3]:= min( fr2, fr4 )= min( 1.0 , 1.0 )= 1.000

Results of Nozzle Reinforcement Area Calculations:AREA AVAILABLE, A1 to A5 Design External MapncArea Required Ar 61.064 8.160 NA cmArea in Shell A1 10.984 55.728 NA cmArea in Nozzle Wall A2 54.775 59.507 NA cmArea in Inward Nozzle A3 0.000 0.000 NA cmArea in Welds A41+A42+A43 0.810 0.810 NA cmArea in Element A5 0.000 0.000 NA cmTOTAL AREA AVAILABLE Atot 66.569 116.044 NA cm

The Internal Pressure Case Governs the Analysis.

Nozzle Angle Used in Area Calculations 90.00 Degs.

The area available without a pad is Sufficient.

Area Required [A]:= ( d * tr*F + 2 * tn * tr*F * (1-fr1) ) UG-37(c)= (456.0000*13.3913*1.0+2*76.8000*13.3913*1.0*(1-1.00))= 61.064 cm

Reinforcement Areas per Figure UG-37.1


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Area Available in Shell [A1]:

calc. reheater

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