Page 1
Table of Contents
Cover Page 1
Title Page 2
Warnings and Errors : 3
Input Echo : 4
XY Coordinate Calculations : 12
Internal Pressure Calculations : 13
External Pressure Calculations : 19
Element and Detail Weights : 25
Nozzle Flange MAWP : 28
Natural Frequency Calculation : 29
Wind Load Calculation : 30
Earthquake Load Calculation : 33
Wind/Earthquake Shear, Bending : 34
Wind Deflection : 35
Longitudinal Stress Constants : 36
Longitudinal Allowable Stresses : 37
Longitudinal Stresses Due to . . 38
Stress due to Combined Loads : 40
Center of Gravity Calculation : 49
Basering Calculations : 50
Nozzle Calcs. : Noz N1 54
Nozzle Calcs. : Noz N3 (8") 63
Nozzle Calcs. : Noz N2 (20") 70
Nozzle Calcs. : Noz(10") 77
Nozzle Calcs. : Noz N6 (6") 84
Nozzle Calcs. : Noz MH 91
Nozzle Schedule : 100
Nozzle Summary : 101
MDMT Summary : 102
Vessel Design Summary : 103
Problems/Failures Summary : 105
Page 2
Cover Page
DESIGN CALCULATION
In Accordance with ASME Section VIII Division 2
ASME Code Version : 2013
Analysis Performed by : L&T HED
Job File : C:\USERS\20057061\DESKTOP\RIL\HECK.PVDB
Date of Analysis : Mar 14,2015 1:41pm
PV Elite 2014 SP1, March 2014
Page 3
Title Page
Note: PV Elite performs all calculations internally in Imperial Unitsto remain compliant with the ASME Code and any built in assumptionsin the ASME Code formulas. The finalized results are reflected to showthe users set of selected units.
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Warnings and Errors : Step: 0 1:41pmMar 14,2015
Class From To : Basic Element Checks.
==========================================================================
Class From To: Check of Additional Element Data
==========================================================================
There were no geometry errors or warnings.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Input Echo : Step: 1 1:41pmMar 14,2015
PV Elite Vessel Analysis Program: Input Data
Design Internal Pressure (for Hydrotest) 19.830 MPa
Design Internal Temperature 454 °C
Type of Hydrotest Hydrostatic
Hydrotest Position Horizontal
Projection of Nozzle from Vessel Top 0.0000 mm
Projection of Nozzle from Vessel Bottom 0.0000 mm
Minimum Design Metal Temperature 16 °C
Type of Construction Welded
Special Service None
Use Higher Longitudinal Stresses (Flag) N
Select t for Internal Pressure (Flag) N
Select t for External Pressure (Flag) N
Select t for Axial Stress (Flag) N
Select Location for Stiff. Rings (Flag) N
Consider Vortex Shedding N
Perform a Corroded Hydrotest Y
Is this a Heat Exchanger No
User Defined Hydro. Press. (Used if > 0) 31.110 MPa
User defined MAWP 0.0000 MPa
User defined MAPnc 24.600 MPa
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 IP+WE+EW
Load Case 14 IP+WF+CW
Load Case 15 IP+VO+OW
Load Case 16 IP+VE+EW
Load Case 17 NP+VO+OW
Load Case 18 FS+BS+IP+OW
Load Case 19 FS+BS+EP+OW
Wind Design Code IS-875
Basic Wind Speed for IS-875 70.000 km/hr
Wind Zone Number 1
Base Elevation 0.0000 mm
Percent Wind for Hydrotest 33.0
Risk Factor 1.0
Terrain Category 1
Equipment Class 1
Topography Factor 1.0
Damping Factor (Beta) for Wind (Ope) 0.0100
Damping Factor (Beta) for Wind (Empty) 0.0000
Damping Factor (Beta) for Wind (Filled) 0.0000
Seismic Design Code IS-1893-SCM
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Importance Factor for IS-1893 1.000
Soil Factor 1.000
Zone Number 1.000
Percent Seismic for Hydrotest 33.000
Design Nozzle for Des. Press. + St. Head Y
Consider MAP New and Cold in Noz. Design N
Consider External Loads for Nozzle Des. Y
Use ASME VIII-1 Appendix 1-9 N
Configuration Directives:
Using Metric Material Databases, ASME II D No
Using ASME VIII-1 Code Case 2695 No
Complete Listing of Vessel Elements and Details:
Element From Node 10
Element To Node 20
Element Type Skirt Sup.
Description Skirt-CS
Distance "FROM" to "TO" 6700.0 mm
Skirt Outside Diameter 6087.0 mm
Diameter of Skirt at Base 6087.0 mm
Skirt Thickness 28.000 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 28.000 mm
External Corrosion Allowance 0.0000 mm
Design Temperature Internal Pressure 100 °C
Design Temperature External Pressure 100 °C
Effective Diameter Multiplier 1.4
Material Name SA-516 60
Allowable Stress, Ambient 147.00 MPa
Allowable Stress, Operating 134.00 MPa
Allowable Stress, Hydrotest 209.60 MPa
Material Density 0.007750 kg/cm³
P Number Thickness 0.0000 mm
Yield Stress, Operating 201.20 MPa
MDMT Curve C
External Pressure Chart Name CS-2
UNS Number K02100
Product Form Plate
Efficiency, Longitudinal Seam 1.0
Efficiency, Head-to-Skirt or Circ. Seam 1.0
--------------------------------------------------------------------
Element From Node 20
Element To Node 30
Element Type Skirt Sup.
Description Skirt
Distance "FROM" to "TO" 1000.0 mm
Skirt Outside Diameter 6087.0 mm
Diameter of Skirt at Base 6087.0 mm
Skirt Thickness 26.000 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 26.000 mm
External Corrosion Allowance 0.0000 mm
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Design Temperature Internal Pressure 454 °C
Design Temperature External Pressure 454 °C
Effective Diameter Multiplier 1.4
Material Name SA-336 F22V
Allowable Stress, Ambient 244.10 MPa
Allowable Stress, Operating 199.30 MPa
Allowable Stress, Hydrotest 393.00 MPa
Material Density 0.007750 kg/cm³
P Number Thickness 0.0000 mm
Yield Stress, Operating 338.00 MPa
MDMT Curve B
External Pressure Chart Name CS-2
UNS Number K31835
Product Form Forgings
Efficiency, Longitudinal Seam 1.0
Efficiency, Head-to-Skirt or Circ. Seam 1.0
--------------------------------------------------------------------
Element From Node 30
Element To Node 40
Element Type Spherical
Description Bottom Head
Distance "FROM" to "TO" 0.0000 mm
Inside Diameter 5661.0 mm
Element Thickness 147.00 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 162.00 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 19.830 MPa
Design Temperature Internal Pressure 454 °C
Design External Pressure 0.1020 MPa
Design Temperature External Pressure 454 °C
Effective Diameter Multiplier 1.2
Material Name SA-336 F22V
Efficiency, Longitudinal Seam 1.0
Efficiency, Circumferential Seam 1.0
Element From Node 30
Detail Type Insulation
Detail ID INS
Dist. from "FROM" Node / Offset dist -2830.5 mm
Height/Length of Insulation 2830.5 mm
Thickness of Insulation 150.00 mm
Density 0.0002400 kg/cm³
Element From Node 30
Detail Type Nozzle
Detail ID Noz N1
Dist. from "FROM" Node / Offset dist 0.0000 mm
Nozzle Diameter 389.0 mm
Nozzle Schedule DIN4.0
Nozzle Class None
Layout Angle 0.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.0000 N
Grade of Attached Flange None
Nozzle Matl SA-336 F22V
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Element From Node 30
Detail Type Nozzle
Detail ID Noz N3 (8")
Dist. from "FROM" Node / Offset dist 2165.0 mm
Nozzle Diameter 212.0 mm
Nozzle Schedule DIN4.0
Nozzle Class None
Layout Angle 0.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.0000 N
Grade of Attached Flange None
Nozzle Matl SA-336 F22V
Element From Node 30
Detail Type Nozzle
Detail ID Noz N2 (20")
Dist. from "FROM" Node / Offset dist 2165.0 mm
Nozzle Diameter 469.0 mm
Nozzle Schedule DIN4.0
Nozzle Class None
Layout Angle 90.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.0000 N
Grade of Attached Flange None
Nozzle Matl SA-336 F22V
--------------------------------------------------------------------
Element From Node 40
Element To Node 50
Element Type Cylinder
Description Shell-1
Distance "FROM" to "TO" 3950.0 mm
Inside Diameter 5513.0 mm
Element Thickness 289.00 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 289.00 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 19.830 MPa
Design Temperature Internal Pressure 454 °C
Design External Pressure 0.1020 MPa
Design Temperature External Pressure 454 °C
Effective Diameter Multiplier 1.4
Material Name SA-336 F22V
Efficiency, Longitudinal Seam 1.0
Efficiency, Circumferential Seam 1.0
Element From Node 40
Detail Type Insulation
Detail ID INS-1
Dist. from "FROM" Node / Offset dist 0.0000 mm
Height/Length of Insulation 3950.0 mm
Thickness of Insulation 150.00 mm
Density 0.0002400 kg/cm³
Element From Node 40
Detail Type Weight
Detail ID WEIGHT-1
Dist. from "FROM" Node / Offset dist 0.0000 mm
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Miscellaneous Weight 1.37E+06 N
Offset from Element Centerline 0.0000 mm
--------------------------------------------------------------------
Element From Node 50
Element To Node 60
Element Type Cylinder
Description Shell-2
Distance "FROM" to "TO" 3950.0 mm
Inside Diameter 5513.0 mm
Element Thickness 289.00 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 289.00 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 19.830 MPa
Design Temperature Internal Pressure 454 °C
Design External Pressure 0.1020 MPa
Design Temperature External Pressure 454 °C
Effective Diameter Multiplier 1.4
Material Name SA-336 F22V
Efficiency, Longitudinal Seam 1.0
Efficiency, Circumferential Seam 1.0
Element From Node 50
Detail Type Insulation
Detail ID INS-2
Dist. from "FROM" Node / Offset dist 0.0000 mm
Height/Length of Insulation 3950.0 mm
Thickness of Insulation 150.00 mm
Density 0.0002400 kg/cm³
Element From Node 50
Detail Type Weight
Detail ID WEIGHT-2
Dist. from "FROM" Node / Offset dist 0.0000 mm
Miscellaneous Weight 1.37E+06 N
Offset from Element Centerline 0.0000 mm
--------------------------------------------------------------------
Element From Node 60
Element To Node 70
Element Type Cylinder
Description Shell-3
Distance "FROM" to "TO" 3350.0 mm
Inside Diameter 5515.0 mm
Element Thickness 289.00 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 289.00 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 19.830 MPa
Design Temperature Internal Pressure 454 °C
Design External Pressure 0.1020 MPa
Design Temperature External Pressure 454 °C
Effective Diameter Multiplier 1.4
Material Name SA-336 F22V
Efficiency, Longitudinal Seam 1.0
Efficiency, Circumferential Seam 1.0
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Element From Node 60
Detail Type Insulation
Detail ID INS
Dist. from "FROM" Node / Offset dist 0.0000 mm
Height/Length of Insulation 3350.0 mm
Thickness of Insulation 150.00 mm
Density 0.0002400 kg/cm³
Element From Node 60
Detail Type Nozzle
Detail ID Noz(10")
Dist. from "FROM" Node / Offset dist 500.00 mm
Nozzle Diameter 266.0 mm
Nozzle Schedule DIN4.0
Nozzle Class None
Layout Angle 0.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 3852.3 N
Grade of Attached Flange None
Nozzle Matl SA-336 F22V
Element From Node 60
Detail Type Nozzle
Detail ID Noz N6 (6")
Dist. from "FROM" Node / Offset dist 300.00 mm
Nozzle Diameter 164.0 mm
Nozzle Schedule DIN4.0
Nozzle Class None
Layout Angle 180.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.0000 N
Grade of Attached Flange None
Nozzle Matl SA-336 F22V
Element From Node 60
Detail Type Weight
Detail ID WEIGHT-3
Dist. from "FROM" Node / Offset dist 0.0000 mm
Miscellaneous Weight 1.37E+06 N
Offset from Element Centerline 0.0000 mm
--------------------------------------------------------------------
Element From Node 70
Element To Node 80
Element Type Cylinder
Description Shell-4
Distance "FROM" to "TO" 3356.0 mm
Inside Diameter 5513.0 mm
Element Thickness 289.00 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 289.00 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 19.830 MPa
Design Temperature Internal Pressure 454 °C
Design External Pressure 0.1020 MPa
Design Temperature External Pressure 454 °C
Effective Diameter Multiplier 1.4
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Material Name SA-336 F22V
Efficiency, Longitudinal Seam 1.0
Efficiency, Circumferential Seam 1.0
Element From Node 70
Detail Type Insulation
Detail ID INS
Dist. from "FROM" Node / Offset dist 0.0000 mm
Height/Length of Insulation 3356.0 mm
Thickness of Insulation 150.00 mm
Density 0.0002400 kg/cm³
Element From Node 70
Detail Type Weight
Detail ID WEIGHT-5
Dist. from "FROM" Node / Offset dist 0.0000 mm
Miscellaneous Weight 1.37E+06 N
Offset from Element Centerline 0.0000 mm
--------------------------------------------------------------------
Element From Node 80
Element To Node 90
Element Type Spherical
Description Top Head
Distance "FROM" to "TO" 0.0000 mm
Inside Diameter 5659.0 mm
Element Thickness 147.00 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 162.00 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 19.830 MPa
Design Temperature Internal Pressure 454 °C
Design External Pressure 0.1020 MPa
Design Temperature External Pressure 454 °C
Effective Diameter Multiplier 1.4
Material Name SA-336 F22V
Efficiency, Longitudinal Seam 1.0
Efficiency, Circumferential Seam 1.0
Element From Node 80
Detail Type Insulation
Detail ID INS
Dist. from "FROM" Node / Offset dist 0.0000 mm
Height/Length of Insulation 2829.5 mm
Thickness of Insulation 150.00 mm
Density 0.0002400 kg/cm³
Element From Node 80
Detail Type Nozzle
Detail ID Noz MH
Dist. from "FROM" Node / Offset dist 0.0000 mm
Nozzle Diameter 778.0 mm
Nozzle Schedule DIN4.0
Nozzle Class None
Layout Angle 0.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.0000 N
Grade of Attached Flange None
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Nozzle Matl SA-336 F22V
Element From Node 80
Detail Type Weight
Detail ID WEIGHT-3
Dist. from "FROM" Node / Offset dist 0.0000 mm
Miscellaneous Weight 1.37E+06 N
Offset from Element Centerline 0.0000 mm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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XY Coordinate Calculations : Step: 2 1:41pmMar 14,2015
XY Coordinate Calculations
| | | | | |
From| To | X (Horiz.)| Y (Vert.) |DX (Horiz.)| DY (Vert.) |
| | mm | mm | mm | mm |
--------------------------------------------------------------
Skirt-CS| ... | 6700.00 | ... | 6700.00 |
Skirt| ... | 7700.00 | ... | 1000.00 |
Bottom Hea| ... | 7700.00 | ... | ... |
Shell-1| ... | 11650.0 | ... | 3950.00 |
Shell-2| ... | 15600.0 | ... | 3950.00 |
Shell-3| ... | 18950.0 | ... | 3350.00 |
Shell-4| ... | 22306.0 | ... | 3356.00 |
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Internal Pressure Calculations : Step: 3 1:41pmMar 14,2015
Element Thickness, Pressure, Diameter and Allowable Stress :
| | Int. Press | Nominal | Total Corr| Element | Allowable |
From| To | + Liq. Hd | Thickness | Allowance | Diameter | Stress(SE)|
| | MPa | mm | mm | mm | MPa |
---------------------------------------------------------------------------
Skirt-CS| ... | 28.000 | ... | 6031.0 | ... |
Skirt| ... | 26.000 | ... | 6035.0 | ... |
Bottom Hea| 19.830 | 162.00 | ... | 5661.0 | 199.30 |
Shell-1| 19.830 | 289.00 | ... | 5513.0 | 199.30 |
Shell-2| 19.830 | 289.00 | ... | 5513.0 | 199.30 |
Shell-3| 19.830 | 289.00 | ... | 5515.0 | 199.00 |
Shell-4| 19.830 | 289.00 | ... | 5513.0 | 199.30 |
Top Head| 19.830 | 162.00 | ... | 5659.0 | 199.30 |
Element Required Thickness and MAWP :
| | Design | M.A.W.P. | M.A.P. | Minimum | Required |
From| To | Pressure | Corroded | New & Cold | Thickness | Thickness |
| | MPa | MPa | MPa | mm | mm |
----------------------------------------------------------------------------
Skirt-CS| ... | No Calc | No Calc | 28.0000 | No Calc |
Skirt| ... | No Calc | No Calc | 26.0000 | No Calc |
Bottom Hea| 19.8300 | 20.1814 | 24.7179 | 147.000 | 144.376 |
Shell-1| 19.8300 | 19.8709 | 24.3376 | 289.000 | 288.375 |
Shell-2| 19.8300 | 19.8709 | 24.3376 | 289.000 | 288.375 |
Shell-3| 19.8300 | 19.8341 | 24.3292 | 289.000 | 288.937 |
Shell-4| 19.8300 | 19.8709 | 24.3376 | 289.000 | 288.375 |
Top Head| 19.8300 | 20.1883 | 24.7264 | 147.000 | 144.325 |
Minimum 19.834 24.600
MAWP: 19.834 MPa, limited by: Shell-3.
Internal Pressure Calculation Results :
ASME Code, Section VIII, Division 2, 2013
Spherical Head From 30 To 40 SA-336 F22V , Fig. 3.8M Curve B at 454 °C
Bottom Head
Spherical Shell Calculation - Section 4.3.5.1
Computed Minimum Required Thickness [t]: = D/2*( exp( 0.5P/(S*E) )-1) + ci + co
= 5661.000/2*(exp( 0.5 * 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 144.3764 + 0.000 + 0.000 = 144.3764 mm
Computed Maximum Allowable Working Pressure [MAWP]: = 2 * S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 2 * 199.3 * 1.000 * Ln( ( 2*147.000 + 5661.000 )/5661.000 ) - 0.000
= 20.181 - 0.000 = 20.1814 MPa
Computed Maximum Allowable Pressure New & Cold [MAPnc]: = 2 * S * E * Ln( ( 2*t + D ) / D )
= 2 * 244.100 * 1.000 * Ln( ( 2*147.000 + 5661.000 )/5661.000 )
= 24.7179 MPa
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Internal Pressure Calculations : Step: 3 1:41pmMar 14,2015
Computed Stress Intensity at Design Pressure [S]: = P * D^2 / ( E( Do^2 - D^2 ) )
= P * 19.830^2/( 5661.00 ( 1.000^2 - 5955.000^2 ) )
= 186.082 MPa
MDMT Calculations in the Spherical Portion:
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -27 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
From Figure 3.8M- with PWHT, the MDMT is : -19 °C
Temperature reduction per Graph 3.13 : 9 °C
The computed stress ratio is : 0.798
The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 117.363 * 1.00 )/( 147.000 - 0.000 - 0.000 )
= 0.798
Cylindrical Shell From 40 To 50 SA-336 F22V , Fig. 3.8M Curve B at 454 °C
Shell-1
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*5513.000 *(exp( 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 288.3754 + 0.000 + 0.000 = 288.3754 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 199.300 * 1.000 * Ln( ( 2*289.000 + 5513.000 )/5513.000 ) - 0.000
= 19.871 - 0.000 = 19.8709 MPa
Computed Maximum Allowable Pressure New & Cold [MAPnc]: = S * E * Ln( ( 2*t + D ) / D )
= 244.100 * 1.000 * Ln( ( 2*289.000 + 5513.000 )/5513.000 )
= 24.3376 MPa
Computed Stress Intensity at Design Pressure [S]: = P * D / ( E( Do - D ) )
= 19.830 * 5513.000/( 1.00 ( 6091.000 - 5513.000 ) )
= 189.1398 MPa
Minimum Design Metal Temperature Results:
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -2978 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
From Figure 3.8M- with PWHT, the MDMT is : -2970 °C
Temperature reduction per Graph 3.13 : 8 °C
The computed stress ratio is : 0.807
The computed stress ratio [sr]:
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Internal Pressure Calculations : Step: 3 1:41pmMar 14,2015
= ( tr * E* ) / ( tnom - ci - cext )
= ( 233.328 * 1.00 )/( 289.000 - 0.000 - 0.000 )
= 0.807
Cylindrical Shell From 50 To 60 SA-336 F22V , Fig. 3.8M Curve B at 454 °C
Shell-2
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*5513.000 *(exp( 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 288.3754 + 0.000 + 0.000 = 288.3754 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 199.300 * 1.000 * Ln( ( 2*289.000 + 5513.000 )/5513.000 ) - 0.000
= 19.871 - 0.000 = 19.8709 MPa
Computed Maximum Allowable Pressure New & Cold [MAPnc]: = S * E * Ln( ( 2*t + D ) / D )
= 244.100 * 1.000 * Ln( ( 2*289.000 + 5513.000 )/5513.000 )
= 24.3376 MPa
Computed Stress Intensity at Design Pressure [S]: = P * D / ( E( Do - D ) )
= 19.830 * 5513.000/( 1.00 ( 6091.000 - 5513.000 ) )
= 189.1398 MPa
Minimum Design Metal Temperature Results:
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -2978 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
From Figure 3.8M- with PWHT, the MDMT is : -2970 °C
Temperature reduction per Graph 3.13 : 8 °C
The computed stress ratio is : 0.807
The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 233.328 * 1.00 )/( 289.000 - 0.000 - 0.000 )
= 0.807
Cylindrical Shell From 60 To 70 SA-336 F22V , Fig. 3.8M Curve B at 454 °C
Shell-3
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*5515.000 *(exp( 19.830/(199.000 *1.000 ))-1) + 0.000 + 0.000
= 288.9370 + 0.000 + 0.000 = 288.9370 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
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Internal Pressure Calculations : Step: 3 1:41pmMar 14,2015
= 199.000 * 1.000 * Ln( ( 2*289.000 + 5515.000 )/5515.000 ) - 0.000
= 19.834 - 0.000 = 19.8341 MPa
Computed Maximum Allowable Pressure New & Cold [MAPnc]: = S * E * Ln( ( 2*t + D ) / D )
= 244.100 * 1.000 * Ln( ( 2*289.000 + 5515.000 )/5515.000 )
= 24.3292 MPa
Computed Stress Intensity at Design Pressure [S]: = P * D / ( E( Do - D ) )
= 19.830 * 5515.000/( 1.00 ( 6093.000 - 5515.000 ) )
= 189.2084 MPa
Minimum Design Metal Temperature Results:
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -2978 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
From Figure 3.8M- with PWHT, the MDMT is : -2970 °C
Temperature reduction per Graph 3.13 : 8 °C
The computed stress ratio is : 0.808
The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 233.413 * 1.00 )/( 289.000 - 0.000 - 0.000 )
= 0.808
Cylindrical Shell From 70 To 80 SA-336 F22V , Fig. 3.8M Curve B at 454 °C
Shell-4
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*5513.000 *(exp( 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 288.3754 + 0.000 + 0.000 = 288.3754 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 199.300 * 1.000 * Ln( ( 2*289.000 + 5513.000 )/5513.000 ) - 0.000
= 19.871 - 0.000 = 19.8709 MPa
Computed Maximum Allowable Pressure New & Cold [MAPnc]: = S * E * Ln( ( 2*t + D ) / D )
= 244.100 * 1.000 * Ln( ( 2*289.000 + 5513.000 )/5513.000 )
= 24.3376 MPa
Computed Stress Intensity at Design Pressure [S]: = P * D / ( E( Do - D ) )
= 19.830 * 5513.000/( 1.00 ( 6091.000 - 5513.000 ) )
= 189.1398 MPa
Minimum Design Metal Temperature Results:
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -2978 °C
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Internal Pressure Calculations : Step: 3 1:41pmMar 14,2015
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
From Figure 3.8M- with PWHT, the MDMT is : -2970 °C
Temperature reduction per Graph 3.13 : 8 °C
The computed stress ratio is : 0.807
The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 233.328 * 1.00 )/( 289.000 - 0.000 - 0.000 )
= 0.807
Spherical Head From 80 To 90 SA-336 F22V , Fig. 3.8M Curve B at 454 °C
Top Head
Spherical Shell Calculation - Section 4.3.5.1
Computed Minimum Required Thickness [t]: = D/2*( exp( 0.5P/(S*E) )-1) + ci + co
= 5659.000/2*(exp( 0.5 * 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 144.3254 + 0.000 + 0.000 = 144.3254 mm
Computed Maximum Allowable Working Pressure [MAWP]: = 2 * S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 2 * 199.3 * 1.000 * Ln( ( 2*147.000 + 5659.000 )/5659.000 ) - 0.000
= 20.188 - 0.000 = 20.1883 MPa
Computed Maximum Allowable Pressure New & Cold [MAPnc]: = 2 * S * E * Ln( ( 2*t + D ) / D )
= 2 * 244.100 * 1.000 * Ln( ( 2*147.000 + 5659.000 )/5659.000 )
= 24.7264 MPa
Computed Stress Intensity at Design Pressure [S]: = P * D^2 / ( E( Do^2 - D^2 ) )
= P * 19.830^2/( 5659.00 ( 1.000^2 - 5953.000^2 ) )
= 186.015 MPa
MDMT Calculations in the Spherical Portion:
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -27 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
From Figure 3.8M- with PWHT, the MDMT is : -19 °C
Temperature reduction per Graph 3.13 : 9 °C
The computed stress ratio is : 0.798
The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 117.321 * 1.00 )/( 147.000 - 0.000 - 0.000 )
= 0.798
Hydrostatic Test Pressure Results:
User Defined Hydrostatic Test Pressure at High Point 31.110 MPa
Test Pressure at high point in vessel per Equation 8.1 = 1.43 * MAWP
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Internal Pressure Calculations : Step: 3 1:41pmMar 14,2015
= 1.43 * 19.8341
= 28.363 MPa
Test Pressure at high point in vessel per Equation 8.2 = 1.25 * MAWP * ST/S
= 1.25 * 19.8341 * 1.225
= 30.366 MPa
Horizontal Test performed per: max( 1.43*MAWP, 1.25*MAWP*ST/S)
Please note that Nozzle, Shell, Head, Flange, etc MAWPs are all consideredwhen determining the hydrotest pressure for those test types that are basedon the MAWP of the vessel.
Stresses on Elements due to Test Pressure:
From To Stress Allowable Ratio Pressure
----------------------------------------------------------------------
Bottom Head 285.5 393.0 0.726 30.42
Shell-1 290.1 393.0 0.738 30.42
Shell-2 290.1 393.0 0.738 30.42
Shell-3 290.3 393.0 0.739 30.42
Shell-4 290.1 393.0 0.738 30.42
Top Head 285.4 393.0 0.726 30.42
----------------------------------------------------------------------
Stress ratios for Nozzle and Pad Materials:
Description Pad/Nozzle Ambient Operating ratio
----------------------------------------------------------------------
Noz N1 Nozzle 244.10 199.30 1.225
Noz N3 (8") Nozzle 244.10 199.30 1.225
Noz N2 (20") Nozzle 244.10 199.30 1.225
Noz(10") Nozzle 244.10 199.30 1.225
Noz N6 (6") Nozzle 244.00 199.00 1.226
Noz MH Nozzle 244.10 199.30 1.225
----------------------------------------------------------------------
Minimum 1.225
Stress ratios for Vessel Elements:
Description Ambient Operating ratio
----------------------------------------------------------------------
Skirt-CS 147.00 134.00 1.097
Skirt 244.10 199.30 1.225
Bottom Head 244.10 199.30 1.225
Shell-1 244.10 199.30 1.225
Shell-2 244.10 199.30 1.225
Shell-3 244.10 199.00 1.227
Shell-4 244.10 199.30 1.225
Top Head 244.10 199.30 1.225
----------------------------------------------------------------------
Minimum 1.097
Elements Suitable for Internal Pressure.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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External Pressure Calculations : Step: 4 1:41pmMar 14,2015
External Pressure Calculation Results :
ASME Code, Section VIII, Division 2, 2013
Spherical Head From 30 to 40 Ext. Chart: CS-2 at 454 °C
Bottom Head
Maximum External Pressure per Code Case 2286 or Div. 2 Section 4.4
Elastic Hoop Compressive Membrane Failure Stress [Fhe]: = 0.075 * Ey * ( t / Ro )
= 0.075 * 178967 * ( 147.000/2977.500 )
= 662.674 MPa
Ratio of Elastic Hoop Compressive Membrane Failure Stress to Yield [Fr]: = Fhe / Sy
= 662.7 / 338.0
= 1.961
Predicted Buckling Stress [Fic]:Since Fr > 1.6 and Fr < 6.25, Fic = 1.31 * Fy /( 1.15 + Sy/Fhe )
= 1.31 * 338.00/( 1.15 + 338.000/662.674 )
= 266.726 MPa
Allowable Circumferential Compressive Stress [Fha]:Since Fr > 1.6 and Fr < 6.25, Fha = 1.31 * Fy / ( FS * (1.15 + Sy/Fhe) )
= 1.31 * 338.00/( 1.82 * (1.15 + 338.00/662.67 ) )
= 146.372 MPa
Allowable External Pressure at the given Thickness [Pa]: = 2 * Fha[t/Ro]
= 2 * 146.372 [147.000/2977.500 ]
= 14.453 MPa
Cylindrical Shell From 40 to 50 Ext. Chart: CS-2 at 454 °C
Shell-1
Maximum External Pressure per Code Case 2286 or Div. 2 Section 4.4
Determine Parameter [Mx]: = L / sqrt( Ro * t )
= 16492.666/sqrt( 3045.500 * 289.000 )
= 17.580
Compute the Factor [Ch]:Since Mx > 13 and Mx < 2 * (Do/t)^(0.94), Ch = 1.12 * Mx^(-1.058)
= 1.12 * 17.580^(-1.058)
= 0.0540
Elastic Hoop Compressive Membrane Failure Stress [Fhe]: = 1.6 * Ch * Ey * ( t / Do )
= 1.6 * 0.054 * 178967 * ( 289.000/6091.000 )
= 732.989 MPa
Ratio of Elastic Hoop Compressive Membrane Failure Stress to Yield [Fr]: = Fhe / Fy
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External Pressure Calculations : Step: 4 1:41pmMar 14,2015
= 733.0/338.0
= 2.169
Predicted Buckling Stress [Fic]:Since Fr > 0.552 and Fr < 2.439, Fic = 0.7 * Fy * Fr^(0.4)
= 0.7 * 338.00 * 2.17^(0.4)
= 322.468 MPa
Compute the Factor of Safety [FS]:Since Fic > 0.55 Fy and Fic < Fy
= 2.407 - 0.741 * Fic / Fy
= 2.407 - 0.741 * 322.47/338.00
= 1.700
Allowable Circumferential Compressive Stress [Fha]:Since Fr > 0.552 and Fr < 2.439, Fha = 0.7 * Fy/FS * Fr^(0.4)
= 0.7 * 338.0/1.700 * 2.169^(0.4)
= 189.682 MPa
Allowable External Pressure at the given Thickness [Pa]: = 2 * Fha * ( t / Do )
= 2 * 189.682 * ( 289.000/6091.000 )
= 18.000 MPa
Cylindrical Shell From 50 to 60 Ext. Chart: CS-2 at 454 °C
Shell-2
Maximum External Pressure per Code Case 2286 or Div. 2 Section 4.4
Determine Parameter [Mx]: = L / sqrt( Ro * t )
= 16492.666/sqrt( 3045.500 * 289.000 )
= 17.580
Compute the Factor [Ch]:Since Mx > 13 and Mx < 2 * (Do/t)^(0.94), Ch = 1.12 * Mx^(-1.058)
= 1.12 * 17.580^(-1.058)
= 0.0540
Elastic Hoop Compressive Membrane Failure Stress [Fhe]: = 1.6 * Ch * Ey * ( t / Do )
= 1.6 * 0.054 * 178967 * ( 289.000/6091.000 )
= 732.989 MPa
Ratio of Elastic Hoop Compressive Membrane Failure Stress to Yield [Fr]: = Fhe / Fy
= 733.0/338.0
= 2.169
Predicted Buckling Stress [Fic]:Since Fr > 0.552 and Fr < 2.439, Fic = 0.7 * Fy * Fr^(0.4)
= 0.7 * 338.00 * 2.17^(0.4)
= 322.468 MPa
Compute the Factor of Safety [FS]:Since Fic > 0.55 Fy and Fic < Fy
= 2.407 - 0.741 * Fic / Fy
= 2.407 - 0.741 * 322.47/338.00
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External Pressure Calculations : Step: 4 1:41pmMar 14,2015
= 1.700
Allowable Circumferential Compressive Stress [Fha]:Since Fr > 0.552 and Fr < 2.439, Fha = 0.7 * Fy/FS * Fr^(0.4)
= 0.7 * 338.0/1.700 * 2.169^(0.4)
= 189.682 MPa
Allowable External Pressure at the given Thickness [Pa]: = 2 * Fha * ( t / Do )
= 2 * 189.682 * ( 289.000/6091.000 )
= 18.000 MPa
Cylindrical Shell From 60 to 70 Ext. Chart: CS-2 at 454 °C
Shell-3
Maximum External Pressure per Code Case 2286 or Div. 2 Section 4.4
Determine Parameter [Mx]: = L / sqrt( Ro * t )
= 16492.668/sqrt( 3046.500 * 289.000 )
= 17.577
Compute the Factor [Ch]:Since Mx > 13 and Mx < 2 * (Do/t)^(0.94), Ch = 1.12 * Mx^(-1.058)
= 1.12 * 17.577^(-1.058)
= 0.0540
Elastic Hoop Compressive Membrane Failure Stress [Fhe]: = 1.6 * Ch * Ey * ( t / Do )
= 1.6 * 0.054 * 178967 * ( 289.000/6093.000 )
= 732.875 MPa
Ratio of Elastic Hoop Compressive Membrane Failure Stress to Yield [Fr]: = Fhe / Fy
= 732.9/338.0
= 2.168
Predicted Buckling Stress [Fic]:Since Fr > 0.552 and Fr < 2.439, Fic = 0.7 * Fy * Fr^(0.4)
= 0.7 * 338.00 * 2.17^(0.4)
= 322.448 MPa
Compute the Factor of Safety [FS]:Since Fic > 0.55 Fy and Fic < Fy
= 2.407 - 0.741 * Fic / Fy
= 2.407 - 0.741 * 322.45/338.00
= 1.700
Allowable Circumferential Compressive Stress [Fha]:Since Fr > 0.552 and Fr < 2.439, Fha = 0.7 * Fy/FS * Fr^(0.4)
= 0.7 * 338.0/1.700 * 2.168^(0.4)
= 189.665 MPa
Allowable External Pressure at the given Thickness [Pa]: = 2 * Fha * ( t / Do )
= 2 * 189.665 * ( 289.000/6093.000 )
= 17.992 MPa
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External Pressure Calculations : Step: 4 1:41pmMar 14,2015
Cylindrical Shell From 70 to 80 Ext. Chart: CS-2 at 454 °C
Shell-4
Maximum External Pressure per Code Case 2286 or Div. 2 Section 4.4
Determine Parameter [Mx]: = L / sqrt( Ro * t )
= 16492.670/sqrt( 3045.500 * 289.000 )
= 17.580
Compute the Factor [Ch]:Since Mx > 13 and Mx < 2 * (Do/t)^(0.94), Ch = 1.12 * Mx^(-1.058)
= 1.12 * 17.580^(-1.058)
= 0.0540
Elastic Hoop Compressive Membrane Failure Stress [Fhe]: = 1.6 * Ch * Ey * ( t / Do )
= 1.6 * 0.054 * 178967 * ( 289.000/6091.000 )
= 732.988 MPa
Ratio of Elastic Hoop Compressive Membrane Failure Stress to Yield [Fr]: = Fhe / Fy
= 733.0/338.0
= 2.169
Predicted Buckling Stress [Fic]:Since Fr > 0.552 and Fr < 2.439, Fic = 0.7 * Fy * Fr^(0.4)
= 0.7 * 338.00 * 2.17^(0.4)
= 322.468 MPa
Compute the Factor of Safety [FS]:Since Fic > 0.55 Fy and Fic < Fy
= 2.407 - 0.741 * Fic / Fy
= 2.407 - 0.741 * 322.47/338.00
= 1.700
Allowable Circumferential Compressive Stress [Fha]:Since Fr > 0.552 and Fr < 2.439, Fha = 0.7 * Fy/FS * Fr^(0.4)
= 0.7 * 338.0/1.700 * 2.169^(0.4)
= 189.682 MPa
Allowable External Pressure at the given Thickness [Pa]: = 2 * Fha * ( t / Do )
= 2 * 189.682 * ( 289.000/6091.000 )
= 18.000 MPa
Spherical Head From 80 to 90 Ext. Chart: CS-2 at 454 °C
Top Head
Maximum External Pressure per Code Case 2286 or Div. 2 Section 4.4
Elastic Hoop Compressive Membrane Failure Stress [Fhe]: = 0.075 * Ey * ( t / Ro )
= 0.075 * 178967 * ( 147.000/2976.500 )
= 662.897 MPa
Ratio of Elastic Hoop Compressive Membrane Failure Stress to Yield [Fr]:
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External Pressure Calculations : Step: 4 1:41pmMar 14,2015
= Fhe / Sy
= 662.9 / 338.0
= 1.961
Predicted Buckling Stress [Fic]:Since Fr > 1.6 and Fr < 6.25, Fic = 1.31 * Fy /( 1.15 + Sy/Fhe )
= 1.31 * 338.00/( 1.15 + 338.000/662.897 )
= 266.754 MPa
Allowable Circumferential Compressive Stress [Fha]:Since Fr > 1.6 and Fr < 6.25, Fha = 1.31 * Fy / ( FS * (1.15 + Sy/Fhe) )
= 1.31 * 338.00/( 1.82 * (1.15 + 338.00/662.90 ) )
= 146.392 MPa
Allowable External Pressure at the given Thickness [Pa]: = 2 * Fha[t/Ro]
= 2 * 146.392 [147.000/2976.500 ]
= 14.460 MPa
External Pressure Calculations
| | Section | Outside | Corroded | Factor | Factor |
From| To | Length | Diameter | Thickness | A | B |
| | mm | mm | mm | | MPa |
---------------------------------------------------------------------------
10| 20| 7700.00 | ... | ... | No Calc | No Calc |
20| 30| 7700.00 | ... | ... | No Calc | No Calc |
30| 40| No Calc | 5955.00 | 147.000 | No Calc | No Calc |
40| 50| 16492.7 | 6091.00 | 289.000 | No Calc | No Calc |
50| 60| 16492.7 | 6091.00 | 289.000 | No Calc | No Calc |
60| 70| 16492.7 | 6093.00 | 289.000 | No Calc | No Calc |
70| 80| 16492.7 | 6091.00 | 289.000 | No Calc | No Calc |
80| 90| No Calc | 5953.00 | 147.000 | No Calc | No Calc |
External Pressure Calculations
| | External | External | External | External |
From| To | Actual T. | Required T.|Des. Press. | M.A.W.P. |
| | mm | mm | MPa | MPa |
----------------------------------------------------------------
10| 20| ... | No Calc | ... | No Calc |
20| 30| ... | No Calc | ... | No Calc |
30| 40| 147.000 | 8.83954 | 0.10200 | 14.4528 |
40| 50| 289.000 | 28.8024 | 0.10200 | 17.9997 |
50| 60| 289.000 | 28.8024 | 0.10200 | 17.9997 |
60| 70| 289.000 | 28.8079 | 0.10200 | 17.9922 |
70| 80| 289.000 | 28.8025 | 0.10200 | 17.9997 |
80| 90| 147.000 | 8.83657 | 0.10200 | 14.4596 |
Minimum 14.453
External Pressure Calculations
| | Actual Len.| Allow. Len.| Ring Inertia | Ring Inertia |
From| To | Bet. Stiff.| Bet. Stiff.| Required | Available |
| | mm | mm | mm**4 | mm**4 |
-------------------------------------------------------------------
10| 20| 7700.00 | No Calc | No Calc | No Calc |
20| 30| 7700.00 | No Calc | No Calc | No Calc |
30| 40| No Calc | No Calc | No Calc | No Calc |
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External Pressure Calculations : Step: 4 1:41pmMar 14,2015
40| 50| 16492.7 | 25.40E+06 | No Calc | No Calc |
50| 60| 16492.7 | 25.40E+06 | No Calc | No Calc |
60| 70| 16492.7 | 25.40E+06 | No Calc | No Calc |
70| 80| 16492.7 | 25.40E+06 | No Calc | No Calc |
80| 90| No Calc | No Calc | No Calc | No Calc |
Elements Suitable for External Pressure.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
Page 26
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Element and Detail Weights : Step: 5 1:41pmMar 14,2015
Element and Detail Weights
| | Element | Element | Corroded | Corroded | Extra due |
From| To | Metal Wgt. | ID Volume |Metal Wgt. | ID Volume | Misc % |
| | kgm | ltr | kgm | ltr | kgm |
---------------------------------------------------------------------------
10| 20| 32397.2 | ... | 32397.2 | ... | ... |
20| 30| 3837.04 | ... | 3837.04 | ... | ... |
30| 40| 66891.4 | 47503.5 | 66891.4 | 47503.5 | ... |
40| 50| 161270. | 94306.3 | 161270. | 94306.3 | ... |
50| 60| 161270. | 94306.3 | 161270. | 94306.3 | ... |
60| 70| 136820. | 80039.4 | 136820. | 80039.4 | ... |
70| 80| 137018. | 80124.6 | 137018. | 80124.6 | ... |
80| 90| 66845.5 | 47453.2 | 66845.5 | 47453.2 | ... |
---------------------------------------------------------------------------
Total 766348 443733.28 766348 443733.28 0
Weight of Details
| | Weight of | X Offset, | Y Offset, |
From|Type| Detail | Dtl. Cent. |Dtl. Cent. | Description
| | kgm | mm | mm |
-------------------------------------------------
30|Insl| 2221.52 | ... | -1415.25 | INS
30|Nozl| 355.590 | ... | -2830.50 | Noz N1
30|Nozl| 158.420 | 2165.00 | -1823.32 | Noz N3 (8")
30|Nozl| 483.092 | ... | -1823.32 | Noz N2 (20")
40|Insl| 2787.85 | ... | 1975.00 | INS-1
40|Wght| 140000. | ... | ... | WEIGHT-1
50|Insl| 2787.85 | ... | 1975.00 | INS-2
50|Wght| 140000. | ... | ... | WEIGHT-2
60|Insl| 2365.14 | ... | 1675.00 | INS
60|Nozl| 392.854 | 2890.50 | 500.000 | Noz(10")
60|Nozl| 307.240 | 2839.50 | 300.000 | Noz N6 (6")
60|Wght| 140000. | ... | ... | WEIGHT-3
70|Insl| 2368.62 | ... | 1678.00 | INS
70|Wght| 140000. | ... | ... | WEIGHT-5
80|Insl| 2220.03 | ... | 1414.75 | INS
80|Nozl| 841.750 | ... | 3134.30 | Noz MH
80|Wght| 140000. | ... | ... | WEIGHT-3
Total Weight of Each Detail Type
Total Weight of Insulation 14751.0
Total Weight of Nozzles 2538.9
Total Weight of Weights 700000.0
---------------------------------------------------------------
Sum of the Detail Weights 717289.9 kgm
Weight Summation
Fabricated Shop Test Shipping Erected Empty Operating
------------------------------------------------------------------------------
766348.2 768887.2 766348.2 768887.2 766348.2 1343638.1
... 443462.4 ... ... ... ...
2538.9 ... 2538.9 ... ... ...
... ... ... 14751.0 ... ...
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Element and Detail Weights : Step: 5 1:41pmMar 14,2015
... ... ... ... 14751.0 ...
... ... ... ... ... 700000.0
... ... ... ... ... -560000.0
... ... ... ... 2538.9 ...
... ... ... ... 560000.0 ...
------------------------------------------------------------------------------
768887.2 1212349.6 783638.2 1343638.1 1343638.1 1483638.1 kgm
Note: The shipping total has been modified because some items havebeen specified as being installed in the shop.
Weight Summary
Fabricated Wt. - Bare Weight W/O Removable Internals 768887.2 kgm
Shop Test Wt. - Fabricated Weight + Water ( Full ) 1212349.6 kgm
Shipping Wt. - Fab. Wt + Rem. Intls.+ Shipping App. 783638.2 kgm
Erected Wt. - Fab. Wt + Rem. Intls.+ Insul. (etc) 1343638.1 kgm
Ope. Wt. no Liq - Fab. Wt + Intls. + Details + Wghts. 1343638.1 kgm
Operating Wt. - Empty Wt + Operating Liq. Uncorroded 1483638.1 kgm
Field Test Wt. - Empty Weight + Water (Full) 1227100.6 kgm
Mass of the Upper 1/3 of the Vertical Vessel 800112.4 kgm
Note: The Field Test weight as computed in the corroded condition.
Outside Surface Areas of Elements
| | Surface |
From| To | Area |
| | mm² |
----------------------------
10| 20| 128.1E+06 |
20| 30| 19.12E+06 |
30| 40| 56.27E+06 |
40| 50| 75.58E+06 |
50| 60| 75.58E+06 |
60| 70| 64.12E+06 |
70| 80| 64.22E+06 |
80| 90| 56.23E+06 |
-------------------------------
Total 539254400.000 mm²
Element and Detail Weights
| To | Total Ele.| Total. Ele.|Total. Ele.| Total Dtl.| Oper. Wgt. |
From| To | Empty Wgt.| Oper. Wgt.|Hydro. Wgt.| Offset Mom.| No Liquid |
| | kgm | kgm | kgm | N-mm | kgm |
---------------------------------------------------------------------------
10| 20| 32397.2 | 32397.2 | 32397.2 | ... | 32397.2 |
20| 30| 3837.04 | 3837.04 | 3837.04 | ... | 3837.04 |
30| 40| 70110.0 | 70110.0 | 117585. | 3.365E+06 | 70110.0 |
40| 50| 304057. | 304057. | 258306. | ... | 304057. |
50| 60| 304057. | 304057. | 258306. | ... | 304057. |
60| 70| 279885. | 279885. | 219876. | 19.70E+06 | 279885. |
70| 80| 279387. | 279387. | 219462. | ... | 279387. |
80| 90| 69907.3 | 209907. | 117332. | ... | 209907. |
Cumulative Vessel Weight
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Element and Detail Weights : Step: 5 1:41pmMar 14,2015
| | Cumulative Ope | Cumulative | Cumulative |
From| To | Wgt. No Liquid | Oper. Wgt. | Hydro. Wgt. |
| | kgm | kgm | kgm |
-------------------------------------------------------
10| 20| 1.484E+06 | 1.484E+06 | 1.227E+06 |
20| 30| 1.451E+06 | 1.451E+06 | 1.195E+06 |
30| 40| 1.447E+06 | 1.447E+06 | 1.191E+06 |
40| 50| 1.377E+06 | 1.377E+06 | 1.073E+06 |
50| 60| 1.073E+06 | 1.073E+06 | 814976. |
60| 70| 769179. | 769179. | 556670. |
70| 80| 489294. | 489294. | 336794. |
80| 90| 209907. | 209907. | 117332. |
Note: The cumulative operating weights no liquid in the column aboveare the cumulative operating weights minus the operating liquidweight minus any weights absent in the empty condition.
Cumulative Vessel Moment
| | Cumulative | Cumulative |Cumulative |
From| To | Empty Mom. | Oper. Mom. |Hydro. Mom.|
| | N-mm | N-mm | N-mm |
-------------------------------------------------
10| 20| 23.06E+06 | 23.06E+06 | 23.06E+06 |
20| 30| 23.06E+06 | 23.06E+06 | 23.06E+06 |
30| 40| 23.06E+06 | 23.06E+06 | 23.06E+06 |
40| 50| 19.70E+06 | 19.70E+06 | 19.70E+06 |
50| 60| 19.70E+06 | 19.70E+06 | 19.70E+06 |
60| 70| 19.70E+06 | 19.70E+06 | 19.70E+06 |
70| 80| ... | ... | ... |
80| 90| ... | ... | ... |
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Nozzle Flange MAWP : Step: 6 1:41pmMar 14,2015
Nozzle Flange MAWP Results :
Nozzle ----- Flange Rating
There does not appear to be any valid flange data to process.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Natural Frequency Calculation : Step: 7 1:41pmMar 14,2015
The Natural Frequencies for the vessel have been computed iterativelyby solving a system of matrices. These matrices describe the massand the stiffness of the vessel. This is the generalized eigenvalue/eigenvector problem and is referenced in some mathematical texts.
The Natural Frequency for the Vessel (Empty.) is 2.30397 Hz.
The Natural Frequency for the Vessel (Ope...) is 2.30397 Hz.
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Wind Load Calculation : Step: 8 1:41pmMar 14,2015
Wind Load Calculations per India Std. IS-875 (Part-3) - 1987, Amd. 1&2 (2003):
Actual Vessel Height to Diameter ratio 3.548
Force Coefficient per IS:875 Table 23, Cf 0.752
User Entered Basic Wind Speed 70.0 km/hr
Base Elevation 0.00 mm
Wind Zone Number 1
Risk Factor (k1) 1.0000
Terrain Category 1
Equipment Class A
Topography Factor (k3) 1.0000
Use Gust Response Factor (Dynamic Analysis) No
User entered Beta Value ( Operating Case ) 0.0100
Checking the requirement for Dynamic Effect of wind (7.1):
Vessel Operating Natural Frequency 2.304 Hz
Vessel Height to Diameter ratio 3.548
Note: Vessel Natural frequency is >= 1 Hz.
Note: Vessel height to diameter ratio (3.548) is <= 5.
Note: Dynamic wind analysis is not required.
From fo` FO E S G(ope) G(emp) G(tst)
------------------------------------------------------------------
10 175.39 35.90 0.0167 0.0306 1.0000 1.0000 1.0000
20 175.39 35.90 0.0167 0.0306 1.0000 1.0000 1.0000
30 175.39 35.90 0.0167 0.0306 1.0000 1.0000 1.0000
40 175.39 35.90 0.0167 0.0306 1.0000 1.0000 1.0000
50 169.10 34.62 0.0171 0.0317 1.0000 1.0000 1.0000
60 164.10 33.59 0.0174 0.0326 1.0000 1.0000 1.0000
70 160.59 32.87 0.0177 0.0332 1.0000 1.0000 1.0000
80 158.91 32.53 0.0178 0.0334 1.0000 1.0000 1.0000
Design Wind Speed (Vz):
= Basic Wind Speed * k1 * k2 * k3
Height Factor :
= 0.6 * Vz²
Element Wind Load : = Wind Area * Cf * Height Factor
From Height k1 k2 k3 Vz Cf
mm m/sec
------------------------------------------------------------
10 3350.00 1.0000 1.0548 1.0000 20.51 0.7516
20 7200.00 1.0000 1.0548 1.0000 20.51 0.7516
30 7699.98 1.0000 1.0548 1.0000 20.51 0.7516
40 9675.00 1.0000 1.0548 1.0000 20.51 0.7516
50 13625.00 1.0000 1.0822 1.0000 21.04 0.7516
60 17275.00 1.0000 1.1031 1.0000 21.45 0.7516
70 20628.00 1.0000 1.1188 1.0000 21.75 0.7516
80 23632.91 1.0000 1.1309 1.0000 21.99 0.7516
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Wind Load Calculation : Step: 8 1:41pmMar 14,2015
Wind Vibration Calculations
This evaluation is based on work by Kanti Mahajan and Ed Zorilla
Nomenclature
Cf - Correction factor for natural frequency
D - Average internal diameter of vessel mm
Df - Damping Factor < 0.75 Unstable, > 0.95 Stable
Dr - Average internal diameter of top half of vessel mm
f - Natural frequency of vibration (Hertz)
f1 - Natural frequency of bare vessel based on a unit value of (D/L²)(10^(4))
L - Total height of structure mm
Lc - Total length of conical section(s) of vessel mm
tb - Uncorroded plate thickness at bottom of vessel mm
V30 - Design Wind Speed provided by user km/hr
Vc - Critical wind velocity km/hr
Vw - Maximum wind speed at top of structure km/hr
W - Total corroded weight of structure N
Ws - Cor. vessel weight excl. weight of parts which do not effect stiff. N
Z - Maximum amplitude of vibration at top of vessel mm
Dl - Logarithmic decrement ( taken as 0.03 for Welded Structures )
Vp - Vib. Chance, <= 0.314E-05 (High); 0.314E-05 < 0.393E-05 (Probable)
P30 - wind pressure 30 feet above the base
Check other Conditions and Basic Assumptions: #1 - Total Cone Length / Total Length < 0.5
0.000/22306.000 = 0.000
#2 - ( D / L² ) * 10^(4) < 8.0 (English Units)
- ( 20.62/73.18² ) * 10^(4) = 38.510 [Geometry Violation]
Compute the vibration possibility. If Vp > 0.393E-05 no chance. [Vp]: = W / ( L * Dr²)
= 14548551/( 22306.00 * 5513.601² )
= 0.21455E-04
Since Vp is > 0.393E-05 no further vibration analysis is required !
Platform Load Calculations
ID Wind Area Elevation Pressure Force Cf
mm² mm kPa N
-------------------------------------------------------------------------
Wind Loads on Masses/Equipment/Piping
ID Wind Area Elevation Pressure Force
mm² mm kPa N
-------------------------------------------------------------------------
WEIGHT-1 0.00 7700.00 0.25 0.00
WEIGHT-2 0.00 11650.00 0.26 0.00
WEIGHT-3 0.00 15600.00 0.27 0.00
WEIGHT-5 0.00 18950.00 0.28 0.00
WEIGHT-3 0.00 22305.97 0.29 0.00
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Wind Load Calculation : Step: 8 1:41pmMar 14,2015
The Natural Frequency for the Vessel (Ope...) is 2.30397 Hz.
Wind Load Calculation
| | Wind | Wind | Wind | Wind | Element |
From| To | Height | Diameter | Area | Pressure | Wind Load |
| | mm | mm | mm² | kPa | N |
---------------------------------------------------------------------------
10| 20| 3350.00 | 8521.80 | 57.10E+06 | 0.25247 | 10830.2 |
20| 30| 7200.00 | 8521.80 | 8.522E+06 | 0.25247 | 1616.45 |
30| 40| 7699.98 | 7506.00 | 228.783 | 0.25247 | 0.043396 |
40| 50| 9675.00 | 8947.40 | 35.34E+06 | 0.25247 | 6703.85 |
50| 60| 13625.0 | 8947.40 | 35.34E+06 | 0.26573 | 7055.98 |
60| 70| 17275.0 | 8950.20 | 29.98E+06 | 0.27613 | 6220.47 |
70| 80| 20628.0 | 8947.40 | 30.03E+06 | 0.28404 | 6408.06 |
80| 90| 23632.9 | 8754.20 | 21.50E+06 | 0.29018 | 4686.65 |
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Earthquake Load Calculation : Step: 9 1:41pmMar 14,2015
Seismic Analysis Results per IS-1893 (1984), Seismic Coefficient Method.
Soil Factor ß 1.0000
Importance Factor as Entered by User I 1.0000
Zone Number 1
Value of Alpha o per table 2 and Zone 0.0100
Horizontal Seismic Coefficient (Alpha h): = ß * I * Alpha o
= 1.0000 * 1.0000 * 0.0100
= 0.0100
Earthquake Element Load, for the first Element: = Earthquake Weight * Alpha h
= 317686.69 * 0.0100
= 3176.9 N
The Natural Frequency for the Vessel (Ope...) is 2.30397 Hz.
Earthquake Load Calculation
| | Earthquake | Earthquake | Element | Element |
From| To | Height | Weight | Ope Load | Emp Load |
| | mm | N | N | N |
--------------------------------------------------------------
10| 20| 3350.00 | 317687. | 3176.87 | 3176.87 |
20| 30| 7200.00 | 37626.0 | 376.260 | 376.260 |
30| 40| 7699.98 | 687499. | 6874.99 | 6874.99 |
40| 50| 9675.00 | 2.982E+06 | 29815.9 | 29815.9 |
50| 60| 13625.0 | 2.982E+06 | 29815.9 | 29815.9 |
60| 70| 17275.0 | 2.745E+06 | 27445.5 | 27445.5 |
70| 80| 20628.0 | 2.740E+06 | 27396.6 | 27396.6 |
80| 90| 22306.0 | 2.058E+06 | 20583.5 | 6855.10 |
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Wind/Earthquake Shear, Bending : Step: 10 1:41pmMar 14,2015
The following table is for the Operating Case.
Wind/Earthquake Shear, Bending
| | Distance to| Cumulative |Earthquake | Wind | Earthquake |
From| To | Support| Wind Shear | Shear | Bending | Bending |
| | mm | N | N | N-mm | N-mm |
---------------------------------------------------------------------------
10| 20| 3350.00 | 43521.7 | 145486. | 559.5E+06 | 2.288E+09 |
20| 30| 7200.00 | 32691.5 | 142309. | 304.1E+06 | 1.323E+09 |
30| 40| 7699.98 | 31075.1 | 141932. | 272.2E+06 | 1.181E+09 |
40| 50| 9675.00 | 31075.0 | 135057. | 272.2E+06 | 1.181E+09 |
50| 60| 13625.0 | 24371.2 | 105242. | 162.7E+06 | 706.2E+06 |
60| 70| 17275.0 | 17315.2 | 75425.7 | 80.32E+06 | 349.2E+06 |
70| 80| 20628.0 | 11094.7 | 47980.1 | 32.71E+06 | 142.4E+06 |
80| 90| 22306.0 | 4686.65 | 20583.5 | 6.221E+06 | 27.32E+06 |
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Wind Deflection : Step: 11 1:41pmMar 14,2015
Wind Deflection Calculations:
The following table is for the Operating Case.
Wind Deflection
| | Cumulative | Centroid | Elem. End | Elem. Ang. |
From| To | Wind Shear | Deflection |Deflection | Rotation |
| | N | mm | mm | |
--------------------------------------------------------------
10| 20| 43521.7 | 0.0059308 | 0.021683 | 0.00001 |
20| 30| 32691.5 | 0.024717 | 0.027927 | 0.00001 |
30| 40| 31075.1 | 0.027927 | 0.027927 | 0.00001 |
40| 50| 31075.0 | 0.041070 | 0.054423 | 0.00001 |
50| 60| 24371.2 | 0.067936 | 0.081566 | 0.00001 |
60| 70| 17315.2 | 0.093188 | 0.10485 | 0.00001 |
70| 80| 11094.7 | 0.11655 | 0.12827 | 0.00001 |
80| 90| 4686.65 | 0.12827 | 0.12827 | 0.00001 |
Critical Wind Velocity for Tower Vibration
| | 1st Crit. | 2nd Crit. |
From| To | Wind Speed | Wind Speed |
| | km/hr | km/hr |
-------------------------------------
10| 20| 352.460 | 2202.87 |
20| 30| 352.460 | 2202.87 |
30| 40| 310.446 | 1940.29 |
40| 50| 370.062 | 2312.89 |
50| 60| 370.062 | 2312.89 |
60| 70| 370.178 | 2313.61 |
70| 80| 370.062 | 2312.89 |
80| 90| 362.072 | 2262.95 |
Allowable deflection at the Tower Top (Ope)( 6.000"/100ft. Criteria)
Allowable deflection : 111.530 Actual Deflection : 0.128 mm
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Longitudinal Stress Constants : Step: 12 1:41pmMar 14,2015
Longitudinal Stress Constants
| | Metal Area | Metal Area |New & Cold | Corroded |
From| To | New & Cold | Corroded |Sect. Mod. | Sect. Mod. |
| | mm² | mm² | mm ³ | mm ³ |
--------------------------------------------------------------
10| 20| 532978. | 532978. | 803.6E+06 | 803.6E+06 |
20| 30| 495070. | 495070. | 747.0E+06 | 747.0E+06 |
30| 40| 2.682E+06 | 2.682E+06 | 3.801E+09 | 3.801E+09 |
40| 50| 5.268E+06 | 5.268E+06 | 7.296E+09 | 7.296E+09 |
50| 60| 5.268E+06 | 5.268E+06 | 7.296E+09 | 7.296E+09 |
60| 70| 5.270E+06 | 5.270E+06 | 7.302E+09 | 7.302E+09 |
70| 80| 5.268E+06 | 5.268E+06 | 7.296E+09 | 7.296E+09 |
80| 90| 2.681E+06 | 2.681E+06 | 3.798E+09 | 3.798E+09 |
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Longitudinal Allowable Stresses : Step: 13 1:41pmMar 14,2015
Longitudinal Allowable Stresses
| | | Hydrotest | | Hydrotest |
From| To | Tensile | Tensile | Compressive | Compressive |
| | MPa | MPa | MPa | MPa |
-------------------------------------------------------------------
10| 20| 134.000 | 209.600 | -89.4807 | -107.377 |
20| 30| 199.300 | 393.000 | -46.3226 | -104.751 |
30| 40| 199.300 | 393.000 | -66.3090 | -145.890 |
40| 50| 199.300 | 393.000 | -72.8100 | -147.277 |
50| 60| 199.300 | 393.000 | -72.8100 | -147.277 |
60| 70| 199.000 | 393.000 | -72.8068 | -147.277 |
70| 80| 199.300 | 393.000 | -72.8100 | -147.277 |
80| 90| 199.300 | 393.000 | -66.3125 | -145.893 |
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Longitudinal Stresses Due to . . . Step: 14 1:41pmMar 14,2015
Longitudinal Stress Report
Note: Longitudinal Operating and Empty Stresses are computed in thecorroded condition. Stresses due to loads in the hydrostatic testcases have also been computed in the corroded condition.
Longitudinal Stresses Due to . . .
| | Long. Str. | Long. Str. |Long. Str. |
From| To | Int. Pres. | Ext. Pres. |Hyd. Pres. |
| | MPa | MPa | MPa |
-------------------------------------------------
10| 20| ... | ... | ... |
20| 30| ... | ... | ... |
30| 40| 186.082 | -1.05916 | 284.948 |
40| 50| 89.8593 | -0.56421 | 137.602 |
50| 60| 89.8593 | -0.56421 | 137.602 |
60| 70| 89.8935 | -0.56439 | 137.654 |
70| 80| 89.8593 | -0.56421 | 137.602 |
80| 90| 186.015 | -1.05881 | 284.845 |
Longitudinal Stresses Due to . . .
| | Wght. Str. | Wght. Str. |Wght. Str. | Wght. Str. | Wght. Str. |
From| To | Empty | Operating |Hydrotest | Emp. Mom. | Opr. Mom. |
| | MPa | MPa | MPa | MPa | MPa |
---------------------------------------------------------------------------
10| 20| -27.2990 | -27.2990 | ... | 0.028689 | 0.028689 |
20| 30| -28.7476 | -28.7476 | ... | 0.030865 | 0.030865 |
30| 40| -5.29206 | -5.29206 | ... | 0.0060658 | 0.0060658 |
40| 50| -2.56407 | -2.56407 | ... | 0.0026988 | 0.0026988 |
50| 60| -1.99801 | -1.99801 | ... | 0.0026988 | 0.0026988 |
60| 70| -1.43147 | -1.43147 | ... | 0.0026969 | 0.0026969 |
70| 80| -0.91090 | -0.91090 | ... | ... | ... |
80| 90| -0.76774 | -0.76774 | ... | ... | ... |
Longitudinal Stresses Due to . . .
| | Wght. Str. | Bend. Str. |Bend. Str. | Bend. Str. | Bend. Str. |
From| To | Hyd. Mom. | Oper. Wind |Oper. Equ. | Hyd. Wind | Hyd. Equ. |
| | MPa | MPa | MPa | MPa | MPa |
---------------------------------------------------------------------------
10| 20| ... | 0.69605 | 2.84571 | ... | ... |
20| 30| ... | 0.40702 | 1.77078 | ... | ... |
30| 40| ... | 0.071601 | 0.31061 | ... | ... |
40| 50| ... | 0.037299 | 0.16180 | ... | ... |
50| 60| ... | 0.022289 | 0.096753 | ... | ... |
60| 70| ... | 0.010997 | 0.047811 | ... | ... |
70| 80| ... | 0.0044820 | 0.019513 | ... | ... |
80| 90| ... | 0.0016375 | 0.0071916 | ... | ... |
Longitudinal Stresses Due to . . .
| | Long. Str. | Long. Str. |Long. Str. | EarthQuake |
From| To | Vortex Ope.| Vortex Emp.|Vortex Tst.| Empty |
| | MPa | MPa | MPa | MPa |
--------------------------------------------------------------
10| 20| ... | ... | ... | 2.44195 |
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Longitudinal Stresses Due to . . . Step: 14 1:41pmMar 14,2015
20| 30| ... | ... | ... | 1.45954 |
30| 40| ... | ... | ... | 0.25305 |
40| 50| ... | ... | ... | 0.13182 |
50| 60| ... | ... | ... | 0.074204 |
60| 70| ... | ... | ... | 0.032707 |
70| 80| ... | ... | ... | 0.010701 |
80| 90| ... | ... | ... | 0.0023951 |
Longitudinal Stresses Due to . . .
| | Long. Str. | Long. Str. |
From| To | Y Forces W | Y ForceS S |
| | MPa | MPa |
-------------------------------------
10| 20| ... | ... |
20| 30| ... | ... |
30| 40| ... | ... |
40| 50| ... | ... |
50| 60| ... | ... |
60| 70| ... | ... |
70| 80| ... | ... |
80| 90| ... | ... |
Long. Stresses due to User Forces and Moments
| |Wind For/Mom| Eqk For/Mom|Wnd For/Mom| Eqk For/Mom|
From| To | Corroded | Corroded | No Corr. | No Corr. |
| | MPa | MPa | MPa | MPa |
--------------------------------------------------------------
10| 20| ... | ... | ... | ... |
20| 30| ... | ... | ... | ... |
30| 40| ... | ... | ... | ... |
40| 50| ... | ... | ... | ... |
50| 60| ... | ... | ... | ... |
60| 70| ... | ... | ... | ... |
70| 80| ... | ... | ... | ... |
80| 90| ... | ... | ... | ... |
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Stress due to Combined Loads : Step: 15 1:41pmMar 14,2015
Stress Combination Load Cases for Vertical Vessels:
Load Case Definition Key
IP = Longitudinal Stress due to Internal Pressure
EP = Longitudinal Stress due to External Pressure
HP = Longitudinal Stress due to Hydrotest Pressure
NP = No Pressure
EW = Longitudinal Stress due to Weight (No Liquid)
OW = Longitudinal Stress due to Weight (Operating)
HW = Longitudinal Stress due to Weight (Hydrotest)
WI = Bending Stress due to Wind Moment (Operating)
EQ = Bending Stress due to Earthquake Moment (Operating)
EE = Bending Stress due to Earthquake Moment (Empty)
HI = Bending Stress due to Wind Moment (Hydrotest)
HE = Bending Stress due to Earthquake Moment (Hydrotest)
WE = Bending Stress due to Wind Moment (Empty) (no CA)
WF = Bending Stress due to Wind Moment (Filled) (no CA)
CW = Longitudinal Stress due to Weight (Empty) (no CA)
VO = Bending Stress due to Vortex Shedding Loads ( Ope )
VE = Bending Stress due to Vortex Shedding Loads ( Emp )
VF = Bending Stress due to Vortex Shedding Loads ( Test No CA. )
FW = Axial Stress due to Vertical Forces for the Wind Case
FS = Axial Stress due to Vertical Forces for the Seismic Case
BW = Bending Stress due to Lat. Forces for the Wind Case, Corroded
BS = Bending Stress due to Lat. Forces for the Seismic Case, Corroded
BN = Bending Stress due to Lat. Forces for the Wind Case, UnCorroded
BU = Bending Stress due to Lat. Forces for the Seismic Case, UnCorroded
General Notes:
Case types HI and HE are in the Corroded condition.
Case types WE, WF, and CW are in the Un-Corroded condition.
A blank stress and stress ratio indicates that the correspondingstress comprising those components that did not contribute to thattype of stress.
For Division 2, stress Sigma1 is the hoop stress due to internalpressure. Stress Sigma2 is the max(abs( positive stress, 0.0 )).The positive magnitude of Sigma3 is the 0.5 times the pressure.The stresses are combined per equation 4.3.44 to determinethe overall stress intensity.
An asterisk (*) in the final column denotes overstress.
Note: Performing Combined Stress Analysis per VIII-2 paragraph 4.3.10.2.
Analysis of Load Case 1 : NP+EW+WI+FW+BW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 18.79 134.00 -28.02 96.20 0.1402 0.2913
20 20.02 199.30 -29.19 155.19 0.1004 0.1881
30 3.69 199.30 -5.37 146.37 0.0185 0.0367
40 1.78 199.30 -2.60 202.76 0.0090 0.0128
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Stress due to Combined Loads : Step: 15 1:41pmMar 14,2015
50 1.40 199.30 -2.02 202.76 0.0070 0.0100
60 1.00 199.00 -1.45 202.76 0.0050 0.0071
70 0.64 199.30 -0.92 202.76 0.0032 0.0045
80 0.54 199.30 -0.77 146.39 0.0027 0.0053
Analysis of Load Case 2 : NP+EW+EE+FS+BS From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 17.56 134.00 -29.77 96.20 0.1310 0.3095
20 19.27 199.30 -30.24 155.19 0.0967 0.1948
30 3.56 199.30 -5.55 146.37 0.0179 0.0379
40 1.72 199.30 -2.70 202.76 0.0086 0.0133
50 1.36 199.30 -2.07 202.76 0.0068 0.0102
60 0.99 199.00 -1.47 202.76 0.0050 0.0072
70 0.64 199.30 -0.92 202.76 0.0032 0.0045
80 0.54 199.30 -0.77 146.39 0.0027 0.0053
Analysis of Load Case 3 : NP+OW+WI+FW+BW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 18.79 134.00 -28.02 96.20 0.1402 0.2913
20 20.02 199.30 -29.19 155.19 0.1004 0.1881
30 3.69 199.30 -5.37 146.37 0.0185 0.0367
40 1.78 199.30 -2.60 202.76 0.0090 0.0128
50 1.40 199.30 -2.02 202.76 0.0070 0.0100
60 1.00 199.00 -1.45 202.76 0.0050 0.0071
70 0.64 199.30 -0.92 202.76 0.0032 0.0045
80 0.54 199.30 -0.77 146.39 0.0027 0.0053
Analysis of Load Case 4 : NP+OW+EQ+FS+BS From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 17.27 134.00 -30.17 96.20 0.1289 0.3137
20 19.05 199.30 -30.55 155.19 0.0956 0.1968
30 3.52 199.30 -5.61 146.37 0.0177 0.0383
40 1.70 199.30 -2.73 202.76 0.0085 0.0135
50 1.34 199.30 -2.10 202.76 0.0067 0.0103
60 0.98 199.00 -1.48 202.76 0.0049 0.0073
70 0.63 199.30 -0.93 202.76 0.0032 0.0046
80 0.54 199.30 -0.77 146.39 0.0027 0.0053
Analysis of Load Case 5 : NP+HW+HI From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 0.00 209.60 0.00 107.38 0.0000 0.0000
20 0.00 393.00 0.00 104.75 0.0000 0.0000
30 0.00 393.00 0.00 145.89 0.0000 0.0000
40 0.00 393.00 0.00 147.28 0.0000 0.0000
50 0.00 393.00 0.00 147.28 0.0000 0.0000
60 0.00 393.00 0.00 147.28 0.0000 0.0000
70 0.00 393.00 0.00 147.28 0.0000 0.0000
80 0.00 393.00 0.00 145.89 0.0000 0.0000
Analysis of Load Case 6 : NP+HW+HE From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 0.00 209.60 0.00 107.38 0.0000 0.0000
20 0.00 393.00 0.00 104.75 0.0000 0.0000
30 0.00 393.00 0.00 145.89 0.0000 0.0000
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Stress due to Combined Loads : Step: 15 1:41pmMar 14,2015
40 0.00 393.00 0.00 147.28 0.0000 0.0000
50 0.00 393.00 0.00 147.28 0.0000 0.0000
60 0.00 393.00 0.00 147.28 0.0000 0.0000
70 0.00 393.00 0.00 147.28 0.0000 0.0000
80 0.00 393.00 0.00 145.89 0.0000 0.0000
Analysis of Load Case 7 : IP+OW+WI+FW+BW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 18.79 134.00 -28.02 96.20 0.1402 0.2913
20 20.02 199.30 -29.19 155.19 0.1004 0.1881
30 193.44 199.30 146.37 0.9706
40 172.40 199.30 202.76 0.8650
50 172.40 199.30 202.76 0.8650
60 172.45 199.00 202.76 0.8666
70 172.39 199.30 202.76 0.8650
80 195.55 199.30 66.31 0.9812
Analysis of Load Case 8 : IP+OW+EQ+FS+BS From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 17.27 134.00 -30.17 96.20 0.1289 0.3137
20 19.05 199.30 -30.55 155.19 0.0956 0.1968
30 193.56 199.30 146.37 0.9712
40 172.40 199.30 202.76 0.8650
50 172.39 199.30 202.76 0.8650
60 172.45 199.00 202.76 0.8666
70 172.39 199.30 202.76 0.8650
80 195.55 199.30 66.31 0.9812
Analysis of Load Case 9 : EP+OW+WI+FW+BW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 18.79 134.00 -28.02 96.20 0.1402 0.2913
20 20.02 199.30 -29.19 155.19 0.1004 0.1881
30 4.44 199.30 -6.43 146.37 0.0223 0.0439
40 2.18 199.30 -3.17 202.76 0.0110 0.0156
50 1.79 199.30 -2.59 202.76 0.0090 0.0128
60 1.40 199.00 -2.01 202.76 0.0070 0.0099
70 1.04 199.30 -1.48 202.76 0.0052 0.0073
80 1.29 199.30 -1.83 146.39 0.0065 0.0125
Analysis of Load Case 10 : EP+OW+EQ+FS+BS From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 17.27 134.00 -30.17 96.20 0.1289 0.3137
20 19.05 199.30 -30.55 155.19 0.0956 0.1968
30 4.27 199.30 -6.67 146.37 0.0214 0.0456
40 2.10 199.30 -3.29 202.76 0.0105 0.0162
50 1.74 199.30 -2.66 202.76 0.0087 0.0131
60 1.38 199.00 -2.05 202.76 0.0069 0.0101
70 1.03 199.30 -1.49 202.76 0.0052 0.0074
80 1.29 199.30 -1.83 146.39 0.0065 0.0125
Analysis of Load Case 11 : HP+HW+HI From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 0.00 209.60 0.00 107.38 0.0000 0.0000
20 0.00 393.00 0.00 104.75 0.0000 0.0000
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Stress due to Combined Loads : Step: 15 1:41pmMar 14,2015
30 284.95 393.00 145.89 0.7251
40 137.60 393.00 147.28 0.3501
50 137.60 393.00 147.28 0.3501
60 137.65 393.00 147.28 0.3503
70 137.60 393.00 147.28 0.3501
80 284.85 393.00 145.89 0.7248
Analysis of Load Case 12 : HP+HW+HE From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 0.00 209.60 0.00 107.38 0.0000 0.0000
20 0.00 393.00 0.00 104.75 0.0000 0.0000
30 284.95 393.00 145.89 0.7251
40 137.60 393.00 147.28 0.3501
50 137.60 393.00 147.28 0.3501
60 137.65 393.00 147.28 0.3503
70 137.60 393.00 147.28 0.3501
80 284.85 393.00 145.89 0.7248
Analysis of Load Case 13 : IP+WE+EW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 19.28 134.00 -27.33 96.20 0.1439 0.2841
20 20.31 199.30 -28.78 155.19 0.1019 0.1854
30 193.41 199.30 146.37 0.9704
40 172.40 199.30 202.76 0.8650
50 172.40 199.30 202.76 0.8650
60 172.45 199.00 202.76 0.8666
70 172.39 199.30 202.76 0.8650
80 195.55 199.30 66.31 0.9812
Analysis of Load Case 14 : IP+WF+CW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 19.30 134.00 -27.30 96.20 0.1441 0.2838
20 20.33 199.30 -28.75 155.19 0.1020 0.1852
30 193.41 199.30 146.37 0.9704
40 172.40 199.30 202.76 0.8650
50 172.40 199.30 202.76 0.8650
60 172.45 199.00 202.76 0.8666
70 172.39 199.30 202.76 0.8650
80 195.55 199.30 66.31 0.9812
Analysis of Load Case 15 : IP+VO+OW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 19.28 134.00 -27.33 96.20 0.1439 0.2841
20 20.31 199.30 -28.78 155.19 0.1019 0.1854
30 193.41 199.30 146.37 0.9704
40 172.40 199.30 202.76 0.8650
50 172.40 199.30 202.76 0.8650
60 172.45 199.00 202.76 0.8666
70 172.39 199.30 202.76 0.8650
80 195.55 199.30 66.31 0.9812
Analysis of Load Case 16 : IP+VE+EW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 19.28 134.00 -27.33 96.20 0.1439 0.2841
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Stress due to Combined Loads : Step: 15 1:41pmMar 14,2015
20 20.31 199.30 -28.78 155.19 0.1019 0.1854
30 193.41 199.30 146.37 0.9704
40 172.40 199.30 202.76 0.8650
50 172.40 199.30 202.76 0.8650
60 172.45 199.00 202.76 0.8666
70 172.39 199.30 202.76 0.8650
80 195.55 199.30 66.31 0.9812
Analysis of Load Case 17 : NP+VO+OW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 19.28 134.00 -27.33 96.20 0.1439 0.2841
20 20.31 199.30 -28.78 155.19 0.1019 0.1854
30 3.74 199.30 -5.30 146.37 0.0188 0.0362
40 1.81 199.30 -2.57 202.76 0.0091 0.0127
50 1.41 199.30 -2.00 202.76 0.0071 0.0099
60 1.01 199.00 -1.43 202.76 0.0051 0.0071
70 0.64 199.30 -0.91 202.76 0.0032 0.0045
80 0.54 199.30 -0.77 146.39 0.0027 0.0052
Analysis of Load Case 18 : FS+BS+IP+OW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 19.28 134.00 -27.33 96.20 0.1439 0.2841
20 20.31 199.30 -28.78 155.19 0.1019 0.1854
30 193.41 199.30 146.37 0.9704
40 172.40 199.30 202.76 0.8650
50 172.40 199.30 202.76 0.8650
60 172.45 199.00 202.76 0.8666
70 172.39 199.30 202.76 0.8650
80 195.55 199.30 66.31 0.9812
Analysis of Load Case 19 : FS+BS+EP+OW From Stress All. Stress Compressive All. Comp. S. I. Comp.
Node Intensity Intensity Stress Stress Fxa Ratio Ratio
10 19.28 134.00 -27.33 96.20 0.1439 0.2841
20 20.31 199.30 -28.78 155.19 0.1019 0.1854
30 4.49 199.30 -6.36 146.37 0.0225 0.0434
40 2.21 199.30 -3.13 202.76 0.0111 0.0154
50 1.81 199.30 -2.56 202.76 0.0091 0.0127
60 1.41 199.00 -2.00 202.76 0.0071 0.0099
70 1.04 199.30 -1.48 202.76 0.0052 0.0073
80 1.29 199.30 -1.83 146.39 0.0065 0.0125
Absolute Maximum of the all of the Stress Ratio's 0.9812
Governing Element: Top HeadGoverning Load Case 8 : IP+OW+EQ+FS+BS
Additional Results per Section 4.4, see 4.4.15
Nomenclature : L - Section Length mm
Fxa - Allowable comp mem stress due to compression with lamc <= 0.15, MPa
Fba - Allowable all comp mem stress due to bending moment, MPa
Fva - Allowable shear stress when only shear is present, MPa
Fha - Allowable hoop comp memb stress under ext pressure alone, MPa
Fxha - Allowable axial comp w/hoop compression and lamc <= 0.15, MPa
Fhxa - Allowable hoop comp w/axial compression and lamc <= 0.15, MPa
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Faha - Allowable axial comp w/hoop compression and lamc > 0.15, MPa
Fbha - Allowable axial comp from bending w/hoop compression, MPa
Fhba - Allowable hoop comp w/long compression due to moment, MPa
Allowable Stress Results for Case 1 : NP+EW+WI+FW+BW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 146 6895 6895 6895 6895
Allowable Stress Results for Case 2 : NP+EW+EE+FS+BS From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 146 6895 6895 6895 6895
Allowable Stress Results for Case 3 : NP+OW+WI+FW+BW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 146 6895 6895 6895 6895
Allowable Stress Results for Case 4 : NP+OW+EQ+FS+BS From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 146 6895 6895 6895 6895
Allowable Stress Results for Case 5 : NP+HW+HI From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
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Stress due to Combined Loads : Step: 15 1:41pmMar 14,2015
Allowable Stress Results for Case 6 : NP+HW+HE From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 7 : IP+OW+WI+FW+BW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 8 : IP+OW+EQ+FS+BS From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 9 : EP+OW+WI+FW+BW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 230 96 221 7 188
50 0.315 16492 202 260 103 189 229 123 220 4 188
60 0.315 16492 202 260 103 189 216 162 207 2 189
70 0.315 16492 202 260 103 189 172 203 165 189
80 146 6895 6895 6895 6895
Allowable Stress Results for Case 10 : EP+OW+EQ+FS+BS From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 230 96 221 28 183
50 0.315 16492 202 260 103 189 229 123 220 17 186
60 0.315 16492 202 260 103 189 216 162 207 8 187
70 0.315 16492 202 260 103 189 172 203 165 3 189
80 146 6895 6895 6895 6895
Allowable Stress Results for Case 11 : HP+HW+HI From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
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Stress due to Combined Loads : Step: 15 1:41pmMar 14,2015
30 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 12 : HP+HW+HE From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 13 : IP+WE+EW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 14 : IP+WF+CW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 15 : IP+VO+OW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 16 : IP+VE+EW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
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Stress due to Combined Loads : Step: 15 1:41pmMar 14,2015
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 17 : NP+VO+OW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 146 6895 6895 6895 6895
Allowable Stress Results for Case 18 : FS+BS+IP+OW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
50 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
60 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
70 0.315 16492 202 260 103 189 6895 202 6895 6895 6895
80 6895 6895 6895 6895
Allowable Stress Results for Case 19 : FS+BS+EP+OW From Lamc L Fxa Fba Fva Fha Fxha Fhxa Faha Fbha Fhba
10 0.204 7700 96 96 53 6895 96 6895 6895 6895
20 0.275 7700 155 155 81 6895 155 6895 6895 6895
30 146 6895 6895 6895 6895
40 0.315 16492 202 260 103 189 230 96 221 189
50 0.315 16492 202 260 103 189 229 123 220 189
60 0.315 16492 202 260 103 189 216 162 207 189
70 0.315 16492 202 260 103 189 172 203 165 6895 6895
80 146 6895 6895 6895 6895
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Center of Gravity Calculation : Step: 16 1:41pmMar 14,2015
Shop/Field Installation Options :
Insulation is installed in the Shop.
Note : The CG is computed from the first Element From Node
Center of Gravity of Insulation 15002.152 mm
Center of Gravity of Nozzles 15016.432 mm
Center of Gravity of Added Weights (Operating) 15241.194 mm
Center of Gravity of Added Weights (Empty) 13475.001 mm
Center of Gravity of Bare Shell New and Cold 14470.746 mm
Center of Gravity of Bare Shell Corroded 14470.746 mm
Vessel CG in the Operating Condition 14840.471 mm
Vessel CG in the Fabricated (Shop/Empty) Condition 14062.604 mm
Vessel CG in the Test Condition 14295.723 mm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Basering Calculations : Step: 17 1:41pmMar 14,2015
Skirt Data : Skirt Outside Diameter at Base SOD 6087.0000 mm
Skirt Thickness STHK 28.0000 mm
Skirt Internal Corrosion Allowance SCA 0.0000 mm
Skirt External Corrosion Allowance 0.0000 mm
Skirt Material SA-516 60
Basering Input: Type of Geometry: Continuous Top Ring W/Gussets
Thickness of Basering TBA 57.0000 mm
Design Temperature of the Basering 38.00 °C
Basering Matl SA-516 60
Basering Operating All. Stress BASOPE 146.79 MPa
Basering Yield Stress 220.54 MPa
Inside Diameter of Basering DI 5755.7998 mm
Outside Diameter of Basering DOU 6467.0000 mm
Nominal Diameter of Bolts BND 56.0000 mm
Bolt Corrosion Allowance BCA 0.0000 mm
Bolt Material SA-193 B7
Bolt Operating Allowable Stress SA 172.38 MPa
Number of Bolts RN 34
Diameter of Bolt Circle DC 6278.0000 mm
Bolt Allowable Shear Stress 100.000 MPa
Ultimate Comp. Strength of Concrete FPC 20.7 MPa
Allowable Comp. Strength of Concrete FC 10.0 MPa
Modular ratio Steel/Concrete 9.833
Thickness of Gusset Plates TGA 20.0000 mm
Width of Gussets at Top Plate TWDT 190.0000 mm
Width of Gussets at Base Plate BWDT 190.0000 mm
Gusset Plate Elastic Modulus E 201746.0 MPa
Gusset Plate Yield Stress SY 220.5 MPa
Height of Gussets HG 300.0000 mm
Distance between Gussets RG 80.0000 mm
Dist. from Bolt Center to Gusset (Rg/2) CG 40.0000 mm
Number of Gussets per bolt NG 2
Thickness of Top Plate or Ring TTA 38.0000 mm
Radial Width of the Top Plate TOPWTH 190.0000 mm
Anchor Bolt Hole Dia. in Top Plate BHOLE 72.0000 mm
External Corrosion Allowance CA 0.0000 mm
Dead Weight of Vessel DW 13175711.0 N
Operating Weight of Vessel ROW 14548552.0 N
Earthquake Moment on Basering EQMOM 2287633152.0 N-mm
Wind Moment on Basering WIMOM 559547520.0 N-mm
Percent Bolt Preload ppl 100.0
Use AISC A5.2 Increase in Fc and Bolt Stress No
Use Allowable Weld Stress per AISC J2.5 No
Factor for Increase of Allowables Fact 1.0000
Results for Brownell and Young Basering Analysis : Analyze Option
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Basering Calculations : Step: 17 1:41pmMar 14,2015
Note: This analysis is based on Neutral Axis shift method for Steel onConcrete (or a material with significantly different Young's modulus).
No Tensile loads on the Bolts
Governing Bolt Load Condition, **** No Tensile Bolt Loads ****
Area Available in one Bolt Abss : 1862.7250 mm²
Area Available in all the Bolts Abss * RN : 63332.6523 mm²
Trial# k knew Cc Ct z j Ft Fc
2 0.165 0.247 1.102 2.739 0.466 0.773 471387.9 730.7
4 0.206 0.185 1.237 2.647 0.458 0.776 469456.1 727.7
6 0.175 0.170 1.137 2.716 0.464 0.774 470868.8 729.9
8 0.167 0.169 1.111 2.733 0.466 0.773 471255.7 730.5
10 0.168 0.168 1.113 2.732 0.466 0.773 471222.8 730.5
The Actual Stress in a Single Bolt [Sbolt]: = 2 * Ft / ( T1 * Dc * Ct )
= 2 * 471222.8/( 3.211 * 6278.000 * 2.732 )
= 17.116 MPa , Should be less than 172.4
Thickness of the Band of Bolting Steel [T1] = RN * Bolt Area / ( 3.14159 * Dc )
= 34 * 1862.725/( 3.14159 * 6278.000 )
= 3.211 mm
Check the Bearing Stress in the Concrete [fc(max)] = fc`[( 2kd + t3 ) / ( 2kd )]
= 226.674[(2*0.168*6278.000+355.600)/(2*0.168*6278.000)]
= 0.411 MPa , Should be less than 10.0
Values for table 10.3, l = 190.000 , b = 290.043 , l/b = 0.655076
Maximum Moment per unit width [Mmax]: = Max( Mx, My ) = Max( 1863.526 , 3459.026 ) = 3459.026 N
Reqd Thickness of Basering, Brownell & Young Method [T]: = ( 6 * Mmax / fallow )½ + Ca
= ( 6 * 3459.026/145.6 )½ + 0.000
= 11.941 mm
Nomenclature: a = ( Dc-Ds )/2 Skirt Distance to Bolt Circle
P = Sa * Abss Maximum Load on one Bolt
l = Avgwdt Average Gusset Width
g1 = Gamma 1 Constant Term f( b/l )
g2 = Gamma 2 Constant Term f( b/l )
g = Flat distance / 2 Nut 1/2 Dimension (from Tema)
Fb Allowable Bending Stress
Values for table 10.6, l = 190.000 , b = 80.000 , b/l = 0.421053As b/l (0.421 ) is less than 1, inverting b/l = 2.375 .
Moment Term, based on geometry [Mo]: = P/(4pi) [ 1.3(ln((2lsin(pi*a/l)/(pi*g))) + 1 ] - [ (0.7-g2)P/(4pi) ]
= 321059.94/(4*3.14) [1.3( ln((2*190.000 *SIN(3.14* 95.500/190.000 ))/
(3.14 * 45.000 )) ) + 1] - [(0.7 - -0.007 )* 321059.94/(4 * 3.14)]
= 40314.0117 N
Required Thickness of Continuous Top Ring [Tc]: = ( 6 * Abs(Mo) / Fb )½ + Ca
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= ( 6 * Abs( 40314.01 )/220.19 )½ + 0.0000
= 33.1454 mm
Required Gusset Plate Thickness [tg]: = P / ( Stress Term * l ) + Ca
= 321059.94/( 124.1100 * 190.000 ) + 0.000
= 13.616 (not less than 9.525 + 0.000 ) mm
Bolt spacing [m]: = pi * Bolt Circle Diameter / number of Bolts
= 3.142 * 6278.00/34 = 580.086 mm
Req. Skirt Thk. to withstand Local Bending, (Brownell and Young) [t]: = 1.76 * ( P*a/( m * ( h + tba ) * 1.5 * Sktope) )^(2/3) * r^(1/3) + Ca
= 1.76*(321059*95.500/(580.09*357.00*201))^(2/3)*3043.50^(1/3)+Ca
= 20.804 + 0.000 = 20.804 mm
Shear Stress in a Single Bolt [taub]: = Shear Force / ( 2 * Bolt Area * Number of Bolts )
= 145485/( 2 * 1862.72 * 34 )
= 1.1 MPa. Must be less than 100.0 MPa .
Summary of Basering Thickness Calculations Required Basering Thickness (tension) 11.9415 mm
Actual Basering Thickness as entered by user 57.0000 mm
Required Thickness of Chair Cap 33.1454 mm
Actual Top Ring Thickness as entered by user 38.0000 mm
Required Gusset thickness, + CA 13.6164 mm
Actual Gusset Thickness as entered by user 20.0000 mm
Required Thickness of Skirt for Local Stress 20.8042 mm
Given Thickness of Skirt 28.0000 mm
Required Gusset Height to meet local stress 171.6423 mm
Weld Size Calculations per Steel Plate Engineering Data - Vol. 2
Compute the Weld load at the Skirt/Base Junction [W] = SkirtStress * ( SkirtThickness - CA )
= 30.173 * ( 28.000 - 0.000 )
= 844.78 N/mm
Results for Computed Minimum Basering Weld Size [BWeld] = W / [( 0.4 * Yield ) * 2 * 0.707]
= 844/[( 0.4 * 201 ) * 2 * 0.707]
= 7.424 mm
Results for Computed Minimum Gusset and Top Plate to Skirt Weld Size
Vertical Plate Load [Wv] = Bolt Load / ( Cmwth + 2 * ( Hg + Tta ) )
= 321059.9/( 164.000 + 2 * ( 300.000 + 38.000 ) )
= 382.214 N/mm
Horizontal Plate Load [Wh] = Bolt Load * e / ( Cmwth * (Hg+Tta) + 0.6667 * (Hg+Tta)² )
= 321059.9 * 95.500/(164.000 * (338.000 ) + 0.6667 * (338.000 )² )
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= 232.997 N/mm
Resultant Weld Load [Wr] = ( Wv² + Wh²)½
= ( 382.21² + 233.00²)½
= 447.633 N/mm
Results for Computed Min Gusset and Top Plate to Skirt Weld Size [GsWeld] = Wr / [( 0.4 * Yield ) * 2 * 0.707]
= 447.63/[( 0.4 * 201 ) * 2 * 0.707]
= 3.934 mm
Results for Computed Minimum Gusset to Top Plate Weld Size
Weld Load [Wv] = Bolt Load / ( 2 * TopWth )
= 321059.9/( 2 * 190.000 )
= 844.895 N/mm
Weld Load [Wh] = Bolt Load * e / ( 2 * Hgt * TopWth )
= 321059.9 * 95.50/( 2 * 338.000 * 190.000 )
= 238.720 N/mm
Resultant Weld Load [Wr] = ( Wv² + Wh²)½
= ( 844.89² + 238.72²)½
= 877.972 N/mm
Results for Computed Min Gusset to Top Plate Weld Size [GtpWeld] = Wr / [( 0.4 * Yield ) * 2 * 0.707]
= 877.97/[( 0.4 * 201 ) * 2 * 0.707]
= 7.716 mm
Note: The calculated weld sizes need not exceed the component thicknessframing into the weld. At the same time, the weld must meet a minimum sizespecification which is 3/16 in. (4.76 mm) or 1/4 in. (6.35 mm), dependingon the component thickness.
Summary of Required Weld Sizes: Required Basering to Skirt Double Fillet Weld Size 7.4241 mm
Required Gusset to Skirt Double Fillet Weld Size 6.3500 mm
Required Top Plate to Skirt Weld Size 7.7158 mm
Required Gusset to Top Plate Double Fillet Weld Size 7.7158 mm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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INPUT VALUES, Nozzle Description: Noz N1 From : 30
Pressure for Reinforcement Calculations P 19.8300 MPa
Temperature for Internal Pressure Temp 454 °C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 454 °C
Shell Material SA-336 F22V
Shell Allowable Stress at Temperature S 199.30 MPa
Shell Allowable Stress At Ambient Sa 244.10 MPa
Inside Diameter of Hemispherical Head D 5661.00 mm
Head Finished (Minimum) Thickness t 147.0000 mm
Head Internal Corrosion Allowance c 0.0000 mm
Head External Corrosion Allowance co 0.0000 mm
Distance from Head Centerline L1 0.0000 mm
User Entered Minimum Design Metal Temperature 16.00 °C
Type of Element Connected to the Shell : Nozzle
Material SA-336 F22V
Material UNS Number K31835
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 199.30 MPa
Allowable Stress At Ambient Sna 244.10 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 0.00 deg
Diameter 389.0000 mm.
Size and Thickness Basis Actual
Actual Thickness tn 34.0000 mm
Hub Height of Integral Nozzle h 150.0000 mm
Height of Beveled Transition L` 79.0000 mm
Hub Thickness of Integral Nozzle ( tn or x+tp ) 109.0000 mm
Corrosion Allowance can 0.0000 mm
Outside Projection ho 500.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 10.0000 mm
Groove weld depth between Nozzle and Vessel Wgnv 147.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
User Defined Nozzle/Shell Centerline Angle 90.0000 deg.
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
| |
/ |
/ |
| |
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| |
_________/| |
| \ | |
| \ | |
|_________\|_____|
Hub Nozzle (Set-in)
Reinforcement CALCULATION, Description: Noz N1
ASME Code, Section VIII, Div. 2, 2013, Section 4.5.1 - 4.5.14
Actual Inside Diameter Used in Calculation 389.000 mm.
Actual Thickness Used in Calculation 34.000 mm
Nozzle input data check completed without errors.
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*389.000 *(exp( 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 20.3479 + 0.000 + 0.000 = 20.3479 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 199.300 * 1.000 * Ln( ( 2*34.000 + 389.000 )/389.000 ) - 0.000
= 32.108 - 0.000 = 32.1080 MPa
Nozzle Minimum Thickness per Table 4.5.2 Min. required Nozzle Neck Thickness + c : 0.328 in. 8.340 mm
Stresses on Nozzle due to External and Pressure Loads per the ASMEB31.3 Piping Code (see 319.4.4 and 302.3.5):
Sustained : 108.8, Allowable : 199.3 MPa Passed
Expansion : 0.0, Allowable : 445.5 MPa Passed
Occasional : 52.2, Allowable : 265.1 MPa Passed
Shear : 26.5, Allowable : 139.5 MPa Passed
Note : The number of cycles on this nozzle was assumed to be 7000 or less forthe determination of the expansion stress allowable.
Nozzle Calculations per Section 4.5: Internal Pressure Case:
Nozzle Material Factor [frn]: = min[Sn/S, 1]
= min[199.3/199.3 , 1]
= 1.000
Thickness of Nozzle at Shell [tn]: = hub thickness - corrosion allowance
= 109.000 - 0.000
= 109.000 mm
Thickness of Nozzle at Top [tn2]: = thickness - corrosion allowance
= 34.000 - 0.000
= 34.000 mm
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Shell Diameter to Thickness ratio [D/t]: = Di/t
= 5661.000/147.000
= 38.510 must be less than 400.
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 5661.000/2 + 0.000
= 2830.500 mm
Effective Length of Vessel Wall [LR]: = min( sqrt( Reff * t ), 2 * Rn )
= min( sqrt( 2830.500 * 147.000 ), 2 * 194.500 )
= 389.000 mm
Intermediate value [Cn]: = min( (( t + te )/tn)^0.35, 1 )
= min( (( 147.000 + 0.000 )/109.000 )^0.35, 1 )
= min( 1.110 , 1 )
= 1.000
Intermediate value [Cp]: = 9999999.000
Effective Nozzle Wall Length Outside the Vessel [LH]: = min( t + te + Fp * sqrt( Rn*tn ), Lpr1 + t )
= min(147.000+0.000+1.000*sqrt(194.500*109.000),500.000+147.000)
= 292.604 mm
Effective Vessel Thickness [teff]: = t + (( A5 * frp ) / LR )
= 147.000+((0.000*1.00)/389.000)
= 147.000 mm
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR
= 147.000 * 389.000
= 57182.996 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 109.000 * 292.604
= 31893.824 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2)
= 0.5 * 10.000^(2)
= 50.000 mm²
The total area contributed by A1 through A43 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 57182.996+1.000(31893.824+0.000)+50.000+0.000+0.000
= 89126.820 mm²
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 109.000/ln[ 1 + 109.000/194.500 ]
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= 244.972 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 147.000/ln[ 1 + 147.000/2830.500 ]
= 2903.382 mm
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 199.300 * 1.000
= 299.0 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 19.830 * 244.972 * 292.604
= 1421287.0 N
Determine Force acting on the Shell [fS]: = P * Rxs * ( LR + tn )/2
= 19.830 * 2903.382 * ( 389.000 + 109.000 )/2
= 14334724.0 N
Discontinuity Force from Internal Pressure [fY]: = ( P * Rxs * Rnc )/2
= ( 19.830 * 2903.382 * 194.500 )/2
= 5598602.0 N
Area Resisting Internal Pressure [Ap]: = ( fS + fY + fN )/P
= ( 14334724 + 5598602 + 1421287 )/19.830
= 1076975.8 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/(2 * teff ) )
= 298.950/( 2 * 1076975/89126.820 - 2903.382/(2*147.000 ) )
= 20.9 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = 2 * S * [t/Rxs]
= 2 * 199.300 * [147.000/2903.382 ]
= 20.2 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 20.918 , 20.181 )
= 20.181 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 1421287 + 14334724 + 5598602 )/89126.820
= 239.618 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / ( 2 * teff )
= 19.830 * 2903.382/( 2 * 147.000 )
= 195.8 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
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= max( 2 * 239.618 - 195.830 , 195.830 )
= 283.4 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 298.95 MPa
Local Primary Membrane Stress PL 283.41 MPa
Maximum Allowable Working Pressure Pmax 20.18 MPa
Strength of Nozzle Attachment Welds per 4.5.14
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 194.500 + 109.000 )/194.500
= 1.560 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 194.500 + 109.000 )
= 476.737 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 7.071, 0.000, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(5598602*1.56,1.5*199.3(31893.824+0.000),pi/4*19.8*194.50^2*1.56^2
= 1434475.250 N
Weld Stress Value [tau]: = fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 1434475/(476.737 (0.49*7.071 + 0.6*147.000 + 0.49*0.000 ) )
= 32.828 < or = to 199.300 Weld Size is OK
Nozzle Calculations per Section 4.5: External Pressure Case:
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 109.000/ln[ 1 + 109.000/194.500 ]
= 244.972 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 147.000/ln[ 1 + 147.000/2830.500 ]
= 2903.382 mm
Allowable Local Primary Membrane Stress [Sallow]: = Shell Fha Value
= 146.372
= 146.4 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 0.102 * 244.972 * 292.604
= 7310.7 N
Determine Force acting on the Shell [fS]: = P * Rxs * ( LR + tn )/2
= 0.102 * 2903.382 * ( 389.000 + 109.000 )/2
= 73733.8 N
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Discontinuity Force from External Pressure [fY]: = ( P * Rxs * Rnc )/2
= ( 0.102 * 2903.382 * 194.500 )/2
= 28797.7 N
Area Resisting External Pressure [Ap]: = ( fS + fY + fN )/P
= ( 73733.8 + 28797.7 + 7310.7 )/0.102
= 1076975.8 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/(2 * teff ) )
= 146.372/( 2 * 1076975/89126.820 - 2903.382/(2*147.000 ) )
= 10.2 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = 2 * Fha * [t/Rxs]
= 2 * 146.372 * [147.000/2903.382 ]
= 14.8 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 10.242 , 14.822 )
= 10.242 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 7310.704 + 73733.836 + 28797.650 )/89126.820
= 1.233 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / ( 2 * teff )
= 0.102 * 2903.382/( 2 * 147.000 )
= 1.0 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 1.233 - 1.007 , 1.007 )
= 1.5 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 146.37 MPa
Local Primary Membrane Stress PL 1.46 MPa
Maximum Allowable External Pressure Pmax 10.24 MPa
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
Nozzle MDMT per 3.7, (Nozzle to Shell/Head Weld), Curve: B ----------------------------------------------------------------------
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -104 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
As the Stress Ratio < 0.241, the MDMT is : -104 °C
The computed stress ratio is : 0.151
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The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 16.460 * 1.00 )/( 109.000 - 0.000 - 0.000 )
= 0.151
Governing MDMT of all the sub-joints of this Junction : -104 °C
The Drop for this Nozzle is : 16.3184 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 663.3183 mm
Input Echo, WRC107/537 Item 1, Description: Noz N1 :
Diameter Basis for Vessel Vbasis ID
Cylindrical or Spherical Vessel Cylsph Spherical
Internal Corrosion Allowance Cas 0.0000 mm
Vessel Diameter Dv 5661.000 mm
Vessel Thickness Tv 147.000 mm
Design Temperature 454.00 °C
Vessel Material SA-336 F22V
Vessel Cold S.I. Allowable Smc 244.10 MPa
Vessel Hot S.I. Allowable Smh 199.30 MPa
Attachment Type Type Round
WRC107 Attachment Classification Holsol Hollow
Diameter Basis for Nozzle Nbasis ID
Corrosion Allowance for Nozzle Can 0.0000 mm
Nozzle Diameter Dn 389.000 mm
Nozzle Thickness Tn 109.000 mm
Nozzle Material SA-336 F22V
Nozzle Cold S.I. Allowable SNmc 244.10 MPa
Nozzle Hot S.I. Allowable SNmh 199.30 MPa
Design Internal Pressure Dp 19.830 MPa
Include Pressure Thrust No
External Forces and Moments in WRC 107/537 Convention: Radial Load (SUS) P 75000.0 N
Longitudinal Shear (SUS) (Vl) V1 75000.0 N
Circumferential Shear (SUS) (Vc) V2 75000.0 N
Circumferential Moment (SUS) (Mc) M1 173000144.0 N-mm
Longitudinal Moment (SUS) (Ml) M2 173000144.0 N-mm
Torsional Moment (SUS) Mt 173000144.0 N-mm
Use Interactive Control No
WRC107 Version Version March 1979
Include Pressure Stress Indices per Div. 2 No
Compute Pressure Stress per WRC-368 No
WRC 107 Stress Calculation for SUStained loads: Radial Load P 75000.0 N
Circumferential Shear (VC) V2 75000.0 N
Longitudinal Shear (VL) V1 75000.0 N
Circumferential Moment (MC) M1 173000144.0 N-mm
Longitudinal Moment (ML) M2 173000144.0 N-mm
Torsional Moment MT 173000144.0 N-mm
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Dimensionless Param: U = 0.46 TAU = 5.00 ( 2.28) RHO = 1.35
Dimensionless Loads for Spherical Shells at Attachment Junction: ------------------------------------------------------------
Curves read for 1979 Figure Value Location
------------------------------------------------------------
N(x) * T / P SP 2 0.07858 (A,B,C,D)
M(x) / P SP 2 0.07930 (A,B,C,D)
N(x) * T * SQRT(Rm * T ) / MC SM 2 0.16564 (A,B,C,D)
M(x) * SQRT(Rm * T ) / MC SM 2 0.20782 (A,B,C,D)
N(x) * T * SQRT(Rm * T ) / ML SM 2 0.16564 (A,B,C,D)
M(x) * SQRT(Rm * T ) / ML SM 2 0.20782 (A,B,C,D)
N(y) * T / P SP 2 0.16389 (A,B,C,D)
M(y) / P SP 2 0.04146 (A,B,C,D)
N(y) * T * SQRT(Rm * T ) / MC SM 2 0.11034 (A,B,C,D)
M(y) * SQRT(Rm * T ) / MC SM 2 0.14077 (A,B,C,D)
N(y) * T * SQRT(Rm * T ) / ML SM 2 0.11034 (A,B,C,D)
M(y) * SQRT(Rm * T ) / ML SM 2 0.14077 (A,B,C,D)
Stress Concentration Factors Kn = 1.00, Kb = 1.00
Stresses in the Vessel at the Attachment Junction ------------------------------------------------------------------------
| Stress Values at
Type of | (MPa )
---------------|--------------------------------------------------------
Stress Load| Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Rad. Memb. P | -0.3 -0.3 -0.3 -0.3 -0.3 -0.3 -0.3 -0.3
Rad. Bend. P | -1.7 1.7 -1.7 1.7 -1.7 1.7 -1.7 1.7
Rad. Memb. MC | 0.0 0.0 0.0 0.0 -2.0 -2.0 2.0 2.0
Rad. Memb. MC | 0.0 0.0 0.0 0.0 -15.3 15.3 15.3 -15.3
Rad. Memb. ML | -2.0 -2.0 2.0 2.0 0.0 0.0 0.0 0.0
Rad. Bend. ML | -15.3 15.3 15.3 -15.3 0.0 0.0 0.0 0.0
|
Tot. Rad. Str.| -19.2 14.6 15.4 -11.9 -19.2 14.6 15.4 -11.9
------------------------------------------------------------------------
Tang. Memb. P | -0.6 -0.6 -0.6 -0.6 -0.6 -0.6 -0.6 -0.6
Tang. Bend. P | -0.9 0.9 -0.9 0.9 -0.9 0.9 -0.9 0.9
Tang. Memb. MC | 0.0 0.0 0.0 0.0 -1.4 -1.4 1.4 1.4
Tang. Bend. MC | 0.0 0.0 0.0 0.0 -10.3 10.3 10.3 -10.3
Tang. Memb. ML | -1.4 -1.4 1.4 1.4 0.0 0.0 0.0 0.0
Tang. Bend. ML | -10.3 10.3 10.3 -10.3 0.0 0.0 0.0 0.0
|
Tot. Tang. Str.| -13.1 9.3 10.3 -8.7 -13.1 9.3 10.3 -8.7
------------------------------------------------------------------------
Shear VC | 0.5 0.5 -0.5 -0.5 0.0 0.0 0.0 0.0
Shear VL | 0.0 0.0 0.0 0.0 -0.5 -0.5 0.5 0.5
Shear MT | 2.0 2.0 2.0 2.0 2.0 2.0 2.0 2.0
|
Tot. Shear| 2.6 2.6 1.5 1.5 1.5 1.5 2.6 2.6
------------------------------------------------------------------------
Str. Int. | 20.2 15.7 15.8 12.5 19.6 15.0 16.4 13.3
------------------------------------------------------------------------
WRC 107/537 Stress Summations:
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Vessel Stress Summation at Attachment Junction ------------------------------------------------------------------------
Type of | Stress Values at
Stress Int. | (MPa )
---------------|--------------------------------------------------------
Location | Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Rad. Pm (SUS) | 195.8 195.8 195.8 195.8 195.8 195.8 195.8 195.8
Rad. Pl (SUS) | -2.3 -2.3 1.8 1.8 -2.3 -2.3 1.8 1.8
Rad. Q (SUS) | -16.9 16.9 13.6 -13.6 -16.9 16.9 13.6 -13.6
------------------------------------------------------------------------
Long. Pm (SUS) | 195.8 195.8 195.8 195.8 195.8 195.8 195.8 195.8
Long. Pl (SUS) | -1.9 -1.9 0.8 0.8 -1.9 -1.9 0.8 0.8
Long. Q (SUS) | -11.2 11.2 9.5 -9.5 -11.2 11.2 9.5 -9.5
------------------------------------------------------------------------
Shear Pm (SUS) | 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Shear Pl (SUS) | 0.5 0.5 -0.5 -0.5 -0.5 -0.5 0.5 0.5
Shear Q (SUS) | 2.0 2.0 2.0 2.0 2.0 2.0 2.0 2.0
------------------------------------------------------------------------
Pm (SUS) | 195.8 195.8 195.8 195.8 195.8 195.8 195.8 195.8
------------------------------------------------------------------------
Pm+Pl (SUS) | 194.3 194.3 197.8 197.8 194.3 194.3 197.8 197.8
------------------------------------------------------------------------
Pm+Pl+Q (Total)| 183.6 211.5 211.6 187.7 183.0 210.8 212.3 188.6
------------------------------------------------------------------------
------------------------------------------------------------------------
Type of | Max. S.I. S.I. Allowable | Result
Stress Int. | MPa |
---------------|--------------------------------------------------------
Pm (SUS) | 195.83 199.30 | Passed
Pm+Pl (SUS) | 197.82 298.95 | Passed
Pm+Pl+Q (TOTAL)| 212.28 665.10 | Passed
------------------------------------------------------------------------
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Nozzle Calcs. : Noz N3 (8") Nozl: 8 1:41pmMar 14,2015
INPUT VALUES, Nozzle Description: Noz N3 (8") From : 30
Pressure for Reinforcement Calculations P 19.8300 MPa
Temperature for Internal Pressure Temp 454 °C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 454 °C
Shell Material SA-336 F22V
Shell Allowable Stress at Temperature S 199.30 MPa
Shell Allowable Stress At Ambient Sa 244.10 MPa
Inside Diameter of Hemispherical Head D 5661.00 mm
Head Finished (Minimum) Thickness t 147.0000 mm
Head Internal Corrosion Allowance c 0.0000 mm
Head External Corrosion Allowance co 0.0000 mm
Distance from Head Centerline L1 2165.0000 mm
User Entered Minimum Design Metal Temperature 16.00 °C
Type of Element Connected to the Shell : Nozzle
Material SA-336 F22V
Material UNS Number K31835
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 199.30 MPa
Allowable Stress At Ambient Sna 244.10 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 0.00 deg
Diameter 212.0000 mm.
Size and Thickness Basis Actual
Actual Thickness tn 18.5000 mm
Hub Height of Integral Nozzle h 150.0000 mm
Height of Beveled Transition L` 63.5000 mm
Hub Thickness of Integral Nozzle ( tn or x+tp ) 82.0000 mm
Corrosion Allowance can 0.0000 mm
Outside Projection ho 700.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 10.0000 mm
Groove weld depth between Nozzle and Vessel Wgnv 147.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
User Defined Nozzle/Shell Centerline Angle 90.0000 deg.
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Hub Nozzle (Set-in)
Reinforcement CALCULATION, Description: Noz N3 (8")
ASME Code, Section VIII, Div. 2, 2013, Section 4.5.1 - 4.5.14
Actual Inside Diameter Used in Calculation 212.000 mm.
Actual Thickness Used in Calculation 18.500 mm
Nozzle input data check completed without errors.
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*212.000 *(exp( 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 11.0894 + 0.000 + 0.000 = 11.0894 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 199.300 * 1.000 * Ln( ( 2*18.500 + 212.000 )/212.000 ) - 0.000
= 32.061 - 0.000 = 32.0607 MPa
Nozzle Minimum Thickness per Table 4.5.2 Min. required Nozzle Neck Thickness + c : 0.319 in. 8.110 mm
Nozzle Calculations per Section 4.5: Internal Pressure Case:
Nozzle Material Factor [frn]: = min[Sn/S, 1]
= min[199.3/199.3 , 1]
= 1.000
Thickness of Nozzle at Shell [tn]: = hub thickness - corrosion allowance
= 82.000 - 0.000
= 82.000 mm
Thickness of Nozzle at Top [tn2]: = thickness - corrosion allowance
= 18.500 - 0.000
= 18.500 mm
Shell Diameter to Thickness ratio [D/t]: = Di/t
= 5661.000/147.000
= 38.510 must be less than 400.
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 5661.000/2 + 0.000
= 2830.500 mm
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Nozzle Calcs. : Noz N3 (8") Nozl: 8 1:41pmMar 14,2015
Effective Length of Vessel Wall [LR]: = min( sqrt( Reff * t ), 2 * Rn )
= min( sqrt( 2830.500 * 147.000 ), 2 * 106.000 )
= 212.000 mm
Intermediate value [Cn]: = min( (( t + te )/tn)^0.35, 1 )
= min( (( 147.000 + 0.000 )/82.000 )^0.35, 1 )
= min( 1.227 , 1 )
= 1.000
Intermediate value [Cp]: = 9999999.000
Effective Nozzle Wall Length Outside the Vessel [LH]: = min( t + te + Fp * sqrt( Rn*tn ), Lpr1 + t )
= min(147.000+0.000+1.000*sqrt(106.000*82.000),700.000+147.000)
= 240.231 mm
Effective Vessel Thickness [teff]: = t + (( A5 * frp ) / LR )
= 147.000+((0.000*1.00)/212.000)
= 147.000 mm
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR
= 147.000 * 212.000
= 31164.000 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 82.000 * 240.231
= 19698.936 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2)
= 0.5 * 10.000^(2)
= 50.000 mm²
The total area contributed by A1 through A43 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 31164.000+1.000(19698.936+0.000)+50.000+0.000+0.000
= 50912.934 mm²
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 82.000/ln[ 1 + 82.000/106.000 ]
= 143.106 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 147.000/ln[ 1 + 147.000/2830.500 ]
= 2903.382 mm
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 199.300 * 1.000
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Nozzle Calcs. : Noz N3 (8") Nozl: 8 1:41pmMar 14,2015
= 299.0 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 19.830 * 143.106 * 240.231
= 681666.1 N
Determine Force acting on the Shell [fS]: = P * Rxs * ( LR + tn )/2
= 19.830 * 2903.382 * ( 212.000 + 82.000 )/2
= 8462669.0 N
Discontinuity Force from Internal Pressure [fY]: = ( P * Rxs * Rnc )/2
= ( 19.830 * 2903.382 * 106.000 )/2
= 3051166.2 N
Area Resisting Internal Pressure [Ap]: = ( fS + fY + fN )/P
= ( 8462669 + 3051166 + 681666 )/19.830
= 615054.9 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/(2 * teff ) )
= 298.950/( 2 * 615054/50912.934 - 2903.382/(2*147.000 ) )
= 20.9 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = 2 * S * [t/Rxs]
= 2 * 199.300 * [147.000/2903.382 ]
= 20.2 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 20.927 , 20.181 )
= 20.181 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 681666 + 8462669 + 3051166 )/50912.934
= 239.557 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / ( 2 * teff )
= 19.830 * 2903.382/( 2 * 147.000 )
= 195.8 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 239.557 - 195.830 , 195.830 )
= 283.3 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 298.95 MPa
Local Primary Membrane Stress PL 283.28 MPa
Maximum Allowable Working Pressure Pmax 20.18 MPa
Strength of Nozzle Attachment Welds per 4.5.14
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Nozzle Calcs. : Noz N3 (8") Nozl: 8 1:41pmMar 14,2015
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 106.000 + 82.000 )/106.000
= 1.774 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 106.000 + 82.000 )
= 295.310 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 7.071, 0.000, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(3051166*1.77,1.5*199.3(19698.936+0.000),pi/4*19.8*106.00^2*1.77^2
= 550416.438 N
Weld Stress Value [tau]: = fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 550416/(295.310 (0.49*7.071 + 0.6*147.000 + 0.49*0.000 ) )
= 20.335 < or = to 199.300 Weld Size is OK
Nozzle Calculations per Section 4.5: External Pressure Case:
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 82.000/ln[ 1 + 82.000/106.000 ]
= 143.106 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 147.000/ln[ 1 + 147.000/2830.500 ]
= 2903.382 mm
Allowable Local Primary Membrane Stress [Sallow]: = Shell Fha Value
= 146.372
= 146.4 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 0.102 * 143.106 * 240.231
= 3506.3 N
Determine Force acting on the Shell [fS]: = P * Rxs * ( LR + tn )/2
= 0.102 * 2903.382 * ( 212.000 + 82.000 )/2
= 43529.6 N
Discontinuity Force from External Pressure [fY]: = ( P * Rxs * Rnc )/2
= ( 0.102 * 2903.382 * 106.000 )/2
= 15694.3 N
Area Resisting External Pressure [Ap]: = ( fS + fY + fN )/P
= ( 43529.6 + 15694.3 + 3506.3 )/0.102
= 615054.9 mm²
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Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/(2 * teff ) )
= 146.372/( 2 * 615054/50912.934 - 2903.382/(2*147.000 ) )
= 10.2 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = 2 * Fha * [t/Rxs]
= 2 * 146.372 * [147.000/2903.382 ]
= 14.8 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 10.246 , 14.822 )
= 10.246 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 3506.301 + 43529.613 + 15694.350 )/50912.934
= 1.232 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / ( 2 * teff )
= 0.102 * 2903.382/( 2 * 147.000 )
= 1.0 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 1.232 - 1.007 , 1.007 )
= 1.5 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 146.37 MPa
Local Primary Membrane Stress PL 1.46 MPa
Maximum Allowable External Pressure Pmax 10.25 MPa
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
Nozzle MDMT per 3.7, (Nozzle to Shell/Head Weld), Curve: B ----------------------------------------------------------------------
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -104 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
As the Stress Ratio < 0.241, the MDMT is : -104 °C
The computed stress ratio is : 0.109
The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 8.971 * 1.00 )/( 82.000 - 0.000 - 0.000 )
= 0.109
Governing MDMT of all the sub-joints of this Junction : -104 °C
The Drop for this Nozzle is : 6.2504 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 853.2503 mm
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Nozzle Calcs. : Noz N3 (8") Nozl: 8 1:41pmMar 14,2015
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Nozzle Calcs. : Noz N2 (20") Nozl: 9 1:41pmMar 14,2015
INPUT VALUES, Nozzle Description: Noz N2 (20") From : 30
Pressure for Reinforcement Calculations P 19.8300 MPa
Temperature for Internal Pressure Temp 454 °C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 454 °C
Shell Material SA-336 F22V
Shell Allowable Stress at Temperature S 199.30 MPa
Shell Allowable Stress At Ambient Sa 244.10 MPa
Inside Diameter of Hemispherical Head D 5661.00 mm
Head Finished (Minimum) Thickness t 147.0000 mm
Head Internal Corrosion Allowance c 0.0000 mm
Head External Corrosion Allowance co 0.0000 mm
Distance from Head Centerline L1 2165.0000 mm
User Entered Minimum Design Metal Temperature 16.00 °C
Type of Element Connected to the Shell : Nozzle
Material SA-336 F22V
Material UNS Number K31835
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 199.30 MPa
Allowable Stress At Ambient Sna 244.10 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 90.00 deg
Diameter 469.0000 mm.
Size and Thickness Basis Actual
Actual Thickness tn 25.5000 mm
Hub Height of Integral Nozzle h 150.0000 mm
Height of Beveled Transition L` 93.5000 mm
Hub Thickness of Integral Nozzle ( tn or x+tp ) 119.0000 mm
Corrosion Allowance can 0.0000 mm
Outside Projection ho 700.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 10.0000 mm
Groove weld depth between Nozzle and Vessel Wgnv 147.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
User Defined Nozzle/Shell Centerline Angle 90.0000 deg.
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Nozzle Calcs. : Noz N2 (20") Nozl: 9 1:41pmMar 14,2015
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| \ | |
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|_________\|_____|
Hub Nozzle (Set-in)
Reinforcement CALCULATION, Description: Noz N2 (20")
ASME Code, Section VIII, Div. 2, 2013, Section 4.5.1 - 4.5.14
Actual Inside Diameter Used in Calculation 469.000 mm.
Actual Thickness Used in Calculation 25.500 mm
Nozzle input data check completed without errors.
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*469.000 *(exp( 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 24.5326 + 0.000 + 0.000 = 24.5326 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 199.300 * 1.000 * Ln( ( 2*25.500 + 469.000 )/469.000 ) - 0.000
= 20.573 - 0.000 = 20.5730 MPa
Nozzle Minimum Thickness per Table 4.5.2 Min. required Nozzle Neck Thickness + c : 0.328 in. 8.340 mm
Nozzle Calculations per Section 4.5: Internal Pressure Case:
Nozzle Material Factor [frn]: = min[Sn/S, 1]
= min[199.3/199.3 , 1]
= 1.000
Thickness of Nozzle at Shell [tn]: = hub thickness - corrosion allowance
= 119.000 - 0.000
= 119.000 mm
Thickness of Nozzle at Top [tn2]: = thickness - corrosion allowance
= 25.500 - 0.000
= 25.500 mm
Shell Diameter to Thickness ratio [D/t]: = Di/t
= 5661.000/147.000
= 38.510 must be less than 400.
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 5661.000/2 + 0.000
= 2830.500 mm
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Nozzle Calcs. : Noz N2 (20") Nozl: 9 1:41pmMar 14,2015
Effective Length of Vessel Wall [LR]: = min( sqrt( Reff * t ), 2 * Rn )
= min( sqrt( 2830.500 * 147.000 ), 2 * 234.500 )
= 469.000 mm
Intermediate value [Cn]: = min( (( t + te )/tn)^0.35, 1 )
= min( (( 147.000 + 0.000 )/119.000 )^0.35, 1 )
= min( 1.077 , 1 )
= 1.000
Intermediate value [Cp]: = 9999999.000
Effective Nozzle Wall Length Outside the Vessel [LH]: = min( t + te + Fp * sqrt( Rn*tn ), Lpr1 + t )
= min(147.000+0.000+1.000*sqrt(234.500*119.000),700.000+147.000)
= 314.049 mm
Effective Vessel Thickness [teff]: = t + (( A5 * frp ) / LR )
= 147.000+((0.000*1.00)/469.000)
= 147.000 mm
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR
= 147.000 * 469.000
= 68943.000 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = A2A + A2B
= 35343.000 + 1883.537
= 37226.535 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2)
= 0.5 * 10.000^(2)
= 50.000 mm²
The total area contributed by A1 through A43 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 68943.000+1.000(37226.535+0.000)+50.000+0.000+0.000
= 106219.539 mm²
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 119.000/ln[ 1 + 119.000/234.500 ]
= 289.941 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 147.000/ln[ 1 + 147.000/2830.500 ]
= 2903.382 mm
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 199.300 * 1.000
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Nozzle Calcs. : Noz N2 (20") Nozl: 9 1:41pmMar 14,2015
= 299.0 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 19.830 * 289.941 * 314.049
= 1805484.6 N
Determine Force acting on the Shell [fS]: = P * Rxs * ( LR + tn )/2
= 19.830 * 2903.382 * ( 469.000 + 119.000 )/2
= 16925338.0 N
Discontinuity Force from Internal Pressure [fY]: = ( P * Rxs * Rnc )/2
= ( 19.830 * 2903.382 * 234.500 )/2
= 6749985.5 N
Area Resisting Internal Pressure [Ap]: = ( fS + fY + fN )/P
= ( 16925338 + 6749985 + 1805484 )/19.830
= 1285071.8 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/(2 * teff ) )
= 298.950/( 2 * 1285071/106219.539 - 2903.382/(2*147.000 ) )
= 20.9 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = 2 * S * [t/Rxs]
= 2 * 199.300 * [147.000/2903.382 ]
= 20.2 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 20.875 , 20.181 )
= 20.181 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 1805484 + 16925338 + 6749985 )/106219.539
= 239.909 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / ( 2 * teff )
= 19.830 * 2903.382/( 2 * 147.000 )
= 195.8 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 239.909 - 195.830 , 195.830 )
= 284.0 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 298.95 MPa
Local Primary Membrane Stress PL 283.99 MPa
Maximum Allowable Working Pressure Pmax 20.18 MPa
Strength of Nozzle Attachment Welds per 4.5.14
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Nozzle Calcs. : Noz N2 (20") Nozl: 9 1:41pmMar 14,2015
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 234.500 + 119.000 )/234.500
= 1.507 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 234.500 + 119.000 )
= 555.276 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 7.071, 0.000, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(6749985*1.51,1.5*199.3(37226.535+0.000),pi/4*19.8*234.50^2*1.51^2
= 1946052.500 N
Weld Stress Value [tau]: = fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 1946052/(555.276 (0.49*7.071 + 0.6*147.000 + 0.49*0.000 ) )
= 38.237 < or = to 199.300 Weld Size is OK
Nozzle Calculations per Section 4.5: External Pressure Case:
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 119.000/ln[ 1 + 119.000/234.500 ]
= 289.941 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 147.000/ln[ 1 + 147.000/2830.500 ]
= 2903.382 mm
Allowable Local Primary Membrane Stress [Sallow]: = Shell Fha Value
= 146.372
= 146.4 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 0.102 * 289.941 * 314.049
= 9286.9 N
Determine Force acting on the Shell [fS]: = P * Rxs * ( LR + tn )/2
= 0.102 * 2903.382 * ( 469.000 + 119.000 )/2
= 87059.2 N
Discontinuity Force from External Pressure [fY]: = ( P * Rxs * Rnc )/2
= ( 0.102 * 2903.382 * 234.500 )/2
= 34720.0 N
Area Resisting External Pressure [Ap]: = ( fS + fY + fN )/P
= ( 87059.2 + 34720.0 + 9286.9 )/0.102
= 1285071.8 mm²
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Nozzle Calcs. : Noz N2 (20") Nozl: 9 1:41pmMar 14,2015
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/(2 * teff ) )
= 146.372/( 2 * 1285071/106219.539 - 2903.382/(2*147.000 ) )
= 10.2 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = 2 * Fha * [t/Rxs]
= 2 * 146.372 * [147.000/2903.382 ]
= 14.8 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 10.221 , 14.822 )
= 10.221 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 9286.910 + 87059.227 + 34720.047 )/106219.539
= 1.234 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / ( 2 * teff )
= 0.102 * 2903.382/( 2 * 147.000 )
= 1.0 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 1.234 - 1.007 , 1.007 )
= 1.5 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 146.37 MPa
Local Primary Membrane Stress PL 1.46 MPa
Maximum Allowable External Pressure Pmax 10.22 MPa
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
Nozzle MDMT per 3.7, (Nozzle to Shell/Head Weld), Curve: B ----------------------------------------------------------------------
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -104 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
As the Stress Ratio < 0.241, the MDMT is : -104 °C
The computed stress ratio is : 0.167
The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 19.845 * 1.00 )/( 119.000 - 0.000 - 0.000 )
= 0.167
Governing MDMT of all the sub-joints of this Junction : -104 °C
The Drop for this Nozzle is : 22.1611 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 869.1610 mm
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Nozzle Calcs. : Noz N2 (20") Nozl: 9 1:41pmMar 14,2015
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Nozzle Calcs. : Noz(10") Nozl: 10 1:41pmMar 14,2015
INPUT VALUES, Nozzle Description: Noz(10") From : 60
Pressure for Reinforcement Calculations P 19.8300 MPa
Temperature for Internal Pressure Temp 454 °C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 454 °C
Shell Material SA-336 F22V
Shell Allowable Stress at Temperature S 199.00 MPa
Shell Allowable Stress At Ambient Sa 244.10 MPa
Inside Diameter of Cylindrical Shell D 5515.00 mm
Design Length of Section L 16492.6680 mm
Shell Finished (Minimum) Thickness t 289.0000 mm
Shell Internal Corrosion Allowance c 0.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Distance from Bottom/Left Tangent 8400.0010 mm
User Entered Minimum Design Metal Temperature 16.00 °C
Type of Element Connected to the Shell : Nozzle
Material SA-336 F22V
Material UNS Number K31835
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 199.30 MPa
Allowable Stress At Ambient Sna 244.10 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 0.00 deg
Diameter 266.0000 mm.
Size and Thickness Basis Actual
Actual Thickness tn 54.5000 mm
Hub Height of Integral Nozzle h 150.0000 mm
Height of Beveled Transition L` 80.5000 mm
Hub Thickness of Integral Nozzle ( tn or x+tp ) 135.0000 mm
Corrosion Allowance can 0.0000 mm
Outside Projection ho 500.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 10.0000 mm
Groove weld depth between Nozzle and Vessel Wgnv 147.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
User Defined Nozzle/Shell Centerline Angle 90.0000 deg.
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Nozzle Calcs. : Noz(10") Nozl: 10 1:41pmMar 14,2015
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Hub Nozzle (Set-in)
Reinforcement CALCULATION, Description: Noz(10")
ASME Code, Section VIII, Div. 2, 2013, Section 4.5.1 - 4.5.14
Actual Inside Diameter Used in Calculation 266.000 mm.
Actual Thickness Used in Calculation 54.500 mm
Nozzle input data check completed without errors.
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*266.000 *(exp( 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 13.9140 + 0.000 + 0.000 = 13.9140 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 199.300 * 1.000 * Ln( ( 2*54.500 + 266.000 )/266.000 ) - 0.000
= 68.446 - 0.000 = 68.4455 MPa
Nozzle Minimum Thickness per Table 4.5.2 Min. required Nozzle Neck Thickness + c : 0.328 in. 8.340 mm
Nozzle Calculations per Section 4.5: Internal Pressure Case:
Nozzle Material Factor [frn]: = min[Sn/S, 1]
= min[199.3/199.0 , 1]
= 1.000
Thickness of Nozzle at Shell [tn]: = hub thickness - corrosion allowance
= 135.000 - 0.000
= 135.000 mm
Thickness of Nozzle at Top [tn2]: = thickness - corrosion allowance
= 54.500 - 0.000
= 54.500 mm
Shell Diameter to Thickness ratio [D/t]: = Di/t
= 5515.000/289.000
= 19.083 must be less than 400.
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 5515.000/2 + 0.000
= 2757.500 mm
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Nozzle Calcs. : Noz(10") Nozl: 10 1:41pmMar 14,2015
Effective Length of Vessel Wall [LR]: = min( sqrt( Reff * t ), 2 * Rn )
= min( sqrt( 2757.500 * 289.000 ), 2 * 133.000 )
= 266.000 mm
Thickness Limit Candidate [LH1]: = min[1.5t,te] + sqrt( Rn * tn )
= min[1.5*289.000 , 0.000 ] + sqrt( 133.000 * 135.000 )
= 133.996 mm
Thickness Limit Candidate [LH2]: = Lpr1
= 500.000
= 500.000 mm
Thickness Limit Candidate [LH3]: = 8( t + te )
= 8( 289.000 + 0.000 )
= 2312.000 mm
Effective Nozzle Wall Length Outside the Vessel [LH]: = min[ LH1, LH2, LH3 ] + t for set-in nozzles
= min[ 133.996 , 500.000 , 2312.000 ) + 0.000
= 422.996 mm
Effective Vessel Thickness [teff]: = t + (( A5 * frp ) / LR )
= 289.000+((0.000*1.00)/266.000)
= 289.000 mm
Determine Parameter [Lamda]: = min( 12, ( 2*Rn + tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 12, (2*133.00 + 135.000 )/( sqrt((5515.00 + 289.000 ) * 289.000 )) )
= 0.310
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR * max( (Lamda/5)^(0.85), 1 )
= 289.000 * 266.000 * max( (0.310/5)^(0.85), 1 )
= 76873.992 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 135.000 * 422.996
= 57104.492 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2)
= 0.5 * 10.000^(2)
= 50.000 mm²
The total area contributed by A1 through A43 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 76873.992+1.000(57104.492+0.000)+50.000+0.000+0.000
= 134028.484 mm²
Nozzle Radius for Force Calculation [Rxn]:
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= tn / ln[1 + tn/Rn ]
= 135.000/ln[ 1 + 135.000/133.000 ]
= 192.682 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 289.000/ln[ 1 + 289.000/2757.500 ]
= 2899.599 mm
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 199.000 * 1.000
= 298.5 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 19.830 * 192.682 * 422.996
= 1616078.8 N
Determine Force acting on the Shell [fS]: = P * Rxs( LR + tn )
= 19.830 * 2899.599 ( 266.000 + 135.000 )
= 23055158.0 N
Discontinuity Force from Internal Pressure [fY]: = P * Rxs * Rnc
= 19.830 * 2899.599 * 133.000
= 7646723.5 N
Area Resisting Internal Pressure [Ap]: = ( fS + fY + fN )/P
= ( 23055158 + 7646723 + 1616078 )/19.830
= 1629889.4 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/teff )
= 298.500/( 2 * 1629889/134028.484 - 2899.599/289.000 )
= 20.9 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = S[t/Rxs]
= 199.000 [289.000/2899.599 ]
= 19.8 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 20.891 , 19.834 )
= 19.834 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 1616078 + 23055158 + 7646723 )/134028.484
= 241.148 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / teff
= 19.830 * 2899.599/289.000
= 199.0 MPa
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Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 241.148 - 198.959 , 198.959 )
= 283.3 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 298.50 MPa
Local Primary Membrane Stress PL 283.34 MPa
Maximum Allowable Working Pressure Pmax 19.83 MPa
Strength of Nozzle Attachment Welds per 4.5.14
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 133.000 + 135.000 )/133.000
= 2.015 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 133.000 + 135.000 )
= 420.973 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 7.071, 0.000, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(7646723*2.02,1.5*199.3(57104.492+0.000),pi/4*19.8*133.00^2*2.02^2
= 1118523.750 N
Weld Stress Value [tau]: = fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 1118523/(420.973 (0.49*7.071 + 0.6*147.000 + 0.49*0.000 ) )
= 28.988 < or = to 199.000 Weld Size is OK
Nozzle Calculations per Section 4.5: External Pressure Case:
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 135.000/ln[ 1 + 135.000/133.000 ]
= 192.682 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 289.000/ln[ 1 + 289.000/2757.500 ]
= 2899.599 mm
Allowable Local Primary Membrane Stress [Sallow]: = Shell Fha Value
= 189.665
= 189.7 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 0.102 * 192.682 * 422.996
= 8312.7 N
Determine Force acting on the Shell [fS]: = P * Rxs( LR + tn )
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= 0.102 * 2899.599 ( 266.000 + 135.000 )
= 118589.3 N
Discontinuity Force from External Pressure [fY]: = P * Rxs * Rnc
= 0.102 * 2899.599 * 133.000
= 39332.6 N
Area Resisting External Pressure [Ap]: = ( fS + fY + fN )/P
= ( 118589.3 + 39332.6 + 8312.7 )/0.102
= 1629889.4 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/teff )
= 189.665/( 2 * 1629889/134028.484 - 2899.599/289.000 )
= 13.3 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = min( Shell Fha, Nozzle Fha ) * [t/Rxs]
= 189.665 [289.000/2899.599 ]
= 18.9 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 13.274 , 18.904 )
= 13.274 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 8312.659 + 118589.320 + 39332.617 )/134028.484
= 1.240 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / teff
= 0.102 * 2899.599/289.000
= 1.0 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 1.240 - 1.023 , 1.023 )
= 1.5 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 189.66 MPa
Local Primary Membrane Stress PL 1.46 MPa
Maximum Allowable External Pressure Pmax 13.27 MPa
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
Nozzle MDMT per 3.7, (Nozzle to Shell/Head Weld), Curve: B ----------------------------------------------------------------------
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -104 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
As the Stress Ratio < 0.241, the MDMT is : -104 °C
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The computed stress ratio is : 0.083
The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 11.256 * 1.00 )/( 135.000 - 0.000 - 0.000 )
= 0.083
Governing MDMT of all the sub-joints of this Junction : -104 °C
The Drop for this Nozzle is : 13.0542 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 802.0542 mm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Nozzle Calcs. : Noz N6 (6") Nozl: 11 1:41pmMar 14,2015
INPUT VALUES, Nozzle Description: Noz N6 (6") From : 60
Pressure for Reinforcement Calculations P 19.8300 MPa
Temperature for Internal Pressure Temp 454 °C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 454 °C
Shell Material SA-336 F22V
Shell Allowable Stress at Temperature S 199.00 MPa
Shell Allowable Stress At Ambient Sa 244.10 MPa
Inside Diameter of Cylindrical Shell D 5515.00 mm
Design Length of Section L 16492.6680 mm
Shell Finished (Minimum) Thickness t 289.0000 mm
Shell Internal Corrosion Allowance c 0.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Distance from Bottom/Left Tangent 8200.0010 mm
User Entered Minimum Design Metal Temperature 16.00 °C
Type of Element Connected to the Shell : Nozzle
Material SA-336 F22V
Material UNS Number K31835
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 199.00 MPa
Allowable Stress At Ambient Sna 244.00 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 180.00 deg
Diameter 164.0000 mm.
Size and Thickness Basis Actual
Actual Thickness tn 35.5000 mm
Hub Height of Integral Nozzle h 150.0000 mm
Height of Beveled Transition L` 126.5000 mm
Hub Thickness of Integral Nozzle ( tn or x+tp ) 162.0000 mm
Corrosion Allowance can 0.0000 mm
Outside Projection ho 500.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 10.0000 mm
Groove weld depth between Nozzle and Vessel Wgnv 147.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
User Defined Nozzle/Shell Centerline Angle 90.0000 deg.
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
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Hub Nozzle (Set-in)
Reinforcement CALCULATION, Description: Noz N6 (6")
ASME Code, Section VIII, Div. 2, 2013, Section 4.5.1 - 4.5.14
Actual Inside Diameter Used in Calculation 164.000 mm.
Actual Thickness Used in Calculation 35.500 mm
Nozzle input data check completed without errors.
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*164.000 *(exp( 19.830/(199.000 *1.000 ))-1) + 0.000 + 0.000
= 8.5921 + 0.000 + 0.000 = 8.5921 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 199.000 * 1.000 * Ln( ( 2*35.500 + 164.000 )/164.000 ) - 0.000
= 71.584 - 0.000 = 71.5841 MPa
Nozzle Minimum Thickness per Table 4.5.2 Min. required Nozzle Neck Thickness + c : 0.319 in. 8.110 mm
Nozzle Calculations per Section 4.5: Internal Pressure Case:
Nozzle Material Factor [frn]: = min[Sn/S, 1]
= min[199.0/199.0 , 1]
= 1.000
Thickness of Nozzle at Shell [tn]: = hub thickness - corrosion allowance
= 162.000 - 0.000
= 162.000 mm
Thickness of Nozzle at Top [tn2]: = thickness - corrosion allowance
= 35.500 - 0.000
= 35.500 mm
Shell Diameter to Thickness ratio [D/t]: = Di/t
= 5515.000/289.000
= 19.083 must be less than 400.
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 5515.000/2 + 0.000
= 2757.500 mm
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Nozzle Calcs. : Noz N6 (6") Nozl: 11 1:41pmMar 14,2015
Effective Length of Vessel Wall [LR]: = min( sqrt( Reff * t ), 2 * Rn )
= min( sqrt( 2757.500 * 289.000 ), 2 * 82.000 )
= 164.000 mm
Thickness Limit Candidate [LH1]: = min[1.5t,te] + sqrt( Rn * tn )
= min[1.5*289.000 , 0.000 ] + sqrt( 82.000 * 162.000 )
= 115.256 mm
Thickness Limit Candidate [LH2]: = Lpr1
= 500.000
= 500.000 mm
Thickness Limit Candidate [LH3]: = 8( t + te )
= 8( 289.000 + 0.000 )
= 2312.000 mm
Effective Nozzle Wall Length Outside the Vessel [LH]: = min[ LH1, LH2, LH3 ] + t for set-in nozzles
= min[ 115.256 , 500.000 , 2312.000 ) + 0.000
= 404.256 mm
Effective Vessel Thickness [teff]: = t + (( A5 * frp ) / LR )
= 289.000+((0.000*1.00)/164.000)
= 289.000 mm
Determine Parameter [Lamda]: = min( 12, ( 2*Rn + tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 12, (2*82.00 + 162.000 )/( sqrt((5515.00 + 289.000 ) * 289.000 )) )
= 0.252
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR * max( (Lamda/5)^(0.85), 1 )
= 289.000 * 164.000 * max( (0.252/5)^(0.85), 1 )
= 47396.000 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 162.000 * 404.256
= 65489.512 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2)
= 0.5 * 10.000^(2)
= 50.000 mm²
The total area contributed by A1 through A43 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 47396.000+1.000(65489.512+0.000)+50.000+0.000+0.000
= 112935.508 mm²
Nozzle Radius for Force Calculation [Rxn]:
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= tn / ln[1 + tn/Rn ]
= 162.000/ln[ 1 + 162.000/82.000 ]
= 148.563 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 289.000/ln[ 1 + 289.000/2757.500 ]
= 2899.599 mm
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 199.000 * 1.000
= 298.5 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 19.830 * 148.563 * 404.256
= 1190836.6 N
Determine Force acting on the Shell [fS]: = P * Rxs( LR + tn )
= 19.830 * 2899.599 ( 164.000 + 162.000 )
= 18743098.0 N
Discontinuity Force from Internal Pressure [fY]: = P * Rxs * Rnc
= 19.830 * 2899.599 * 82.000
= 4714521.5 N
Area Resisting Internal Pressure [Ap]: = ( fS + fY + fN )/P
= ( 18743098 + 4714521 + 1190836 )/19.830
= 1243093.9 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/teff )
= 298.500/( 2 * 1243093/112935.508 - 2899.599/289.000 )
= 24.9 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = S[t/Rxs]
= 199.000 [289.000/2899.599 ]
= 19.8 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 24.914 , 19.834 )
= 19.834 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 1190836 + 18743098 + 4714521 )/112935.508
= 218.271 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / teff
= 19.830 * 2899.599/289.000
= 199.0 MPa
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Nozzle Calcs. : Noz N6 (6") Nozl: 11 1:41pmMar 14,2015
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 218.271 - 198.959 , 198.959 )
= 237.6 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 298.50 MPa
Local Primary Membrane Stress PL 237.58 MPa
Maximum Allowable Working Pressure Pmax 19.83 MPa
Strength of Nozzle Attachment Welds per 4.5.14
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 82.000 + 162.000 )/82.000
= 2.976 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 82.000 + 162.000 )
= 383.274 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 7.071, 0.000, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(4714521*2.98,1.5*199.0(65489.512+0.000),pi/4*19.8*82.00^2*2.98^2)
= 927161.500 N
Weld Stress Value [tau]: = fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 927161/(383.274 (0.49*7.071 + 0.6*147.000 + 0.49*0.000 ) )
= 26.392 < or = to 199.000 Weld Size is OK
Nozzle Calculations per Section 4.5: External Pressure Case:
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 162.000/ln[ 1 + 162.000/82.000 ]
= 148.563 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 289.000/ln[ 1 + 289.000/2757.500 ]
= 2899.599 mm
Allowable Local Primary Membrane Stress [Sallow]: = Shell Fha Value
= 189.665
= 189.7 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 0.102 * 148.563 * 404.256
= 6125.3 N
Determine Force acting on the Shell [fS]: = P * Rxs( LR + tn )
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= 0.102 * 2899.599 ( 164.000 + 162.000 )
= 96409.3 N
Discontinuity Force from External Pressure [fY]: = P * Rxs * Rnc
= 0.102 * 2899.599 * 82.000
= 24250.2 N
Area Resisting External Pressure [Ap]: = ( fS + fY + fN )/P
= ( 96409.3 + 24250.2 + 6125.3 )/0.102
= 1243093.9 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/teff )
= 189.665/( 2 * 1243093/112935.508 - 2899.599/289.000 )
= 15.8 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = min( Shell Fha, Nozzle Fha ) * [t/Rxs]
= 189.665 [289.000/2899.599 ]
= 18.9 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 15.830 , 18.904 )
= 15.830 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 6125.332 + 96409.281 + 24250.186 )/112935.508
= 1.123 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / teff
= 0.102 * 2899.599/289.000
= 1.0 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 1.123 - 1.023 , 1.023 )
= 1.2 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 189.66 MPa
Local Primary Membrane Stress PL 1.22 MPa
Maximum Allowable External Pressure Pmax 15.83 MPa
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
Nozzle MDMT per 3.7, (Nozzle to Shell/Head Weld), Curve: B ----------------------------------------------------------------------
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -104 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
As the Stress Ratio < 0.241, the MDMT is : -104 °C
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The computed stress ratio is : 0.043
The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 6.942 * 1.00 )/( 162.000 - 0.000 - 0.000 )
= 0.043
Governing MDMT of all the sub-joints of this Junction : -104 °C
The Drop for this Nozzle is : 10.8164 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 799.8164 mm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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INPUT VALUES, Nozzle Description: Noz MH From : 80
Pressure for Reinforcement Calculations P 19.8300 MPa
Temperature for Internal Pressure Temp 454 °C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 454 °C
Shell Material SA-336 F22V
Shell Allowable Stress at Temperature S 199.30 MPa
Shell Allowable Stress At Ambient Sa 244.10 MPa
Inside Diameter of Hemispherical Head D 5659.00 mm
Head Finished (Minimum) Thickness t 147.0000 mm
Head Internal Corrosion Allowance c 0.0000 mm
Head External Corrosion Allowance co 0.0000 mm
Distance from Head Centerline L1 0.0000 mm
User Entered Minimum Design Metal Temperature 16.00 °C
Type of Element Connected to the Shell : Nozzle
Material SA-336 F22V
Material UNS Number K31835
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 199.30 MPa
Allowable Stress At Ambient Sna 244.10 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 0.00 deg
Diameter 778.0000 mm.
Size and Thickness Basis Actual
Actual Thickness tn 316.0000 mm
Hub Height of Integral Nozzle h 80.0000 mm
Height of Beveled Transition L` 20.0000 mm
Hub Thickness of Integral Nozzle ( tn or x+tp ) 316.0000 mm
Corrosion Allowance can 0.0000 mm
Outside Projection ho 100.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 10.0000 mm
Groove weld depth between Nozzle and Vessel Wgnv 147.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
User Defined Nozzle/Shell Centerline Angle 90.0000 deg.
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
| |
/ |
/ |
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| |
_________/| |
| \ | |
| \ | |
|_________\|_____|
Hub Nozzle (Set-in)
Reinforcement CALCULATION, Description: Noz MH
ASME Code, Section VIII, Div. 2, 2013, Section 4.5.1 - 4.5.14
Actual Inside Diameter Used in Calculation 778.000 mm.
Actual Thickness Used in Calculation 316.000 mm
Nozzle input data check completed without errors.
Cylindrical Shell Calculation - Section 4.3.3.1
Computed Minimum Required Thickness [t]: = 0.5*D*( exp( P/(S*E) )-1)+ci+co
= 0.5*778.000 *(exp( 19.830/(199.300 *1.000 ))-1) + 0.000 + 0.000
= 40.6958 + 0.000 + 0.000 = 40.6958 mm Equation 4.3.1
Computed Maximum Allowable Working Pressure [MAWP]: = S * E * Ln( ( 2*t + D ) / D ) - Pliq
= 199.300 * 1.000 * Ln( ( 2*316.000 + 778.000 )/778.000 ) - 0.000
= 118.507 - 0.000 = 118.5075 MPa
Nozzle Minimum Thickness per Table 4.5.2 Min. required Nozzle Neck Thickness + c : 0.328 in. 8.340 mm
Stresses on Nozzle due to External and Pressure Loads per the ASMEB31.3 Piping Code (see 319.4.4 and 302.3.5):
Sustained : 11.5, Allowable : 199.3 MPa Passed
Expansion : 0.0, Allowable : 542.7 MPa Passed
Occasional : 8.7, Allowable : 265.1 MPa Passed
Shear : 2.3, Allowable : 139.5 MPa Passed
Note : The number of cycles on this nozzle was assumed to be 7000 or less forthe determination of the expansion stress allowable.
Nozzle Calculations per Section 4.5: Internal Pressure Case:
Nozzle Material Factor [frn]: = min[Sn/S, 1]
= min[199.3/199.3 , 1]
= 1.000
Thickness of Nozzle at Shell [tn]: = hub thickness - corrosion allowance
= 316.000 - 0.000
= 316.000 mm
Thickness of Nozzle at Top [tn2]: = thickness - corrosion allowance
= 316.000 - 0.000
= 316.000 mm
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Shell Diameter to Thickness ratio [D/t]: = Di/t
= 5659.000/147.000
= 38.497 must be less than 400.
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 5659.000/2 + 0.000
= 2829.500 mm
Effective Length of Vessel Wall [LR]: = min( sqrt( Reff * t ), 2 * Rn )
= min( sqrt( 2829.500 * 147.000 ), 2 * 389.000 )
= 644.931 mm
Intermediate value [Cn]: = min( (( t + te )/tn)^0.35, 1 )
= min( (( 147.000 + 0.000 )/316.000 )^0.35, 1 )
= min( 0.765 , 1 )
= 0.765
Intermediate value [Cp]: = 9999999.000
Effective Nozzle Wall Length Outside the Vessel [LH]: = min( t + te + Fp * sqrt( Rn*tn ), Lpr1 + t )
= min(147.000+0.000+0.765*sqrt(389.000*316.000),100.000+147.000)
= 247.000 mm
Effective Vessel Thickness [teff]: = t + (( A5 * frp ) / LR )
= 147.000+((0.000*1.00)/644.931)
= 147.000 mm
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR
= 147.000 * 644.931
= 94804.914 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 316.000 * 247.000
= 78051.992 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2)
= 0.5 * 10.000^(2)
= 50.000 mm²
The total area contributed by A1 through A43 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 94804.914+1.000(78051.992+0.000)+50.000+0.000+0.000
= 172906.906 mm²
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 316.000/ln[ 1 + 316.000/389.000 ]
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= 531.433 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 147.000/ln[ 1 + 147.000/2829.500 ]
= 2902.382 mm
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 199.300 * 1.000
= 299.0 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 19.830 * 531.433 * 247.000
= 2602743.8 N
Determine Force acting on the Shell [fS]: = P * Rxs * ( LR + tn )/2
= 19.830 * 2902.382 * ( 644.931 + 316.000 )/2
= 27650484.0 N
Discontinuity Force from Internal Pressure [fY]: = ( P * Rxs * Rnc )/2
= ( 19.830 * 2902.382 * 389.000 )/2
= 11193346.0 N
Area Resisting Internal Pressure [Ap]: = ( fS + fY + fN )/P
= ( 27650484 + 11193346 + 2602743 )/19.830
= 2090272.1 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/(2 * teff ) )
= 298.950/( 2 * 2090272/172906.906 - 2902.382/(2*147.000 ) )
= 20.9 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = 2 * S * [t/Rxs]
= 2 * 199.300 * [147.000/2902.382 ]
= 20.2 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 20.897 , 20.188 )
= 20.188 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 2602743 + 27650484 + 11193346 )/172906.906
= 239.725 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / ( 2 * teff )
= 19.830 * 2902.382/( 2 * 147.000 )
= 195.8 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
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= max( 2 * 239.725 - 195.763 , 195.763 )
= 283.7 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 298.95 MPa
Local Primary Membrane Stress PL 283.69 MPa
Maximum Allowable Working Pressure Pmax 20.19 MPa
Strength of Nozzle Attachment Welds per 4.5.14
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 389.000 + 316.000 )/389.000
= 1.812 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 389.000 + 316.000 )
= 1107.411 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 7.071, 0.000, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(11193346*1.81,1.5*199.3(78051.992+0.000),pi/4*19.8*389.00^2*1.81^
= 7740230.500 N
Weld Stress Value [tau]: = fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 7740230/(1107.411 (0.49*7.071 + 0.6*147.000 + 0.49*0.000 ) )
= 76.257 < or = to 199.300 Weld Size is OK
Nozzle Calculations per Section 4.5: External Pressure Case:
Nozzle Radius for Force Calculation [Rxn]: = tn / ln[1 + tn/Rn ]
= 316.000/ln[ 1 + 316.000/389.000 ]
= 531.433 mm
Shell Radius for Force Calculation [Rxs]: = teff / ln[ 1 + teff/Reff ]
= 147.000/ln[ 1 + 147.000/2829.500 ]
= 2902.382 mm
Allowable Local Primary Membrane Stress [Sallow]: = Shell Fha Value
= 146.392
= 146.4 MPa
Determine Force acting on the Nozzle [fN]: = P * Rxn * LH
= 0.102 * 531.433 * 247.000
= 13387.8 N
Determine Force acting on the Shell [fS]: = P * Rxs * ( LR + tn )/2
= 0.102 * 2902.382 * ( 644.931 + 316.000 )/2
= 142226.4 N
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Discontinuity Force from External Pressure [fY]: = ( P * Rxs * Rnc )/2
= ( 0.102 * 2902.382 * 389.000 )/2
= 57575.5 N
Area Resisting External Pressure [Ap]: = ( fS + fY + fN )/P
= ( 142226.4 + 57575.5 + 13387.8 )/0.102
= 2090272.1 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/(2 * teff ) )
= 146.392/( 2 * 2090272/172906.906 - 2902.382/(2*147.000 ) )
= 10.2 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = 2 * Fha * [t/Rxs]
= 2 * 146.392 * [147.000/2902.382 ]
= 14.8 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 10.233 , 14.829 )
= 10.233 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 13387.789 + 142226.391 + 57575.457 )/172906.906
= 1.233 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Rxs / ( 2 * teff )
= 0.102 * 2902.382/( 2 * 147.000 )
= 1.0 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 1.233 - 1.007 , 1.007 )
= 1.5 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 146.39 MPa
Local Primary Membrane Stress PL 1.46 MPa
Maximum Allowable External Pressure Pmax 10.23 MPa
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
Nozzle MDMT per 3.7, (Nozzle to Shell/Head Weld), Curve: B ----------------------------------------------------------------------
This element is Post Weld Heat Treated PWHT
Computed Minimum Design Metal Temperature : -27 °C
User entered Minimum Design Temperature : 16 °C
The curve for this material is curve : B
From Figure 3.8M- with PWHT, the MDMT is : -19 °C
Temperature reduction per Graph 3.13 : 9 °C
The computed stress ratio is : 0.798
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The computed stress ratio [sr]: = ( tr * E* ) / ( tnom - ci - cext )
= ( 117.296 * 1.00 )/( 147.000 - 0.000 - 0.000 )
= 0.798
Governing MDMT of all the sub-joints of this Junction : -27 °C
The Drop for this Nozzle is : 89.2362 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 336.2361 mm
Input Echo, WRC107/537 Item 1, Description: Noz MH :
Diameter Basis for Vessel Vbasis ID
Cylindrical or Spherical Vessel Cylsph Spherical
Internal Corrosion Allowance Cas 0.0000 mm
Vessel Diameter Dv 5659.000 mm
Vessel Thickness Tv 147.000 mm
Design Temperature 454.00 °C
Vessel Material SA-336 F22V
Vessel Cold S.I. Allowable Smc 244.10 MPa
Vessel Hot S.I. Allowable Smh 199.30 MPa
Attachment Type Type Round
WRC107 Attachment Classification Holsol Hollow
Diameter Basis for Nozzle Nbasis ID
Corrosion Allowance for Nozzle Can 0.0000 mm
Nozzle Diameter Dn 778.000 mm
Nozzle Thickness Tn 316.000 mm
Nozzle Material SA-336 F22V
Nozzle Cold S.I. Allowable SNmc 244.10 MPa
Nozzle Hot S.I. Allowable SNmh 199.30 MPa
Design Internal Pressure Dp 19.830 MPa
Include Pressure Thrust No
External Forces and Moments in WRC 107/537 Convention: Radial Load (SUS) P -139534.2 N
Longitudinal Shear (SUS) (Vl) V1 139534.2 N
Circumferential Shear (SUS) (Vc) V2 139534.2 N
Circumferential Moment (SUS) (Mc) M1 526758464.0 N-mm
Longitudinal Moment (SUS) (Ml) M2 526758464.0 N-mm
Torsional Moment (SUS) Mt 526758464.0 N-mm
Use Interactive Control No
WRC107 Version Version March 1979
Include Pressure Stress Indices per Div. 2 No
Compute Pressure Stress per WRC-368 No
WRC 107 Stress Calculation for SUStained loads: Radial Load P -139534.2 N
Circumferential Shear (VC) V2 139534.2 N
Longitudinal Shear (VL) V1 139534.2 N
Circumferential Moment (MC) M1 526758464.0 N-mm
Longitudinal Moment (ML) M2 526758464.0 N-mm
Torsional Moment MT 526758464.0 N-mm
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Dimensionless Param: U = 1.08 TAU = 5.00 ( 1.73) RHO = 0.47
Dimensionless Loads for Spherical Shells at Attachment Junction: ------------------------------------------------------------
Curves read for 1979 Figure Value Location
------------------------------------------------------------
N(x) * T / P SP 1 0.03753 (A,B,C,D)
M(x) / P SP 1 0.03905 (A,B,C,D)
N(x) * T * SQRT(Rm * T ) / MC SM 1 0.04329 (A,B,C,D)
M(x) * SQRT(Rm * T ) / MC SM 1 0.06827 (A,B,C,D)
N(x) * T * SQRT(Rm * T ) / ML SM 1 0.04329 (A,B,C,D)
M(x) * SQRT(Rm * T ) / ML SM 1 0.06827 (A,B,C,D)
N(y) * T / P SP 1 0.06025 (A,B,C,D)
M(y) / P SP 1 0.01127 (A,B,C,D)
N(y) * T * SQRT(Rm * T ) / MC SM 1 0.05953 (A,B,C,D)
M(y) * SQRT(Rm * T ) / MC SM 1 0.02175 (A,B,C,D)
N(y) * T * SQRT(Rm * T ) / ML SM 1 0.05953 (A,B,C,D)
M(y) * SQRT(Rm * T ) / ML SM 1 0.02175 (A,B,C,D)
Stress Concentration Factors Kn = 1.00, Kb = 1.00
Stresses in the Vessel at the Attachment Junction ------------------------------------------------------------------------
| Stress Values at
Type of | (MPa )
---------------|--------------------------------------------------------
Stress Load| Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Rad. Memb. P | 0.2 0.2 0.2 0.2 0.2 0.2 0.2 0.2
Rad. Bend. P | 1.5 -1.5 1.5 -1.5 1.5 -1.5 1.5 -1.5
Rad. Memb. MC | 0.0 0.0 0.0 0.0 -1.6 -1.6 1.6 1.6
Rad. Memb. MC | 0.0 0.0 0.0 0.0 -15.3 15.3 15.3 -15.3
Rad. Memb. ML | -1.6 -1.6 1.6 1.6 0.0 0.0 0.0 0.0
Rad. Bend. ML | -15.3 15.3 15.3 -15.3 0.0 0.0 0.0 0.0
|
Tot. Rad. Str.| -15.1 12.4 18.7 -14.9 -15.1 12.4 18.7 -14.9
------------------------------------------------------------------------
Tang. Memb. P | 0.4 0.4 0.4 0.4 0.4 0.4 0.4 0.4
Tang. Bend. P | 0.4 -0.4 0.4 -0.4 0.4 -0.4 0.4 -0.4
Tang. Memb. MC | 0.0 0.0 0.0 0.0 -2.2 -2.2 2.2 2.2
Tang. Bend. MC | 0.0 0.0 0.0 0.0 -4.9 4.9 4.9 -4.9
Tang. Memb. ML | -2.2 -2.2 2.2 2.2 0.0 0.0 0.0 0.0
Tang. Bend. ML | -4.9 4.9 4.9 -4.9 0.0 0.0 0.0 0.0
|
Tot. Tang. Str.| -6.3 2.6 7.9 -2.7 -6.3 2.6 7.9 -2.7
------------------------------------------------------------------------
Shear VC | 0.4 0.4 -0.4 -0.4 0.0 0.0 0.0 0.0
Shear VL | 0.0 0.0 0.0 0.0 -0.4 -0.4 0.4 0.4
Shear MT | 1.1 1.1 1.1 1.1 1.1 1.1 1.1 1.1
|
Tot. Shear| 1.6 1.6 0.7 0.7 0.7 0.7 1.6 1.6
------------------------------------------------------------------------
Str. Int. | 15.4 12.6 18.7 15.0 15.2 12.4 18.9 15.1
------------------------------------------------------------------------
WRC 107/537 Stress Summations:
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Vessel Stress Summation at Attachment Junction ------------------------------------------------------------------------
Type of | Stress Values at
Stress Int. | (MPa )
---------------|--------------------------------------------------------
Location | Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Rad. Pm (SUS) | 195.8 195.8 195.8 195.8 195.8 195.8 195.8 195.8
Rad. Pl (SUS) | -1.4 -1.4 1.9 1.9 -1.4 -1.4 1.9 1.9
Rad. Q (SUS) | -13.8 13.8 16.8 -16.8 -13.8 13.8 16.8 -16.8
------------------------------------------------------------------------
Long. Pm (SUS) | 195.8 195.8 195.8 195.8 195.8 195.8 195.8 195.8
Long. Pl (SUS) | -1.8 -1.8 2.6 2.6 -1.8 -1.8 2.6 2.6
Long. Q (SUS) | -4.4 4.4 5.3 -5.3 -4.4 4.4 5.3 -5.3
------------------------------------------------------------------------
Shear Pm (SUS) | 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Shear Pl (SUS) | 0.4 0.4 -0.4 -0.4 -0.4 -0.4 0.4 0.4
Shear Q (SUS) | 1.1 1.1 1.1 1.1 1.1 1.1 1.1 1.1
------------------------------------------------------------------------
Pm (SUS) | 195.8 195.8 195.8 195.8 195.8 195.8 195.8 195.8
------------------------------------------------------------------------
Pm+Pl (SUS) | 194.6 194.6 198.6 198.6 194.6 194.6 198.6 198.6
------------------------------------------------------------------------
Pm+Pl+Q (Total)| 189.8 208.4 214.5 193.1 189.6 208.2 214.6 193.3
------------------------------------------------------------------------
------------------------------------------------------------------------
Type of | Max. S.I. S.I. Allowable | Result
Stress Int. | MPa |
---------------|--------------------------------------------------------
Pm (SUS) | 195.76 199.30 | Passed
Pm+Pl (SUS) | 198.57 298.95 | Passed
Pm+Pl+Q (TOTAL)| 214.64 665.10 | Passed
------------------------------------------------------------------------
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Nozzle Schedule:
Nominal Flange Noz. Wall Re-Pad Cut
Description Size Sch/Type O/Dia Thk ODia Thick Length
mm Cls mm mm mm mm mm
------------------------------------------------------------------------------
Noz N6 (6") 164 - None 235.000 35.500 - - 799
Noz N3 (8") 212 - None 249.000 18.500 - - 853
Noz(10") 266 - None 375.000 54.500 - - 802
Noz N1 389 - None 457.000 34.000 - - 663
Noz N2 (20") 469 - None 520.000 25.500 - - 869
Noz MH 778 - None 1410.00 316.00 - - 336
General Notes for the above table:
The Cut Length is the Outside Projection + Inside Projection + Drop +In Plane Shell Thickness. This value does not include weld gaps,nor does it account for shrinkage.
In the case of Oblique Nozzles, the Outside Diameter mustbe increased. The Re-Pad WIDTH around the nozzle is calculated as follows:Width of Pad = (Pad Outside Dia. (per above) - Nozzle Outside Dia.)/2
For hub nozzles, the thickness and diameter shown are those of the smallerand thinner section.
Nozzle Material and Weld Fillet Leg Size Details: Shl Grve Noz Shl/Pad Pad OD Pad Grve Inside
Nozzle Material Weld Weld Weld Weld Weld
mm mm mm mm mm
------------------------------------------------------------------------------
Noz N6 SA-336 F22V 147.000 10.000 - - -
Noz N3 SA-336 F22V 147.000 10.000 - - -
Noz(10" SA-336 F22V 147.000 10.000 - - -
Noz N1 SA-336 F22V 147.000 10.000 - - -
Noz N2 SA-336 F22V 147.000 10.000 - - -
Noz MH SA-336 F22V 147.000 10.000 - - -
Note: The Outside projections below do not include the flange thickness.
Nozzle Miscellaneous Data:
Elevation/Distance Layout Projection Installed In
Nozzle From Datum Angle Outside Inside Component
mm deg. mm mm
----------------------------------------------------------------------------
Noz N6 (6") 8199.976 180.00 500.00 0.00 Shell-3
Noz N3 (8") 0.00 700.00 0.00 Bottom Head
Noz(10") 8399.975 0.00 500.00 0.00 Shell-3
Noz N1 0.00 500.00 0.00 Bottom Head
Noz N2 (20") 90.00 700.00 0.00 Bottom Head
Noz MH 0.00 100.00 0.00 Top Head
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2014
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Nozzle Calculation Summary:
Description MAWP Ext MAPNC Table 4.5.2 Weld
---------------------------------------------------------------------------
Noz N1 20.1814 OK ... OK OK Passed
Noz N3 (8") 20.1814 OK ... OK OK Passed
Noz N2 (20") 20.1814 OK ... OK OK Passed
Noz(10") 19.8341 OK ... OK OK Passed
Noz N6 (6") 19.8341 OK ... OK OK Passed
Noz MH 20.1883 OK ... OK OK Passed
---------------------------------------------------------------------------
Min. - Nozzles 19.8341 Noz N6 (6"
Min. Shell&Flgs 19.8341 60 70 24.600
Computed Vessel M.A.W.P. 19.834 MPa
Note: MAWPs (Internal Case) shown above are at the High Point.
Check the Spatial Relationship between the Nozzles
From Node Nozzle Description Y Coordinate, Layout Angle, Inside Radius
30 Noz N1 0.000 0.000 194.500
30 Noz N3 (8") 0.000 0.000 106.000
30 Noz N2 (20") 0.000 90.000 234.500
60 Noz(10") 8400.001 0.000 133.000
60 Noz N6 (6") 8200.001 180.000 82.000
80 Noz MH 0.000 0.000 389.000
The nozzle spacing is computed by the following:= Sqrt( ll² + lc² ) wherell - 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 !
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MDMT Summary : Step: 26 1:41pmMar 14,2015
Minimum Design Metal Temperature Results Summary :
Curve Basic Reduced PWHT Thickness Gov E*
Description MDMT MDMT ratio Thk
Notes °C °C mm
----------------------------------------------------------------------------
Bottom Head [9] B -19 -27 Yes 0.798 147.000 1.000
Top Head [9] B -19 -27 Yes 0.798 147.000 1.000
Noz N1 [1] B -104 -104 Yes 0.151 109.000 1.000
Noz N3 (8") [1] B -104 -104 Yes 0.109 82.000 1.000
Noz N2 (20") [1] B -104 -104 Yes 0.167 119.000 1.000
Noz(10") [1] B -104 -104 Yes 0.083 135.000 1.000
Noz N6 (6") [1] B -104 -104 Yes 0.043 162.000 1.000
Noz MH [1] B -19 -27 Yes 0.798 147.000 1.000
----------------------------------------------------------------------------
Required Minimum Design Metal Temperature 16 °C
Warmest Computed Minimum Design Metal Temperature -27 °C
Notes:[ ! ] - This was an impact tested material.[ 1] - Governing Nozzle Weld.[ 4] - ANSI Flange MDMT Calcs; Thickness ratio per equation 3.1.[ 5] - ANSI Flange MDMT Calcs; Thickness ratio per equation 3.3.[ 6] - MDMT Calculations at the Shell/Head Joint.[ 7] - MDMT Calculations for the Straight Flange.[ 8] - Cylinder/Cone/Flange Junction MDMT.[ 9] - Calculations in the Spherical Portion of the Head.[10] - Calculations in the Knuckle Portion of the Head.[11] - Calculated (Body Flange) Flange MDMT.[12] - Calculated Flat Head MDMT per 3.11.2.3[13] - Tubesheet MDMT, shell side, if applicable[14] - Tubesheet MDMT, tube side, if applicable[15] - Nozzle Material[16] - Shell or Head Material
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Vessel Design Summary : Step: 27 1:41pmMar 14,2015
ASME Code, Section VIII, Division 2, 2013
Diameter Spec : 5513.000 x 5515.000 x 5513.000 mm ID
Vessel Design Length, Tangent to Tangent 14606.00 mm
Distance of Bottom Tangent above Grade 7700.00 mm
Distance of Base above Grade 0.00 mm
Specified Datum Line Distance 7700.03 mm
Skirt Material SA-336 F22V
Shell Material SA-336 F22V
Internal Design Temperature 454 °C
Internal Design Pressure 19.830 MPa
External Design Temperature 454 °C
External Design Pressure 0.102 MPa
Maximum Allowable Working Pressure 19.834 MPa
External Max. Allowable Working Pressure 14.453 MPa
Hydrostatic Test Pressure 30.366 MPa
Required Minimum Design Metal Temperature 16 °C
Warmest Computed Minimum Design Metal Temperature -27 °C
Wind Design Code IS-875
Earthquake Design Code IS-1893 SCM
Element Pressures and MAWP: MPa
Element Desc | Design Pres. | External | M.A.W.P | Corrosion
| + Stat. head | Pressure | | Allowance
---------------------------------------------------------------------
Bottom Head 19.830 0.102 20.181 0.0000
Shell-1 19.830 0.102 19.871 0.0000
Shell-2 19.830 0.102 19.871 0.0000
Shell-3 19.830 0.102 19.834 0.0000
Shell-4 19.830 0.102 19.871 0.0000
Top Head 19.830 0.102 20.188 0.0000
Element "To" Elev Length Element Thk R e q d T h k Joint Eff
Type mm mm mm Int. Ext. Long Circ
-----------------------------------------------------------------------
Skirt -1000.0 6700.0 28.0 No Calc No Calc 1.00 1.00
Skirt 0.0 1000.0 26.0 No Calc No Calc 1.00 1.00
Sphere 0.0 0.0 162.0 144.4 8.8 1.00 1.00
Cylinder 3950.0 3950.0 289.0 288.4 28.8 1.00 1.00
Cylinder 7900.0 3950.0 289.0 288.4 28.8 1.00 1.00
Cylinder 11250.0 3350.0 289.0 288.9 28.8 1.00 1.00
Cylinder 14606.0 3356.0 289.0 288.4 28.8 1.00 1.00
Sphere 14606.0 0.0 162.0 144.3 8.8 1.00 1.00
Element thicknesses are shown as Nominal if specified, otherwise are Minimum
Wind/Earthquake Shear, Bending
| | Distance to| Cumulative |Earthquake | Wind | Earthquake |
From| To | Support| Wind Shear | Shear | Bending | Bending |
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Vessel Design Summary : Step: 27 1:41pmMar 14,2015
| | mm | N | N | N-mm | N-mm |
---------------------------------------------------------------------------
10| 20| 3350.00 | 43521.7 | 145486. | 559.5E+06 | 2.288E+09 |
20| 30| 7200.00 | 32691.5 | 142309. | 304.1E+06 | 1.323E+09 |
30| 40| 7699.98 | 31075.1 | 141932. | 272.2E+06 | 1.181E+09 |
40| 50| 9675.00 | 31075.0 | 135057. | 272.2E+06 | 1.181E+09 |
50| 60| 13625.0 | 24371.2 | 105242. | 162.7E+06 | 706.2E+06 |
60| 70| 17275.0 | 17315.2 | 75425.7 | 80.32E+06 | 349.2E+06 |
70| 80| 20628.0 | 11094.7 | 47980.1 | 32.71E+06 | 142.4E+06 |
80| 90| 22306.0 | 4686.65 | 20583.5 | 6.221E+06 | 27.32E+06 |
Abs Max of the all of the Stress Ratio's : 0.9812
Basering Data : Continuous Top Ring W/Gussets Thickness of Basering 57.0000 mm
Inside Diameter of Basering 5755.7998 mm
Outside Diameter of Basering 6467.0000 mm
Nominal Diameter of Bolts 56.0000 mm
Diameter of Bolt Circle 6278.0000 mm
Number of Bolts 34
Thickness of Gusset Plates 20.0000 mm
Average Width of Gusset Plates 190.0000 mm
Height of Gussets 300.0000 mm
Distance between Gussets 80.0000 mm
Thickness of Top Plate or Ring 38.0000 mm
Circumferential Width of the Top Plate 164.0000 mm
Radial Width of the Top Plate 190.0000 mm
Total Wind Shear on Support 43522. N
Total Earthquake Shear on Support 145486. N
Wind Moment on Support 559547520. N-mm
Earthquake Moment on Support 2287633152. N-mm
Note: Wind and Earthquake moments include the effects of user definedforces and moments if any exist in the job and were specifiedto act (compute loads and stresses) during these cases. Alsoincluded are moment effects due to eccentric weights if any arepresent in the input.
Weights: Fabricated - Bare W/O Removable Internals 768887.2 kgm
Shop Test - Fabricated + Water ( Full ) 1212349.6 kgm
Shipping - Fab. + Rem. Intls.+ Shipping App. 783638.2 kgm
Erected - Fab. + Rem. Intls.+ Insul. (etc) 1343638.1 kgm
Empty - Fab. + Intls. + Details + Wghts. 1343638.1 kgm
Operating - Empty + Operating Liquid (No CA) 1483638.1 kgm
Field Test - Empty Weight + Water (Full) 1227100.6 kgm
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Problems/Failures Summary : Step: 28 1:41pmMar 14,2015
Listed below are the known problem areas for the current design. Ifone 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.
** Error: Maximum Temperature Exceeded when computing compressive allowables !
Please review all reports carefully!
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