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Table of Contents
Cover Page 1
Title Page 2
Warnings and Errors : 3
Input Echo : 4
XY Coordinate Calculations : 9
Flg Calc [Int P] : FC COVER 10
Flg Calc [Int P] : FC#CV FLANGE 12
Flg Calc [Int P] : FC#SH FLANGE 15
Flg Calc [Int P] : SH#FC FLANGE 18
Flg Calc [Int P] : SH#RC FLANGE 21
Flg Calc [Int P] : RC#SH FLANGE 24
Internal Pressure Calculations : 27
External Pressure Calculations : 30
Element and Detail Weights : 32
Nozzle Flange MAWP : 34
Wind Load Calculation : 35
Earthquake Load Calculation : 37
Center of Gravity Calculation : 38
Horizontal Vessel Analysis (Ope.) 39
Horizontal Vessel Analysis (Test) 46
Nozzle Calcs. : T1 53
Nozzle Calcs. : T2 58
Nozzle Calcs. : S1 63
Nozzle Calcs. : S2A 68
Nozzle Calcs. : S2B 73
Nozzle Schedule : 78
Nozzle Summary : 79
MDMT Summary : 80
ASME TS Calc : NORMAL OPERATIO 81
ASME Fl-TS Calc : NORMAL OPERATIO 88
Flohead Analysis : FLOATING COVER 90
Vessel Design Summary : 93
Cover Page
DESIGN CALCULATION
In Accordance with ASME Section VIII Division 1
ASME Code Version : 2010 Edition, 2011a Addenda
Analysis Performed by : JACOBS H&G
Job File : C:\DOCUMENTS AND SETTINGS\PANCHALAS\DESKTOP\FLOA
Date of Analysis : Jul 11,2013
PV Elite 2012, January 2012
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 customary Imperial database isused for consistency. The finalized results are reflected to showthe users set of selected units.
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 3 of 94
Warnings and Errors : Step: 0 9:50a Jul 11,2013
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. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 4 of 94
Input Echo : Step: 1 9:50a Jul 11,2013
PV Elite Vessel Analysis Program: Input Data
Exchanger Design Pressures and Temperatures
Shell Side Design Pressure 2.0000 MPa
Channel Side Design Pressure 0.5000 MPa
Shell Side Design Temperature 100 C
Channel Side Design Temperature 15 C
Type of Hydrotest UG99-b
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 0 C
Type of Construction Welded
Special Service None
Degree of Radiography RT 1
Miscellaneous Weight Percent 0.0
Use Higher Longitudinal Stresses (Flag) Y
Select t for Internal Pressure (Flag) N
Select t for External Pressure (Flag) N
Select t for Axial Stress (Flag) N
Select Location for Stiff. Rings (Flag) N
Consider Vortex Shedding N
Perform a Corroded Hydrotest N
Is this a Heat Exchanger Yes
User Defined Hydro. Press. (Used if > 0) 0.0000 MPa
User defined MAWP 0.0000 MPa
User defined MAPnc 0.0000 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 ASCE-7 93
Basic Wind Speed [V] 112.65 km/hr
Surface Roughness Category C: Open Terrain
Importance Factor 1.0
Type of Surface Moderately Smooth
Base Elevation 0.0000 mm
Percent Wind for Hydrotest 33.0
Using User defined Wind Press. Vs Elev. N
Damping Factor (Beta) for Wind (Ope) 0.0100
Damping Factor (Beta) for Wind (Empty) 0.0000
Damping Factor (Beta) for Wind (Filled) 0.0000
Seismic Design Code UBC 94
UBC Seismic Zone (1=1,2=2a,3=2b,4=3,5=4) 0.000
UBC Importance Factor 1.000
UBC Soil Type S1
UBC Horizontal Force Factor 3.000
UBC Percent Seismic for Hydrotest 0.000
Design Nozzle for Des. Press. + St. Head Y
Consider MAP New and Cold in Noz. Design N
Consider External Loads for Nozzle Des. Y
Use ASME VIII-1 Appendix 1-9 N
Material Database Year Current w/Addenda or Code Year
Configuration Directives:
Do not use Nozzle MDMT Interpretation VIII-1 01-37 No
Use Table G instead of exact equation for "A" Yes
Shell Head Joints are Tapered Yes
Compute "K" in corroded condition Yes
Use Code Case 2286 No
Use the MAWP to compute the MDMT Yes
Using Metric Material Databases, ASME II D No
Complete Listing of Vessel Elements and Details:
Element From Node 10
Element To Node 20
Element Type Flange
Description FC COVER
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 5 of 94
Input Echo : Step: 1 9:50a Jul 11,2013
Distance "FROM" to "TO" 43.000 mm
Flange Inside Diameter 984.25 mm
Element Thickness 43.000 mm
Internal Corrosion Allowance 3.1750 mm
Nominal Thickness 0.0000 mm
External Corrosion Allowance 3.0000 mm
Design Internal Pressure 0.5000 MPa
Design Temperature Internal Pressure 15 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Allowable Stress, Ambient 137.90 MPa
Allowable Stress, Operating 137.90 MPa
Allowable Stress, Hydrotest 235.81 MPa
Material Density 0.007750 kg/cm³
P Number Thickness 31.750 mm
Yield Stress, Operating 262.01 MPa
UCS-66 Chart Curve Designation B
External Pressure Chart Name CS-2
UNS Number K02700
Product Form Plate
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 N
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
--------------------------------------------------------------------
Element From Node 20
Element To Node 30
Element Type Flange
Description FC#CV FLANGE
Distance "FROM" to "TO" 47.000 mm
Flange Inside Diameter 984.25 mm
Element Thickness 47.000 mm
Internal Corrosion Allowance 3.0000 mm
Nominal Thickness 0.0000 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 0.5000 MPa
Design Temperature Internal Pressure 15 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 N
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
--------------------------------------------------------------------
Element From Node 30
Element To Node 40
Element Type Cylinder
Description FC SHELL
Distance "FROM" to "TO" 650.00 mm
Inside Diameter 635.00 mm
Element Thickness 10.000 mm
Internal Corrosion Allowance 3.0000 mm
Nominal Thickness 10.000 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 0.5000 MPa
Design Temperature Internal Pressure 15 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Efficiency, Longitudinal Seam 0.85
Efficiency, Circumferential Seam 0.85
Element From Node 30
Detail Type Nozzle
Detail ID T1
Dist. from "FROM" Node / Offset dist 325.00 mm
Nozzle Diameter 300.0 mm
Nozzle Schedule 40
Nozzle Class 300
Layout Angle -45.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 556.16 N
Grade of Attached Flange GR 1.1
Nozzle Matl SA-106 B
Element From Node 30
Detail Type Nozzle
Detail ID T2
Dist. from "FROM" Node / Offset dist 325.00 mm
Nozzle Diameter 300.0 mm
Nozzle Schedule 40
Nozzle Class 300
Layout Angle 225.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 556.16 N
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 6 of 94
Input Echo : Step: 1 9:50a Jul 11,2013
Grade of Attached Flange GR 1.1
Nozzle Matl SA-106 B
--------------------------------------------------------------------
Element From Node 40
Element To Node 50
Element Type Flange
Description FC#SH FLANGE
Distance "FROM" to "TO" 76.000 mm
Flange Inside Diameter 0.0000 mm
Element Thickness 76.000 mm
Internal Corrosion Allowance 3.0000 mm
Nominal Thickness 0.0000 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 0.5000 MPa
Design Temperature Internal Pressure 15 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 N
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
--------------------------------------------------------------------
Element From Node 50
Element To Node 60
Element Type Flange
Description SH#FC FLANGE
Distance "FROM" to "TO" 93.000 mm
Flange Inside Diameter 0.0000 mm
Element Thickness 60.000 mm
Internal Corrosion Allowance 3.0000 mm
Nominal Thickness 0.0000 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 2.0000 MPa
Design Temperature Internal Pressure 100 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 N
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
--------------------------------------------------------------------
Element From Node 60
Element To Node 70
Element Type Cylinder
Description SHELL
Distance "FROM" to "TO" 3625.0 mm
Inside Diameter 635.00 mm
Element Thickness 10.000 mm
Internal Corrosion Allowance 3.0000 mm
Nominal Thickness 10.000 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 2.0000 MPa
Design Temperature Internal Pressure 100 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Efficiency, Longitudinal Seam 0.85
Efficiency, Circumferential Seam 0.85
Element From Node 60
Detail Type Saddle
Detail ID LEFT SADDLE
Dist. from "FROM" Node / Offset dist 600.00 mm
Width of Saddle 101.60 mm
Height of Saddle at Bottom 609.60 mm
Saddle Contact Angle 120.0
Height of Composite Ring Stiffener 0.0000 mm
Width of Wear Plate 152.40 mm
Thickness of Wear Plate 9.5250 mm
Contact Angle, Wear Plate (degrees) 130.0
Element From Node 60
Detail Type Saddle
Detail ID RIGHT SADDLE
Dist. from "FROM" Node / Offset dist 3025.0 mm
Width of Saddle 101.60 mm
Height of Saddle at Bottom 609.60 mm
Saddle Contact Angle 120.0
Height of Composite Ring Stiffener 0.0000 mm
Width of Wear Plate 152.40 mm
Thickness of Wear Plate 9.5250 mm
Contact Angle, Wear Plate (degrees) 130.0
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 7 of 94
Input Echo : Step: 1 9:50a Jul 11,2013
Element From Node 60
Detail Type Nozzle
Detail ID S1
Dist. from "FROM" Node / Offset dist 1812.0 mm
Nozzle Diameter 200.0 mm
Nozzle Schedule 80
Nozzle Class 300
Layout Angle 270.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.0000 N
Grade of Attached Flange GR 1.1
Nozzle Matl SA-106 B
Element From Node 60
Detail Type Nozzle
Detail ID S2A
Dist. from "FROM" Node / Offset dist 300.00 mm
Nozzle Diameter 150.0 mm
Nozzle Schedule 80
Nozzle Class 300
Layout Angle 180.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.0000 N
Grade of Attached Flange GR 1.1
Nozzle Matl SA-106 B
Element From Node 60
Detail Type Nozzle
Detail ID S2B
Dist. from "FROM" Node / Offset dist 3300.0 mm
Nozzle Diameter 150.0 mm
Nozzle Schedule 80
Nozzle Class 300
Layout Angle 180.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 0.0000 N
Grade of Attached Flange GR 1.1
Nozzle Matl SA-106 B
--------------------------------------------------------------------
Element From Node 70
Element To Node 80
Element Type Flange
Description SH#RC FLANGE
Distance "FROM" to "TO" 108.00 mm
Flange Inside Diameter 0.0000 mm
Element Thickness 75.000 mm
Internal Corrosion Allowance 3.0000 mm
Nominal Thickness 0.0000 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 2.0000 MPa
Design Temperature Internal Pressure 100 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 N
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
--------------------------------------------------------------------
Element From Node 80
Element To Node 90
Element Type Flange
Description RC#SH FLANGE
Distance "FROM" to "TO" 90.000 mm
Flange Inside Diameter 0.0000 mm
Element Thickness 80.000 mm
Internal Corrosion Allowance 3.0000 mm
Nominal Thickness 0.0000 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 2.0000 MPa
Design Temperature Internal Pressure 100 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Perform Flange Stress Calculation (Y/N) Y
Weight of ANSI B16.5/B16.47 Flange 0.0000 N
Class of ANSI B16.5/B16.47 Flange
Grade of ANSI B16.5/B16.47 Flange
--------------------------------------------------------------------
Element From Node 90
Element To Node 100
Element Type Cylinder
Description RC SHELL
Distance "FROM" to "TO" 300.00 mm
Inside Diameter 724.00 mm
Element Thickness 10.000 mm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 8 of 94
Input Echo : Step: 1 9:50a Jul 11,2013
Internal Corrosion Allowance 3.0000 mm
Nominal Thickness 10.000 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 2.0000 MPa
Design Temperature Internal Pressure 100 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Efficiency, Longitudinal Seam 0.85
Efficiency, Circumferential Seam 0.85
--------------------------------------------------------------------
Element From Node 100
Element To Node 110
Element Type Elliptical
Description RC HEAD
Distance "FROM" to "TO" 50.000 mm
Inside Diameter 724.00 mm
Element Thickness 10.000 mm
Internal Corrosion Allowance 3.0000 mm
Nominal Thickness 12.000 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 2.0000 MPa
Design Temperature Internal Pressure 100 C
Design External Pressure 0.1030 MPa
Design Temperature External Pressure 100 C
Effective Diameter Multiplier 1.2
Material Name SA-516 70
Efficiency, Longitudinal Seam 0.85
Efficiency, Circumferential Seam 0.85
Elliptical Head Factor 2.0
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 9 of 94
XY Coordinate Calculations : Step: 2 9:50a Jul 11,2013
XY Coordinate Calculations
| | | | | |
From| To | X (Horiz.)| Y (Vert.) |DX (Horiz.)| DY (Vert.) |
| | mm | mm | mm | mm |
--------------------------------------------------------------
FC COVER| 43.0000 | ... | 43.0000 | ... |
FC#CV FLAN| 90.0000 | ... | 47.0000 | ... |
FC SHELL| 693.000 | ... | 650.000 | ... |
FC#SH FLAN| 693.000 | ... | -76.0000 | ... |
SH#FC FLAN| 840.000 | ... | 93.0000 | ... |
SHELL| 4465.00 | ... | 3625.00 | ... |
SH#RC FLAN| 4573.00 | ... | 108.000 | ... |
RC#SH FLAN| 4663.00 | ... | 90.0000 | ... |
RC SHELL| 4873.00 | ... | 300.000 | ... |
RC HEAD| 4923.00 | ... | 50.0000 | ... |
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 10 of 94
Flg Calc [Int P] : FC COVER Flng: 19 9:50a Jul 11,2013
Flange Input Data Values Description: FC COVER :
FC COVER
Description of Flange Geometry (Type) Blind
Design Pressure P 0.50 MPa
Design Temperature 15 C
Internal Corrosion Allowance ci 3.1750 mm
External Corrosion Allowance ce 3.0000 mm
Use Corrosion Allowance in Thickness Calcs. Yes
Flange Outside Diameter A 816.000 mm
Flange Thickness t 43.0000 mm
Flange Material SA-516 70
Flange Material UNS number K02700
Flange Allowable Stress At Temperature Sfo 137.90 MPa
Flange Allowable Stress At Ambient Sfa 137.90 MPa
Bolt Material SA-193 B7
Bolt Allowable Stress At Temperature Sb 172.38 MPa
Bolt Allowable Stress At Ambient Sa 172.38 MPa
Diameter of the Load Reaction, Long Span D 0.000 mm
Diameter of the Load Reaction, Short Span d 0.000 mm
Perimeter along the Center of the Bolts L 2393.894 mm
Diameter of Bolt Circle C 762.000 mm
Nominal Bolt Diameter dB 20.0000 mm
Type of Threads TEMA Metric
Number of Bolts 28
Flange Face Outside Diameter Fod 732.000 mm
Flange Face Inside Diameter Fid 632.000 mm
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 728.000 mm
Gasket Inside Diameter Gi 684.000 mm
Gasket Factor m 2.0000
Gasket Design Seating Stress y 11.03 MPa
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 3.0000 mm
Length of Partition Gasket lp 1026.0000 mm
Width of Partition Gasket tp 10.0000 mm
Partition Gasket Factor mPart 2.0000
Partition Gasket Design Seating Stress yPart 11.03 MPa
ASME Code, Section VIII, Division 1, 2010, 2011a
Gasket Contact Width, N = (Go - Gi) / 2 22.000 mm
Basic Gasket Width, bo = N / 2 11.000 mm
Effective Gasket Width, b = Cb sqrt(bo) 8.358 mm
Gasket Reaction Diameter, G = Go - 2 * b 711.285 mm
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]: = 0.785 * G² * Peq
= 0.785 * 711.2847² * 0.500
= 198659.766 N
Contact Load on Gasket Surfaces [Hp]: = 2 * b * Pi * G * m * P + 2 * lp * bPart * mPart * P
= 2 * 8.3576 * 3.1416 * 711.2847 * 2.0000 * 0.50
+ 2.0 * 1026.0000 * 5.0000 * 2.0000 * 0.5000
= 47607.312 N
Operating Bolt Load [Wm1]: = max( H + Hp + H'p, 0 )
= max( 198659 + 47607 + 0 , 0 )
= 246267.078 N
Gasket Seating Bolt Load [Wm2]: = y * b * Pi * G + yPart * bPart * lp
= 11.03*8.3576*3.141*711.285+11.03*5.0000*1026.00
= 262601.938 N
Required Bolt Area [Am]: = Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 246267/172 , 262601/172
= 1523.564 mm²
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]: = 2a + 6t/(m + 0.5)
= 2 * 20.000 + 6 * 33.825/(2.00 + 0.5)
= 121.180 mm
Actual Circumferential Bolt Spacing [Bs]: = C * sin( pi / n ) )
= 762.000 * sin( 3.142/28 )
= 85.317 mm
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]: = max( sqrt( Bs/( 2a + t )), 1 )
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 11 of 94
Flg Calc [Int P] : FC COVER Flng: 19 9:50a Jul 11,2013
= max( sqrt( 85.317/( 2 * 20.000 + 33.825 )), 1 )
= 1.0750
Bolting Information for TEMA Metric Thread Series (Non Mandatory): -----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, mm² 1523.564 6077.428
Radial distance bet. bolts and the edge 23.810 24.000
Circumferential spacing between bolts 52.390 85.317 121.180
-----------------------------------------------------------------------------
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]: = Ab * Sa/( y * Pi * (Go + Gi) )
= 6077.428 * 172.38/(11.03 * 3.14 * (728.000 + 684.00 ) )
= 21.407 mm
Flange Design Bolt Load, Gasket Seating [W]: = Sa * ( Am + Ab ) / 2
= 172.38 * ( 1523.5636 + 6077.4277 )/2
= 655054.81 N
Gasket Load for the Operating Condition [HG]: = Wm1
= 246267.08 N
Moment Arm Calculations:Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 762.0000 - 711.2847 )/2
= 25.3576 mm
Tangential Flange Stress, Flat Head (UG-34), Operating [STo]: = 1.9 * Wm1 * hG * Bcor/(t² * G) + C * Z * Peq * G²/t²
= 1.9*246267*25.3576*1.0750/(33.8250²*711.2847)+
0.30*1.0000*0.50*711.2847²/33.8250²
= 82.00 MPa
Tangential Flange Stress, Flat Head (UG-34), Seating [STa]: = 1.9 * W * hG * Bcor / (t² * G)
= 1.9*655054*25.3576*1.075/(33.8250²*711.2847)
= 41.69 MPa
Bolt Stress, Operating [BSo]: = ( Wm1 / Ab )
= (246267/6077.4277)
= 40.53 MPa
Bolt Stress, Seating [BSa]: = ( Wm2 / Ab )
= (262601/6077.4277)
= 43.21 MPa
Stress Computation Results: Operating Gasket Seating
Actual Allowed Actual Allowed
Tangential Flange 82. 138. 42. 138. MPa
Bolting 41. 172. 43. 172. MPa
Reqd. Blind Flange Thickness at Center 35.259 mm
Reqd. Blind Flange Thickness at Gasket 27.774 mm
Estimated M.A.W.P. ( Operating ) 0.8 MPa
Estimated Finished Weight of Flange at given Thk. 174.3 kgm
Estimated Unfinished Weight of Forging at given Thk 174.3 kgm
Minimum Design Metal Temperature Results:Stress Ratio = 1.000 , Temperature Reduction per Fig. UCS 66.1 = 0 C
Min Metal Temp. w/o impact per UCS-66 -27 C
Min Metal Temp. w/o impact per UG-20(f) -29 C
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 12 of 94
Flg Calc [Int P] : FC#CV FLANGE Flng: 20 9:50a Jul 11,2013
Flange Input Data Values Description: FC#CV FLANGE :
FC#CV FLANGE
Description of Flange Geometry (Type) Lap Joint
Design Pressure P 0.50 MPa
Design Temperature 15 C
Internal Corrosion Allowance ci 3.0000 mm
External Corrosion Allowance ce 0.0000 mm
Use Corrosion Allowance in Thickness Calcs. Yes
Flange Inside Diameter B 660.000 mm
Flange Outside Diameter A 816.000 mm
Flange Thickness t 47.0000 mm
Flange Material SA-516 70
Flange Material UNS number K02700
Flange Allowable Stress At Temperature Sfo 137.90 MPa
Flange Allowable Stress At Ambient Sfa 137.90 MPa
Bolt Material SA-193 B7
Bolt Allowable Stress At Temperature Sb 172.38 MPa
Bolt Allowable Stress At Ambient Sa 172.38 MPa
Lap Joint Contact ID LjID 688.0000 mm
Lap Joint Contact OD LjOD 728.0000 mm
Diameter of Bolt Circle C 762.000 mm
Nominal Bolt Diameter dB 20.0000 mm
Type of Threads TEMA Metric
Number of Bolts 28
Flange Face Outside Diameter Fod 728.000 mm
Flange Face Inside Diameter Fid 680.000 mm
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 728.000 mm
Gasket Inside Diameter Gi 684.000 mm
Gasket Factor m 2.0000
Gasket Design Seating Stress y 11.03 MPa
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 3.0000 mm
Length of Partition Gasket lp 1026.0000 mm
Width of Partition Gasket tp 10.0000 mm
Partition Gasket Factor mPart 2.0000
Partition Gasket Design Seating Stress yPart 11.03 MPa
Warning: The rigidity index calculation has been turned off andis required for ASME Code Stamped vessels (if Code Case 2547is not being cited). Please insure the check box is properly checked.
ASME Code, Section VIII, Division 1, 2010, 2011a
Code R Dimension, R = (C-B)/2 - g1 51.000 mm
Gasket Contact Width, N = (Go - Gi) / 2 22.000 mm
Basic Gasket Width, bo = N / 2 11.000 mm
Effective Gasket Width, b = Cb sqrt(bo) 8.358 mm
Gasket Reaction Diameter, G = (LPODC+LPIDC) / 2 708.000 mm
Note: For Lap Joints, the Flange Face OD cannot be greater than thelap joint contact OD.
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]: = 0.785 * G² * Peq
= 0.785 * 708.0000² * 0.500
= 196829.172 N
Contact Load on Gasket Surfaces [Hp]: = 2 * b * Pi * G * m * P + 2 * lp * bPart * mPart * P
= 2 * 8.3576 * 3.1416 * 708.0000 * 2.0000 * 0.50
+ 2.0 * 1026.0000 * 5.0000 * 2.0000 * 0.5000
= 47434.836 N
Hydrostatic End Load at Flange ID [Hd]: = Pi * Bcor² * P / 4
= 3.1416 * 660.0000² *0.5000/4
= 171045.188 N
Pressure Force on Flange Face [Ht]: = H - Hd
= 196829 - 171045
= 25783.996 N
Operating Bolt Load [Wm1]: = max( H + Hp + H'p, 0 )
= max( 196829 + 47434 + 0 , 0 )
= 244264.000 N
Gasket Seating Bolt Load [Wm2]: = y * b * Pi * G + yPart * bPart * lp
= 11.03*8.3576*3.141*708.000+11.03*5.0000*1026.00
= 261650.562 N
Required Bolt Area [Am]:
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 13 of 94
Flg Calc [Int P] : FC#CV FLANGE Flng: 20 9:50a Jul 11,2013
= Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 244264/172 , 261650/172
= 1518.044 mm²
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]: = 2a + 6t/(m + 0.5)
= 2 * 20.000 + 6 * 47.000/(2.00 + 0.5)
= 152.800 mm
Actual Circumferential Bolt Spacing [Bs]: = C * sin( pi / n ) )
= 762.000 * sin( 3.142/28 )
= 85.317 mm
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]: = max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 85.317/( 2 * 20.000 + 47.000 )), 1 )
= 1.0000
Bolting Information for TEMA Metric Thread Series (Non Mandatory): -----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, mm² 1518.044 6077.428
Radial distance bet. hub and bolts 31.750 51.000
Radial distance bet. bolts and the edge 23.810 27.000
Circumferential spacing between bolts 52.390 85.317 152.800
-----------------------------------------------------------------------------
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]: = Ab * Sa/( y * Pi * (Go + Gi) )
= 6077.428 * 172.38/(11.03 * 3.14 * (728.000 + 684.00 ) )
= 21.407 mm
Note: Recommended Min. Width for Sheet and Composite Gaskets per table 2-4 : = 25.000 mm[Note: Exceeds actual gasket width, 22.000 ]
Flange Design Bolt Load, Gasket Seating [W]: = Sa * ( Am + Ab ) / 2
= 172.38 * ( 1518.0438 + 6077.4277 )/2
= 654579.06 N
Gasket Load for the Operating Condition [HG]: = Wm1 - H
= 244264 - 196829
= 47434.83 N
Moment Arm Calculations:Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 762.0000 - 708.0000 )/2
= 27.0000 mm
Distance to Face Pressure Reaction [ht]: = ( C - G ) / 2.0
= ( 762.0000 - 708.0000 )/2.0
= 27.0000 mm
Distance to End Pressure Reaction [hd]: = ( C - Bcor ) / 2
= ( 762.0000 - 660.0000 )/2
= 51.0000 mm
Summary of Moments for Internal Pressure: Loading Force Distance Bolt Corr Moment
End Pressure, Md 171045. 51.0000 1.0000 8726839. N-mm
Face Pressure, Mt 25784. 27.0000 1.0000 696450. N-mm
Gasket Load, Mg 47435. 27.0000 1.0000 1281260. N-mm
Gasket Seating, Matm 654579. 27.0000 1.0000 17680800. N-mm
Total Moment for Operation, Mop 10704549. N-mm
Total Moment for Gasket seating, Matm 17680800. N-mm
Effective Hub Length, ho = 0.000 mm
Hub Ratio, h/h0 = Defined as 0.0 0.000
Thickness Ratio, g1/g0 = Defined as 0.0 0.000
Factors from Figure 2-7.1 K = 1.236
T = 1.824 U = 10.190
Y = 9.273 Z = 4.784
Tangential Flange Stress, Operating [Sto]: = ( Y * Mo )/( t² * Bcor )
= (9.2731*10704549)/(47.0000²*660.0000)
= 68.06 MPa
Tangential Flange Stress, Seating [STa]: = ( Y * Matm )/( t² * Bcor )
= (9.2731*17680800)/(47.0000²*660.0000)
= 112.42 MPa
Bolt Stress, Operating [BSo]: = ( Wm1 / Ab )
= (244264/6077.4277)
= 40.20 MPa
Bolt Stress, Seating [BSa]: = ( Wm2 / Ab )
= (261650/6077.4277)
= 43.06 MPa
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 14 of 94
Flg Calc [Int P] : FC#CV FLANGE Flng: 20 9:50a Jul 11,2013
Stress Computation Results: Operating Gasket Seating
Actual Allowed Actual Allowed
Tangential Flange 68. 138. 112. 138. MPa
Bolting 40. 172. 43. 172. MPa
Minimum Required Flange Thickness 42.774 mm
Estimated M.A.W.P. ( Operating ) 1.0 MPa
Estimated M.A.W.P. ( Gasket Seating ) 1.0 MPa
Estimated Finished Weight of Flange at given Thk. 65.9 kgm
Estimated Unfinished Weight of Forging at given Thk 65.9 kgm
Required Lap Thickness Calculations for Lap Joint Flanges:
Required Lap Thickness due to Shear Stress, Operating [trlo]: = Wm1 / ( pi * Gid * 0.8 * So )
= 244264.0/( pi * 684.000 * 110.32 )
= 1.030 mm
Required Lap Thickness due to Shear Stress, Seating [trla]: = W / ( pi * Gid * 0.8 * Sa )
= 654579/( pi * 684.000 * 110.32 )
= 2.761 mm
Flange Rigidity Based on Required Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 109.4 * Ma / Bsc * Cnv_fac / ( Eamb * t^(3) * ln(K) * Kl )
= 109.4 * 17680800/1.0152 * 1.000/( 202713 * 42.774^(3)
* 0.212 * 0.20 )
= 2.829 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 109.4 * Mo / Bsc * Cnv_fac / ( Eop * tc^(3) * ln(K) * Kl )
= 109.4 * 10704548/1.0152 * 1.000/( 203114 * 42.774^(3)
* 0.212 * 0.20 )
= 1.710 (should be <= 1)
Flange Rigidity Based on Given Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 109.4 * Ma / Bsc * Cnv_fac / ( Eamb * t^(3) * ln(K) * Kl )
= 109.4 * 17680800/1.0000 * 1.000/( 202713 * 47.000^(3)
* 0.212 * 0.20 )
= 2.165 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 109.4 * Mo / Bsc * Cnv_fac / ( Eop * tc^(3) * ln(K) * Kl )
= 109.4 * 10704548/1.0000 * 1.000/( 203114 * 47.000^(3)
* 0.212 * 0.20 )
= 1.308 (should be <= 1)
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 15 of 94
Flg Calc [Int P] : FC#SH FLANGE Flng: 21 9:50a Jul 11,2013
Flange Input Data Values Description: FC#SH FLANGE :
FC#SH FLANGE
Description of Flange Geometry (Type) Loose Ring
Design Pressure P 0.50 MPa
Design Temperature 15 C
Internal Corrosion Allowance ci 3.0000 mm
External Corrosion Allowance ce 0.0000 mm
Use Corrosion Allowance in Thickness Calcs. No
Flange Inside Diameter B 660.000 mm
Flange Outside Diameter A 776.000 mm
Flange Thickness t 76.0000 mm
Flange Material SA-516 70
Flange Material UNS number K02700
Flange Allowable Stress At Temperature Sfo 137.90 MPa
Flange Allowable Stress At Ambient Sfa 137.90 MPa
Bolt Material SA-193 B7
Bolt Allowable Stress At Temperature Sb 172.38 MPa
Bolt Allowable Stress At Ambient Sa 172.38 MPa
Length of Weld Leg at Back of Ring tw 0.0000 mm
Number of Splits in Ring Flange n 0
Diameter of Bolt Circle C 728.000 mm
Nominal Bolt Diameter dB 20.0000 mm
Type of Threads TEMA Metric
Number of Bolts 28
Flange Face Outside Diameter Fod 698.000 mm
Flange Face Inside Diameter Fid 660.000 mm
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 695.000 mm
Gasket Inside Diameter Gi 651.000 mm
Gasket Factor m 2.0000
Gasket Design Seating Stress y 11.03 MPa
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 3.0000 mm
Length of Partition Gasket lp 1026.0000 mm
Width of Partition Gasket tp 10.0000 mm
Partition Gasket Factor mPart 0.0000
Partition Gasket Design Seating Stress yPart 0.00 MPa
ASME Code, Section VIII, Division 1, 2010, 2011a
Code R Dimension, R = (C-B)/2 - g1 34.000 mm
Gasket Contact Width, N = (Go - Gi) / 2 17.500 mm
Basic Gasket Width, bo = N / 2 8.750 mm
Effective Gasket Width, b = Cb sqrt(bo) 7.454 mm
Gasket Reaction Diameter, G = Go - 2 * b 680.092 mm
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]: = 0.785 * G² * Peq
= 0.785 * 680.0920² * 0.500
= 181617.734 N
Contact Load on Gasket Surfaces [Hp]: = 2 * b * Pi * G * m * P + 2 * lp * bPart * mPart * P
= 2 * 7.4540 * 3.1416 * 680.0920 * 2.0000 * 0.50
+ 2.0 * 1026.0000 * 5.0000 * 0.0000 * 0.5000
= 31849.412 N
Hydrostatic End Load at Flange ID [Hd]: = Pi * Bcor² * P / 4
= 3.1416 * 660.0000² *0.5000/4
= 171045.188 N
Pressure Force on Flange Face [Ht]: = H - Hd
= 181617 - 171045
= 10572.549 N
Operating Bolt Load [Wm1]: = max( H + Hp + H'p, 0 )
= max( 181617 + 31849 + 0 , 0 )
= 213467.141 N
= 865076.938 N , Mating Flange Load Governs
Gasket Seating Bolt Load [Wm2]: = y * b * Pi * G + yPart * bPart * lp
= 11.03*7.4540*3.141*680.092+0.00*5.0000*1026.00
= 175681.344 N
= 196454.781 N , Mating Flange Load Governs
Required Bolt Area [Am]: = Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 865076/172 , 196454/172
= 5019.002 mm²
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]:
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 16 of 94
Flg Calc [Int P] : FC#SH FLANGE Flng: 21 9:50a Jul 11,2013
= 2a + 6t/(m + 0.5)
= 2 * 20.000 + 6 * 76.000/(2.00 + 0.5)
= 222.400 mm
Actual Circumferential Bolt Spacing [Bs]: = C * sin( pi / n ) )
= 728.000 * sin( 3.142/28 )
= 81.510 mm
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]: = max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 81.510/( 2 * 20.000 + 76.000 )), 1 )
= 1.0000
Bolting Information for TEMA Metric Thread Series (Non Mandatory): -----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, mm² 5019.002 6077.428
Radial distance bet. hub and bolts 23.810 34.000
Radial distance bet. bolts and the edge 23.810 24.000
Circumferential spacing between bolts 52.390 81.510 222.400
-----------------------------------------------------------------------------
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]: = Ab * Sa/( y * Pi * (Go + Gi) )
= 6077.428 * 172.38/(11.03 * 3.14 * (695.000 + 660.00 ) )
= 22.307 mm[Note: Exceeds actual gasket width, 17.500 ]
Note: Recommended Min. Width for Sheet and Composite Gaskets per table 2-4 : = 25.000 mm[Note: Exceeds actual gasket width, 17.500 ]
Flange Design Bolt Load, Gasket Seating [W]: = Sa * ( Am + Ab ) / 2
= 172.38 * ( 5019.0020 + 6077.4277 )/2
= 956292.25 N
Gasket Load for the Operating Condition [HG]: = Wm1 - H
= 865076 - 181617
= 683459.19 N
Moment Arm Calculations:Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 728.0000 - 680.0920 )/2
= 23.9540 mm
Distance to Face Pressure Reaction [ht]: = ( hD + hG ) / 2
= ( 34.0000 + 23.9540 )/2
= 28.9770 mm
Distance to End Pressure Reaction [hd]: = ( C - Bcor )/ 2
= ( 728.0000 - 660.0000 )/2
= 34.0000 mm
Summary of Moments for Internal Pressure: Loading Force Distance Bolt Corr Moment
End Pressure, Md 171045. 34.0000 1.0000 5817891. N-mm
Face Pressure, Mt 10573. 28.9770 1.0000 306485. N-mm
Gasket Load, Mg 683459. 23.9540 1.0000 16378227. N-mm
Gasket Seating, Matm 956292. 23.9540 1.0000 22916324. N-mm
Total Moment for Operation, Mop 22502604. N-mm
Total Moment for Gasket seating, Matm 22916324. N-mm
Effective Hub Length, ho = 0.000 mm
Hub Ratio, h/h0 = Defined as 0.0 0.000
Thickness Ratio, g1/g0 = Defined as 0.0 0.000
Factors from Figure 2-7.1 K = 1.176
T = 1.849 U = 13.266
Y = 12.072 Z = 6.230
Tangential Flange Stress, Operating [Sto]: = ( Y * Mo )/( t² * Bcor )
= (12.0717*22502604)/(76.0000²*660.0000)
= 71.23 MPa
Tangential Flange Stress, Seating [STa]: = ( Y * Matm )/( t² * Bcor )
= (12.0717*22916324)/(76.0000²*660.0000)
= 72.54 MPa
Bolt Stress, Operating [BSo]: = ( Wm1 / Ab )
= (865076/6077.4277)
= 142.35 MPa
Bolt Stress, Seating [BSa]: = ( Wm2 / Ab )
= (196454/6077.4277)
= 32.33 MPa
Stress Computation Results: Operating Gasket Seating
Actual Allowed Actual Allowed
Tangential Flange 71. 138. 73. 138. MPa
Bolting 142. 172. 32. 172. MPa
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 17 of 94
Flg Calc [Int P] : FC#SH FLANGE Flng: 21 9:50a Jul 11,2013
Minimum Required Flange Thickness [Rigidity] 72.568 mm
Flange Rigidity Index, Seating (should be <= 1) 0.870
Flange Rigidity Index Oper. (should be <= 1) 0.852
Estimated M.A.W.P. ( Operating ) 0.6 MPa
Estimated M.A.W.P. ( Gasket Seating ) 0.5 MPa
Estimated Finished Weight of Flange at given Thk. 77.1 kgm
Estimated Unfinished Weight of Forging at given Thk 77.1 kgm
Flange Rigidity Based on Required Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 109.4 * Ma / Bsc * Cnv_fac / ( Eamb * t^(3) * ln(K) * Kl )
= 109.4 * 22916324/1.0000 * 1.000/( 202713 * 72.568^(3)
* 0.162 * 0.20 )
= 0.999 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 109.4 * Mo / Bsc * Cnv_fac / ( Eop * tc^(3) * ln(K) * Kl )
= 109.4 * 22502604/1.0000 * 1.000/( 203114 * 72.568^(3)
* 0.162 * 0.20 )
= 0.979 (should be <= 1)
Flange Rigidity Based on Given Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 109.4 * Ma / Bsc * Cnv_fac / ( Eamb * t^(3) * ln(K) * Kl )
= 109.4 * 22916324/1.0000 * 1.000/( 202713 * 76.000^(3)
* 0.162 * 0.20 )
= 0.870 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 109.4 * Mo / Bsc * Cnv_fac / ( Eop * tc^(3) * ln(K) * Kl )
= 109.4 * 22502604/1.0000 * 1.000/( 203114 * 76.000^(3)
* 0.162 * 0.20 )
= 0.852 (should be <= 1)
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 18 of 94
Flg Calc [Int P] : SH#FC FLANGE Flng: 22 9:50a Jul 11,2013
Flange Input Data Values Description: SH#FC FLANGE :
SH#FC FLANGE
Description of Flange Geometry (Type) Integral Weld Neck
Design Pressure P 2.00 MPa
Design Temperature 100 C
Internal Corrosion Allowance ci 3.0000 mm
External Corrosion Allowance ce 0.0000 mm
Use Corrosion Allowance in Thickness Calcs. No
Flange Inside Diameter B 635.000 mm
Flange Outside Diameter A 776.000 mm
Flange Thickness t 60.0000 mm
Thickness of Hub at Small End go 10.0000 mm
Thickness of Hub at Large End g1 13.0000 mm
Length of Hub h 33.0000 mm
Flange Material SA-516 70
Flange Material UNS number K02700
Flange Allowable Stress At Temperature Sfo 137.90 MPa
Flange Allowable Stress At Ambient Sfa 137.90 MPa
Bolt Material SA-193 B7
Bolt Allowable Stress At Temperature Sb 172.38 MPa
Bolt Allowable Stress At Ambient Sa 172.38 MPa
Diameter of Bolt Circle C 728.000 mm
Nominal Bolt Diameter dB 20.0000 mm
Type of Threads TEMA Metric
Number of Bolts 28
Flange Face Outside Diameter Fod 698.000 mm
Flange Face Inside Diameter Fid 635.000 mm
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 695.000 mm
Gasket Inside Diameter Gi 651.000 mm
Gasket Factor m 2.0000
Gasket Design Seating Stress y 11.03 MPa
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 3.0000 mm
ASME Code, Section VIII, Division 1, 2010, 2011a
Hub Small End Required Thickness due to Internal Pressure: = (P*(D/2+Ca))/(S*E-0.6*P) per UG-27 (c)(1)
= (2.00*(635.0000/2+3.0000))/(137.90*1.00-0.6*2.00)+Ca
= 7.6891 mm
Hub Small End Hub MAWP: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90 * 1.00 * 7.0000 )/(320.5000 + 0.6 * 7.0000 )
= 2.973 MPa
Corroded Flange ID, Bcor = B+2*Fcor 641.000 mm
Corroded Large Hub, g1Cor = g1-ci 10.000 mm
Corroded Small Hub, g0Cor = go-ci 7.000 mm
Code R Dimension, R = ((C-Bcor)/2)-g1cor 33.500 mm
Gasket Contact Width, N = (Go - Gi) / 2 22.000 mm
Basic Gasket Width, bo = N / 2 11.000 mm
Effective Gasket Width, b = Cb sqrt(bo) 8.358 mm
Gasket Reaction Diameter, G = Go - 2 * b 678.285 mm
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]: = 0.785 * G² * Peq
= 0.785 * 678.2847² * 2.000
= 722615.125 N
Contact Load on Gasket Surfaces [Hp]: = 2 * b * Pi * G * m * P
= 2 * 8.3576 * 3.1416 * 678.2847 * 2.0000 * 2.00
= 142461.766 N
Hydrostatic End Load at Flange ID [Hd]: = Pi * Bcor² * P / 4
= 3.1416 * 641.0000² *2.0000/4
= 645355.500 N
Pressure Force on Flange Face [Ht]: = H - Hd
= 722615 - 645355
= 77259.602 N
Operating Bolt Load [Wm1]: = max( H + Hp + H'p, 0 )
= max( 722615 + 142461 + 0 , 0 )
= 865076.938 N
Gasket Seating Bolt Load [Wm2]: = y * b * Pi * G + yPart * bPart * lp
= 11.03*8.3576*3.141*678.285+0.00*0.0000*0.00
= 196454.781 N
Required Bolt Area [Am]:
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 19 of 94
Flg Calc [Int P] : SH#FC FLANGE Flng: 22 9:50a Jul 11,2013
= Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 865076/172 , 196454/172
= 5019.002 mm²
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]: = 2a + 6t/(m + 0.5)
= 2 * 20.000 + 6 * 60.000/(2.00 + 0.5)
= 184.000 mm
Actual Circumferential Bolt Spacing [Bs]: = C * sin( pi / n ) )
= 728.000 * sin( 3.142/28 )
= 81.510 mm
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]: = max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 81.510/( 2 * 20.000 + 60.000 )), 1 )
= 1.0000
Bolting Information for TEMA Metric Thread Series (Non Mandatory): -----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, mm² 5019.002 6077.428
Radial distance bet. hub and bolts 31.750 33.500
Radial distance bet. bolts and the edge 23.810 24.000
Circumferential spacing between bolts 52.390 81.510 184.000
-----------------------------------------------------------------------------
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]: = Ab * Sa/( y * Pi * (Go + Gi) )
= 6077.428 * 172.38/(11.03 * 3.14 * (695.000 + 651.00 ) )
= 22.457 mm[Note: Exceeds actual gasket width, 22.000 ]
Note: Recommended Min. Width for Sheet and Composite Gaskets per table 2-4 : = 25.000 mm[Note: Exceeds actual gasket width, 22.000 ]
Flange Design Bolt Load, Gasket Seating [W]: = Sa * ( Am + Ab ) / 2
= 172.38 * ( 5019.0020 + 6077.4277 )/2
= 956292.25 N
Gasket Load for the Operating Condition [HG]: = Wm1 - H
= 865076 - 722615
= 142461.80 N
Moment Arm Calculations:Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 728.0000 - 678.2847 )/2
= 24.8576 mm
Distance to Face Pressure Reaction [ht]: = ( R + g1 + hg ) / 2
= ( 33.5000 + 10.0000 + 24.8576 )/2
= 34.1788 mm
Distance to End Pressure Reaction [hd]: = R + ( g1 / 2 )
= 33.5000 + ( 10.0000/2.0 )
= 38.5000 mm
Summary of Moments for Internal Pressure: Loading Force Distance Bolt Corr Moment
End Pressure, Md 645356. 38.5000 1.0000 24856250. N-mm
Face Pressure, Mt 77260. 34.1788 1.0000 2641711. N-mm
Gasket Load, Mg 142462. 24.8576 1.0000 3542696. N-mm
Gasket Seating, Matm 956292. 24.8576 1.0000 23780782. N-mm
Total Moment for Operation, Mop 31040658. N-mm
Total Moment for Gasket seating, Matm 23780782. N-mm
Effective Hub Length, ho = sqrt(Bcor*goCor) 66.985 mm
Hub Ratio, h/h0 = HL / H0 0.493
Thickness Ratio, g1/g0 = (g1Cor/goCor) 1.429
Flange Factors for Integral Flange: Factor F per 2-7.2 0.855
Factor V per 2-7.3 0.334
Factor f per 2-7.6 1.000
Factors from Figure 2-7.1 K = 1.211
T = 1.835 U = 11.282
Y = 10.266 Z = 5.296
d = .11079E+06 mm ³ e = 0.0128 mm ^-1
Stress Factors ALPHA = 1.766
BETA = 2.021 GAMMA = 0.962
DELTA = 1.950 Lamda = 2.912
Longitudinal Hub Stress, Operating [SHo]: = ( f * Mop / Bcor ) / ( L * g1² )
= (1.0000*31040658/641.0000)/(2.9121*10.0000²)
= 166.24 MPa
Longitudinal Hub Stress, Seating [SHa]: = ( f * Matm / Bcor ) / ( L * g1² )
= (1.0000*23780782/641.0000)/(2.9121*10.0000²)
= 127.36 MPa
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 20 of 94
Flg Calc [Int P] : SH#FC FLANGE Flng: 22 9:50a Jul 11,2013
Radial Flange Stress, Operating [SRo]: = ( Beta * Mop / Bcor ) / ( L * t² )
= (2.0211*31040658/641.0000)/(2.9121*60.0000²)
= 9.33 MPa
Radial Flange Stress, Seating [SRa]: = ( Beta * Matm/Bcor ) / ( L * t² )
= (2.0211*23780782/641.0000)/(2.9121*60.0000²)
= 7.15 MPa
Tangential Flange Stress, Operating [STo]: = ( Y * Mo / (t² * Bcor) ) - Z * SRo
= (10.2664*31040658/(60.0000²*641.0000))-5.2958*9
= 88.63 MPa
Tangential Flange Stress, Seating [STa]: = ( y * Matm / (t² * Bcor) ) - Z * SRa
= (10.2664*23780782/(60.0000²*641.0000))-5.2958*7
= 67.90 MPa
Average Flange Stress, Operating [SAo]: = ( SHo + max( SRo, STo ) ) / 2
= (166+max(9,88))/2
= 127.43 MPa
Average Flange Stress, Seating [SAa]: = ( SHa + max( SRa, STa ) ) / 2
= (127+max(7,67))/2
= 97.63 MPa
Bolt Stress, Operating [BSo]: = ( Wm1 / Ab )
= (865076/6077.4277)
= 142.35 MPa
Bolt Stress, Seating [BSa]: = ( Wm2 / Ab )
= (196454/6077.4277)
= 32.33 MPa
Stress Computation Results: Operating Gasket Seating
Actual Allowed Actual Allowed
Longitudinal Hub 166. 207. 127. 207. MPa
Radial Flange 9. 138. 7. 138. MPa
Tangential Flange 89. 138. 68. 138. MPa
Maximum Average 127. 138. 98. 138. MPa
Bolting 142. 172. 32. 172. MPa
Minimum Required Flange Thickness [Rigidity] 58.649 mm
Estimated M.A.W.P. ( Operating ) 2.1 MPa
Estimated Finished Weight of Flange at given Thk. 78.6 kgm
Estimated Unfinished Weight of Forging at given Thk 112.6 kgm
Flange Rigidity Based on Required Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 52.14 * Ma / Bsc * Cnv_fac * V / ( Lambda * Eamb * go^(2) * ho * Ki )
= 52.14 * 23780782/1.0000 * 1.000 * 0.334/( 2.771 * 202713 *
7.000^(2) * 66.985 * 0.300 )
= 0.749 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 52.14 * Mo / Bsc * Cnv_fac * V / ( Lambda * Eop * goc^(2) * ho * Ki )
= 52.14 * 31040656/1.0000 * 1.000 * 0.334/( 2.771 * 198162
* 7.000^(2) * 66.985 * 0.300 )
= 1.000 (should be <= 1)
Flange Rigidity Based on Given Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 52.14 * Ma / Bsc * Cnv_fac * V / ( Lambda * Eamb * go^(2) * ho * Ki )
= 52.14 * 23780782/1.0000 * 1.000 * 0.334/( 2.912 * 202713 *
7.000^(2) * 66.985 * 0.300 )
= 0.713 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 52.14 * Mo / Bsc * Cnv_fac * V / ( Lambda * Eop * goc^(2) * ho * Ki )
= 52.14 * 31040656/1.0000 * 1.000 * 0.334/( 2.912 * 198162
* 7.000^(2) * 66.985 * 0.300 )
= 0.952 (should be <= 1)
Minimum Design Metal Temperature Results:Stress Ratio = 1.000 , Temperature Reduction per Fig. UCS 66.1 = 0 C
Min Metal Temp. w/o impact per UCS-66 -29 C
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 21 of 94
Flg Calc [Int P] : SH#RC FLANGE Flng: 23 9:50a Jul 11,2013
Flange Input Data Values Description: SH#RC FLANGE :
SH#RC FLANGE
Description of Flange Geometry (Type) Integral Weld Neck
Design Pressure P 2.00 MPa
Design Temperature 100 C
Internal Corrosion Allowance ci 3.0000 mm
External Corrosion Allowance ce 0.0000 mm
Use Corrosion Allowance in Thickness Calcs. No
Flange Inside Diameter B 641.000 mm
Flange Outside Diameter A 858.000 mm
Flange Thickness t 75.0000 mm
Thickness of Hub at Small End go 10.0000 mm
Thickness of Hub at Large End g1 18.0000 mm
Length of Hub h 33.0000 mm
Flange Material SA-516 70
Flange Material UNS number K02700
Flange Allowable Stress At Temperature Sfo 137.90 MPa
Flange Allowable Stress At Ambient Sfa 137.90 MPa
Bolt Material SA-193 B7
Bolt Allowable Stress At Temperature Sb 172.38 MPa
Bolt Allowable Stress At Ambient Sa 172.38 MPa
Diameter of Bolt Circle C 810.000 mm
Nominal Bolt Diameter dB 20.0000 mm
Type of Threads TEMA Metric
Number of Bolts 32
Flange Face Outside Diameter Fod 779.000 mm
Flange Face Inside Diameter Fid 641.000 mm
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 776.000 mm
Gasket Inside Diameter Gi 730.000 mm
Gasket Factor m 2.0000
Gasket Design Seating Stress y 11.03 MPa
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 3.0000 mm
ASME Code, Section VIII, Division 1, 2010, 2011a
Hub Small End Required Thickness due to Internal Pressure: = (P*(D/2+Ca))/(S*E-0.6*P) per UG-27 (c)(1)
= (2.00*(641.0000/2+3.0000))/(137.90*1.00-0.6*2.00)+Ca
= 7.7330 mm
Hub Small End Hub MAWP: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90 * 1.00 * 7.0000 )/(323.5000 + 0.6 * 7.0000 )
= 2.946 MPa
Corroded Flange ID, Bcor = B+2*Fcor 647.000 mm
Corroded Large Hub, g1Cor = g1-ci 15.000 mm
Corroded Small Hub, g0Cor = go-ci 7.000 mm
Code R Dimension, R = ((C-Bcor)/2)-g1cor 66.500 mm
Gasket Contact Width, N = (Go - Gi) / 2 23.000 mm
Basic Gasket Width, bo = N / 2 11.500 mm
Effective Gasket Width, b = Cb sqrt(bo) 8.545 mm
Gasket Reaction Diameter, G = Go - 2 * b 758.909 mm
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]: = 0.785 * G² * Peq
= 0.785 * 758.9091² * 2.000
= 904612.250 N
Contact Load on Gasket Surfaces [Hp]: = 2 * b * Pi * G * m * P
= 2 * 8.5455 * 3.1416 * 758.9091 * 2.0000 * 2.00
= 162977.812 N
Hydrostatic End Load at Flange ID [Hd]: = Pi * Bcor² * P / 4
= 3.1416 * 647.0001² *2.0000/4
= 657493.625 N
Pressure Force on Flange Face [Ht]: = H - Hd
= 904612 - 657493
= 247118.641 N
Operating Bolt Load [Wm1]: = max( H + Hp + H'p, 0 )
= max( 904612 + 162977 + 0 , 0 )
= 1067590.000 N
Gasket Seating Bolt Load [Wm2]: = y * b * Pi * G + yPart * bPart * lp
= 11.03*8.5455*3.141*758.909+0.00*0.0000*0.00
= 224746.391 N
Required Bolt Area [Am]:
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 22 of 94
Flg Calc [Int P] : SH#RC FLANGE Flng: 23 9:50a Jul 11,2013
= Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 1067590/172 , 224746/172
= 6193.942 mm²
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]: = 2a + 6t/(m + 0.5)
= 2 * 20.000 + 6 * 75.000/(2.00 + 0.5)
= 220.000 mm
Actual Circumferential Bolt Spacing [Bs]: = C * sin( pi / n ) )
= 810.000 * sin( 3.142/32 )
= 79.394 mm
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]: = max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 79.394/( 2 * 20.000 + 75.000 )), 1 )
= 1.0000
Bolting Information for TEMA Metric Thread Series (Non Mandatory): -----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, mm² 6193.942 6945.631
Radial distance bet. hub and bolts 31.750 66.500
Radial distance bet. bolts and the edge 23.810 24.000
Circumferential spacing between bolts 52.390 79.394 220.000
-----------------------------------------------------------------------------
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]: = Ab * Sa/( y * Pi * (Go + Gi) )
= 6945.631 * 172.38/(11.03 * 3.14 * (776.000 + 730.00 ) )
= 22.938 mm
Note: Recommended Min. Width for Sheet and Composite Gaskets per table 2-4 : = 25.000 mm[Note: Exceeds actual gasket width, 23.000 ]
Flange Design Bolt Load, Gasket Seating [W]: = Sa * ( Am + Ab ) / 2
= 172.38 * ( 6193.9419 + 6945.6313 )/2
= 1132370.75 N
Gasket Load for the Operating Condition [HG]: = Wm1 - H
= 1067590 - 904612
= 162977.78 N
Moment Arm Calculations:Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 810.0000 - 758.9091 )/2
= 25.5455 mm
Distance to Face Pressure Reaction [ht]: = ( R + g1 + hg ) / 2
= ( 66.5000 + 15.0000 + 25.5455 )/2
= 53.5227 mm
Distance to End Pressure Reaction [hd]: = R + ( g1 / 2 )
= 66.5000 + ( 15.0000/2.0 )
= 74.0000 mm
Summary of Moments for Internal Pressure: Loading Force Distance Bolt Corr Moment
End Pressure, Md 657494. 74.0000 1.0000 48674248. N-mm
Face Pressure, Mt 247119. 53.5227 1.0000 13231826. N-mm
Gasket Load, Mg 162978. 25.5455 1.0000 4165030. N-mm
Gasket Seating, Matm 1132371. 25.5455 1.0000 28938662. N-mm
Total Moment for Operation, Mop 66071104. N-mm
Total Moment for Gasket seating, Matm 28938662. N-mm
Effective Hub Length, ho = sqrt(Bcor*goCor) 67.298 mm
Hub Ratio, h/h0 = HL / H0 0.490
Thickness Ratio, g1/g0 = (g1Cor/goCor) 2.143
Flange Factors for Integral Flange: Factor F per 2-7.2 0.825
Factor V per 2-7.3 0.215
Factor f per 2-7.6 1.461
Factors from Figure 2-7.1 K = 1.326
T = 1.786 U = 7.727
Y = 7.031 Z = 3.636
d = .11830E+06 mm ³ e = 0.0123 mm ^-1
Stress Factors ALPHA = 1.919
BETA = 2.225 GAMMA = 1.074
DELTA = 3.566 Lamda = 4.640
Longitudinal Hub Stress, Operating [SHo]: = ( f * Mop / Bcor ) / ( L * g1² )
= (1.4609*66071104/647.0001)/(4.6404*15.0000²)
= 142.84 MPa
Longitudinal Hub Stress, Seating [SHa]: = ( f * Matm / Bcor ) / ( L * g1² )
= (1.4609*28938662/647.0001)/(4.6404*15.0000²)
= 62.56 MPa
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 23 of 94
Flg Calc [Int P] : SH#RC FLANGE Flng: 23 9:50a Jul 11,2013
Radial Flange Stress, Operating [SRo]: = ( Beta * Mop / Bcor ) / ( L * t² )
= (2.2252*66071104/647.0001)/(4.6404*75.0000²)
= 8.70 MPa
Radial Flange Stress, Seating [SRa]: = ( Beta * Matm/Bcor ) / ( L * t² )
= (2.2252*28938662/647.0001)/(4.6404*75.0000²)
= 3.81 MPa
Tangential Flange Stress, Operating [STo]: = ( Y * Mo / (t² * Bcor) ) - Z * SRo
= (7.0313*66071104/(75.0000²*647.0001))-3.6364*8
= 95.96 MPa
Tangential Flange Stress, Seating [STa]: = ( y * Matm / (t² * Bcor) ) - Z * SRa
= (7.0313*28938662/(75.0000²*647.0001))-3.6364*3
= 42.03 MPa
Average Flange Stress, Operating [SAo]: = ( SHo + max( SRo, STo ) ) / 2
= (142+max(8,95))/2
= 119.40 MPa
Average Flange Stress, Seating [SAa]: = ( SHa + max( SRa, STa ) ) / 2
= (62+max(3,42))/2
= 52.30 MPa
Bolt Stress, Operating [BSo]: = ( Wm1 / Ab )
= (1067590/6945.6313)
= 153.72 MPa
Bolt Stress, Seating [BSa]: = ( Wm2 / Ab )
= (224746/6945.6313)
= 32.36 MPa
Stress Computation Results: Operating Gasket Seating
Actual Allowed Actual Allowed
Longitudinal Hub 143. 207. 63. 207. MPa
Radial Flange 9. 138. 4. 138. MPa
Tangential Flange 96. 138. 42. 138. MPa
Maximum Average 119. 138. 52. 138. MPa
Bolting 154. 172. 32. 172. MPa
Minimum Required Flange Thickness 69.723 mm
Estimated M.A.W.P. ( Operating ) 2.2 MPa
Estimated Finished Weight of Flange at given Thk. 155.9 kgm
Estimated Unfinished Weight of Forging at given Thk 213.8 kgm
Flange Rigidity Based on Required Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 52.14 * Ma / Bsc * Cnv_fac * V / ( Lambda * Eamb * go^(2) * ho * Ki )
= 52.14 * 28938662/1.0000 * 1.000 * 0.215/( 3.901 * 202713 *
7.000^(2) * 67.298 * 0.300 )
= 0.415 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 52.14 * Mo / Bsc * Cnv_fac * V / ( Lambda * Eop * goc^(2) * ho * Ki )
= 52.14 * 66071104/1.0000 * 1.000 * 0.215/( 3.901 * 198162
* 7.000^(2) * 67.298 * 0.300 )
= 0.970 (should be <= 1)
Flange Rigidity Based on Given Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 52.14 * Ma / Bsc * Cnv_fac * V / ( Lambda * Eamb * go^(2) * ho * Ki )
= 52.14 * 28938662/1.0000 * 1.000 * 0.215/( 4.640 * 202713 *
7.000^(2) * 67.298 * 0.300 )
= 0.349 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 52.14 * Mo / Bsc * Cnv_fac * V / ( Lambda * Eop * goc^(2) * ho * Ki )
= 52.14 * 66071104/1.0000 * 1.000 * 0.215/( 4.640 * 198162
* 7.000^(2) * 67.298 * 0.300 )
= 0.815 (should be <= 1)
Minimum Design Metal Temperature Results:Stress Ratio = 0.937 , Temperature Reduction per Fig. UCS 66.1 = 3 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -32 C
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 24 of 94
Flg Calc [Int P] : RC#SH FLANGE Flng: 24 9:50a Jul 11,2013
Flange Input Data Values Description: RC#SH FLANGE :
RC#SH FLANGE
Description of Flange Geometry (Type) Integral Ring
Design Pressure P 2.00 MPa
Design Temperature 100 C
Internal Corrosion Allowance ci 3.0000 mm
External Corrosion Allowance ce 0.0000 mm
Use Corrosion Allowance in Thickness Calcs. No
Attached Shell Inside Diameter B 724.0000 mm
Integral Ring Inside Diameter 744.0000 mm
Flange Outside Diameter A 858.000 mm
Flange Thickness t 80.0000 mm
Thickness of Hub at Small End go 10.0000 mm
Thickness of Hub at Large End g1 20.0000 mm
Length of Hub h 10.0000 mm
Flange Material SA-516 70
Flange Material UNS number K02700
Flange Allowable Stress At Temperature Sfo 137.90 MPa
Flange Allowable Stress At Ambient Sfa 137.90 MPa
Bolt Material SA-193 B7
Bolt Allowable Stress At Temperature Sb 172.38 MPa
Bolt Allowable Stress At Ambient Sa 172.38 MPa
Length of Weld Leg at Back of Ring tw 0.0000 mm
Number of Splits in Ring Flange n 0
Diameter of Bolt Circle C 810.000 mm
Nominal Bolt Diameter dB 20.0000 mm
Type of Threads TEMA Metric
Number of Bolts 32
Flange Face Outside Diameter Fod 779.000 mm
Flange Face Inside Diameter Fid 744.000 mm
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 776.000 mm
Gasket Inside Diameter Gi 730.000 mm
Gasket Factor m 2.0000
Gasket Design Seating Stress y 11.03 MPa
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 3.0000 mm
ASME Code, Section VIII, Division 1, 2010, 2011a
Corroded Flange ID, Bcor = B+2*Fcor 730.000 mm
Corroded Large Hub, g1Cor = g1-ci 17.000 mm
Corroded Small Hub, g0Cor = go-ci 7.000 mm
Code R Dimension, R = ((C-Bcor)/2)-g1cor 23.000 mm
Gasket Contact Width, N = (Go - Gi) / 2 16.000 mm
Basic Gasket Width, bo = N / 2 8.000 mm
Effective Gasket Width, b = Cb sqrt(bo) 7.127 mm
Gasket Reaction Diameter, G = Go - 2 * b 761.745 mm
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]: = 0.785 * G² * Peq
= 0.785 * 761.7452² * 2.000
= 911386.062 N
Contact Load on Gasket Surfaces [Hp]: = 2 * b * Pi * G * m * P
= 2 * 7.1274 * 3.1416 * 761.7452 * 2.0000 * 2.00
= 136440.844 N
Hydrostatic End Load at Flange ID [Hd]: = Pi * Bcor² * P / 4
= 3.1416 * 730.0000² *2.0000/4
= 837006.188 N
Pressure Force on Flange Face [Ht]: = H - Hd
= 911386 - 837006
= 74379.875 N
Operating Bolt Load [Wm1]: = max( H + Hp + H'p, 0 )
= max( 911386 + 136440 + 0 , 0 )
= 1047826.938 N
Gasket Seating Bolt Load [Wm2]: = y * b * Pi * G + yPart * bPart * lp
= 11.03*7.1274*3.141*761.745+0.00*0.0000*0.00
= 188151.906 N
Required Bolt Area [Am]: = Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 1047826/172 , 188151/172
= 6079.280 mm²
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]: = 2a + 6t/(m + 0.5)
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 25 of 94
Flg Calc [Int P] : RC#SH FLANGE Flng: 24 9:50a Jul 11,2013
= 2 * 20.000 + 6 * 80.000/(2.00 + 0.5)
= 232.000 mm
Actual Circumferential Bolt Spacing [Bs]: = C * sin( pi / n ) )
= 810.000 * sin( 3.142/32 )
= 79.394 mm
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]: = max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 79.394/( 2 * 20.000 + 80.000 )), 1 )
= 1.0000
Bolting Information for TEMA Metric Thread Series (Non Mandatory): Distance Across Corners for Nuts 39.260 mm
Circular Wrench End Diameter a 0.000 mm
-----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, mm² 6079.280 6945.631
Radial distance bet. hub and bolts 23.810 43.000
Radial distance bet. bolts and the edge 23.810 24.000
Circumferential spacing between bolts 52.390 79.394 232.000
-----------------------------------------------------------------------------
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calc] [Nmin]: = Ab * Sa/( y * Pi * (Go + Gi) )
= 6945.631 * 172.38/(11.03 * 3.14 * (776.000 + 744.00 ) )
= 22.727 mm[Note: Exceeds actual gasket width, 16.000 ]
Note: Recommended Min. Width for Sheet and Composite Gaskets per table 2-4 : = 25.000 mm[Note: Exceeds actual gasket width, 16.000 ]
Flange Design Bolt Load, Gasket Seating [W]: = Sa * ( Am + Ab ) / 2
= 172.38 * ( 6079.2803 + 6945.6313 )/2
= 1122489.25 N
Gasket Load for the Operating Condition [HG]: = Wm1 - H
= 1047826 - 911386
= 136440.88 N
Moment Arm Calculations:Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 810.0000 - 761.7452 )/2
= 24.1274 mm
Distance to Face Pressure Reaction [ht]: = ( R + g1 + hg ) / 2
= ( 23.0000 + 17.0000 + 24.1274 )/2
= 32.0637 mm
Distance to End Pressure Reaction [hd]: = R + ( g1 / 2 )
= 23.0000 + ( 17.0000/2.0 )
= 31.5000 mm
Summary of Moments for Internal Pressure: Loading Force Distance Bolt Corr Moment
End Pressure, Md 837006. 31.5000 1.0000 26376390. N-mm
Face Pressure, Mt 74380. 32.0637 1.0000 2385861. N-mm
Gasket Load, Mg 136441. 24.1274 1.0000 3293298. N-mm
Gasket Seating, Matm 1122489. 24.1274 1.0000 27093730. N-mm
Total Moment for Operation, Mop 32055552. N-mm
Total Moment for Gasket seating, Matm 27093730. N-mm
Effective Hub Length, ho = sqrt(Bcor*goCor) 71.484 mm
Hub Ratio, h/h0 = HL / H0 0.140
Thickness Ratio, g1/g0 = (g1Cor/goCor) 2.429
Flange Factors for Integral Flange: Factor F per 2-7.2 0.900
Factor V per 2-7.3 0.388
Factor f per 2-7.6 4.451
Factors from Figure 2-7.1 K = 1.175
T = 1.849 U = 13.294
Y = 12.097 Z = 6.243
d = .12013E+06 mm ³ e = 0.0126 mm ^-1
Stress Factors ALPHA = 2.007
BETA = 2.343 GAMMA = 1.086
DELTA = 4.262 Lamda = 5.348
Longitudinal Hub Stress, Operating [SHo]: = ( f * Mop / Bcor ) / ( L * g1² )
= (4.4515*32055552/730.0000)/(5.3475*17.0000²)
= 126.44 MPa
Longitudinal Hub Stress, Seating [SHa]: = ( f * Matm / Bcor ) / ( L * g1² )
= (4.4515*27093730/730.0000)/(5.3475*17.0000²)
= 106.87 MPa
Radial Flange Stress, Operating [SRo]: = ( Beta * Mop / Bcor ) / ( L * t² )
= (2.3427*32055552/730.0000)/(5.3475*80.0000²)
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 26 of 94
Flg Calc [Int P] : RC#SH FLANGE Flng: 24 9:50a Jul 11,2013
= 3.00 MPa
Radial Flange Stress, Seating [SRa]: = ( Beta * Matm/Bcor ) / ( L * t² )
= (2.3427*27093730/730.0000)/(5.3475*80.0000²)
= 2.54 MPa
Tangential Flange Stress, Operating [STo]: = ( Y * Mo / (t² * Bcor) ) - Z * SRo
= (12.0975*32055552/(80.0000²*730.0000))-6.2434*3
= 64.22 MPa
Tangential Flange Stress, Seating [STa]: = ( y * Matm / (t² * Bcor) ) - Z * SRa
= (12.0975*27093730/(80.0000²*730.0000))-6.2434*2
= 54.28 MPa
Average Flange Stress, Operating [SAo]: = ( SHo + max( SRo, STo ) ) / 2
= (126+max(3,64))/2
= 95.33 MPa
Average Flange Stress, Seating [SAa]: = ( SHa + max( SRa, STa ) ) / 2
= (106+max(2,54))/2
= 80.57 MPa
Bolt Stress, Operating [BSo]: = ( Wm1 / Ab )
= (1047826/6945.6313)
= 150.87 MPa
Bolt Stress, Seating [BSa]: = ( Wm2 / Ab )
= (188151/6945.6313)
= 27.09 MPa
Stress Computation Results: Operating Gasket Seating
Actual Allowed Actual Allowed
Longitudinal Hub 126. 207. 107. 207. MPa
Radial Flange 3. 138. 3. 138. MPa
Tangential Flange 64. 138. 54. 138. MPa
Maximum Average 95. 138. 81. 138. MPa
Bolting 151. 172. 27. 172. MPa
Minimum Required Flange Thickness 66.827 mm
Estimated M.A.W.P. ( Operating ) 2.3 MPa
Estimated Finished Weight of Flange at given Thk. 103.2 kgm
Estimated Unfinished Weight of Forging at given Thk 103.2 kgm
Flange Rigidity Based on Required Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 52.14 * Ma / Bsc * Cnv_fac * V / ( Lambda * Eamb * go^(2) * ho * Ki )
= 52.14 * 27093730/1.0000 * 1.000 * 0.388/( 3.480 * 202713 *
7.000^(2) * 71.484 * 0.300 )
= 0.738 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 52.14 * Mo / Bsc * Cnv_fac * V / ( Lambda * Eop * goc^(2) * ho * Ki )
= 52.14 * 32055550/1.0000 * 1.000 * 0.388/( 3.480 * 198162
* 7.000^(2) * 71.484 * 0.300 )
= 0.894 (should be <= 1)
Flange Rigidity Based on Given Thickness [ASME]:
Flange Rigidity Index, Seating (rotation check) per APP. 2 [Js]: = 52.14 * Ma / Bsc * Cnv_fac * V / ( Lambda * Eamb * go^(2) * ho * Ki )
= 52.14 * 27093730/1.0000 * 1.000 * 0.388/( 5.348 * 202713 *
7.000^(2) * 71.484 * 0.300 )
= 0.481 (should be <= 1)
Flange Rigidity Index Operating (rotation check) per APP. 2 [J]: = 52.14 * Mo / Bsc * Cnv_fac * V / ( Lambda * Eop * goc^(2) * ho * Ki )
= 52.14 * 32055550/1.0000 * 1.000 * 0.388/( 5.348 * 198162
* 7.000^(2) * 71.484 * 0.300 )
= 0.582 (should be <= 1)
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 27 of 94
Internal Pressure Calculations : Step: 9 9:50a Jul 11,2013
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 |
---------------------------------------------------------------------------
FC COVER| 0.5000 | ... | 6.1750 | 984.25 | 137.90 |
FC#CV FLAN| 0.5000 | ... | 3.0000 | 984.25 | 137.90 |
FC SHELL| 0.5000 | 10.000 | 3.0000 | 635.00 | 117.22 |
FC#SH FLAN| 0.5000 | ... | 3.0000 | ... | 137.90 |
SH#FC FLAN| 2.0000 | ... | 3.0000 | ... | 137.90 |
SHELL| 2.0000 | 10.000 | 3.0000 | 635.00 | 117.22 |
SH#RC FLAN| 2.0000 | ... | 3.0000 | ... | 137.90 |
RC#SH FLAN| 2.0000 | ... | 3.0000 | ... | 137.90 |
RC SHELL| 2.0000 | 10.000 | 3.0000 | 724.00 | 117.22 |
RC HEAD| 2.0000 | 12.000 | 3.0000 | 724.00 | 117.22 |
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 |
----------------------------------------------------------------------------
FC COVER| 0.50000 | 0.84078 | 1.37369 | 43.0000 | 35.2589 |
FC#CV FLAN| 0.50000 | 1.01301 | 1.01301 | 47.0000 | 42.7736 |
FC SHELL| 0.50000 | 2.52696 | 3.62334 | 10.0000 | 4.50000 |
FC#SH FLAN| 0.50000 | 0.51706 | 2.45352 | 76.0000 | 72.5678 |
SH#FC FLAN| 2.00000 | 2.10153 | 2.42173 | 60.0000 | 58.6486 |
SHELL| 2.00000 | 2.52696 | 3.62334 | 10.0000 | 8.52515 |
SH#RC FLAN| 2.00000 | 2.24267 | 2.24267 | 75.0000 | 69.7230 |
RC#SH FLAN| 2.00000 | 2.28500 | 2.28500 | 80.0000 | 66.8274 |
RC SHELL| 2.00000 | 2.22239 | 3.18519 | 10.0000 | 9.29229 |
RC HEAD| 2.00000 | 2.26816 | 3.22906 | 10.0000 | 9.17098 |
Summary of Heat Exchanger Maximum Allowable Working Pressures :
Note: For ASME UHX designs, the following values include MAWPs thatconsider the tubesheet, tubes, tube/tubesheet joint etc. Thesevalues were determined by iteration. Review the tubesheet analysisreport for more information.
Shell Side MAWP = 2.102 MPa
Shell Side MAPnc = 2.243 MPa
Channel Side MAWP = 0.517 MPa
Channel Side MAPnc = 1.013 MPa
Internal Pressure Calculation Results :
ASME Code, Section VIII, Division 1, 2010, 2011a
Cylindrical Shell From 30 To 40 SA-516 70 , UCS-66 Crv. B at 15 C
FC SHELL
Longitudinal Joint: Spot Radiography per UW-11(b) Type 1Circumferential Joint: Spot Radiography per UW-11(b) Type 1
Material UNS Number: K02700
Required Thickness due to Internal Pressure [tr]: = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (0.500*320.5000)/(137.90*0.85-0.6*0.500)
= 1.3707 + 3.0000 = 4.3707 mm
Note: The thickness required was less than the Code Minimum, thereforethe Code Minimum value of 1.5000 mm per UG-16 will be used.
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90*0.85*7.0000)/(320.5000+0.6*7.0000)
= 2.527 MPa
Maximum Allowable Pressure, New and Cold [MAPNC]: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90*0.85*10.0000)/(317.5000+0.6*10.0000)
= 3.623 MPa
Actual stress at given pressure and thickness, corroded [Sact]: = (P*(R+0.6*t))/(E*t)
= (0.500*(320.5000+0.6*7.0000))/(0.85*7.0000)
= 27.286 MPa
Percent Elongation per UCS-79 (50*tnom/Rf)*(1-Rf/Ro) 1.550 %
Minimum Design Metal Temperature Results:
Govrn. thk, tg = 10.000 , tr = 2.309 , c = 3.0000 mm , E* = 0.85Stress Ratio = tr * (E*)/(tg - c) = 0.280 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
Cylindrical Shell From 60 To 70 SA-516 70 , UCS-66 Crv. B at 100 C
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FileName : Floating Head HE ------------------------------ Page 28 of 94
Internal Pressure Calculations : Step: 9 9:50a Jul 11,2013
SHELL
Longitudinal Joint: Spot Radiography per UW-11(b) Type 1Circumferential Joint: Spot Radiography per UW-11(b) Type 1
Material UNS Number: K02700
Required Thickness due to Internal Pressure [tr]: = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (2.000*320.5000)/(137.90*0.85-0.6*2.000)
= 5.5251 + 3.0000 = 8.5251 mm
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90*0.85*7.0000)/(320.5000+0.6*7.0000)
= 2.527 MPa
Maximum Allowable Pressure, New and Cold [MAPNC]: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90*0.85*10.0000)/(317.5000+0.6*10.0000)
= 3.623 MPa
Actual stress at given pressure and thickness, corroded [Sact]: = (P*(R+0.6*t))/(E*t)
= (2.000*(320.5000+0.6*7.0000))/(0.85*7.0000)
= 109.143 MPa
Percent Elongation per UCS-79 (50*tnom/Rf)*(1-Rf/Ro) 1.550 %
Minimum Design Metal Temperature Results:
Govrn. thk, tg = 10.000 , tr = 5.809 , c = 3.0000 mm , E* = 0.85Stress Ratio = tr * (E*)/(tg - c) = 0.705 , Temp. Reduction = 16 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -45 C
Cylindrical Shell From 90 To 100 SA-516 70 , UCS-66 Crv. B at 100 C
RC SHELL
Longitudinal Joint: Spot Radiography per UW-11(b) Type 1Circumferential Joint: Spot Radiography per UW-11(a,5,b) Type 1
Material UNS Number: K02700
Required Thickness due to Internal Pressure [tr]: = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (2.000*365.0000)/(137.90*0.85-0.6*2.000)
= 6.2923 + 3.0000 = 9.2923 mm
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90*0.85*7.0000)/(365.0000+0.6*7.0000)
= 2.222 MPa
Maximum Allowable Pressure, New and Cold [MAPNC]: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90*0.85*10.0000)/(362.0000+0.6*10.0000)
= 3.185 MPa
Actual stress at given pressure and thickness, corroded [Sact]: = (P*(R+0.6*t))/(E*t)
= (2.000*(365.0000+0.6*7.0000))/(0.85*7.0000)
= 124.101 MPa
Percent Elongation per UCS-79 (50*tnom/Rf)*(1-Rf/Ro) 1.362 %
Minimum Design Metal Temperature Results:
Govrn. thk, tg = 10.000 , tr = 6.615 , c = 3.0000 mm , E* = 0.85Stress Ratio = tr * (E*)/(tg - c) = 0.803 , Temp. Reduction = 11 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -40 C
Elliptical Head From 100 To 110 SA-516 70 , UCS-66 Crv. B at 100 C
RC HEAD
Longitudinal Joint: SeamlessCircumferential Joint: Spot Radiography per UW-11(b) Type 1
Material UNS Number: K02700
Required Thickness due to Internal Pressure [tr]: = (P*D*Kcor)/(2*S*E-0.2*P) Appendix 1-4(c)
= (2.000*730.0000*0.989)/(2*137.90*0.85-0.2*2.000)
= 6.1710 + 3.0000 = 9.1710 mm
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: = (2*S*E*t)/(Kcor*D+0.2*t) per Appendix 1-4 (c)
= (2*137.90*0.85*7.0000)/(0.989*730.0000+0.2*7.0000)
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FileName : Floating Head HE ------------------------------ Page 29 of 94
Internal Pressure Calculations : Step: 9 9:50a Jul 11,2013
= 2.268 MPa
Maximum Allowable Pressure, New and Cold [MAPNC]: = (2*S*E*t)/(K*D+0.2*t) per Appendix 1-4 (c)
= (2*137.90*0.85*10.0000)/(1.000*724.0000+0.2*10.0000)
= 3.229 MPa
Actual stress at given pressure and thickness, corroded [Sact]: = (P*(Kcor*D+0.2*t))/(2*E*t)
= (2.000*(0.989*730.0000+0.2*7.0000))/(2*0.85*7.0000)
= 121.596 MPa
Straight Flange Required Thickness: = (P*R)/(S*E-0.6*P) + c per UG-27 (c)(1)
= (2.000*365.0000)/(137.90*0.85-0.6*2.000)+3.000
= 9.292 mm
Straight Flange Maximum Allowable Working Pressure: = (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90 * 0.85 * 9.0000 )/(365.0000 + 0.6 * 9.0000 )
= 2.848 MPa
Factor K, corroded condition [Kcor]: = ( 2 + ( Inside Diameter/( 2 * Inside Head Depth ))^(2))/6
= ( 2 + ( 730.000/( 2 * 184.000 ))^(2))/6
= 0.989175
Percent Elong. per UCS-79, VIII-1-01-57 (75*tnom/Rf)*(1-Rf/Ro) 6.972 %
Note: Please Check Requirements of UCS-79 as Elongation is > 5%.
MDMT Calculations in the Knuckle Portion:
Govrn. thk, tg = 10.000 , tr = 6.485 , c = 3.0000 mm , E* = 0.85Stress Ratio = tr * (E*)/(tg - c) = 0.787 , Temp. Reduction = 12 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -41 C
MDMT Calculations in the Head Straight Flange:
Govrn. thk, tg = 12.000 , tr = 6.615 , c = 3.0000 mm , E* = 0.85Stress Ratio = tr * (E*)/(tg - c) = 0.625 , Temp. Reduction = 21 C
Min Metal Temp. w/o impact per UCS-66 -23 C
Min Metal Temp. at Required thickness (UCS 66.1) -44 C
Min Metal Temp. w/o impact per UG-20(f) -29 C
Note: Heads and Shells Exempted to -20F (-29C) by paragraph UG-20F
Hydrostatic Test Pressure Results:
Exchanger Shell Side Hydrostatic Test Pressures:
Pressure per UG99b = 1.3 * M.A.W.P. * Sa/S 2.732 MPa
Pressure per UG99b[34] = 1.3 * Design Pres * Sa/S 2.600 MPa
Pressure per UG99c = 1.3 * M.A.P. - Head(Hyd) 2.915 MPa
Pressure per UG100 = 1.1 * M.A.W.P. * Sa/S 2.312 MPa
Pressure per PED = 1.43 * MAWP 3.005 MPa
Exchanger Channel Side Hydrostatic Test Pressures:
Pressure per UG99b = 1.3 * M.A.W.P. * Sa/S 0.672 MPa
Pressure per UG99b[34] = 1.3 * Design Pres * Sa/S 0.650 MPa
Pressure per UG99c = 1.3 * M.A.P. - Head(Hyd) 1.317 MPa
Pressure per UG100 = 1.1 * M.A.W.P. * Sa/S 0.569 MPa
Pressure per PED = 1.43 * MAWP 0.739 MPa
Horizontal Test performed per: UG-99b
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 Hydrostatic Test Pressure:
From To Stress Allowable Ratio Pressure
FC SHELL 25.8 235.8 0.109 0.68
SHELL 104.2 235.8 0.442 2.74
RC SHELL 118.6 235.8 0.503 2.74
RC HEAD 117.0 235.8 0.496 2.74
Elements Suitable for Internal Pressure.
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 30 of 94
External Pressure Calculations : Step: 10 9:50a Jul 11,2013
External Pressure Calculation Results :
ASME Code, Section VIII, Division 1, 2010, 2011a
Cylindrical Shell From 30 to 40 Ext. Chart: CS-2 at 100 C
FC SHELL
Elastic Modulus from Chart: CS-2 at 100 C : 0.200E+06 MPa
Results for Maximum Allowable External Pressure (MAEP): Tca OD SLEN D/t L/D Factor A B
7.000 655.00 650.00 93.57 0.9924 0.0015102 96.96
EMAP = (4*B)/(3*(D/t)) = (4*96.9644 )/(3*93.5714 ) = 1.3817 MPa
Results for Required Thickness (Tca): Tca OD SLEN D/t L/D Factor A B
2.091 655.00 650.00 313.26 0.9924 0.0002421 24.20
EMAP = (4*B)/(3*(D/t)) = (4*24.2006 )/(3*313.2550 ) = 0.1030 MPa
Results for Maximum Stiffened Length (Slen): Tca OD SLEN D/t L/D Factor A B
7.000 655.00 14759.37 93.57 22.5334 0.0001287 12.87
EMAP = (4*B)/(3*(D/t)) = (4*12.8690 )/(3*93.5714 ) = 0.1834 MPa
Cylindrical Shell From 60 to 70 Ext. Chart: CS-2 at 100 C
SHELL
Elastic Modulus from Chart: CS-2 at 100 C : 0.200E+06 MPa
Results for Maximum Allowable External Pressure (MAEP): Tca OD SLEN D/t L/D Factor A B
7.000 655.00 3625.00 93.57 5.5344 0.0002369 23.68
EMAP = (4*B)/(3*(D/t)) = (4*23.6810 )/(3*93.5714 ) = 0.3374 MPa
Results for Required Thickness (Tca): Tca OD SLEN D/t L/D Factor A B
4.333 655.00 3625.00 151.16 5.5344 0.0001168 11.68
EMAP = (4*B)/(3*(D/t)) = (4*11.6781 )/(3*151.1646 ) = 0.1030 MPa
Results for Maximum Stiffened Length (Slen): Tca OD SLEN D/t L/D Factor A B
7.000 655.00 91925.30 93.57 50.0000 0.0001278 12.78
EMAP = (4*B)/(3*(D/t)) = (4*12.7766 )/(3*93.5714 ) = 0.1821 MPa
Cylindrical Shell From 90 to 100 Ext. Chart: CS-2 at 100 C
RC SHELL
Elastic Modulus from Chart: CS-2 at 100 C : 0.200E+06 MPa
Results for Maximum Allowable External Pressure (MAEP): Tca OD SLEN D/t L/D Factor A B
7.000 744.00 410.33 106.29 0.5515 0.0023388 107.13
EMAP = (4*B)/(3*(D/t)) = (4*107.1335 )/(3*106.2857 ) = 1.3440 MPa
Results for Required Thickness (Tca): Tca OD SLEN D/t L/D Factor A B
1.867 744.00 410.33 398.57 0.5515 0.0003080 30.79
EMAP = (4*B)/(3*(D/t)) = (4*30.7915 )/(3*398.5727 ) = 0.1030 MPa
Results for Maximum Stiffened Length (Slen): Tca OD SLEN D/t L/D Factor A B
7.000 744.00 9050.47 106.29 12.1646 0.0001063 10.63
EMAP = (4*B)/(3*(D/t)) = (4*10.6295 )/(3*106.2857 ) = 0.1333 MPa
Elliptical Head From 100 to 110 Ext. Chart: CS-2 at 100 C
RC HEAD
Elastic Modulus from Chart: CS-2 at 100 C : 0.200E+06 MPa
Results for Maximum Allowable External Pressure (MAEP): Tca OD D/t Factor A B
7.000 744.00 106.29 0.0013068 93.10
EMAP = B/(K0*D/t) = 93.1003/(0.9000 *106.2857 ) = 0.9733 MPa
Results for Required Thickness (Tca): Tca OD D/t Factor A B
1.922 744.00 387.01 0.0003589 35.88
EMAP = B/(K0*D/t) = 35.8792/(0.9000 *387.0145 ) = 0.1030 MPa
Check the requirements of UG-33(a)(1) using P = 1.67 * External Designpressure for this head.
Material UNS Number: K02700
Required Thickness due to Internal Pressure [tr]: = (P*D*Kcor)/(2*S*E-0.2*P) Appendix 1-4(c)
= (0.172*730.0000*0.989)/(2*137.90*1.00-0.2*0.172)
= 0.4504 + 3.0000 = 3.4504 mm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 31 of 94
External Pressure Calculations : Step: 10 9:50a Jul 11,2013
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]: = ((2*S*E*t)/(Kcor*D+0.2*t))/1.67 per Appendix 1-4 (c)
= ((2*137.90*1.00*7.0000)/(0.989*730.0000+0.2*7.0000))/1.67
= 1.598 MPa
Maximum Allowable External Pressure [MAEP]: = min( MAEP, MAWP )
= min( 0.97 , 1.5979 )
= 0.973 MPa
Thickness requirements per UG-33(a)(1) do not govern the requiredthickness of this head.
External Pressure Calculations
| | Section | Outside | Corroded | Factor | Factor |
From| To | Length | Diameter | Thickness | A | B |
| | mm | mm | mm | | MPa |
---------------------------------------------------------------------------
10| 20| No Calc | ... | 36.8250 | No Calc | No Calc |
20| 30| No Calc | ... | 44.0000 | No Calc | No Calc |
30| 40| 650.000 | 655.000 | 7.00000 | 0.0015102 | 96.9644 |
40| 50| No Calc | ... | 73.0000 | No Calc | No Calc |
50| 60| No Calc | ... | 57.0000 | No Calc | No Calc |
60| 70| 3625.00 | 655.000 | 7.00000 | 0.00023686 | 23.6810 |
70| 80| No Calc | ... | 72.0000 | No Calc | No Calc |
80| 90| No Calc | ... | 77.0000 | No Calc | No Calc |
90| 100| 410.333 | 744.000 | 7.00000 | 0.0023388 | 107.133 |
100| 110| No Calc | 744.000 | 7.00000 | 0.0013068 | 93.1003 |
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| 43.0000 | 28.8036 | 0.10300 | No Calc |
20| 30| 47.0000 | 42.7736 | 0.10300 | No Calc |
30| 40| 10.0000 | 5.09095 | 0.10300 | 1.38168 |
40| 50| 76.0000 | 62.5094 | 0.10300 | No Calc |
50| 60| 60.0000 | 38.4302 | 0.10300 | No Calc |
60| 70| 10.0000 | 7.33302 | 0.10300 | 0.33744 |
70| 80| 75.0000 | 28.4480 | 0.10300 | No Calc |
80| 90| 80.0000 | 46.6852 | 0.10300 | No Calc |
90| 100| 10.0000 | 4.86666 | 0.10300 | 1.34397 |
100| 110| 10.0000 | 4.92241 | 0.10300 | 0.97327 |
Minimum 0.337
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| No Calc | No Calc | No Calc | No Calc |
20| 30| No Calc | No Calc | No Calc | No Calc |
30| 40| 650.000 | 14759.4 | No Calc | No Calc |
40| 50| No Calc | No Calc | No Calc | No Calc |
50| 60| No Calc | No Calc | No Calc | No Calc |
60| 70| 3625.00 | 91925.3 | No Calc | No Calc |
70| 80| No Calc | No Calc | No Calc | No Calc |
80| 90| No Calc | No Calc | No Calc | No Calc |
90| 100| 410.333 | 9050.47 | No Calc | No Calc |
100| 110| No Calc | No Calc | No Calc | No Calc |
Elements Suitable for External Pressure.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 32 of 94
Element and Detail Weights : Step: 11 9:50a Jul 11,2013
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| 174.288 | ... | 174.288 | ... | ... |
20| 30| 65.8762 | ... | 65.8762 | ... | ... |
30| 40| 102.083 | 205.887 | 71.7903 | 209.796 | ... |
40| 50| 77.0630 | ... | 77.0630 | ... | ... |
50| 60| 78.6376 | 29.8185 | 74.3034 | 30.0170 | ... |
60| 70| 569.307 | 664.587 | 400.368 | 686.388 | ... |
70| 80| 155.874 | 35.3137 | 150.793 | 35.5140 | ... |
80| 90| 103.234 | ... | 103.234 | ... | ... |
90| 100| 53.6164 | 106.718 | 37.6848 | 108.774 | ... |
100| 110| 71.0511 | 70.2738 | 53.2883 | 71.8620 | ... |
---------------------------------------------------------------------------
Total 1451 1112.60 1208 1142.35 0
For elements specified as shell side elements, the volume(s) shownabove for those elements, reflects the displacement of the tubes.
Weight of Details
| | Weight of | X Offset, | Y Offset, |
From|Type| Detail | Dtl. Cent. |Dtl. Cent. | Description
| | kgm | mm | mm |
-------------------------------------------------
30|Nozl| 56.7164 | 325.000 | 469.113 | T1
30|Nozl| 56.7164 | 325.000 | 469.113 | T2
60|Sadl| 31.6460 | 600.000 | 453.787 | LEFT SADDLE
60|Sadl| 31.6460 | 3025.00 | 453.787 | RIGHT SADDLE
60|Nozl| 43.0006 | 1812.00 | 414.337 | S1
60|Nozl| 28.7396 | 300.000 | 390.665 | S2A
60|Nozl| 28.7396 | 3300.00 | 390.665 | S2B
40|FTsh| 102.948 | 97.0000 | ... | STATIONARY TUBE
40|Tube| 1653.67 | 2100.00 | ... |
40|FlTs| 72.5749 | 4130.00 | ... |
40|FlHd| 68.5092 | 4162.50 | ... |
Total Weight of Each Detail Type
Total Weight of Saddles 63.3
Total Weight of Nozzles 213.9
Total Weight of Exchanger Components 1897.7
Total Weight of Liquid in Tubes 328.1
---------------------------------------------------------------
Sum of the Detail Weights 2503.0 kgm
Weight Summation
Fabricated Shop Test Shipping Erected Empty Operating
------------------------------------------------------------------------------
1451.0 3625.9 1451.0 3625.9 1451.0 3625.9
63.3 1111.9 63.3 ... 63.3 ...
213.9 ... 213.9 ... ... ...
... 328.1 ... ... ... ...
... ... ... ... ... ...
... ... ... ... ... ...
... ... ... ... 213.9 328.1
1897.7 ... 1897.7 ... ... ...
... ... ... ... 1897.7 ...
------------------------------------------------------------------------------
3625.9 5065.9 3625.9 3625.9 3625.9 3954.0 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 3625.9 kgm
Shop Test Wt. - Fabricated Weight + Water ( Full ) 5065.9 kgm
Shipping Wt. - Fab. Wt + Rem. Intls.+ Shipping App. 3625.9 kgm
Erected Wt. - Fab. Wt + Rem. Intls.+ Insul. (etc) 3625.9 kgm
Ope. Wt. no Liq - Fab. Wt + Intls. + Details + Wghts. 3625.9 kgm
Operating Wt. - Empty Wt + Operating Liq. Uncorroded 3954.0 kgm
Oper. Wt. + CA - Corr Wt. + Operating Liquid 3711.7 kgm
Field Test Wt. - Empty Weight + Water (Full) 5065.9 kgm
Exchanger Tube Data Volume of Exchanger tubes : 328.3 ltr
Weight of Ope Liq in tubes : 328.1 kgm
Weight of Water in tubes : 328.1 kgm
Note: The Corroded Weight and thickness are used in the HorizontalVessel Analysis (Ope Case) and Earthquake Load Calculations.
Outside Surface Areas of Elements
| | Surface |
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 33 of 94
Element and Detail Weights : Step: 11 9:50a Jul 11,2013
From| To | Area |
| | mm² |
----------------------------
10| 20| 633194. |
20| 30| 301329. |
30| 40| 1.338E+06 |
40| 50| 316107. |
50| 60| 371056. |
60| 70| 7.459E+06 |
70| 80| 527825. |
80| 90| 382134. |
90| 100| 701204. |
100| 110| 723990. |
------------------------------
Total 12753689.000 mm²
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 34 of 94
Nozzle Flange MAWP : Step: 12 9:50a Jul 11,2013
Nozzle Flange MAWP Results :
Nozzle ----- Flange Rating
Description Operating Ambient Temperature Class Grade|Group
MPa MPa C
----------------------------------------------------------------------------
T1 5.1 5.1 15 300 GR 1.1
T2 5.1 5.1 15 300 GR 1.1
S1 4.7 5.1 100 300 GR 1.1
S2A 4.7 5.1 100 300 GR 1.1
S2B 4.7 5.1 100 300 GR 1.1
Shellside Flange Rating Lowest Flange Pressure Rating was (Ope)[ShellSide]: 4.660 MPa
Lowest Flange Pressure Rating was (Amb)[ShellSide]: 5.110 MPa
Channelside Flange Rating Lowest Flange Pressure Rating was (Ope)[TubeSide ]: 5.110 MPa
Lowest Flange Pressure Rating was (Amb)[TubeSide ]: 5.110 MPa
Note: ANSI Ratings are per ANSI/ASME B16.5 2009 Metric Edition
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 35 of 94
Wind Load Calculation : Step: 13 9:50a Jul 11,2013
Wind Analysis Results
User Entered Importance Factor is 1.000
Gust Factor (Gh, Gbar) Static Dynamic 1.392
Shape Factor (Cf) for the Vessel is 0.606
User Entered Basic Wind Speed 112.7 km/hr
Exposure Category C
Table Lookup Value Alpha from Table C6 7.0000
Table Lookup Value Zg from Table C6 900.0000
Table Lookup Value Do from Table C6 0.0050
Wind Load Results per ASCE-7 93:
Sample Calculation for the First Element:
Rougness Factor = 1.000
Values [cf1] and [cf2] Because RoughFact = 1 and DQZ > 2.5 and H/D > 7.0
Interpolating to find the final cf:
Because H / D < 25.0
CF = CF1 + (CF2-CF1) * ( H/D - 7.0 )/( 25.0 - 7.0 )
= 0.600 + (0.700 -0.600 ) * ( 8.021 - 7.0 )/( 25.0 - 7.0 )
= 0.606
Value of Alpha, Zg is taken from Table C6-2 [Alpha, Zg] For Exposure Category C:
Alpha = 7.000 , Zg = 274320.000 mm
Height of Interest for First Element [z] = Centroid Hgt + Base Height
= 609.600 + 0.000 = 609.600 mm
but: z = Max(4572.000 , 609.600 ) = 4572.000 mm
Note: Because z < 15 feet, use 15 feet to compute kz.
Velocity Pressure Coefficient [kZ]: = 2.58( z/zg )^(2/Alpha) : z is Elevation of First Element
= 2.58( 4572.000/900 )^(2/7.0 )
= 0.801
Determine if Static or Dynamic Gust Factor Applies
Height to Diameter ratio : = Maximum Height(length)^2 / Sum of Area of the Elements
= 5114.000 (^2)/3260715
= 8.021
Vibration Frequency = 33.000 HzBecause H/D > 5 Or Freqency < 1.0: Dynamic Analysis Implemented
Element O/Dia = 3 mm
Vibration Damping Factor (Operating) Beta = 0.01000
For Terrain Category C
S = 1.000 , Gamma = 0.230 , Drag Coeff. = 0.005 , Alpha = 7.000
Compute [fbar] = 10.5 * Frequency(Hz) * Vessel Height(ft) / (S * Vr(mph))
= 10.5 * 33.000 (Hz) * 16.778 (ft)/S * 1.000 (mph)
= 83.052
Because FBAR > 40: FBAR = 40.000
Wind Pressure - (performed in Imperial Units) [qz] Importance Factor: I = 1.000
Wind Speed = 112.651 km/hr Converts to 70.000 mph
qz = 0.00256 * kZ * (I * Vr)²
= 0.00256 * 0.801 *(1.000 * 70.000 )² = 10.046 psf
Converts to: 0.481 kPa
Force on the First Element [Fz] = qz * Gh * CF * Wind Area
= 0.481 * 1.392 * 0.606 * 50787.305
= 20.593 N
Element z GH Area qz Force
mm mm² kPa N
------------------------------------------------------------------------
FC COVER 609.6 1.392 50787.3 0.5 20.6
FC#CV FLANGE 609.6 1.392 55511.7 0.5 22.5
FC SHELL 609.6 1.392 510900.0 0.5 207.2
FC#SH FLANGE 609.6 1.392 0.0 0.5 0.0
SH#FC FLANGE 609.6 1.392 0.0 0.5 0.0
SHELL 609.6 1.392 2849250.2 0.5 1155.3
SH#RC FLANGE 609.6 1.392 0.0 0.5 0.0
RC#SH FLANGE 609.6 1.392 0.0 0.5 0.0
RC SHELL 609.6 1.392 267840.0 0.5 108.6
RC HEAD 609.6 1.392 156248.2 0.5 63.4
Wind Load Calculation
| | Wind | Wind | Wind | Wind | Element |
From| To | Height | Diameter | Area | Pressure | Wind Load |
| | mm | mm | mm² | kPa | N |
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FileName : Floating Head HE ------------------------------ Page 36 of 94
Wind Load Calculation : Step: 13 9:50a Jul 11,2013
---------------------------------------------------------------------------
10| 20| 609.600 | 1181.10 | 50787.3 | 0.48101 | 20.5927 |
20| 30| 609.600 | 1181.10 | 55511.7 | 0.48101 | 22.5082 |
30| 40| 609.600 | 786.000 | 510900. | 0.48101 | 207.154 |
40| 50| 609.600 | ... | ... | 0.48101 | ... |
50| 60| 609.600 | ... | ... | 0.48101 | ... |
60| 70| 609.600 | 786.000 | 2.849E+06 | 0.48101 | 1155.28 |
70| 80| 609.600 | ... | ... | 0.48101 | ... |
80| 90| 609.600 | ... | ... | 0.48101 | ... |
90| 100| 609.600 | 892.800 | 267840. | 0.48101 | 108.601 |
100| 110| 609.600 | 892.800 | 156248. | 0.48101 | 63.3537 |
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 37 of 94
Earthquake Load Calculation : Step: 14 9:50a Jul 11,2013
Earthquake Analysis Results
The UBC Zone Factor for the Vessel is ............. 0.0000
The Importance Factor as Specified by the User is . 1.000
The UBC Frequency and Soil Factor (C) is ......... 2.750
The UBC Force Factor as Specified by the User is .. 3.000
The UBC Total Weight (W) for the Vessel is ........ 36396.4 N
The UBC Total Shear (V) for the Vessel is ......... 0.0 N
The UBC Top Shear (Ft) for the Vessel is .......... 0.0 N
Earthquake Load Calculation
| | Earthquake | Earthquake | Element |
From| To | Height | Weight | Ope Load |
| | mm | N | N |
-------------------------------------------------
10| 20| 492.125 | 3033.04 | ... |
20| 30| 492.125 | 3033.04 | ... |
30| 40| 317.500 | 3033.04 | ... |
40| 50| ... | 3033.04 | ... |
50| 60| ... | 3033.04 | ... |
60|Sadl| 317.500 | 3033.04 | ... |
Sadl| 70| 317.500 | 3033.04 | ... |
60| 70| 317.500 | 3033.04 | ... |
70| 80| ... | 3033.04 | ... |
80| 90| ... | 3033.04 | ... |
90| 100| 362.000 | 3033.04 | ... |
100| 110| 362.000 | 3033.04 | ... |
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 38 of 94
Center of Gravity Calculation : Step: 15 9:50a Jul 11,2013
Shop/Field Installation Options :
Note : The CG is computed from the first Element From Node
Center of Gravity of Saddles 2652.500 mm
Center of Gravity of Nozzles 1437.624 mm
Center of Gravity of Tubesheet(s) 2533.560 mm
Center of Gravity of Tubes 2869.000 mm
Center of Gravity of the Floating Head 4931.500 mm
Center of Gravity of Bare Shell New and Cold 2383.005 mm
Center of Gravity of Bare Shell Corroded 2323.352 mm
Vessel CG in the Operating Condition 2603.901 mm
Vessel CG in the Fabricated (Shop/Empty) Condition 2609.022 mm
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 39 of 94
Horizontal Vessel Analysis (Ope.) : Step: 16 9:50a Jul 11,2013
ASME Horizontal Vessel Analysis: Stresses for the Left Saddle(per ASME Sec. VIII Div. 2 based on the Zick method.)
Horizontal Vessel Stress Calculations : Operating Case
Note: Wear Pad Width (152.40) is less than 1.56*sqrt(rm*t)and less than 2a. The wear plate will be ignored.
Minimum Wear Plate Width to be considered in analysis [b1]: = min( b + 1.56*sqrt( Rm * t ), 2a )
= min( 101.600 + 1.56*sqrt( 324.0000 * 7.0000 ), 2 * 209.550 )
= 175.8927 mm
Input and Calculated Values:
Vessel Mean Radius Rm 324.00 mm
Stiffened Vessel Length per 4.15.6 L 3625.00 mm
Distance from Saddle to Vessel tangent a 209.55 mm
Saddle Width b 101.60 mm
Saddle Bearing Angle theta 120.00 degrees
Shell Allowable Stress used in Calculation 137.90 MPa
Head Allowable Stress used in Calculation 137.90 MPa
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
Saddle Force Q, Operating Case 19632.12 N
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 40.24 137.90 MPa
Long. Stress at Bottom of Midspan 52.33 137.90 MPa
Long. Stress at Top of Saddles 46.10 137.90 MPa
Long. Stress at Bottom of Saddles 46.39 137.90 MPa
Tangential Shear in Shell 8.96 110.32 MPa
Circ. Stress at Horn of Saddle 18.92 172.38 MPa
Circ. Compressive Stress in Shell 1.21 137.90 MPa
Intermediate Results: Saddle Reaction Q due to Wind or Seismic
Saddle Reaction Force due to Wind Ft [Fwt]: = Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 1577.5/2 + 0 ) * 609.6000/561.1845
= 2570.4 N
Saddle Reaction Force due to Wind Fl or Friction [Fwl]: = Max( Fl, Friction Load, Sum of X Forces) * B / Ls
= Max( 194.49 , 0.00 , 0 ) * 609.6000/2425.0002
= 48.9 N
Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 17061 + Max( 48 , 2570 , 0 , 0 )
= 19632.1 N
Summary of Loads at the base of this Saddle: Vertical Load (including saddle weight) 19942.44 N
Transverse Shear Load Saddle 788.75 N
Longitudinal Shear Load Saddle 194.49 N
Formulas and Substitutions for Horizontal Vessel Analysis:
Note: Wear Plate is Welded to the Shell, k = 0.1
The Computed K values from Table 4.15.1: K1 = 0.1066 K2 = 1.1707 K3 = 0.8799 K4 = 0.4011
K5 = 0.7603 K6 = 0.0529 K7 = 0.0248 K8 = 0.3405
K9 = 0.2711 K10 = 0.0581 K1* = 0.1923
Note: Dimension a is greater than or equal to Rm / 2.
Moment per Equation 4.15.3 [M1]: = -Q*a [1 - (1- a/L + (R²-h2²)/(2a*L))/(1+(4h2)/3L)]
= -19632*209.55[1-(1-209.55/3625.00+(324.000²-0.000²)/
(2*209.55*3625.00))/(1+(4*0.00)/(3*3625.00))]
= 46468.7 N-mm
Moment per Equation 4.15.4 [M2]: = Q*L/4(1+2(R²-h2²)/(L²))/(1+(4h2)/( 3L))-4a/L
= 19632*3625/4(1+2(323²-0²)/(3625²))/(1+(4*0)/
(3*3625))-4*209/3625
= 13967619.0 N-mm
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]: = P * Rm/(2t) - M2/(pi*Rm²t)
= 2.00 * 324.000/(2*7.000 ) - 13967619/(pi*324.0²*7.000 )
= 40.24 MPa
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]: = P * Rm/(2t) + M2/(pi * Rm² * t)
= 2.00 * 324.000/(2 * 7.000 ) + 13967619/(pi * 324.0² * 7.000 )
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FileName : Floating Head HE ------------------------------ Page 40 of 94
Horizontal Vessel Analysis (Ope.) : Step: 16 9:50a Jul 11,2013
= 52.33 MPa
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]: = P * Rm/(2t) - M1/(K1*pi*Rm²t)
= 2.00*324.000/(2*7.000)-46468.7/(0.1066*pi*324.0²*7.000)
= 46.10 MPa
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]: = P * Rm/(2t) + M1/(K1* * pi * Rm² * t)
= 2.00*324.000/(2*7.000)+46468.7/(0.1923*pi*324.0²*7.000)
= 46.39 MPa
Maximum Shear Force in the Saddle (4.15.5) [T]: = Q(L-2a)/(L+(4*h2/3))
= 19632 ( 3625.00 - 2 * 209.55 )/(3625.00 + ( 4 * 0.00/3))
= 17362.4 N
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]: = K2 * T / ( Rm * t )
= 1.1707 * 17362.37/( 324.0000 * 7.0000 )
= 8.96 MPa
Decay Length (4.15.22) [x1,x2]: = 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 324.000 * 7.000 )
= 37.146 mm
Circumferential Stress in shell, no rings (4.15.23) [sigma6]: = -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7603 * 19632 * 0.1/( 7.000 * ( 101.60 + 37.15 + 37.15 ) )
= -1.21 MPa
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]: = -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t²)
= -19632/(4*7.000 *(101.600 +37.146 +37.146 )) -
3*0.0248 *19632/(2*7.000²)
= -18.92 MPa
Effective reinforcing plate width (4.15.1) [B1]: = min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 101.60 + 1.56 * sqrt( 324.000 * 7.000 ), 2 * 209.550 )
= 175.89 mm
Free Un-Restrained Thermal Expansion between the Saddles [Exp]: = Alpha * Ls * ( Design Temperature - Ambient Temperature )
= 0.121E-04 * 2425.000 * ( 100.0 - 21.1 )
= 2.315 mm
Results for Vessel Ribs, Web and Base: Baseplate Length Bplen 685.8000 mm
Baseplate Thickness Bpthk 12.7000 mm
Baseplate Width Bpwid 101.6000 mm
Number of Ribs ( inc. outside ribs ) Nribs 4
Rib Thickness Ribtk 6.3500 mm
Web Thickness Webtk 6.3500 mm
Web Location Webloc Center
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 3. 1584. 5544. 25872.
Wearplate 12. 1452. 17075. 211814.
Web 116. 1266. 147129. 21291940.
BasePlate 222. 1290. 286774. 63752716.
Totals 354. 5592. 456521. 85282344.
Value C1 = Sumof(Ay)/Sumof(A) = 82. mm
Value I = Sumof(Io) - C1*Sumof(Ay) = 48012772. mm**4
Value As = Sumof(A) - Ashell = 4008. mm²
K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035
Fh = K1 * Q = 0.2035 * 19632.117 = 3995.5620 N
Tension Stress, St = ( Fh/As ) = 0.9970 MPa
Allowed Stress, Sa = 0.6 * Yield Str = 143.9676 MPa
d = B - R*Sin(theta) / theta = 284.0486 mm
Bending Moment, M = Fh * d = 1135394.0000 N-mm
Bending Stress, Sb = ( M * C1 / I ) = 1.9299 MPa
Allowed Stress, Sa = 2/3 * Yield Str = 159.9640 MPa
Minimum Thickness of Baseplate per Moss : = ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 4 * BasePlateLength *
AllStress ))½
= ( 3 * (19632 + 310 ) * 101.60/( 4 * 685.800 * 159.964 ))½
= 3.722 mm
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1)
= ( 685.8000 - 25.4 )/( 4 - 1 ) = 220.1333 mm
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FileName : Floating Head HE ------------------------------ Page 41 of 94
Horizontal Vessel Analysis (Ope.) : Step: 16 9:50a Jul 11,2013
Baseplate Pressure Area [Ap]: = e * Bpwid / 2
= 220.1333 * 101.6000/2 = 11182.7734 mm²
Axial Load [P]: = Ap * Bp
= 11182.8 * 0.28 = 3150.8 N
Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 101.600 - 25.4 - 6.350 ) * 6.350 + 220.1333/2 * 6.350
= 1142.471 mm²
Compressive Stress [Sc]: = P/Ar
= 3150.8/1142.4708 = 2.7581 MPa
Check of Outside Ribs:Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay² Io
Rib 50.8 524.2 26629.0 0.0 371789.7
Web 50.8 698.9 35505.3 0.0 4697.1
Values 50.8 1223.1 62134.3 0.0 376486.7
Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2
= 194.5/( 2 * 685.80 ) * 220.133 * 385.35/2
= 6016.734 N-mm
KL/R < Cc ( 21.2277 < 128.2550 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 21.23 )²/(2 * 128.25² )) * 239/
( 5/3+3*(21.23 )/(8* 128.25 )-( 21.23³)/(8*128.25³)
Sca = 136.94 MPa
AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba
Check = 2.76/136.94 + (6016.73/7411.156 )/159.96
Check = 0.03
Check of Inside RibsInertia of Saddle, Inner Ribs - Axial Direction
Y A AY Ay² Io
Rib 38.1 443.5 16899.2 0.0 234129.9
Web 38.1 1397.8 53258.0 0.0 4697.1
Values 38.1 1841.4 70157.1 0.0 238827.0
KL/R < Cc ( 20.2444 < 128.2550 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 20.24 )²/(2 * 128.25² )) * 239/
( 5/3+3*(20.24 )/(8* 128.25 )-( 20.24³)/(8*128.25³)
Sca = 137.34 MPa
AISC Unity Check on Inside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba
Check = 3.42/137.34 + ( 7199.61/6268.425 )/159.96
Check = 0.03
Input Data for Base Plate Bolting Calculations:
Total Number of Bolts per BasePlate Nbolts 2
Total Number of Bolts in Tension/Baseplate Nbt 1
Bolt Material Specification SA-193 B7
Bolt Allowable Stress Stba 172.38 MPa
Bolt Corrosion Allowance Bca 0.0000 mm
Distance from Bolts to Edge Edgedis 101.6000 mm
Nominal Bolt Diameter Bnd 25.4000 mm
Thread Series Series TEMA
BasePlate Allowable Stress S 95.15 MPa
Area Available in a Single Bolt BltArea 355.4832 mm²
Saddle Load QO (Weight) QO 17372.1 N
Saddle Load QL (Wind/Seismic contribution) QL 48.9 N
Maximum Transverse Force Ft 788.7 N
Maximum Longitudinal Force Fl 194.5 N
Saddle Bolted to Steel Foundation No
Bolt Area Calculation per Dennis R. Moss
Bolt Area Requirement Due to Longitudinal Load [Bltarearl]: = 0.0 (QO > QL --> No Uplift in Longitudinal direction)
Bolt Area due to Shear Load [Bltarears]: = Fl / (Stba * Nbolts)
= 194.49/(172.38 * 2.00 )
= 0.5642 mm²
Bolt Area due to Transverse Load
Moment on Baseplate Due to Transverse Load [Rmom]: = B * Ft + Sum of X Moments
= 609.60 * 788.75 + 0.00
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FileName : Floating Head HE ------------------------------ Page 42 of 94
Horizontal Vessel Analysis (Ope.) : Step: 16 9:50a Jul 11,2013
= 481014.09 N-mm
Eccentricity (e): = Rmom / QO
= 481014.09/17372.06
= 27.68 mm < Bplen/6 --> No Uplift in Transverse direction
Bolt Area due to Transverse Load [Bltareart]: = 0 (No Uplift)
Required of a Single Bolt [Bltarear] = max[Bltarearl, Bltarears, Bltareart]
= max[0.0000 , 0.5642 , 0.0000 ]
= 0.5642 mm²
ASME Horizontal Vessel Analysis: Stresses for the Right Saddle(per ASME Sec. VIII Div. 2 based on the Zick method.)
Note: Wear Pad Width (152.40) is less than 1.56*sqrt(rm*t)and less than 2a. The wear plate will be ignored.
Minimum Wear Plate Width to be considered in analysis [b1]: = min( b + 1.56*sqrt( Rm * t ), 2a )
= min( 101.600 + 1.56*sqrt( 324.0000 * 7.0000 ), 2 * 209.550 )
= 175.8927 mm
Input and Calculated Values:
Vessel Mean Radius Rm 324.00 mm
Stiffened Vessel Length per 4.15.6 L 3625.00 mm
Distance from Saddle to Vessel tangent a 209.55 mm
Saddle Width b 101.60 mm
Saddle Bearing Angle theta 120.00 degrees
Shell Allowable Stress used in Calculation 137.90 MPa
Head Allowable Stress used in Calculation 137.90 MPa
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
Saddle Force Q, Operating Case 21284.45 N
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 39.73 137.90 MPa
Long. Stress at Bottom of Midspan 52.84 137.90 MPa
Long. Stress at Top of Saddles 46.08 137.90 MPa
Long. Stress at Bottom of Saddles 46.40 137.90 MPa
Tangential Shear in Shell 9.72 110.32 MPa
Circ. Stress at Horn of Saddle 20.51 172.38 MPa
Circ. Compressive Stress in Shell 1.31 137.90 MPa
Intermediate Results: Saddle Reaction Q due to Wind or Seismic
Saddle Reaction Force due to Wind Ft [Fwt]: = Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 1577.5/2 + 0 ) * 609.6000/561.1845
= 2570.4 N
Saddle Reaction Force due to Wind Fl or Friction [Fwl]: = Max( Fl, Friction Load, Sum of X Forces) * B / Ls
= Max( 194.49 , 0.00 , 0 ) * 609.6000/2425.0002
= 48.9 N
Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 18714 + Max( 48 , 2570 , 0 , 0 )
= 21284.5 N
Summary of Loads at the base of this Saddle: Vertical Load (including saddle weight) 21594.77 N
Transverse Shear Load Saddle 788.75 N
Longitudinal Shear Load Saddle 194.49 N
Formulas and Substitutions for Horizontal Vessel Analysis:
Note: Wear Plate is Welded to the Shell, k = 0.1
The Computed K values from Table 4.15.1: K1 = 0.1066 K2 = 1.1707 K3 = 0.8799 K4 = 0.4011
K5 = 0.7603 K6 = 0.0529 K7 = 0.0248 K8 = 0.3405
K9 = 0.2711 K10 = 0.0581 K1* = 0.1923
Note: Dimension a is greater than or equal to Rm / 2.
Moment per Equation 4.15.3 [M1]: = -Q*a [1 - (1- a/L + (R²-h2²)/(2a*L))/(1+(4h2)/3L)]
= -21284*209.55[1-(1-209.55/3625.00+(324.000²-0.000²)/
(2*209.55*3625.00))/(1+(4*0.00)/(3*3625.00))]
= 50379.7 N-mm
Moment per Equation 4.15.4 [M2]:
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FileName : Floating Head HE ------------------------------ Page 43 of 94
Horizontal Vessel Analysis (Ope.) : Step: 16 9:50a Jul 11,2013
= Q*L/4(1+2(R²-h2²)/(L²))/(1+(4h2)/( 3L))-4a/L
= 21284*3625/4(1+2(323²-0²)/(3625²))/(1+(4*0)/
(3*3625))-4*209/3625
= 15143204.0 N-mm
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]: = P * Rm/(2t) - M2/(pi*Rm²t)
= 2.00 * 324.000/(2*7.000 ) - 15143204/(pi*324.0²*7.000 )
= 39.73 MPa
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]: = P * Rm/(2t) + M2/(pi * Rm² * t)
= 2.00 * 324.000/(2 * 7.000 ) + 15143204/(pi * 324.0² * 7.000 )
= 52.84 MPa
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]: = P * Rm/(2t) - M1/(K1*pi*Rm²t)
= 2.00*324.000/(2*7.000)-50379.7/(0.1066*pi*324.0²*7.000)
= 46.08 MPa
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]: = P * Rm/(2t) + M1/(K1* * pi * Rm² * t)
= 2.00*324.000/(2*7.000)+50379.7/(0.1923*pi*324.0²*7.000)
= 46.40 MPa
Maximum Shear Force in the Saddle (4.15.5) [T]: = Q(L-2a)/(L+(4*h2/3))
= 21284 ( 3625.00 - 2 * 209.55 )/(3625.00 + ( 4 * 0.00/3))
= 18823.7 N
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]: = K2 * T / ( Rm * t )
= 1.1707 * 18823.68/( 324.0000 * 7.0000 )
= 9.72 MPa
Decay Length (4.15.22) [x1,x2]: = 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 324.000 * 7.000 )
= 37.146 mm
Circumferential Stress in shell, no rings (4.15.23) [sigma6]: = -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7603 * 21284 * 0.1/( 7.000 * ( 101.60 + 37.15 + 37.15 ) )
= -1.31 MPa
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]: = -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t²)
= -21284/(4*7.000 *(101.600 +37.146 +37.146 )) -
3*0.0248 *21284/(2*7.000²)
= -20.51 MPa
Effective reinforcing plate width (4.15.1) [B1]: = min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 101.60 + 1.56 * sqrt( 324.000 * 7.000 ), 2 * 209.550 )
= 175.89 mm
Results for Vessel Ribs, Web and Base
Baseplate Length Bplen 685.8000 mm
Baseplate Thickness Bpthk 12.7000 mm
Baseplate Width Bpwid 101.6000 mm
Number of Ribs ( inc. outside ribs ) Nribs 4
Rib Thickness Ribtk 6.3500 mm
Web Thickness Webtk 6.3500 mm
Web Location Webloc Center
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 3. 1584. 5544. 25872.
Wearplate 12. 1452. 17075. 211814.
Web 116. 1266. 147129. 21291940.
BasePlate 222. 1290. 286774. 63752716.
Totals 354. 5592. 456521. 85282344.
Value C1 = Sumof(Ay)/Sumof(A) = 82. mm
Value I = Sumof(Io) - C1*Sumof(Ay) = 48012772. mm**4
Value As = Sumof(A) - Ashell = 4008. mm²
K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035
Fh = K1 * Q = 0.2035 * 21284.453 = 4331.8481 N
Tension Stress, St = ( Fh/As ) = 1.0809 MPa
Allowed Stress, Sa = 0.6 * Yield Str = 143.9676 MPa
d = B - R*Sin(theta) / theta = 284.0486 mm
Bending Moment, M = Fh * d = 1230954.3750 N-mm
Bending Stress, Sb = ( M * C1 / I ) = 2.0924 MPa
Allowed Stress, Sa = 2/3 * Yield Str = 159.9640 MPa
Minimum Thickness of Baseplate per Moss : = ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 4 * BasePlateLength *
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Horizontal Vessel Analysis (Ope.) : Step: 16 9:50a Jul 11,2013
AllStress ))½
= ( 3 * (21284 + 310 ) * 101.60/( 4 * 685.800 * 159.964 ))½
= 3.873 mm
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1)
= ( 685.8000 - 25.4 )/( 4 - 1 ) = 220.1333 mm
Baseplate Pressure Area [Ap]: = e * Bpwid / 2
= 220.1333 * 101.6000/2 = 11182.7734 mm²
Axial Load [P]: = Ap * Bp
= 11182.8 * 0.31 = 3416.0 N
Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 101.600 - 25.4 - 6.350 ) * 6.350 + 220.1333/2 * 6.350
= 1142.471 mm²
Compressive Stress [Sc]: = P/Ar
= 3416.0/1142.4708 = 2.9903 MPa
Check of Outside Ribs:Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay² Io
Rib 50.8 524.2 26629.0 0.0 371789.7
Web 50.8 698.9 35505.3 0.0 4697.1
Values 50.8 1223.1 62134.3 0.0 376486.7
Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2
= 194.5/( 2 * 685.80 ) * 220.133 * 385.35/2
= 6016.734 N-mm
KL/R < Cc ( 21.2277 < 128.2550 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 21.23 )²/(2 * 128.25² )) * 239/
( 5/3+3*(21.23 )/(8* 128.25 )-( 21.23³)/(8*128.25³)
Sca = 136.94 MPa
AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba
Check = 2.99/136.94 + (6016.73/7411.156 )/159.96
Check = 0.03
Check of Inside RibsInertia of Saddle, Inner Ribs - Axial Direction
Y A AY Ay² Io
Rib 38.1 443.5 16899.2 0.0 234129.9
Web 38.1 1397.8 53258.0 0.0 4697.1
Values 38.1 1841.4 70157.1 0.0 238827.0
KL/R < Cc ( 20.2444 < 128.2550 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 20.24 )²/(2 * 128.25² )) * 239/
( 5/3+3*(20.24 )/(8* 128.25 )-( 20.24³)/(8*128.25³)
Sca = 137.34 MPa
AISC Unity Check on Inside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba
Check = 3.71/137.34 + ( 7199.61/6268.425 )/159.96
Check = 0.03
Input Data for Base Plate Bolting Calculations:
Total Number of Bolts per BasePlate Nbolts 2
Total Number of Bolts in Tension/Baseplate Nbt 1
Bolt Material Specification SA-193 B7
Bolt Allowable Stress Stba 172.38 MPa
Bolt Corrosion Allowance Bca 0.0000 mm
Distance from Bolts to Edge Edgedis 101.6000 mm
Nominal Bolt Diameter Bnd 25.4000 mm
Thread Series Series TEMA
BasePlate Allowable Stress S 95.15 MPa
Area Available in a Single Bolt BltArea 355.4832 mm²
Saddle Load QO (Weight) QO 19024.4 N
Saddle Load QL (Wind/Seismic contribution) QL 48.9 N
Maximum Transverse Force Ft 788.7 N
Maximum Longitudinal Force Fl 194.5 N
Saddle Bolted to Steel Foundation No
Bolt Area Calculation per Dennis R. Moss
Bolt Area Requirement Due to Longitudinal Load [Bltarearl]: = 0.0 (QO > QL --> No Uplift in Longitudinal direction)
Bolt Area due to Shear Load [Bltarears]:
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FileName : Floating Head HE ------------------------------ Page 45 of 94
Horizontal Vessel Analysis (Ope.) : Step: 16 9:50a Jul 11,2013
= Fl / (Stba * Nbolts)
= 194.49/(172.38 * 2.00 )
= 0.5642 mm²
Bolt Area due to Transverse Load
Moment on Baseplate Due to Transverse Load [Rmom]: = B * Ft + Sum of X Moments
= 609.60 * 788.75 + 0.00
= 481014.09 N-mm
Eccentricity (e): = Rmom / QO
= 481014.09/19024.39
= 25.27 mm < Bplen/6 --> No Uplift in Transverse direction
Bolt Area due to Transverse Load [Bltareart]: = 0 (No Uplift)
Required of a Single Bolt [Bltarear] = max[Bltarearl, Bltarears, Bltareart]
= max[0.0000 , 0.5642 , 0.0000 ]
= 0.5642 mm²
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 46 of 94
Horizontal Vessel Analysis (Test) : Step: 17 9:50a Jul 11,2013
ASME Horizontal Vessel Analysis: Stresses for the Left Saddle(per ASME Sec. VIII Div. 2 based on the Zick method.)
Horizontal Vessel Stress Calculations : Test Case
Note: Wear Pad Width (152.40) is less than 1.56*sqrt(rm*t)and less than 2a. The wear plate will be ignored.
Minimum Wear Plate Width to be considered in analysis [b1]: = min( b + 1.56*sqrt( Rm * t ), 2a )
= min( 101.600 + 1.56*sqrt( 322.5000 * 10.0000 ), 2 * 209.550 )
= 190.1910 mm
Input and Calculated Values:
Vessel Mean Radius Rm 322.50 mm
Stiffened Vessel Length per 4.15.6 L 3625.00 mm
Distance from Saddle to Vessel tangent a 209.55 mm
Saddle Width b 101.60 mm
Saddle Bearing Angle theta 120.00 degrees
Shell Allowable Stress used in Calculation 137.90 MPa
Head Allowable Stress used in Calculation 137.90 MPa
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
Saddle Force Q, Test Case, no Ext. Forces 24752.28 N
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 38.72 137.90 MPa
Long. Stress at Bottom of Midspan 49.49 137.90 MPa
Long. Stress at Top of Saddles 43.95 137.90 MPa
Long. Stress at Bottom of Saddles 44.19 137.90 MPa
Tangential Shear in Shell 7.95 110.32 MPa
Circ. Stress at Horn of Saddle 12.57 172.38 MPa
Circ. Compressive Stress in Shell 0.99 137.90 MPa
Intermediate Results: Saddle Reaction Q due to Wind or Seismic
Saddle Reaction Force due to Wind Ft [Fwt]: = Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 520.6/2 + 0 ) * 609.6000/558.5864
= 852.2 N
Saddle Reaction Force due to Wind Fl or Friction [Fwl]: = Max( Fl, Friction Load, Sum of X Forces) * B / Ls
= Max( 194.49 , 0.00 , 0 ) * 609.6000/2425.0002
= 16.1 N
Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 23900 + Max( 16 , 852 , 0 , 0 )
= 24752.3 N
Summary of Loads at the base of this Saddle: Vertical Load (including saddle weight) 25062.60 N
Transverse Shear Load Saddle 260.29 N
Longitudinal Shear Load Saddle 64.18 N
Hydrostatic Test Pressure at center of Vessel: 2.735 MPa
Formulas and Substitutions for Horizontal Vessel Analysis:
Note: Wear Plate is Welded to the Shell, k = 0.1
The Computed K values from Table 4.15.1: K1 = 0.1066 K2 = 1.1707 K3 = 0.8799 K4 = 0.4011
K5 = 0.7603 K6 = 0.0529 K7 = 0.0251 K8 = 0.3405
K9 = 0.2711 K10 = 0.0581 K1* = 0.1923
Note: Dimension a is greater than or equal to Rm / 2.
Moment per Equation 4.15.3 [M1]: = -Q*a [1 - (1- a/L + (R²-h2²)/(2a*L))/(1+(4h2)/3L)]
= -24752*209.55[1-(1-209.55/3625.00+(322.500²-0.000²)/
(2*209.55*3625.00))/(1+(4*0.00)/(3*3625.00))]
= 55275.7 N-mm
Moment per Equation 4.15.4 [M2]: = Q*L/4(1+2(R²-h2²)/(L²))/(1+(4h2)/( 3L))-4a/L
= 24752*3625/4(1+2(322²-0²)/(3625²))/(1+(4*0)/
(3*3625))-4*209/3625
= 17607140.0 N-mm
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]: = P * Rm/(2t) - M2/(pi*Rm²t)
= 2.74 * 322.500/(2*10.000 ) - 17607140/(pi*322.5²*10.000 )
= 38.72 MPa
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:
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Horizontal Vessel Analysis (Test) : Step: 17 9:50a Jul 11,2013
= P * Rm/(2t) + M2/(pi * Rm² * t)
= 2.74 * 322.500/(2 * 10.000 ) + 17607140/(pi * 322.5² * 10.000 )
= 49.49 MPa
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]: = P * Rm/(2t) - M1/(K1*pi*Rm²t)
= 2.74*322.500/(2*10.000)-55275.7/(0.1066*pi*322.5²*10.000)
= 43.95 MPa
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]: = P * Rm/(2t) + M1/(K1* * pi * Rm² * t)
= 2.74*322.500/(2*10.000)+55275.7/(0.1923*pi*322.5²*10.000)
= 44.19 MPa
Maximum Shear Force in the Saddle (4.15.5) [T]: = Q(L-2a)/(L+(4*h2/3))
= 24752 ( 3625.00 - 2 * 209.55 )/(3625.00 + ( 4 * 0.00/3))
= 21890.6 N
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]: = K2 * T / ( Rm * t )
= 1.1707 * 21890.58/( 322.5000 * 10.0000 )
= 7.95 MPa
Decay Length (4.15.22) [x1,x2]: = 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 322.500 * 10.000 )
= 44.295 mm
Circumferential Stress in shell, no rings (4.15.23) [sigma6]: = -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7603 * 24752 * 0.1/( 10.000 * ( 101.60 + 44.30 + 44.30 ) )
= -0.99 MPa
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]: = -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t²)
= -24752/(4*10.000 *(101.600 +44.295 +44.295 )) -
3*0.0251 *24752/(2*10.000²)
= -12.57 MPa
Effective reinforcing plate width (4.15.1) [B1]: = min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 101.60 + 1.56 * sqrt( 322.500 * 10.000 ), 2 * 209.550 )
= 190.19 mm
Results for Vessel Ribs, Web and Base: Baseplate Length Bplen 685.8000 mm
Baseplate Thickness Bpthk 12.7000 mm
Baseplate Width Bpwid 101.6000 mm
Number of Ribs ( inc. outside ribs ) Nribs 4
Rib Thickness Ribtk 6.3500 mm
Web Thickness Webtk 6.3500 mm
Web Location Webloc Center
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 5. 2403. 12015. 80100.
Wearplate 15. 1452. 21429. 327326.
Web 118. 1247. 146785. 21285732.
BasePlate 222. 1290. 286774. 63752716.
Totals 360. 6392. 467003. 85445872.
Value C1 = Sumof(Ay)/Sumof(A) = 73. mm
Value I = Sumof(Io) - C1*Sumof(Ay) = 51325968. mm**4
Value As = Sumof(A) - Ashell = 3989. mm²
K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035
Fh = K1 * Q = 0.2035 * 24752.281 = 5037.6265 N
Tension Stress, St = ( Fh/As ) = 1.2630 MPa
Allowed Stress, Sa = 0.6 * Yield Str = 143.9676 MPa
d = B - R*Sin(theta) / theta = 283.5296 mm
Bending Moment, M = Fh * d = 1428895.3750 N-mm
Bending Stress, Sb = ( M * C1 / I ) = 2.0333 MPa
Allowed Stress, Sa = 2/3 * Yield Str = 159.9640 MPa
Minimum Thickness of Baseplate per Moss : = ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 4 * BasePlateLength *
AllStress ))½
= ( 3 * (24752 + 310 ) * 101.60/( 4 * 685.800 * 159.964 ))½
= 4.173 mm
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1)
= ( 685.8000 - 25.4 )/( 4 - 1 ) = 220.1333 mm
Baseplate Pressure Area [Ap]: = e * Bpwid / 2
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Horizontal Vessel Analysis (Test) : Step: 17 9:50a Jul 11,2013
= 220.1333 * 101.6000/2 = 11182.7734 mm²
Axial Load [P]: = Ap * Bp
= 11182.8 * 0.36 = 3972.6 N
Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 101.600 - 25.4 - 6.350 ) * 6.350 + 220.1333/2 * 6.350
= 1142.471 mm²
Compressive Stress [Sc]: = P/Ar
= 3972.6/1142.4708 = 3.4775 MPa
Check of Outside Ribs:Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay² Io
Rib 50.8 524.2 26629.0 0.0 371789.7
Web 50.8 698.9 35505.3 0.0 4697.1
Values 50.8 1223.1 62134.3 0.0 376486.7
Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2
= 64.2/( 2 * 685.80 ) * 220.133 * 382.35/2
= 1970.065 N-mm
KL/R < Cc ( 21.0624 < 128.2550 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 21.06 )²/(2 * 128.25² )) * 239/
( 5/3+3*(21.06 )/(8* 128.25 )-( 21.06³)/(8*128.25³)
Sca = 137.01 MPa
AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba
Check = 3.48/137.01 + (1970.06/7411.156 )/159.96
Check = 0.03
Check of Inside RibsInertia of Saddle, Inner Ribs - Axial Direction
Y A AY Ay² Io
Rib 38.1 443.5 16899.2 0.0 234129.9
Web 38.1 1397.8 53258.0 0.0 4697.1
Values 38.1 1841.4 70157.1 0.0 238827.0
KL/R < Cc ( 19.9810 < 128.2550 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 19.98 )²/(2 * 128.25² )) * 239/
( 5/3+3*(19.98 )/(8* 128.25 )-( 19.98³)/(8*128.25³)
Sca = 137.44 MPa
AISC Unity Check on Inside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba
Check = 4.32/137.44 + ( 2344.96/6268.425 )/159.96
Check = 0.03
Input Data for Base Plate Bolting Calculations:
Total Number of Bolts per BasePlate Nbolts 2
Total Number of Bolts in Tension/Baseplate Nbt 1
Bolt Material Specification SA-193 B7
Bolt Allowable Stress Stba 172.38 MPa
Bolt Corrosion Allowance Bca 0.0000 mm
Distance from Bolts to Edge Edgedis 101.6000 mm
Nominal Bolt Diameter Bnd 25.4000 mm
Thread Series Series TEMA
BasePlate Allowable Stress S 95.15 MPa
Area Available in a Single Bolt BltArea 355.4832 mm²
Saddle Load QO (Weight) QO 24210.4 N
Saddle Load QL (Wind/Seismic contribution) QL 16.1 N
Maximum Transverse Force Ft 260.3 N
Maximum Longitudinal Force Fl 64.2 N
Saddle Bolted to Steel Foundation No
Bolt Area Calculation per Dennis R. Moss
Bolt Area Requirement Due to Longitudinal Load [Bltarearl]: = 0.0 (QO > QL --> No Uplift in Longitudinal direction)
Bolt Area due to Shear Load [Bltarears]: = Fl / (Stba * Nbolts)
= 64.18/(172.38 * 2.00 )
= 0.1862 mm²
Bolt Area due to Transverse Load
Moment on Baseplate Due to Transverse Load [Rmom]: = B * Ft + Sum of X Moments
= 609.60 * 260.29 + 0.00
= 158734.66 N-mm
Eccentricity (e):
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 49 of 94
Horizontal Vessel Analysis (Test) : Step: 17 9:50a Jul 11,2013
= Rmom / QO
= 158734.66/24210.43
= 6.55 mm < Bplen/6 --> No Uplift in Transverse direction
Bolt Area due to Transverse Load [Bltareart]: = 0 (No Uplift)
Required of a Single Bolt [Bltarear] = max[Bltarearl, Bltarears, Bltareart]
= max[0.0000 , 0.1862 , 0.0000 ]
= 0.1862 mm²
ASME Horizontal Vessel Analysis: Stresses for the Right Saddle(per ASME Sec. VIII Div. 2 based on the Zick method.)
Note: Wear Pad Width (152.40) is less than 1.56*sqrt(rm*t)and less than 2a. The wear plate will be ignored.
Minimum Wear Plate Width to be considered in analysis [b1]: = min( b + 1.56*sqrt( Rm * t ), 2a )
= min( 101.600 + 1.56*sqrt( 322.5000 * 10.0000 ), 2 * 209.550 )
= 190.1910 mm
Input and Calculated Values:
Vessel Mean Radius Rm 322.50 mm
Stiffened Vessel Length per 4.15.6 L 3625.00 mm
Distance from Saddle to Vessel tangent a 209.55 mm
Saddle Width b 101.60 mm
Saddle Bearing Angle theta 120.00 degrees
Shell Allowable Stress used in Calculation 137.90 MPa
Head Allowable Stress used in Calculation 137.90 MPa
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
Saddle Force Q, Test Case, no Ext. Forces 26007.74 N
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 38.44 137.90 MPa
Long. Stress at Bottom of Midspan 49.76 137.90 MPa
Long. Stress at Top of Saddles 43.94 137.90 MPa
Long. Stress at Bottom of Saddles 44.20 137.90 MPa
Tangential Shear in Shell 8.35 110.32 MPa
Circ. Stress at Horn of Saddle 13.21 172.38 MPa
Circ. Compressive Stress in Shell 1.04 137.90 MPa
Intermediate Results: Saddle Reaction Q due to Wind or Seismic
Saddle Reaction Force due to Wind Ft [Fwt]: = Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 520.6/2 + 0 ) * 609.6000/558.5864
= 852.2 N
Saddle Reaction Force due to Wind Fl or Friction [Fwl]: = Max( Fl, Friction Load, Sum of X Forces) * B / Ls
= Max( 194.49 , 0.00 , 0 ) * 609.6000/2425.0002
= 16.1 N
Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 25155 + Max( 16 , 852 , 0 , 0 )
= 26007.7 N
Summary of Loads at the base of this Saddle: Vertical Load (including saddle weight) 26318.06 N
Transverse Shear Load Saddle 260.29 N
Longitudinal Shear Load Saddle 64.18 N
Hydrostatic Test Pressure at center of Vessel: 2.735 MPa
Formulas and Substitutions for Horizontal Vessel Analysis:
Note: Wear Plate is Welded to the Shell, k = 0.1
The Computed K values from Table 4.15.1: K1 = 0.1066 K2 = 1.1707 K3 = 0.8799 K4 = 0.4011
K5 = 0.7603 K6 = 0.0529 K7 = 0.0251 K8 = 0.3405
K9 = 0.2711 K10 = 0.0581 K1* = 0.1923
Note: Dimension a is greater than or equal to Rm / 2.
Moment per Equation 4.15.3 [M1]: = -Q*a [1 - (1- a/L + (R²-h2²)/(2a*L))/(1+(4h2)/3L)]
= -26007*209.55[1-(1-209.55/3625.00+(322.500²-0.000²)/
(2*209.55*3625.00))/(1+(4*0.00)/(3*3625.00))]
= 58079.4 N-mm
Moment per Equation 4.15.4 [M2]: = Q*L/4(1+2(R²-h2²)/(L²))/(1+(4h2)/( 3L))-4a/L
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Horizontal Vessel Analysis (Test) : Step: 17 9:50a Jul 11,2013
= 26007*3625/4(1+2(322²-0²)/(3625²))/(1+(4*0)/
(3*3625))-4*209/3625
= 18500192.0 N-mm
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]: = P * Rm/(2t) - M2/(pi*Rm²t)
= 2.74 * 322.500/(2*10.000 ) - 18500192/(pi*322.5²*10.000 )
= 38.44 MPa
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]: = P * Rm/(2t) + M2/(pi * Rm² * t)
= 2.74 * 322.500/(2 * 10.000 ) + 18500192/(pi * 322.5² * 10.000 )
= 49.76 MPa
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]: = P * Rm/(2t) - M1/(K1*pi*Rm²t)
= 2.74*322.500/(2*10.000)-58079.4/(0.1066*pi*322.5²*10.000)
= 43.94 MPa
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]: = P * Rm/(2t) + M1/(K1* * pi * Rm² * t)
= 2.74*322.500/(2*10.000)+58079.4/(0.1923*pi*322.5²*10.000)
= 44.20 MPa
Maximum Shear Force in the Saddle (4.15.5) [T]: = Q(L-2a)/(L+(4*h2/3))
= 26007 ( 3625.00 - 2 * 209.55 )/(3625.00 + ( 4 * 0.00/3))
= 23000.9 N
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]: = K2 * T / ( Rm * t )
= 1.1707 * 23000.89/( 322.5000 * 10.0000 )
= 8.35 MPa
Decay Length (4.15.22) [x1,x2]: = 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 322.500 * 10.000 )
= 44.295 mm
Circumferential Stress in shell, no rings (4.15.23) [sigma6]: = -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7603 * 26007 * 0.1/( 10.000 * ( 101.60 + 44.30 + 44.30 ) )
= -1.04 MPa
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.24) [sigma7]: = -Q/(4*t*(b+X1+X2)) - 3*K7*Q/(2*t²)
= -26007/(4*10.000 *(101.600 +44.295 +44.295 )) -
3*0.0251 *26007/(2*10.000²)
= -13.21 MPa
Effective reinforcing plate width (4.15.1) [B1]: = min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 101.60 + 1.56 * sqrt( 322.500 * 10.000 ), 2 * 209.550 )
= 190.19 mm
Results for Vessel Ribs, Web and Base
Baseplate Length Bplen 685.8000 mm
Baseplate Thickness Bpthk 12.7000 mm
Baseplate Width Bpwid 101.6000 mm
Number of Ribs ( inc. outside ribs ) Nribs 4
Rib Thickness Ribtk 6.3500 mm
Web Thickness Webtk 6.3500 mm
Web Location Webloc Center
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 5. 2403. 12015. 80100.
Wearplate 15. 1452. 21429. 327326.
Web 118. 1247. 146785. 21285732.
BasePlate 222. 1290. 286774. 63752716.
Totals 360. 6392. 467003. 85445872.
Value C1 = Sumof(Ay)/Sumof(A) = 73. mm
Value I = Sumof(Io) - C1*Sumof(Ay) = 51325968. mm**4
Value As = Sumof(A) - Ashell = 3989. mm²
K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035
Fh = K1 * Q = 0.2035 * 26007.742 = 5293.1401 N
Tension Stress, St = ( Fh/As ) = 1.3271 MPa
Allowed Stress, Sa = 0.6 * Yield Str = 143.9676 MPa
d = B - R*Sin(theta) / theta = 283.5296 mm
Bending Moment, M = Fh * d = 1501370.3750 N-mm
Bending Stress, Sb = ( M * C1 / I ) = 2.1365 MPa
Allowed Stress, Sa = 2/3 * Yield Str = 159.9640 MPa
Minimum Thickness of Baseplate per Moss : = ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 4 * BasePlateLength *
AllStress ))½
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FileName : Floating Head HE ------------------------------ Page 51 of 94
Horizontal Vessel Analysis (Test) : Step: 17 9:50a Jul 11,2013
= ( 3 * (26007 + 310 ) * 101.60/( 4 * 685.800 * 159.964 ))½
= 4.276 mm
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1)
= ( 685.8000 - 25.4 )/( 4 - 1 ) = 220.1333 mm
Baseplate Pressure Area [Ap]: = e * Bpwid / 2
= 220.1333 * 101.6000/2 = 11182.7734 mm²
Axial Load [P]: = Ap * Bp
= 11182.8 * 0.37 = 4174.1 N
Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 101.600 - 25.4 - 6.350 ) * 6.350 + 220.1333/2 * 6.350
= 1142.471 mm²
Compressive Stress [Sc]: = P/Ar
= 4174.1/1142.4708 = 3.6539 MPa
Check of Outside Ribs:Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay² Io
Rib 50.8 524.2 26629.0 0.0 371789.7
Web 50.8 698.9 35505.3 0.0 4697.1
Values 50.8 1223.1 62134.3 0.0 376486.7
Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2
= 64.2/( 2 * 685.80 ) * 220.133 * 382.35/2
= 1970.065 N-mm
KL/R < Cc ( 21.0624 < 128.2550 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 21.06 )²/(2 * 128.25² )) * 239/
( 5/3+3*(21.06 )/(8* 128.25 )-( 21.06³)/(8*128.25³)
Sca = 137.01 MPa
AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba
Check = 3.65/137.01 + (1970.06/7411.156 )/159.96
Check = 0.03
Check of Inside RibsInertia of Saddle, Inner Ribs - Axial Direction
Y A AY Ay² Io
Rib 38.1 443.5 16899.2 0.0 234129.9
Web 38.1 1397.8 53258.0 0.0 4697.1
Values 38.1 1841.4 70157.1 0.0 238827.0
KL/R < Cc ( 19.9810 < 128.2550 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 19.98 )²/(2 * 128.25² )) * 239/
( 5/3+3*(19.98 )/(8* 128.25 )-( 19.98³)/(8*128.25³)
Sca = 137.44 MPa
AISC Unity Check on Inside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba
Check = 4.53/137.44 + ( 2344.96/6268.425 )/159.96
Check = 0.04
Input Data for Base Plate Bolting Calculations:
Total Number of Bolts per BasePlate Nbolts 2
Total Number of Bolts in Tension/Baseplate Nbt 1
Bolt Material Specification SA-193 B7
Bolt Allowable Stress Stba 172.38 MPa
Bolt Corrosion Allowance Bca 0.0000 mm
Distance from Bolts to Edge Edgedis 101.6000 mm
Nominal Bolt Diameter Bnd 25.4000 mm
Thread Series Series TEMA
BasePlate Allowable Stress S 95.15 MPa
Area Available in a Single Bolt BltArea 355.4832 mm²
Saddle Load QO (Weight) QO 25465.9 N
Saddle Load QL (Wind/Seismic contribution) QL 16.1 N
Maximum Transverse Force Ft 260.3 N
Maximum Longitudinal Force Fl 64.2 N
Saddle Bolted to Steel Foundation No
Bolt Area Calculation per Dennis R. Moss
Bolt Area Requirement Due to Longitudinal Load [Bltarearl]: = 0.0 (QO > QL --> No Uplift in Longitudinal direction)
Bolt Area due to Shear Load [Bltarears]: = Fl / (Stba * Nbolts)
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FileName : Floating Head HE ------------------------------ Page 52 of 94
Horizontal Vessel Analysis (Test) : Step: 17 9:50a Jul 11,2013
= 64.18/(172.38 * 2.00 )
= 0.1862 mm²
Bolt Area due to Transverse Load
Moment on Baseplate Due to Transverse Load [Rmom]: = B * Ft + Sum of X Moments
= 609.60 * 260.29 + 0.00
= 158734.66 N-mm
Eccentricity (e): = Rmom / QO
= 158734.66/25465.89
= 6.23 mm < Bplen/6 --> No Uplift in Transverse direction
Bolt Area due to Transverse Load [Bltareart]: = 0 (No Uplift)
Required of a Single Bolt [Bltarear] = max[Bltarearl, Bltarears, Bltareart]
= max[0.0000 , 0.1862 , 0.0000 ]
= 0.1862 mm²
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 53 of 94
Nozzle Calcs. : T1 Nozl: 6 9:50a Jul 11,2013
INPUT VALUES, Nozzle Description: T1 From : 30
Pressure for Reinforcement Calculations P 0.5000 MPa
Temperature for Internal Pressure Temp 15 C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 100 C
Shell Material SA-516 70
Shell Allowable Stress at Temperature S 137.90 MPa
Shell Allowable Stress At Ambient Sa 137.90 MPa
Inside Diameter of Cylindrical Shell D 635.00 mm
Design Length of Section L 650.0000 mm
Shell Finished (Minimum) Thickness t 10.0000 mm
Shell Internal Corrosion Allowance c 3.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Physical Maximum for Diameter Limit Dmax 500.0000 mm
Physical Maximum for Thickness Limit Tmax 0.0000 mm
Distance from Bottom/Left Tangent 415.0000 mm
User Entered Minimum Design Metal Temperature 0.00 C
Type of Element Connected to the Shell : Nozzle
Material SA-106 B
Material UNS Number K03006
Material Specification/Type Smls. pipe
Allowable Stress at Temperature Sn 117.90 MPa
Allowable Stress At Ambient Sna 117.90 MPa
Diameter Basis (for tr calc only) ID
Layout Angle -45.00 deg
Diameter 300.0000 mm.
Size and Thickness Basis Nominal
Nominal Thickness tn 40
Flange Material SA-105
Flange Type Weld Neck Flange
Corrosion Allowance can 3.0000 mm
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 200.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 9.5250 mm
Groove weld depth between Nozzle and Vessel Wgnv 6.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
Pad Material SA-516 70
Pad Allowable Stress at Temperature Sp 137.90 MPa
Pad Allowable Stress At Ambient Spa 137.90 MPa
Diameter of Pad along vessel surface Dp 523.8500 mm
Thickness of Pad te 10.0000 mm
Weld leg size between Pad and Shell Wp 10.0000 mm
Groove weld depth between Pad and Nozzle Wgpn 10.0000 mm
Reinforcing Pad Width 100.0000 mm
ASME Code Weld Type per UW-16 None
Class of attached Flange 300
Grade of attached Flange GR 1.1
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration) | |
| |
| |
| |
__________/| |
____/|__________\| |
| \ | |
| \ | |
|________________\|__|
Insert Nozzle With Pad, no Inside projection
Reinforcement CALCULATION, Description: T1
ASME Code, Section VIII, Division 1, 2010, 2011a, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 303.225 mm.
Actual Thickness Used in Calculation 10.312 mm
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (0.50*320.5000)/(137*1.00-0.6*0.50)
= 1.1646 mm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 54 of 94
Nozzle Calcs. : T1 Nozl: 6 9:50a Jul 11,2013
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (0.50*154.61)/(117*1.00-0.6*0.50)
= 0.6573 mm
Required Nozzle thickness under External Pressure per UG-28 : 0.8481 mm
UG-40, Limits of Reinforcement : [External Pressure] Parallel to Vessel Wall (Diameter Limit) Dl 500.0000 mm
Parallel to Vessel Wall, opening length d 250.0000 mm
Normal to Vessel Wall (Thickness Limit), pad side Tlwp 17.5000 mm
Note : The Pad diameter is greater than the Diameter Limit, theexcess will not be considered .
Weld Strength Reduction Factor [fr1]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr2]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr4]: = min( 1, Sp/S )
= min( 1, 137.9/137.9 )
= 1.000
Weld Strength Reduction Factor [fr3]: = min( fr2, fr4 )
= min( 0.9 , 1.0 )
= 0.855
Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc
Area Required Ar NA 325.504 NA mm²
Area in Shell A1 NA 926.113 NA mm²
Area in Nozzle Wall A2 NA 193.443 NA mm²
Area in Inward Nozzle A3 NA 0.000 NA mm²
Area in Welds A41+A42+A43 NA 74.064 NA mm²
Area in Element A5 NA 1321.125 NA mm²
TOTAL AREA AVAILABLE Atot NA 2514.745 NA mm²
Nozzle Angle Used in Area Calculations 90.00 Degs.
The area available without a pad is Sufficient.The area available with the given pad is Sufficient.
Area Required [A]: = 0.5( d * tr*F + 2 * tn * tr*F * (1-fr1) ) per UG-37(d) or UG-39
= 0.5(309.2252*2.0909*1+2*7.3124*2.0909*1*(1-0.86))
= 325.504 mm²
Reinforcement Areas per Figure UG-37.1
Area Available in Shell [A1]: = d( E1*t - F*tr ) - 2 * tn( E1*t - F*tr ) * ( 1 - fr1 )
= 190.775 ( 1.00 * 7.0000 - 1.0 * 2.091 ) - 2 * 7.312
( 1.00 * 7.0000 - 1.0 * 2.0909 ) * ( 1 - 0.855 )
= 926.113 mm²
Area Available in Nozzle Wall Projecting Outward [A2]: = ( 2 * Tlwp ) * ( tn - trn ) * fr2
= ( 2 * 17.50 ) * ( 7.31 - 0.85 ) * 0.8550
= 193.443 mm²
Area Available in Welds [A41 + A42 + A43]: = (Wo² - Ar Lost)*Fr3+((Wi-can/0.707)² - Ar Lost)*fr2 + Wp²*fr4
= (86.6250 ) * 0.86 + (0.0000 ) * 0.86 + 0.0000² * 1.00
= 74.064 mm²
Area Available in Element [A5]: = (min(Dp,DL)-(Nozzle OD))*(min(tp,Tlwp,te))*fr4
= ( 500.0000 - 323.8500 ) * 10.0000 * 1.0000
= 1321.125 mm²
Note: Per user request, A5 multiplied by 0.75, see UG-37(h).
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness for Internal/External pressures ta = 3.8481 mm
Wall Thickness per UG16(b), tr16b = 4.5000 mm
Wall Thickness, shell/head, internal pressure trb1 = 4.1646 mm
Wall Thickness tb1 = max(trb1, tr16b) = 4.5000 mm
Wall Thickness tb2 = max(trb2, tr16b) = 4.5000 mm
Wall Thickness per table UG-45 tb3 = 11.3312 mm
Determine Nozzle Thickness candidate [tb]: = min[ tb3, max( tb1,tb2) ]
= min[ 11.331 , max( 4.500 , 4.500 ) ]
= 4.5000 mm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 55 of 94
Nozzle Calcs. : T1 Nozl: 6 9:50a Jul 11,2013
Minimum Wall Thickness of Nozzle Necks [tUG-45]: = max( ta, tb )
= max( 3.8481 , 4.5000 )
= 4.5000 mm
Available Nozzle Neck Thickness = 0.875 * 10.312 = 9.023 mm --> OK
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
MDMT of the Nozzle Neck to Flange Weld, ���Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.023 , tr = 0.657 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.109 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle Neck to Pad Weld for the Nozzle, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.023 , tr = 0.657 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.109 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle Neck to Pad Weld for Reinforcement pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.023 , tr = 0.657 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.109 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Shell to Pad Weld at Pad OD for pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 10.000 , tr = 1.165 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.166 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle-Shell/Head Weld for the Nozzle (UCS-66(a)1(b)), ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.023 , tr = 0.657 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.109 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
Governing MDMT of the Nozzle : -104 C
Governing MDMT of the Reinforcement Pad : -104 C
Governing MDMT of all the sub-joints of this Junction : -104 C
ANSI Flange MDMT including Temperature reduction per UCS-66.1:
Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -29 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(b) -104 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(c) -104 C
Where the Stress Reduction Ratio per UCS-66(b)(1)(b) is : Design Pressure/Ambient Rating = 0.50/5.11 = 0.098
Note: Using the minimum value from (b)(1)(b) and (b)(1)(c) aboveas the calculated nozzle flange MDMT.
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]: = thickness - corrosion allowance
= 10.312 - 3.000
= 7.312 mm
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 635.000/2 + 3.000
= 320.500 mm
Effective Length of Vessel Wall [LR]:Note : Pad Thk >= 0.5T and Pad Width < 8(Shell Thk + Pad Thk)
= 10 * t
= 10 * 7.000
= 70.000 mm
Thickness Limit Candidate [LH1]: = t + 0.78 * sqrt( Rn * tn )
= 7.000 + 0.78 * sqrt( 154.613 * 7.312 )
= 33.227 mm
Thickness Limit Candidate [LH2]: = Lpr1 + T
= 200.000 + 7.000
= 207.000 mm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 56 of 94
Nozzle Calcs. : T1 Nozl: 6 9:50a Jul 11,2013
Thickness Limit Candidate [LH3]: = 8( t + te )
= 8( 7.000 + 10.000 )
= 136.000 mm
Effective Nozzle Wall Length Outside the Vessel [LH]: = min[ LH1, LH2, LH3 ]
= min[ 33.227 , 207.000 , 136.000 )
= 33.227 mm
Effective Vessel Thickness [teff]: = t
= 7.000 mm
Determine Parameter [Lamda]: = min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (309.23 + 7.312 )/( sqrt((641.00 + 7.000 ) * 7.000 )) )
= 4.700
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR * max( Lamda/4, 1 )
= 7.000 * 70.000 * max( 4.700/4, 1 )
= 575.738 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 7.312 * 33.227
= 242.968 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2)
= 0.5 * 9.525^(2)
= 45.363 mm²
Area Contributed by the Reinforcing Pad [A5]: = min( W * te , LR * te )
= min( 100.000 * 10.000 , 70.000 * 10.000 )
= 700.000 mm²
The total area contributed by A1 through A5 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )
= 575.738+1.000(242.968+0.000)+45.363+0.000+0.000+1.000(700.000)
= 1564.069 mm²
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 137.900 * 1.000
= 206.9 MPa
Determine Force acting on the Nozzle [fN]: = P * Rn( LH - t )
= 0.500 * 154.613 ( 33.227 - 7.000 )
= 2027.3 N
Determine Force acting on the Shell [fS]: = P * Reff * ( LR + tn )
= 0.500 * 320.500 * ( 70.000 + 7.312 )
= 12388.3 N
Discontinuity Force from Internal Pressure [fY]: = P * Reff * Rnc
= 0.500 * 320.500 * 154.613
= 24774.6 N
Area Resisting Internal Pressure [Ap]: = Rn( LH - t ) + Reff( LR + tn + Rnc )
= 154.613 ( 33.227 - 7.000 ) + 320.500 ( 70.000 + 7.312 + 154.613 )
= 78387.0 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/teff )
= 206.850/( 2 * 78386.969/1564.069 - 320.500/7.000 )
= 3.8 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = S[t/Reff]
= 137.900 [7.000/320.500 ]
= 3.0 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 3.799 , 3.012 )
= 3.012 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 2027.332 + 12388.258 + 24774.562 )/1564.069
= 25.059 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Reff / teff
= 0.500 * 320.500/7.000
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 57 of 94
Nozzle Calcs. : T1 Nozl: 6 9:50a Jul 11,2013
= 22.9 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 25.059 - 22.893 , 22.893 )
= 27.2 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 206.85 MPa
Local Primary Membrane Stress PL 27.22 MPa
Maximum Allowable Working Pressure Pmax 3.01 MPa
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 154.613 + 7.312 )/154.613
= 1.047 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 154.613 + 7.312 )
= 254.351 mm
Weld Length of Pad to Shell Weld [LtauP]: = pi/2 * ( Rn + tn + W )
= pi/2 * ( 154.613 + 7.312 + 100.000 )
= 411.431 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 6.735, 7.071, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(24774*1.05,1.5*117.9(242.968+0.000),pi/4*0.5*154.61^2*1.05^2)
= 10295.579 N
Discontinuity Force [fws]: = fwelds * t * S/( t * S + te * Sp )
= 10295.6*7.00*137/(7.000*137+10.000*137)
= 4239.356 N
Discontinuity Force [fwp]: = fwelds * te * Sp / ( t * S + te * Sp )
= 10295.6*10.00*137/(7.000*137+10.000*137)
= 6056.223 N
Shear Stress [tau1]: = fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )
= 4239.356/( 254.351 * ( 0.6 * 6.000 + 0.49 * 0.000 ) )
= 4.630 MPa
Shear Stress [tau2]: = fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )
= 6056.223/( 254.351 * ( 0.6 * 10.000 + 0.49 * 6.735 ) )
= 2.560 MPa
Shear Stress [tau3]: = fwp / ( Ltau * ( 0.49 * L42T ) )
= 6056.223/( 411.431 * ( 0.49 * 7.071 ) )
= 4.249 MPa
Maximum Shear Stress in the Welds: = max( tau1, tau2, tau3 )
= max( 4.630 , 2.560 , 4.249 )
= 4.6 must be less than or equal to 137.9 MPa
Weld Size Calculations, Description: T1
Intermediate Calc. for nozzle/shell Welds Tmin 7.3124 mm
Intermediate Calc. for pad/shell Welds TminPad 7.0000 mm
Results Per UW-16.1: Required Thickness Actual Thickness
Nozzle Weld 5.1187 = 0.7 * tmin. 6.7342 = 0.7 * Wo mm
Pad Weld 3.5000 = 0.5*TminPad 7.0700 = 0.7 * Wp mm
Maximum Allowable Pressure for this Nozzle at this Location: Converged Max. Allow. Pressure in Operating case 2.5270 MPa
Note: The MAWP of this junction was limited by the parent Shell/Head.
Nozzle is O.K. for the External Pressure 0.103 MPa
The Drop for this Nozzle is : 44.3946 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 254.3946 mm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 58 of 94
Nozzle Calcs. : T2 Nozl: 7 9:50a Jul 11,2013
INPUT VALUES, Nozzle Description: T2 From : 30
Pressure for Reinforcement Calculations P 0.5000 MPa
Temperature for Internal Pressure Temp 15 C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 100 C
Shell Material SA-516 70
Shell Allowable Stress at Temperature S 137.90 MPa
Shell Allowable Stress At Ambient Sa 137.90 MPa
Inside Diameter of Cylindrical Shell D 635.00 mm
Design Length of Section L 650.0000 mm
Shell Finished (Minimum) Thickness t 10.0000 mm
Shell Internal Corrosion Allowance c 3.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Physical Maximum for Diameter Limit Dmax 500.0000 mm
Physical Maximum for Thickness Limit Tmax 0.0000 mm
Distance from Bottom/Left Tangent 415.0000 mm
User Entered Minimum Design Metal Temperature 0.00 C
Type of Element Connected to the Shell : Nozzle
Material SA-106 B
Material UNS Number K03006
Material Specification/Type Smls. pipe
Allowable Stress at Temperature Sn 117.90 MPa
Allowable Stress At Ambient Sna 117.90 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 225.00 deg
Diameter 300.0000 mm.
Size and Thickness Basis Nominal
Nominal Thickness tn 40
Flange Material SA-105
Flange Type Weld Neck Flange
Corrosion Allowance can 3.0000 mm
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 200.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 9.5250 mm
Groove weld depth between Nozzle and Vessel Wgnv 6.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
Pad Material SA-516 70
Pad Allowable Stress at Temperature Sp 137.90 MPa
Pad Allowable Stress At Ambient Spa 137.90 MPa
Diameter of Pad along vessel surface Dp 523.8500 mm
Thickness of Pad te 10.0000 mm
Weld leg size between Pad and Shell Wp 10.0000 mm
Groove weld depth between Pad and Nozzle Wgpn 10.0000 mm
Reinforcing Pad Width 100.0000 mm
ASME Code Weld Type per UW-16 None
Class of attached Flange 300
Grade of attached Flange GR 1.1
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration) | |
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Insert Nozzle With Pad, no Inside projection
Reinforcement CALCULATION, Description: T2
ASME Code, Section VIII, Division 1, 2010, 2011a, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 303.225 mm.
Actual Thickness Used in Calculation 10.312 mm
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (0.50*320.5000)/(137*1.00-0.6*0.50)
= 1.1646 mm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 59 of 94
Nozzle Calcs. : T2 Nozl: 7 9:50a Jul 11,2013
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (0.50*154.61)/(117*1.00-0.6*0.50)
= 0.6573 mm
Required Nozzle thickness under External Pressure per UG-28 : 0.8481 mm
UG-40, Limits of Reinforcement : [External Pressure] Parallel to Vessel Wall (Diameter Limit) Dl 500.0000 mm
Parallel to Vessel Wall, opening length d 250.0000 mm
Normal to Vessel Wall (Thickness Limit), pad side Tlwp 17.5000 mm
Note : The Pad diameter is greater than the Diameter Limit, theexcess will not be considered .
Weld Strength Reduction Factor [fr1]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr2]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr4]: = min( 1, Sp/S )
= min( 1, 137.9/137.9 )
= 1.000
Weld Strength Reduction Factor [fr3]: = min( fr2, fr4 )
= min( 0.9 , 1.0 )
= 0.855
Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc
Area Required Ar NA 325.504 NA mm²
Area in Shell A1 NA 926.113 NA mm²
Area in Nozzle Wall A2 NA 193.443 NA mm²
Area in Inward Nozzle A3 NA 0.000 NA mm²
Area in Welds A41+A42+A43 NA 74.064 NA mm²
Area in Element A5 NA 1321.125 NA mm²
TOTAL AREA AVAILABLE Atot NA 2514.745 NA mm²
Nozzle Angle Used in Area Calculations 90.00 Degs.
The area available without a pad is Sufficient.The area available with the given pad is Sufficient.
Area Required [A]: = 0.5( d * tr*F + 2 * tn * tr*F * (1-fr1) ) per UG-37(d) or UG-39
= 0.5(309.2252*2.0909*1+2*7.3124*2.0909*1*(1-0.86))
= 325.504 mm²
Reinforcement Areas per Figure UG-37.1
Area Available in Shell [A1]: = d( E1*t - F*tr ) - 2 * tn( E1*t - F*tr ) * ( 1 - fr1 )
= 190.775 ( 1.00 * 7.0000 - 1.0 * 2.091 ) - 2 * 7.312
( 1.00 * 7.0000 - 1.0 * 2.0909 ) * ( 1 - 0.855 )
= 926.113 mm²
Area Available in Nozzle Wall Projecting Outward [A2]: = ( 2 * Tlwp ) * ( tn - trn ) * fr2
= ( 2 * 17.50 ) * ( 7.31 - 0.85 ) * 0.8550
= 193.443 mm²
Area Available in Welds [A41 + A42 + A43]: = (Wo² - Ar Lost)*Fr3+((Wi-can/0.707)² - Ar Lost)*fr2 + Wp²*fr4
= (86.6250 ) * 0.86 + (0.0000 ) * 0.86 + 0.0000² * 1.00
= 74.064 mm²
Area Available in Element [A5]: = (min(Dp,DL)-(Nozzle OD))*(min(tp,Tlwp,te))*fr4
= ( 500.0000 - 323.8500 ) * 10.0000 * 1.0000
= 1321.125 mm²
Note: Per user request, A5 multiplied by 0.75, see UG-37(h).
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness for Internal/External pressures ta = 3.8481 mm
Wall Thickness per UG16(b), tr16b = 4.5000 mm
Wall Thickness, shell/head, internal pressure trb1 = 4.1646 mm
Wall Thickness tb1 = max(trb1, tr16b) = 4.5000 mm
Wall Thickness tb2 = max(trb2, tr16b) = 4.5000 mm
Wall Thickness per table UG-45 tb3 = 11.3312 mm
Determine Nozzle Thickness candidate [tb]: = min[ tb3, max( tb1,tb2) ]
= min[ 11.331 , max( 4.500 , 4.500 ) ]
= 4.5000 mm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 60 of 94
Nozzle Calcs. : T2 Nozl: 7 9:50a Jul 11,2013
Minimum Wall Thickness of Nozzle Necks [tUG-45]: = max( ta, tb )
= max( 3.8481 , 4.5000 )
= 4.5000 mm
Available Nozzle Neck Thickness = 0.875 * 10.312 = 9.023 mm --> OK
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
MDMT of the Nozzle Neck to Flange Weld, ���Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.023 , tr = 0.657 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.109 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle Neck to Pad Weld for the Nozzle, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.023 , tr = 0.657 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.109 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle Neck to Pad Weld for Reinforcement pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.023 , tr = 0.657 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.109 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Shell to Pad Weld at Pad OD for pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 10.000 , tr = 1.165 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.166 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle-Shell/Head Weld for the Nozzle (UCS-66(a)1(b)), ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.023 , tr = 0.657 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.109 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
Governing MDMT of the Nozzle : -104 C
Governing MDMT of the Reinforcement Pad : -104 C
Governing MDMT of all the sub-joints of this Junction : -104 C
ANSI Flange MDMT including Temperature reduction per UCS-66.1:
Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -29 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(b) -104 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(c) -104 C
Where the Stress Reduction Ratio per UCS-66(b)(1)(b) is : Design Pressure/Ambient Rating = 0.50/5.11 = 0.098
Note: Using the minimum value from (b)(1)(b) and (b)(1)(c) aboveas the calculated nozzle flange MDMT.
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]: = thickness - corrosion allowance
= 10.312 - 3.000
= 7.312 mm
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 635.000/2 + 3.000
= 320.500 mm
Effective Length of Vessel Wall [LR]:Note : Pad Thk >= 0.5T and Pad Width < 8(Shell Thk + Pad Thk)
= 10 * t
= 10 * 7.000
= 70.000 mm
Thickness Limit Candidate [LH1]: = t + 0.78 * sqrt( Rn * tn )
= 7.000 + 0.78 * sqrt( 154.613 * 7.312 )
= 33.227 mm
Thickness Limit Candidate [LH2]: = Lpr1 + T
= 200.000 + 7.000
= 207.000 mm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 61 of 94
Nozzle Calcs. : T2 Nozl: 7 9:50a Jul 11,2013
Thickness Limit Candidate [LH3]: = 8( t + te )
= 8( 7.000 + 10.000 )
= 136.000 mm
Effective Nozzle Wall Length Outside the Vessel [LH]: = min[ LH1, LH2, LH3 ]
= min[ 33.227 , 207.000 , 136.000 )
= 33.227 mm
Effective Vessel Thickness [teff]: = t
= 7.000 mm
Determine Parameter [Lamda]: = min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (309.23 + 7.312 )/( sqrt((641.00 + 7.000 ) * 7.000 )) )
= 4.700
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR * max( Lamda/4, 1 )
= 7.000 * 70.000 * max( 4.700/4, 1 )
= 575.738 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 7.312 * 33.227
= 242.968 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2)
= 0.5 * 9.525^(2)
= 45.363 mm²
Area Contributed by the Reinforcing Pad [A5]: = min( W * te , LR * te )
= min( 100.000 * 10.000 , 70.000 * 10.000 )
= 700.000 mm²
The total area contributed by A1 through A5 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )
= 575.738+1.000(242.968+0.000)+45.363+0.000+0.000+1.000(700.000)
= 1564.069 mm²
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 137.900 * 1.000
= 206.9 MPa
Determine Force acting on the Nozzle [fN]: = P * Rn( LH - t )
= 0.500 * 154.613 ( 33.227 - 7.000 )
= 2027.3 N
Determine Force acting on the Shell [fS]: = P * Reff * ( LR + tn )
= 0.500 * 320.500 * ( 70.000 + 7.312 )
= 12388.3 N
Discontinuity Force from Internal Pressure [fY]: = P * Reff * Rnc
= 0.500 * 320.500 * 154.613
= 24774.6 N
Area Resisting Internal Pressure [Ap]: = Rn( LH - t ) + Reff( LR + tn + Rnc )
= 154.613 ( 33.227 - 7.000 ) + 320.500 ( 70.000 + 7.312 + 154.613 )
= 78387.0 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/teff )
= 206.850/( 2 * 78386.969/1564.069 - 320.500/7.000 )
= 3.8 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = S[t/Reff]
= 137.900 [7.000/320.500 ]
= 3.0 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 3.799 , 3.012 )
= 3.012 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 2027.332 + 12388.258 + 24774.562 )/1564.069
= 25.059 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Reff / teff
= 0.500 * 320.500/7.000
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 62 of 94
Nozzle Calcs. : T2 Nozl: 7 9:50a Jul 11,2013
= 22.9 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 25.059 - 22.893 , 22.893 )
= 27.2 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 206.85 MPa
Local Primary Membrane Stress PL 27.22 MPa
Maximum Allowable Working Pressure Pmax 3.01 MPa
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 154.613 + 7.312 )/154.613
= 1.047 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 154.613 + 7.312 )
= 254.351 mm
Weld Length of Pad to Shell Weld [LtauP]: = pi/2 * ( Rn + tn + W )
= pi/2 * ( 154.613 + 7.312 + 100.000 )
= 411.431 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 6.735, 7.071, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(24774*1.05,1.5*117.9(242.968+0.000),pi/4*0.5*154.61^2*1.05^2)
= 10295.579 N
Discontinuity Force [fws]: = fwelds * t * S/( t * S + te * Sp )
= 10295.6*7.00*137/(7.000*137+10.000*137)
= 4239.356 N
Discontinuity Force [fwp]: = fwelds * te * Sp / ( t * S + te * Sp )
= 10295.6*10.00*137/(7.000*137+10.000*137)
= 6056.223 N
Shear Stress [tau1]: = fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )
= 4239.356/( 254.351 * ( 0.6 * 6.000 + 0.49 * 0.000 ) )
= 4.630 MPa
Shear Stress [tau2]: = fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )
= 6056.223/( 254.351 * ( 0.6 * 10.000 + 0.49 * 6.735 ) )
= 2.560 MPa
Shear Stress [tau3]: = fwp / ( Ltau * ( 0.49 * L42T ) )
= 6056.223/( 411.431 * ( 0.49 * 7.071 ) )
= 4.249 MPa
Maximum Shear Stress in the Welds: = max( tau1, tau2, tau3 )
= max( 4.630 , 2.560 , 4.249 )
= 4.6 must be less than or equal to 137.9 MPa
Weld Size Calculations, Description: T2
Intermediate Calc. for nozzle/shell Welds Tmin 7.3124 mm
Intermediate Calc. for pad/shell Welds TminPad 7.0000 mm
Results Per UW-16.1: Required Thickness Actual Thickness
Nozzle Weld 5.1187 = 0.7 * tmin. 6.7342 = 0.7 * Wo mm
Pad Weld 3.5000 = 0.5*TminPad 7.0700 = 0.7 * Wp mm
Maximum Allowable Pressure for this Nozzle at this Location: Converged Max. Allow. Pressure in Operating case 2.5270 MPa
Note: The MAWP of this junction was limited by the parent Shell/Head.
Nozzle is O.K. for the External Pressure 0.103 MPa
The Drop for this Nozzle is : 44.3946 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 254.3946 mm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 63 of 94
Nozzle Calcs. : S1 Nozl: 8 9:50a Jul 11,2013
INPUT VALUES, Nozzle Description: S1 From : 60
Pressure for Reinforcement Calculations P 2.0000 MPa
Temperature for Internal Pressure Temp 100 C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 100 C
Shell Material SA-516 70
Shell Allowable Stress at Temperature S 137.90 MPa
Shell Allowable Stress At Ambient Sa 137.90 MPa
Inside Diameter of Cylindrical Shell D 635.00 mm
Design Length of Section L 3625.0005 mm
Shell Finished (Minimum) Thickness t 10.0000 mm
Shell Internal Corrosion Allowance c 3.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Distance from Bottom/Left Tangent 2652.0000 mm
User Entered Minimum Design Metal Temperature 0.00 C
Type of Element Connected to the Shell : Nozzle
Material SA-106 B
Material UNS Number K03006
Material Specification/Type Smls. pipe
Allowable Stress at Temperature Sn 117.90 MPa
Allowable Stress At Ambient Sna 117.90 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 270.00 deg
Diameter 200.0000 mm.
Size and Thickness Basis Nominal
Nominal Thickness tn 80
Flange Material SA-105
Flange Type Weld Neck Flange
Corrosion Allowance can 3.0000 mm
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 200.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 9.5250 mm
Groove weld depth between Nozzle and Vessel Wgnv 10.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
Pad Material SA-516 70
Pad Allowable Stress at Temperature Sp 137.90 MPa
Pad Allowable Stress At Ambient Spa 137.90 MPa
Diameter of Pad along vessel surface Dp 319.0000 mm
Thickness of Pad te 10.0000 mm
Weld leg size between Pad and Shell Wp 10.0000 mm
Groove weld depth between Pad and Nozzle Wgpn 10.0000 mm
Reinforcing Pad Width 49.9625 mm
ASME Code Weld Type per UW-16 None
Class of attached Flange 300
Grade of attached Flange GR 1.1
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration) | |
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Insert Nozzle With Pad, no Inside projection
Reinforcement CALCULATION, Description: S1
ASME Code, Section VIII, Division 1, 2010, 2011a, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 193.675 mm.
Actual Thickness Used in Calculation 12.700 mm
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (2.00*320.5000)/(137*1.00-0.6*2.00)
= 4.6891 mm
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 64 of 94
Nozzle Calcs. : S1 Nozl: 8 9:50a Jul 11,2013
= (2.00*99.84)/(117*1.00-0.6*2.00)
= 1.7109 mm
Required Nozzle thickness under External Pressure per UG-28 : 0.6739 mm
UG-40, Limits of Reinforcement : [External Pressure] Parallel to Vessel Wall (Diameter Limit) Dl 399.3500 mm
Parallel to Vessel Wall, opening length d 199.6750 mm
Normal to Vessel Wall (Thickness Limit), pad side Tlwp 17.5000 mm
Weld Strength Reduction Factor [fr1]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr2]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr4]: = min( 1, Sp/S )
= min( 1, 137.9/137.9 )
= 1.000
Weld Strength Reduction Factor [fr3]: = min( fr2, fr4 )
= min( 0.9 , 1.0 )
= 0.855
Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc
Area Required Ar NA 438.693 NA mm²
Area in Shell A1 NA 525.026 NA mm²
Area in Nozzle Wall A2 NA 270.105 NA mm²
Area in Inward Nozzle A3 NA 0.000 NA mm²
Area in Welds A41+A42+A43 NA 174.064 NA mm²
Area in Element A5 NA 749.438 NA mm²
TOTAL AREA AVAILABLE Atot NA 1718.633 NA mm²
Nozzle Angle Used in Area Calculations 90.00 Degs.
The area available without a pad is Sufficient.The area available with the given pad is Sufficient.
Area Required [A]: = 0.5( d * tr*F + 2 * tn * tr*F * (1-fr1) ) per UG-37(d) or UG-39
= 0.5(199.6750*4.3330*1+2*9.7000*4.3330*1*(1-0.86))
= 438.693 mm²
Reinforcement Areas per Figure UG-37.1
Area Available in Shell [A1]: = d( E1*t - F*tr ) - 2 * tn( E1*t - F*tr ) * ( 1 - fr1 )
= 199.675 ( 1.00 * 7.0000 - 1.0 * 4.333 ) - 2 * 9.700
( 1.00 * 7.0000 - 1.0 * 4.3330 ) * ( 1 - 0.855 )
= 525.026 mm²
Area Available in Nozzle Wall Projecting Outward [A2]: = ( 2 * Tlwp ) * ( tn - trn ) * fr2
= ( 2 * 17.50 ) * ( 9.70 - 0.67 ) * 0.8550
= 270.105 mm²
Area Available in Welds [A41 + A42 + A43]: = (Wo² - Ar Lost)*Fr3+((Wi-can/0.707)² - Ar Lost)*fr2 + Wp²*fr4
= (86.6250 ) * 0.86 + (0.0000 ) * 0.86 + 100.0000² * 1.00
= 174.064 mm²
Area Available in Element [A5]: = (min(Dp,DL)-(Nozzle OD))*(min(tp,Tlwp,te))*fr4
= ( 319.0000 - 219.0750 ) * 10.0000 * 1.0000
= 749.438 mm²
Note: Per user request, A5 multiplied by 0.75, see UG-37(h).
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness for Internal/External pressures ta = 4.7109 mm
Wall Thickness per UG16(b), tr16b = 4.5000 mm
Wall Thickness, shell/head, internal pressure trb1 = 7.6891 mm
Wall Thickness tb1 = max(trb1, tr16b) = 7.6891 mm
Wall Thickness tb2 = max(trb2, tr16b) = 4.5000 mm
Wall Thickness per table UG-45 tb3 = 10.1600 mm
Determine Nozzle Thickness candidate [tb]: = min[ tb3, max( tb1,tb2) ]
= min[ 10.160 , max( 7.689 , 4.500 ) ]
= 7.6891 mm
Minimum Wall Thickness of Nozzle Necks [tUG-45]: = max( ta, tb )
= max( 4.7109 , 7.6891 )
= 7.6891 mm
Available Nozzle Neck Thickness = 0.875 * 12.700 = 11.113 mm --> OK
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 65 of 94
Nozzle Calcs. : S1 Nozl: 8 9:50a Jul 11,2013
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
MDMT of the Nozzle Neck to Flange Weld, ���Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 11.113 , tr = 1.711 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.211 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -26 C
Min Metal Temp. at Required thickness (UCS 66.1) -103 C
Min Metal Temp. w/o impact per UG-20(f) -29 C
MDMT of Nozzle Neck to Pad Weld for the Nozzle, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 10.000 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.670 , Temp. Reduction = 18 CPad governing, Conservatively assuming Pad stress = Shell stress(Div. 1 L-9.3)
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -47 C
MDMT of Nozzle Neck to Pad Weld for Reinforcement pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 10.000 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.670 , Temp. Reduction = 18 CPad governing, Conservatively assuming Pad stress = Shell stress(Div. 1 L-9.3)
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -47 C
MDMT of Shell to Pad Weld at Pad OD for pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 10.000 , tr = 4.689 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.670 , Temp. Reduction = 18 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -47 C
MDMT of Nozzle-Shell/Head Weld for the Nozzle (UCS-66(a)1(b)), ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 10.000 , tr = 4.689 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.670 , Temp. Reduction = 18 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -47 C
Governing MDMT of the Nozzle : -47 C
Governing MDMT of the Reinforcement Pad : -47 C
Governing MDMT of all the sub-joints of this Junction : -47 C
ANSI Flange MDMT including Temperature reduction per UCS-66.1:
Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -29 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(b) -48 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(c) -104 C
Where the Stress Reduction Ratio per UCS-66(b)(1)(b) is : Design Pressure/Ambient Rating = 2.00/5.11 = 0.391
Note: Using the minimum value from (b)(1)(b) and (b)(1)(c) aboveas the calculated nozzle flange MDMT.
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]: = thickness - corrosion allowance
= 12.700 - 3.000
= 9.700 mm
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 635.000/2 + 3.000
= 320.500 mm
Effective Length of Vessel Wall [LR]:Note : Pad Thk >= 0.5T and Pad Width < 8(Shell Thk + Pad Thk)
= 10 * t
= 10 * 7.000
= 70.000 mm
Thickness Limit Candidate [LH1]: = t + 0.78 * sqrt( Rn * tn )
= 7.000 + 0.78 * sqrt( 99.837 * 9.700 )
= 31.273 mm
Thickness Limit Candidate [LH2]: = Lpr1 + T
= 200.000 + 7.000
= 207.000 mm
Thickness Limit Candidate [LH3]: = 8( t + te )
= 8( 7.000 + 10.000 )
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 66 of 94
Nozzle Calcs. : S1 Nozl: 8 9:50a Jul 11,2013
= 136.000 mm
Effective Nozzle Wall Length Outside the Vessel [LH]: = min[ LH1, LH2, LH3 ]
= min[ 31.273 , 207.000 , 136.000 )
= 31.273 mm
Effective Vessel Thickness [teff]: = t
= 7.000 mm
Determine Parameter [Lamda]: = min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (199.67 + 9.700 )/( sqrt((641.00 + 7.000 ) * 7.000 )) )
= 3.109
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR * max( Lamda/4, 1 )
= 7.000 * 70.000 * max( 3.109/4, 1 )
= 490.000 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 9.700 * 31.273
= 303.350 mm²
Area Contributed by the Pad Fillet Weld [A42]: = 0.5 * Leg42^(2)
= 0.5 * 10.000^(2)
= 50.000 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2)
= 0.5 * 9.525^(2)
= 45.363 mm²
Area Contributed by the Reinforcing Pad [A5]: = min( W * te , LR * te )
= min( 49.963 * 10.000 , 70.000 * 10.000 )
= 499.625 mm²
The total area contributed by A1 through A5 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )
= 490.000+1.000(303.350+0.000)+45.363+50.000+0.000+1.000(499.625)
= 1388.338 mm²
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 137.900 * 1.000
= 206.9 MPa
Determine Force acting on the Nozzle [fN]: = P * Rn( LH - t )
= 2.000 * 99.837 ( 31.273 - 7.000 )
= 4846.3 N
Determine Force acting on the Shell [fS]: = P * Reff * ( LR + tn )
= 2.000 * 320.500 * ( 70.000 + 9.700 )
= 51083.4 N
Discontinuity Force from Internal Pressure [fY]: = P * Reff * Rnc
= 2.000 * 320.500 * 99.837
= 63990.4 N
Area Resisting Internal Pressure [Ap]: = Rn( LH - t ) + Reff( LR + tn + Rnc )
= 99.837 ( 31.273 - 7.000 ) + 320.500 ( 70.000 + 9.700 + 99.837 )
= 59965.1 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/teff )
= 206.850/( 2 * 59965.141/1388.338 - 320.500/7.000 )
= 5.1 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = S[t/Reff]
= 137.900 [7.000/320.500 ]
= 3.0 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 5.095 , 3.012 )
= 3.012 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 4846.341 + 51083.352 + 63990.391 )/1388.338
= 86.384 MPa
General Primary Membrane Stress [SigmaCirc]:
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 67 of 94
Nozzle Calcs. : S1 Nozl: 8 9:50a Jul 11,2013
= P * Reff / teff
= 2.000 * 320.500/7.000
= 91.6 MPa
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 86.384 - 91.571 , 91.571 )
= 91.6 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 206.85 MPa
Local Primary Membrane Stress PL 91.57 MPa
Maximum Allowable Working Pressure Pmax 3.01 MPa
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 99.837 + 9.700 )/99.837
= 1.097 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 99.837 + 9.700 )
= 172.061 mm
Weld Length of Pad to Shell Weld [LtauP]: = pi/2 * ( Rn + tn + W )
= pi/2 * ( 99.837 + 9.700 + 49.963 )
= 250.542 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 6.735, 7.071, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(63990*1.10,1.5*117.9(303.350+0.000),pi/4*2.0*99.84^2*1.10^2)
= 18845.537 N
Discontinuity Force [fws]: = fwelds * t * S/( t * S + te * Sp )
= 18845.5*7.00*137/(7.000*137+10.000*137)
= 7759.927 N
Discontinuity Force [fwp]: = fwelds * te * Sp / ( t * S + te * Sp )
= 18845.5*10.00*137/(7.000*137+10.000*137)
= 11085.610 N
Shear Stress [tau1]: = fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )
= 7759.927/( 172.061 * ( 0.6 * 7.000 + 0.49 * 0.000 ) )
= 10.739 MPa
Shear Stress [tau2]: = fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )
= 11085.610/( 172.061 * ( 0.6 * 10.000 + 0.49 * 6.735 ) )
= 6.928 MPa
Shear Stress [tau3]: = fwp / ( Ltau * ( 0.49 * L42T ) )
= 11085.610/( 250.542 * ( 0.49 * 7.071 ) )
= 12.771 MPa
Maximum Shear Stress in the Welds: = max( tau1, tau2, tau3 )
= max( 10.739 , 6.928 , 12.771 )
= 12.8 must be less than or equal to 137.9 MPa
Weld Size Calculations, Description: S1
Intermediate Calc. for nozzle/shell Welds Tmin 9.7000 mm
Intermediate Calc. for pad/shell Welds TminPad 7.0000 mm
Results Per UW-16.1: Required Thickness Actual Thickness
Nozzle Weld 6.0000 = Min per Code 6.7342 = 0.7 * Wo mm
Pad Weld 3.5000 = 0.5*TminPad 7.0700 = 0.7 * Wp mm
Maximum Allowable Pressure for this Nozzle at this Location: Converged Max. Allow. Pressure in Operating case 2.5270 MPa
Note: The MAWP of this junction was limited by the parent Shell/Head.
Nozzle is O.K. for the External Pressure 0.103 MPa
The Drop for this Nozzle is : 19.4937 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 229.4936 mm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 68 of 94
Nozzle Calcs. : S2A Nozl: 9 9:50a Jul 11,2013
INPUT VALUES, Nozzle Description: S2A From : 60
Pressure for Reinforcement Calculations P 2.0000 MPa
Temperature for Internal Pressure Temp 100 C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 100 C
Shell Material SA-516 70
Shell Allowable Stress at Temperature S 137.90 MPa
Shell Allowable Stress At Ambient Sa 137.90 MPa
Inside Diameter of Cylindrical Shell D 635.00 mm
Design Length of Section L 3625.0005 mm
Shell Finished (Minimum) Thickness t 10.0000 mm
Shell Internal Corrosion Allowance c 3.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Distance from Bottom/Left Tangent 1139.9999 mm
User Entered Minimum Design Metal Temperature 0.00 C
Type of Element Connected to the Shell : Nozzle
Material SA-106 B
Material UNS Number K03006
Material Specification/Type Smls. pipe
Allowable Stress at Temperature Sn 117.90 MPa
Allowable Stress At Ambient Sna 117.90 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 180.00 deg
Diameter 150.0000 mm.
Size and Thickness Basis Nominal
Nominal Thickness tn 80
Flange Material SA-105
Flange Type Weld Neck Flange
Corrosion Allowance can 3.0000 mm
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 200.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 9.5250 mm
Groove weld depth between Nozzle and Vessel Wgnv 10.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
Pad Material SA-516 70
Pad Allowable Stress at Temperature Sp 137.90 MPa
Pad Allowable Stress At Ambient Spa 137.90 MPa
Diameter of Pad along vessel surface Dp 268.2750 mm
Thickness of Pad te 10.0000 mm
Weld leg size between Pad and Shell Wp 10.0000 mm
Groove weld depth between Pad and Nozzle Wgpn 10.0000 mm
Reinforcing Pad Width 50.0000 mm
ASME Code Weld Type per UW-16 None
Class of attached Flange 300
Grade of attached Flange GR 1.1
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration) | |
| |
| |
| |
__________/| |
____/|__________\| |
| \ | |
| \ | |
|________________\|__|
Insert Nozzle With Pad, no Inside projection
Reinforcement CALCULATION, Description: S2A
ASME Code, Section VIII, Division 1, 2010, 2011a, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 146.329 mm.
Actual Thickness Used in Calculation 10.973 mm
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (2.00*320.5000)/(137*1.00-0.6*2.00)
= 4.6891 mm
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 69 of 94
Nozzle Calcs. : S2A Nozl: 9 9:50a Jul 11,2013
= (2.00*76.16)/(117*1.00-0.6*2.00)
= 1.3053 mm
Required Nozzle thickness under External Pressure per UG-28 : 0.5796 mm
UG-40, Limits of Reinforcement : [External Pressure] Parallel to Vessel Wall (Diameter Limit) Dl 304.6588 mm
Parallel to Vessel Wall, opening length d 152.3294 mm
Normal to Vessel Wall (Thickness Limit), pad side Tlwp 17.5000 mm
Weld Strength Reduction Factor [fr1]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr2]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr4]: = min( 1, Sp/S )
= min( 1, 137.9/137.9 )
= 1.000
Weld Strength Reduction Factor [fr3]: = min( fr2, fr4 )
= min( 0.9 , 1.0 )
= 0.855
Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc
Area Required Ar NA 335.033 NA mm²
Area in Shell A1 NA 400.092 NA mm²
Area in Nozzle Wall A2 NA 221.242 NA mm²
Area in Inward Nozzle A3 NA 0.000 NA mm²
Area in Welds A41+A42+A43 NA 174.064 NA mm²
Area in Element A5 NA 750.000 NA mm²
TOTAL AREA AVAILABLE Atot NA 1545.399 NA mm²
Nozzle Angle Used in Area Calculations 90.00 Degs.
The area available without a pad is Sufficient.The area available with the given pad is Sufficient.
Area Required [A]: = 0.5( d * tr*F + 2 * tn * tr*F * (1-fr1) ) per UG-37(d) or UG-39
= 0.5(152.3294*4.3330*1+2*7.9728*4.3330*1*(1-0.86))
= 335.033 mm²
Reinforcement Areas per Figure UG-37.1
Area Available in Shell [A1]: = d( E1*t - F*tr ) - 2 * tn( E1*t - F*tr ) * ( 1 - fr1 )
= 152.329 ( 1.00 * 7.0000 - 1.0 * 4.333 ) - 2 * 7.973
( 1.00 * 7.0000 - 1.0 * 4.3330 ) * ( 1 - 0.855 )
= 400.092 mm²
Area Available in Nozzle Wall Projecting Outward [A2]: = ( 2 * Tlwp ) * ( tn - trn ) * fr2
= ( 2 * 17.50 ) * ( 7.97 - 0.58 ) * 0.8550
= 221.242 mm²
Area Available in Welds [A41 + A42 + A43]: = (Wo² - Ar Lost)*Fr3+((Wi-can/0.707)² - Ar Lost)*fr2 + Wp²*fr4
= (86.6250 ) * 0.86 + (0.0000 ) * 0.86 + 100.0000² * 1.00
= 174.064 mm²
Area Available in Element [A5]: = (min(Dp,DL)-(Nozzle OD))*(min(tp,Tlwp,te))*fr4
= ( 268.2750 - 168.2750 ) * 10.0000 * 1.0000
= 750.000 mm²
Note: Per user request, A5 multiplied by 0.75, see UG-37(h).
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness for Internal/External pressures ta = 4.3053 mm
Wall Thickness per UG16(b), tr16b = 4.5000 mm
Wall Thickness, shell/head, internal pressure trb1 = 7.6891 mm
Wall Thickness tb1 = max(trb1, tr16b) = 7.6891 mm
Wall Thickness tb2 = max(trb2, tr16b) = 4.5000 mm
Wall Thickness per table UG-45 tb3 = 9.2200 mm
Determine Nozzle Thickness candidate [tb]: = min[ tb3, max( tb1,tb2) ]
= min[ 9.220 , max( 7.689 , 4.500 ) ]
= 7.6891 mm
Minimum Wall Thickness of Nozzle Necks [tUG-45]: = max( ta, tb )
= max( 4.3053 , 7.6891 )
= 7.6891 mm
Available Nozzle Neck Thickness = 0.875 * 10.973 = 9.601 mm --> OK
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 70 of 94
Nozzle Calcs. : S2A Nozl: 9 9:50a Jul 11,2013
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
MDMT of the Nozzle Neck to Flange Weld, ���Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.601 , tr = 1.305 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.198 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle Neck to Pad Weld for the Nozzle, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.601 , tr = 1.305 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.198 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle Neck to Pad Weld for Reinforcement pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.601 , tr = 1.305 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.198 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Shell to Pad Weld at Pad OD for pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 10.000 , tr = 4.689 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.670 , Temp. Reduction = 18 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -47 C
MDMT of Nozzle-Shell/Head Weld for the Nozzle (UCS-66(a)1(b)), ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.601 , tr = 1.305 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.198 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
Governing MDMT of the Nozzle : -104 C
Governing MDMT of the Reinforcement Pad : -47 C
Governing MDMT of all the sub-joints of this Junction : -47 C
ANSI Flange MDMT including Temperature reduction per UCS-66.1:
Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -29 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(b) -48 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(c) -104 C
Where the Stress Reduction Ratio per UCS-66(b)(1)(b) is : Design Pressure/Ambient Rating = 2.00/5.11 = 0.391
Note: Using the minimum value from (b)(1)(b) and (b)(1)(c) aboveas the calculated nozzle flange MDMT.
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]: = thickness - corrosion allowance
= 10.973 - 3.000
= 7.973 mm
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 635.000/2 + 3.000
= 320.500 mm
Effective Length of Vessel Wall [LR]:Note : Pad Thk >= 0.5T and Pad Width < 8(Shell Thk + Pad Thk)
= 10 * t
= 10 * 7.000
= 70.000 mm
Thickness Limit Candidate [LH1]: = t + 0.78 * sqrt( Rn * tn )
= 7.000 + 0.78 * sqrt( 76.165 * 7.973 )
= 26.221 mm
Thickness Limit Candidate [LH2]: = Lpr1 + T
= 200.000 + 7.000
= 207.000 mm
Thickness Limit Candidate [LH3]: = 8( t + te )
= 8( 7.000 + 10.000 )
= 136.000 mm
Effective Nozzle Wall Length Outside the Vessel [LH]:
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 71 of 94
Nozzle Calcs. : S2A Nozl: 9 9:50a Jul 11,2013
= min[ LH1, LH2, LH3 ]
= min[ 26.221 , 207.000 , 136.000 )
= 26.221 mm
Effective Vessel Thickness [teff]: = t
= 7.000 mm
Determine Parameter [Lamda]: = min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (152.33 + 7.973 )/( sqrt((641.00 + 7.000 ) * 7.000 )) )
= 2.380
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR * max( Lamda/4, 1 )
= 7.000 * 70.000 * max( 2.380/4, 1 )
= 490.000 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 7.973 * 26.221
= 209.055 mm²
Area Contributed by the Pad Fillet Weld [A42]: = 0.5 * Leg42^(2)
= 0.5 * 10.000^(2)
= 50.000 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2) - Area cut by thickness limit
= 0.5 * 9.525^(2) - 0.046
= 45.317 mm²
Area Contributed by the Reinforcing Pad [A5]: = min( W * te , LR * te )
= min( 50.000 * 10.000 , 70.000 * 10.000 )
= 500.000 mm²
The total area contributed by A1 through A5 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )
= 490.000+1.000(209.055+0.000)+45.317+50.000+0.000+1.000(500.000)
= 1294.372 mm²
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 137.900 * 1.000
= 206.9 MPa
Determine Force acting on the Nozzle [fN]: = P * Rn( LH - t )
= 2.000 * 76.165 ( 26.221 - 7.000 )
= 2927.7 N
Determine Force acting on the Shell [fS]: = P * Reff * ( LR + tn )
= 2.000 * 320.500 * ( 70.000 + 7.973 )
= 49976.3 N
Discontinuity Force from Internal Pressure [fY]: = P * Reff * Rnc
= 2.000 * 320.500 * 76.165
= 48817.4 N
Area Resisting Internal Pressure [Ap]: = Rn( LH - t ) + Reff( LR + tn + Rnc )
= 76.165 ( 26.221 - 7.000 ) + 320.500 ( 70.000 + 7.973 + 76.165 )
= 50865.0 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/teff )
= 206.850/( 2 * 50865.031/1294.372 - 320.500/7.000 )
= 6.3 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = S[t/Reff]
= 137.900 [7.000/320.500 ]
= 3.0 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 6.305 , 3.012 )
= 3.012 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 2927.680 + 49976.312 + 48817.418 )/1294.372
= 78.594 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Reff / teff
= 2.000 * 320.500/7.000
= 91.6 MPa
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 72 of 94
Nozzle Calcs. : S2A Nozl: 9 9:50a Jul 11,2013
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 78.594 - 91.571 , 91.571 )
= 91.6 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 206.85 MPa
Local Primary Membrane Stress PL 91.57 MPa
Maximum Allowable Working Pressure Pmax 3.01 MPa
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 76.165 + 7.973 )/76.165
= 1.105 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 76.165 + 7.973 )
= 132.163 mm
Weld Length of Pad to Shell Weld [LtauP]: = pi/2 * ( Rn + tn + W )
= pi/2 * ( 76.165 + 7.973 + 50.000 )
= 210.703 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 6.735, 7.071, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(48817*1.10,1.5*117.9(209.055+0.000),pi/4*2.0*76.16^2*1.10^2)
= 11118.906 N
Discontinuity Force [fws]: = fwelds * t * S/( t * S + te * Sp )
= 11118.9*7.00*137/(7.000*137+10.000*137)
= 4578.373 N
Discontinuity Force [fwp]: = fwelds * te * Sp / ( t * S + te * Sp )
= 11118.9*10.00*137/(7.000*137+10.000*137)
= 6540.533 N
Shear Stress [tau1]: = fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )
= 4578.373/( 132.163 * ( 0.6 * 7.000 + 0.49 * 0.000 ) )
= 8.249 MPa
Shear Stress [tau2]: = fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )
= 6540.533/( 132.163 * ( 0.6 * 10.000 + 0.49 * 6.735 ) )
= 5.322 MPa
Shear Stress [tau3]: = fwp / ( Ltau * ( 0.49 * L42T ) )
= 6540.533/( 210.703 * ( 0.49 * 7.071 ) )
= 8.960 MPa
Maximum Shear Stress in the Welds: = max( tau1, tau2, tau3 )
= max( 8.249 , 5.322 , 8.960 )
= 9.0 must be less than or equal to 137.9 MPa
Weld Size Calculations, Description: S2A
Intermediate Calc. for nozzle/shell Welds Tmin 7.9728 mm
Intermediate Calc. for pad/shell Welds TminPad 7.0000 mm
Results Per UW-16.1: Required Thickness Actual Thickness
Nozzle Weld 5.5810 = 0.7 * tmin. 6.7342 = 0.7 * Wo mm
Pad Weld 3.5000 = 0.5*TminPad 7.0700 = 0.7 * Wp mm
Maximum Allowable Pressure for this Nozzle at this Location: Converged Max. Allow. Pressure in Operating case 2.5270 MPa
Note: The MAWP of this junction was limited by the parent Shell/Head.
Nozzle is O.K. for the External Pressure 0.103 MPa
The Drop for this Nozzle is : 11.3511 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 221.3511 mm
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 73 of 94
Nozzle Calcs. : S2B Nozl: 10 9:50a Jul 11,2013
INPUT VALUES, Nozzle Description: S2B From : 60
Pressure for Reinforcement Calculations P 2.0000 MPa
Temperature for Internal Pressure Temp 100 C
Design External Pressure Pext 0.10 MPa
Temperature for External Pressure Tempex 100 C
Shell Material SA-516 70
Shell Allowable Stress at Temperature S 137.90 MPa
Shell Allowable Stress At Ambient Sa 137.90 MPa
Inside Diameter of Cylindrical Shell D 635.00 mm
Design Length of Section L 3625.0005 mm
Shell Finished (Minimum) Thickness t 10.0000 mm
Shell Internal Corrosion Allowance c 3.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Distance from Bottom/Left Tangent 4139.9995 mm
User Entered Minimum Design Metal Temperature 0.00 C
Type of Element Connected to the Shell : Nozzle
Material SA-106 B
Material UNS Number K03006
Material Specification/Type Smls. pipe
Allowable Stress at Temperature Sn 117.90 MPa
Allowable Stress At Ambient Sna 117.90 MPa
Diameter Basis (for tr calc only) ID
Layout Angle 180.00 deg
Diameter 150.0000 mm.
Size and Thickness Basis Nominal
Nominal Thickness tn 80
Flange Material SA-105
Flange Type Weld Neck Flange
Corrosion Allowance can 3.0000 mm
Joint Efficiency of Shell Seam at Nozzle E1 1.00
Joint Efficiency of Nozzle Neck En 1.00
Outside Projection ho 200.0000 mm
Weld leg size between Nozzle and Pad/Shell Wo 9.5250 mm
Groove weld depth between Nozzle and Vessel Wgnv 10.0000 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
Pad Material SA-516 70
Pad Allowable Stress at Temperature Sp 137.90 MPa
Pad Allowable Stress At Ambient Spa 137.90 MPa
Diameter of Pad along vessel surface Dp 268.2750 mm
Thickness of Pad te 10.0000 mm
Weld leg size between Pad and Shell Wp 10.0000 mm
Groove weld depth between Pad and Nozzle Wgpn 10.0000 mm
Reinforcing Pad Width 50.0000 mm
ASME Code Weld Type per UW-16 None
Class of attached Flange 300
Grade of attached Flange GR 1.1
The Pressure Design option was Design Pressure + static head.
Nozzle Sketch (may not represent actual weld type/configuration) | |
| |
| |
| |
__________/| |
____/|__________\| |
| \ | |
| \ | |
|________________\|__|
Insert Nozzle With Pad, no Inside projection
Reinforcement CALCULATION, Description: S2B
ASME Code, Section VIII, Division 1, 2010, 2011a, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 146.329 mm.
Actual Thickness Used in Calculation 10.973 mm
Nozzle input data check completed without errors.
Reqd thk per UG-37(a)of Cylindrical Shell, Tr [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
= (2.00*320.5000)/(137*1.00-0.6*2.00)
= 4.6891 mm
Reqd thk per UG-37(a)of Nozzle Wall, Trn [Int. Press] = (P*R)/(S*E-0.6*P) per UG-27 (c)(1)
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FileName : Floating Head HE ------------------------------ Page 74 of 94
Nozzle Calcs. : S2B Nozl: 10 9:50a Jul 11,2013
= (2.00*76.16)/(117*1.00-0.6*2.00)
= 1.3053 mm
Required Nozzle thickness under External Pressure per UG-28 : 0.5796 mm
UG-40, Limits of Reinforcement : [External Pressure] Parallel to Vessel Wall (Diameter Limit) Dl 304.6588 mm
Parallel to Vessel Wall, opening length d 152.3294 mm
Normal to Vessel Wall (Thickness Limit), pad side Tlwp 17.5000 mm
Weld Strength Reduction Factor [fr1]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr2]: = min( 1, Sn/S )
= min( 1, 117.9/137.9 )
= 0.855
Weld Strength Reduction Factor [fr4]: = min( 1, Sp/S )
= min( 1, 137.9/137.9 )
= 1.000
Weld Strength Reduction Factor [fr3]: = min( fr2, fr4 )
= min( 0.9 , 1.0 )
= 0.855
Results of Nozzle Reinforcement Area Calculations: AREA AVAILABLE, A1 to A5 Design External Mapnc
Area Required Ar NA 335.033 NA mm²
Area in Shell A1 NA 400.092 NA mm²
Area in Nozzle Wall A2 NA 221.242 NA mm²
Area in Inward Nozzle A3 NA 0.000 NA mm²
Area in Welds A41+A42+A43 NA 174.064 NA mm²
Area in Element A5 NA 750.000 NA mm²
TOTAL AREA AVAILABLE Atot NA 1545.399 NA mm²
Nozzle Angle Used in Area Calculations 90.00 Degs.
The area available without a pad is Sufficient.The area available with the given pad is Sufficient.
Area Required [A]: = 0.5( d * tr*F + 2 * tn * tr*F * (1-fr1) ) per UG-37(d) or UG-39
= 0.5(152.3294*4.3330*1+2*7.9728*4.3330*1*(1-0.86))
= 335.033 mm²
Reinforcement Areas per Figure UG-37.1
Area Available in Shell [A1]: = d( E1*t - F*tr ) - 2 * tn( E1*t - F*tr ) * ( 1 - fr1 )
= 152.329 ( 1.00 * 7.0000 - 1.0 * 4.333 ) - 2 * 7.973
( 1.00 * 7.0000 - 1.0 * 4.3330 ) * ( 1 - 0.855 )
= 400.092 mm²
Area Available in Nozzle Wall Projecting Outward [A2]: = ( 2 * Tlwp ) * ( tn - trn ) * fr2
= ( 2 * 17.50 ) * ( 7.97 - 0.58 ) * 0.8550
= 221.242 mm²
Area Available in Welds [A41 + A42 + A43]: = (Wo² - Ar Lost)*Fr3+((Wi-can/0.707)² - Ar Lost)*fr2 + Wp²*fr4
= (86.6250 ) * 0.86 + (0.0000 ) * 0.86 + 100.0000² * 1.00
= 174.064 mm²
Area Available in Element [A5]: = (min(Dp,DL)-(Nozzle OD))*(min(tp,Tlwp,te))*fr4
= ( 268.2750 - 168.2750 ) * 10.0000 * 1.0000
= 750.000 mm²
Note: Per user request, A5 multiplied by 0.75, see UG-37(h).
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.] Wall Thickness for Internal/External pressures ta = 4.3053 mm
Wall Thickness per UG16(b), tr16b = 4.5000 mm
Wall Thickness, shell/head, internal pressure trb1 = 7.6891 mm
Wall Thickness tb1 = max(trb1, tr16b) = 7.6891 mm
Wall Thickness tb2 = max(trb2, tr16b) = 4.5000 mm
Wall Thickness per table UG-45 tb3 = 9.2200 mm
Determine Nozzle Thickness candidate [tb]: = min[ tb3, max( tb1,tb2) ]
= min[ 9.220 , max( 7.689 , 4.500 ) ]
= 7.6891 mm
Minimum Wall Thickness of Nozzle Necks [tUG-45]: = max( ta, tb )
= max( 4.3053 , 7.6891 )
= 7.6891 mm
Available Nozzle Neck Thickness = 0.875 * 10.973 = 9.601 mm --> OK
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FileName : Floating Head HE ------------------------------ Page 75 of 94
Nozzle Calcs. : S2B Nozl: 10 9:50a Jul 11,2013
Nozzle Junction Minimum Design Metal Temperature (MDMT) Calculations:
MDMT of the Nozzle Neck to Flange Weld, ���Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.601 , tr = 1.305 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.198 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle Neck to Pad Weld for the Nozzle, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.601 , tr = 1.305 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.198 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Nozzle Neck to Pad Weld for Reinforcement pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.601 , tr = 1.305 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.198 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
MDMT of Shell to Pad Weld at Pad OD for pad, ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 10.000 , tr = 4.689 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.670 , Temp. Reduction = 18 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -47 C
MDMT of Nozzle-Shell/Head Weld for the Nozzle (UCS-66(a)1(b)), ��Curve: B ----------------------------------------------------------------------
Govrn. thk, tg = 9.601 , tr = 1.305 , c = 3.0000 mm , E* = 1.00Stress Ratio = tr * (E*)/(tg - c) = 0.198 , Temp. Reduction = 78 C
Min Metal Temp. w/o impact per UCS-66 -29 C
Min Metal Temp. at Required thickness (UCS 66.1) -104 C
Governing MDMT of the Nozzle : -104 C
Governing MDMT of the Reinforcement Pad : -47 C
Governing MDMT of all the sub-joints of this Junction : -47 C
ANSI Flange MDMT including Temperature reduction per UCS-66.1:
Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -29 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(b) -48 C
Flange MDMT with Temp reduction per UCS-66(b)(1)(c) -104 C
Where the Stress Reduction Ratio per UCS-66(b)(1)(b) is : Design Pressure/Ambient Rating = 2.00/5.11 = 0.391
Note: Using the minimum value from (b)(1)(b) and (b)(1)(c) aboveas the calculated nozzle flange MDMT.
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]: = thickness - corrosion allowance
= 10.973 - 3.000
= 7.973 mm
Effective Pressure Radius [Reff]: = Di/2 + corrosion allowance
= 635.000/2 + 3.000
= 320.500 mm
Effective Length of Vessel Wall [LR]:Note : Pad Thk >= 0.5T and Pad Width < 8(Shell Thk + Pad Thk)
= 10 * t
= 10 * 7.000
= 70.000 mm
Thickness Limit Candidate [LH1]: = t + 0.78 * sqrt( Rn * tn )
= 7.000 + 0.78 * sqrt( 76.165 * 7.973 )
= 26.221 mm
Thickness Limit Candidate [LH2]: = Lpr1 + T
= 200.000 + 7.000
= 207.000 mm
Thickness Limit Candidate [LH3]: = 8( t + te )
= 8( 7.000 + 10.000 )
= 136.000 mm
Effective Nozzle Wall Length Outside the Vessel [LH]:
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FileName : Floating Head HE ------------------------------ Page 76 of 94
Nozzle Calcs. : S2B Nozl: 10 9:50a Jul 11,2013
= min[ LH1, LH2, LH3 ]
= min[ 26.221 , 207.000 , 136.000 )
= 26.221 mm
Effective Vessel Thickness [teff]: = t
= 7.000 mm
Determine Parameter [Lamda]: = min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (152.33 + 7.973 )/( sqrt((641.00 + 7.000 ) * 7.000 )) )
= 2.380
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
Area Contributed by the Vessel Wall [A1]: = t * LR * max( Lamda/4, 1 )
= 7.000 * 70.000 * max( 2.380/4, 1 )
= 490.000 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]: = tn * LH
= 7.973 * 26.221
= 209.055 mm²
Area Contributed by the Pad Fillet Weld [A42]: = 0.5 * Leg42^(2)
= 0.5 * 10.000^(2)
= 50.000 mm²
Area Contributed by the Outside Fillet Weld [A41]: = 0.5 * Leg41^(2) - Area cut by thickness limit
= 0.5 * 9.525^(2) - 0.046
= 45.317 mm²
Area Contributed by the Reinforcing Pad [A5]: = min( W * te , LR * te )
= min( 50.000 * 10.000 , 70.000 * 10.000 )
= 500.000 mm²
The total area contributed by A1 through A5 [AT]: = A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )
= 490.000+1.000(209.055+0.000)+45.317+50.000+0.000+1.000(500.000)
= 1294.372 mm²
Allowable Local Primary Membrane Stress [Sallow]: = 1.5 * S * E
= 1.5 * 137.900 * 1.000
= 206.9 MPa
Determine Force acting on the Nozzle [fN]: = P * Rn( LH - t )
= 2.000 * 76.165 ( 26.221 - 7.000 )
= 2927.7 N
Determine Force acting on the Shell [fS]: = P * Reff * ( LR + tn )
= 2.000 * 320.500 * ( 70.000 + 7.973 )
= 49976.3 N
Discontinuity Force from Internal Pressure [fY]: = P * Reff * Rnc
= 2.000 * 320.500 * 76.165
= 48817.4 N
Area Resisting Internal Pressure [Ap]: = Rn( LH - t ) + Reff( LR + tn + Rnc )
= 76.165 ( 26.221 - 7.000 ) + 320.500 ( 70.000 + 7.973 + 76.165 )
= 50865.0 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]: = Sallow /( 2 * Ap/AT - Rxs/teff )
= 206.850/( 2 * 50865.031/1294.372 - 320.500/7.000 )
= 6.3 MPa
Maximum Allowable Working Pressure Candidate [Pmax2]: = S[t/Reff]
= 137.900 [7.000/320.500 ]
= 3.0 MPa
Maximum Allowable Working Pressure [Pmax]: = min( Pmax1, Pmax2 )
= min( 6.305 , 3.012 )
= 3.012 MPa
Average Primary Membrane Stress [SigmaAvg]: = ( fN + fS + fY ) / AT
= ( 2927.680 + 49976.312 + 48817.418 )/1294.372
= 78.594 MPa
General Primary Membrane Stress [SigmaCirc]: = P * Reff / teff
= 2.000 * 320.500/7.000
= 91.6 MPa
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FileName : Floating Head HE ------------------------------ Page 77 of 94
Nozzle Calcs. : S2B Nozl: 10 9:50a Jul 11,2013
Maximum Local Primary Membrane Stress [PL]: = max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 78.594 - 91.571 , 91.571 )
= 91.6 MPa
Summary of Nozzle Pressure/Stress Results: Allowed Local Primary Membrane Stress Sallow 206.85 MPa
Local Primary Membrane Stress PL 91.57 MPa
Maximum Allowable Working Pressure Pmax 3.01 MPa
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]: = ( Rnc + tn ) / Rnc
= ( 76.165 + 7.973 )/76.165
= 1.105 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]: = pi/2 * ( Rn + tn )
= pi/2 * ( 76.165 + 7.973 )
= 132.163 mm
Weld Length of Pad to Shell Weld [LtauP]: = pi/2 * ( Rn + tn + W )
= pi/2 * ( 76.165 + 7.973 + 50.000 )
= 210.703 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]: = 6.735, 7.071, 0.000, mm
Weld Load Value [fwelds]: = min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(48817*1.10,1.5*117.9(209.055+0.000),pi/4*2.0*76.16^2*1.10^2)
= 11118.906 N
Discontinuity Force [fws]: = fwelds * t * S/( t * S + te * Sp )
= 11118.9*7.00*137/(7.000*137+10.000*137)
= 4578.373 N
Discontinuity Force [fwp]: = fwelds * te * Sp / ( t * S + te * Sp )
= 11118.9*10.00*137/(7.000*137+10.000*137)
= 6540.533 N
Shear Stress [tau1]: = fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )
= 4578.373/( 132.163 * ( 0.6 * 7.000 + 0.49 * 0.000 ) )
= 8.249 MPa
Shear Stress [tau2]: = fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )
= 6540.533/( 132.163 * ( 0.6 * 10.000 + 0.49 * 6.735 ) )
= 5.322 MPa
Shear Stress [tau3]: = fwp / ( Ltau * ( 0.49 * L42T ) )
= 6540.533/( 210.703 * ( 0.49 * 7.071 ) )
= 8.960 MPa
Maximum Shear Stress in the Welds: = max( tau1, tau2, tau3 )
= max( 8.249 , 5.322 , 8.960 )
= 9.0 must be less than or equal to 137.9 MPa
Weld Size Calculations, Description: S2B
Intermediate Calc. for nozzle/shell Welds Tmin 7.9728 mm
Intermediate Calc. for pad/shell Welds TminPad 7.0000 mm
Results Per UW-16.1: Required Thickness Actual Thickness
Nozzle Weld 5.5810 = 0.7 * tmin. 6.7342 = 0.7 * Wo mm
Pad Weld 3.5000 = 0.5*TminPad 7.0700 = 0.7 * Wp mm
Maximum Allowable Pressure for this Nozzle at this Location: Converged Max. Allow. Pressure in Operating case 2.5270 MPa
Note: The MAWP of this junction was limited by the parent Shell/Head.
Nozzle is O.K. for the External Pressure 0.103 MPa
The Drop for this Nozzle is : 11.3511 mmThe Cut Length for this Nozzle is, Drop + Ho + H + T : 221.3511 mm
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 78 of 94
Nozzle Schedule : Step: 23 9:50a Jul 11,2013
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
------------------------------------------------------------------------------
S2A 150 80 WNF 168.275 10.973 268.27 10.00 221
S2B 150 80 WNF 168.275 10.973 268.27 10.00 221
S1 200 80 WNF 219.075 12.700 319.00 10.00 229
T1 300 40 WNF 323.850 10.312 523.85 10.00 254
T2 300 40 WNF 323.850 10.312 523.85 10.00 254
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
------------------------------------------------------------------------------
S2A SA-106 B 10.000 9.525 10.000 10.000 -
S2B SA-106 B 10.000 9.525 10.000 10.000 -
S1 SA-106 B 10.000 9.525 10.000 10.000 -
T1 SA-106 B 6.000 9.525 10.000 10.000 -
T2 SA-106 B 6.000 9.525 10.000 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
----------------------------------------------------------------------------
S2A 1140.000 180.00 200.00 0.00 SHELL
S2B 4140.000 180.00 200.00 0.00 SHELL
S1 2652.000 270.00 200.00 0.00 SHELL
T1 368.000 -45.00 200.00 0.00 FC SHELL
T2 368.000 225.00 200.00 0.00 FC SHELL
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PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 79 of 94
Nozzle Summary : Step: 24 9:50a Jul 11,2013
Nozzle Calculation Summary:
Description MAWP Ext MAPNC UG45 [tr] Weld Areas or
MPa MPa Path Stresses
---------------------------------------------------------------------------
T1 2.5270 OK 0.00 OK 4.50 OK Passed
T2 2.5270 OK 0.00 OK 4.50 OK Passed
S1 2.5270 OK 0.00 OK 7.69 OK Passed
S2A 2.5270 OK 0.00 OK 7.69 OK Passed
S2B 2.5270 OK 0.00 OK 7.69 OK Passed
---------------------------------------------------------------------------
Min. - Nozzles 2.5270 S2B 0.000 S2B
Note: MAWPs (Internal Case) shown above are at the High Point.
Check the Spatial Relationship between the Nozzles
From Node Nozzle Description X Coordinate, Layout Angle, Dia. Limit
30 T1 415.000 -45.000 500.000
30 T2 415.000 225.000 500.000
60 S1 2652.000 270.000 399.350
60 S2A 1140.000 180.000 308.275
60 S2B 4140.000 180.000 308.275
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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FileName : Floating Head HE ------------------------------ Page 80 of 94
MDMT Summary : Step: 25 9:50a Jul 11,2013
Minimum Design Metal Temperature Results Summary :
Curve Basic Reduced UG-20(f) Thickness Gov E*
Description MDMT MDMT MDMT ratio Thk
Notes C C C mm
----------------------------------------------------------------------------
FC COVER [11] B -27 -27 -29 1.000 10.750 1.000
SH#FC FLANGE [11] B -29 -29 -29 1.000 10.000 1.000
SH#RC FLANGE [11] B -29 -32 -29 0.937 10.000 1.000
FC SHELL [8] B -29 -104 -29 0.280 10.000 0.850
SHELL [8] B -29 -45 -29 0.705 10.000 0.850
RC SHELL [8] B -29 -40 -29 0.803 10.000 0.850
RC HEAD [10] B -29 -41 -29 0.787 10.000 0.850
RC HEAD [7] B -23 -44 -29 0.625 12.000 0.850
T1 [1] B -29 -104 0.109 9.023 1.000
Nozzle Flg [4] -29 -104 0.109
T2 [1] B -29 -104 0.109 9.023 1.000
Nozzle Flg [4] -29 -104 0.109
S1 [1] B -29 -47 -29 0.670 10.000 1.000
Nozzle Flg [4] -29 -104 0.211
S2A [1] B -29 -47 -29 0.670 10.000 1.000
Nozzle Flg [4] -29 -104 0.198
S2B [1] B -29 -47 -29 0.670 10.000 1.000
Nozzle Flg [4] -29 -104 0.198
----------------------------------------------------------------------------
Required Minimum Design Metal Temperature �� 0 CWarmest Computed Minimum Design Metal Temperature� -29 C
Notes:[ ! ] - This was an impact tested material.[ 1] - Governing Nozzle Weld.[ 4] - ANSI Flange MDMT Calcs; Thickness ratio per UCS-66(b)(1)(c).[ 5] - ANSI Flange MDMT Calcs; Thickness ratio per UCS-66(b)(1)(b).[ 6] - MDMT Calculations at the Shell/Head Joint.[ 7] - MDMT Calculations for the Straight Flange.[ 8] - Cylinder/Cone/Flange Junction MDMT.[ 9] - Calculations in the Spherical Portion of the Head.[10] - Calculations in the Knuckle Portion of the Head.[11] - Calculated (Body Flange) Flange MDMT.[12] - Calculated Flat Head MDMT per UCS-66(3)
UG-84(b)(2) was not considered.UCS-66(g) was not considered.UCS-66(i) was not considered.
Notes:Impact test temps were not entered in and not considered in the analysis.UCS-66(i) applies to impact tested materials not by specification andUCS-66(g) applies to materials impact tested per UG-84.1 General Note (c).The Basic MDMT includes the (30F) PWHT credit if applicable.
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FileName : Floating Head HE ------------------------------ Page 81 of 94
ASME TS Calc : NORMAL OPERATIO Case: 1 9:50a Jul 11,2013
Input Echo, Tubesheet Number 1, Description: STATIONARY TUBE
Shell Data:Main Shell Description: SHELL
Shell Design Pressure Ps 2.00 MPa
Shell Thickness ts 10.0000 mm
Shell Corrosion Allowance cas 3.0000 mm
Inside Diameter of Shell Ds 635.000 mm
Shell Temperature for Internal Pressure Ts 100.00 C
Shell Material SA-516 70
Note: Using 2 * Yield for Discontinuity Stress Allowable (UG-23(e)), Sps.Make sure that material properties at this temperature are nottime-dependent for Material: SA-516 70
Shell Material UNS Number K02700
Shell Allowable Stress at Temperature Ss 137.90 MPa
Shell Allowable Stress at Ambient 137.90 MPa
Channel Description: FC SHELL Channel Type: Cylinder
Channel Design Pressure Pt 0.50 MPa
Channel Thickness tc 10.0000 mm
Channel Corrosion Allowance cac 3.0000 mm
Inside Diameter of Channel Dc 635.000 mm
Channel Design Temperature TEMPC 15.00 C
Channel Material SA-516 70
Note: Using 2 * Yield for Discontinuity Stress Allowable (UG-23(e)), Sps.Make sure that material properties at this temperature are nottime-dependent for Material: SA-516 70
Channel Material UNS Number K02700
Channel Allowable Stress at Temperature Sc 137.90 MPa
Channel Allowable Stress at Ambient 137.90 MPa
Tube Data: Number of Tube Holes Nt 468
Tube Wall Thickness et 2.1100 mm
Tube Outside Diameter D 19.0500 mm
Straight Tube Length (bet. inner tubsht faces) L 3952.00 mm
Design Temperature of the Tubes 100.00 C
Tube Material SA-179
Tube Material UNS Number K01200
Is this a Welded Tube No
Tube Material Specification used Smls. tube
Tube Allowable Stress at Temperature 92.39 MPa
Tube Allowable Stress At Ambient 92.39 MPa
Tube Yield Stress At design Temperature Syt 163.44 MPa
Tube Pitch (Center to Center Spacing) P 23.8120 mm
Tube Layout Pattern Triangular
Fillet Weld Leg af 2.0000 mm
Groove Weld Leg ag 0.0000 mm
Tube-Tubesheet Joint Weld Type Partial Strength
Method for Tube-Tubesheet Jt. Allow. UW-20
Tube-Tubesheet Joint Classification i
Radius to Outermost Tube Hole Center ro 310.000 mm
Largest Center-to-Center Tube Distance Ul 38.0000 mm
Length of Expanded Portion of Tube ltx 40.0000 mm
Tube-side pass partition groove depth hg 5.0000 mm
Tubesheet Data:
Tubesheet TYPE: Stationary, Gasketed both Sides, Conf. d Exchanger TYPE: With an Immersed Floating Head, Conf. a
Tubesheet Design Metal Temperature T 100.00 C
Tubesheet Material Specification SA-266 4
Note: Using 2 * Yield for Discontinuity Stress Allowable (UG-23(e)), Sps.Make sure that material properties at this temperature are nottime-dependent for Material: SA-266 4
Tubesheet Material UNS Number K03017
Tubesheet Allowable Stress at Temperature S 137.90 MPa
Tubesheet Allowable Stress at Ambient Tt 137.90 MPa
Thickness of Tubesheet h 54.0000 mm
Tubesheet Corr. Allowance (Shell side) Cats 3.0000 mm
Tubesheet Corr. Allowance (Channel side) Catc 3.0000 mm
Tubesheet Outside Diameter A 695.000 mm
Dimension G for the Channel Side Gc 680.092 mm
Area of the Untubed Lanes AL 47182.0 mm²
Additional Data for Fixed/Floating Tubesheet Exchangers: Unsupported Tube Span under consideration l 380.000 mm
Tube End condition corresponding to Span (l) k 0.80
Ignore Radial Thermal Exp. effects (UHX-13.8/14.6) YES
Note: The Metal temperatures at the Rim are set to ambient (21 C)
Tubesheet Metal Temp. at Rim T' 21.11 C
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FileName : Floating Head HE ------------------------------ Page 82 of 94
ASME TS Calc : NORMAL OPERATIO Case: 1 9:50a Jul 11,2013
Shell Metal Temp. at Tubesheet T'S 21.11 C
Channel Metal Temp. at Tubesheet T'C 21.11 C
Perform Differential Pressure Design N
Run Multiple Load Cases YES
Junction Stress Reduction option None
Additional Data for Gasketed Tubesheets: Tubesheet Gasket on which Side Both
Flange Outside Diameter A 776.000 mm
Flange Inside Diameter B 635.000 mm
Flange Face Outside Diameter Fod 698.000 mm
Flange Face Inside Diameter Fid 635.000 mm
Gasket Outside Diameter Go 695.000 mm
Gasket Inside Diameter Gi 651.000 mm
Small end Hub thk. g0 10.0000 mm
Large end Hub thk. g1 13.0000 mm
Gasket Factor, m 2.00
Gasket Design Seating Stress y 11.03 MPa
Flange Facing Sketch Code Sketch 1a
Column for Gasket Seating Code Column II
Gasket Thickness tg 3.0000 mm
Full face Gasket Flange Option Program Selects
Bolting Information: Diameter of Bolt Circle C 728.000 mm
Nominal Bolt Diameter dB 20.0000 mm
Type of Thread Series TEMA Metric Thread
Number of Bolts n 28
Bolt Material SA-193 B7
Bolt Material UNS Number G41400
Bolt Allowable Stress At Temperature Sb 172.38 MPa
Bolt Allowable Stress At Ambient Sa 172.38 MPa
Weld between Flange and Shell/Channel 0.0000 mm
Alternate Flange Operating Bolt Load, Wm1 865076.94 N
Alternate Flange Seating Bolt Load, Wm2 196454.78 N
Alternate Flange Design Bolt Load, W 956292.25 N
Tubesheet Integral with None
Tubesheet Extended as Flange No
Is Exchanger in Creep range (skip EP, Use 3S for Sps) NO
ASME TubeSheet Results per Part UHX, 2010, 2011a
Elasticity/Expansion Material Properties:
Shell - TE-1 Carbon & Low Alloy Steels, Group 1Shell - TM-1 Carbon Steels with C<= 0.3%
-----------------------------------------------------------------
Th. Exp. Coeff. Metal Temp. along Len 100.0 C 0.0000121022 /C
Elastic Mod. at Design Temperature 100.0 C 0.19816E+06 MPa
Th. Exp. Coeff. Metal Temp. at Tubsht 21.1 C 0.0000115190 /C
Elastic Mod. at Metal Temp. along Len 100.0 C 0.19816E+06 MPa
Elastic Mod. at Ambient Temperature 21.1 C 0.20271E+06 MPa
Channel - TE-1 Carbon & Low Alloy Steels, Group 1Channel - TM-1 Carbon Steels with C<= 0.3%
-----------------------------------------------------------------
Th. Exp. Coeff. Metal Temp. at Tubsht 21.1 C 0.0000115190 /C
Elastic Mod. at Design Temperature 15.0 C 0.20311E+06 MPa
Elastic Mod. at Ambient Temperature 21.1 C 0.20271E+06 MPa
Tubes - TE-1 Carbon & Low Alloy Steels, Group 1Tubes - TM-1 Carbon Steels with C<= 0.3%
-----------------------------------------------------------------
Th. Exp. Coeff. Metal Temp. along Len 15.0 C 0.0000114311 /C
Elastic Mod. at Design Temperature 100.0 C 0.19816E+06 MPa
Elastic Mod. at Metal Temp. along Len 15.0 C 0.20311E+06 MPa
Elastic Mod. at Tubsht. Design Temp. 100.0 C 0.19816E+06 MPa
Elastic Mod. at Ambient Temperature 21.1 C 0.20271E+06 MPa
TubeSheet - TE-1 Carbon & Low Alloy Steels, Group 1TubeSheet - TM-1 Carbon Steels with C<= 0.3%
-----------------------------------------------------------------
Th. Exp. Coeff. Metal Temp. at Rim 21.1 C 0.0000115190 /C
Elastic Mod. at Design Temperature 100.0 C 0.19816E+06 MPa
Elastic Mod. at Metal Temp. at Rim 21.1 C 0.20271E+06 MPa
Elastic Mod. at Ambient Temperature 21.1 C 0.20271E+06 MPa
Note:The Elasticity and Alpha values are taken from Tables in ASME II D.Please insure these properties are consistent with thetype of Material for the tubes, shell, channel etc.
Tube Required Thickness under Internal Pressure (Tubeside pressure) :
Thickness Due to Internal Pressure: = (P*(D/2-CAE)) / (S*E+0.4*P) per Appendix 1-1 (a)(1)
= (0.50*(19.0500/2-0.000)/(92.39*1.00+0.4*0.50)
= 0.0514 + 0.0000 = 0.0514 mm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 83 of 94
ASME TS Calc : NORMAL OPERATIO Case: 1 9:50a Jul 11,2013
Tube Required Thickness under External Pressure (Shellside pressure) :
External Pressure Chart CS-1 at 100.00 C
Elastic Modulus for Material 199955.00 MPa
Results for Max. Allowable External Pressure (Emawp): TCA ODCA SLEN D/T L/D Factor A B
2.1100 19.05 3952.00 9.03 50.0000 0.0134948 95.84
EMAWP = (2.167/(D/T)-0.0833)*B = 15.0201 MPa
Results for Required Thickness: No Conversion TCA ODCA SLEN D/T L/D Factor A B
0.4508 19.05 3952.00 42.26 50.0000 0.0006159 61.57
EMAWP = (4*B)/(3*(D/T)) = ( 4 *61.5720 )/( 3 *42.2626 ) = 1.9425 MPa
Summary of Tube Required Thickness Results: Total Required Thickness including Corrosion all. 0.4508 mm
Allowable Internal Pressure at Corroded thickness 22.46 MPa
Required Internal Design Pressure 0.50 MPa
Allowable External Pressure at Corroded thickness 15.02 MPa
Required External Design Pressure 2.00 MPa
Required Thickness due to Shell Side pressure 0.4508 mm
-----------------------------------------------------------------
Detailed Results for load Case 3 un-corr. (Ps + Pt - Th) -----------------------------------------------------------------
Intermediate Calculations For Gasketed Tubesheets:
ASME Code, Section VIII, Div. 1, 2010, 2011a
Gasket Contact Width, N = (Goc-Gic) / 2 22.000 mm
Basic Gasket Width, b0 = N / 2.0 11.000 mm
Effective Gasket Width, b = SQRT(b0) * 2.5 8.355 mm
Gasket Reaction Diameter, G = Go-2.0*b 678.291 mm
Flange Design Bolt Load, Seating Condition W : 956292.25 N
Flange Design Bolt Load, Operating Condition Wm1: 865039.12 N
Results for ASME Stationary Tubesheet Calculations for Configuration d,
Results for Tubesheet Calculations Original Thickness :
UHX-14.5.1 Step 1:
Compute the Tube Expansion Depth Ratio [rho]: = ltx / h ( modified for corrosion if present )
= 40.0000 / 54.0000 = 0.7407 ( must be 0 <= rho <= 1 )
Compute the Effective Tube Hole Diameter [d*]: = Max( dt - 2tt*( Et/E )( St/S )( rho ), dt - 2tt)
= Max( 19.0500 -2*2.1100 *(198162 /198162 )*
( 92 /137 )*(0.741 ), 19.0500 -2*2.1100 )
= 16.9556 mm
Compute the Equivalent Outer Tube Limit Circle Diameter [Do]: = 2 * ro + dt = 2 * 310.000 + 19.050 = 639.050 mm
Determine the Basic Ligament Efficiency for Shear [mu]: = (p - dt)/p = (23.8120 - 19.0500 )/23.8120 = 0.2000
Compute the Equivalent Outer Tube Limit Radius [ao]: = Do / 2 = 639.0500 / 2 = 319.5250 mm
Compute the Effective Tube Pitch [p*]: = p / sqrt( 1 - 4 * min( AL * CNV_factor, 4*Do*p)/(Pi * Do²) )
= 23.8120 / sqrt( 1 - 4 * min( 47182.00 *1.000 , 4*639.050 *23.812 )
/ ( 3.141 * 639.050²) )
= 25.7838 mm
Compute the Effective Ligament Efficiency for Bending [mu*]: = (p* - d*) / p* = (25.7838 - 16.9556 ) / 25.7838 = 0.3424
Compute the Ratio [Rhos]: = as / ao = 339.1454 / 319.5250 = 1.061405
Compute the Ratio [Rhoc]: = ac / ao = 340.0460 / 319.5250 = 1.064223
Compute Parameter [xt]: = 1 - Nt * (( dt - 2 * tt )/( 2 * ao ))^(2)
= 1 - 468 * ((19.0500 - 2 * 2.1100 )/(2 * 319.5250 ))^(2) = 0.7480
Determine Parameter [xs]: = 1 - Nt*( dt/(2*ao) )^(2)
= 1 - 468 *( 19.0500 /(2*319.5250 ) )^(2) = 0.5841
Determine the Value [h'g]: = Max(( hg - CATC ), 0 ) (For pressure only cases)
= Max(( 5.000 - 0.000 ), 0 ) = 5.000 mm
UHX-14.5.2 Step 2:
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FileName : Floating Head HE ------------------------------ Page 84 of 94
ASME TS Calc : NORMAL OPERATIO Case: 1 9:50a Jul 11,2013
Intermediate parameters for Tubesheet Gasketed on the Shell Side:betaS, ks, Lambdas, deltaS = 0
Intermediate parameters for Tubesheet Gasketed on the Channel Side:betac, kc, deltaC, Lambdac = 0
UHX-14.5.3 Step 3:
E*/E and nu* for Triangular pattern from Fig. UHX-11.3. h/p = 2.267764 ; mu* = 0.342393
E*/E = 0.337089 ; nu* = 0.329849 ; E* = 66799. MPa
Note: As h/p (2.268) is > 2, data values for h/p = 2 were used.
Compute the Tube Bundle Stiffness Factor [Xa]: = ((24 *(1 - nu*^(2))*Nt * Et* tt* (dt - tt)* ao²) /
( E* * L * H^(3) ) )^(0.25)
= ((24 *(1 - 0.330 ^(2))*468 *198162 *2.1100 *
(19.0500 - 2.1100 )*319.5250 ^(2))/( 66798 *
3952.00 * 54.000 ^(3) ))^(0.25)
= 3.6327
Values from Table UHX-13.1 Zd = 0.032043 ; Zv = 0.077130 ; Zm = 0.414666
Za = 0.436054E+01 ; Zw = 0.077130
UHX-14.5.4 Step 4:
Compute the Diameter Ratio [K]: = A / Do = 695.0000 / 639.0500 = 1.0876
Compute Coefficient [F]: = (1 - nu*) / (E*) * ( Lambdas + Lambdac + E * ln(K) )
= (1 - 0.33 ) / (66798 ) * ( 0.00 + 0.00 +
198162 * ln(1.09 ) )
= 0.1669
Compute Parameter [Phi]: = (1 + nu*) * F = (1 + 0.3298 ) * 0.1669 = 0.2219
Compute Parameter [Q1]: = (Rhos - 1 - Phi * Zv)/(1 + Phi * Zm)
= (1.0614 - 1 - 0.2219 *0.0771 )/(1 + 0.2219 *0.4147 )
= 0.040558711
UHX-14.5.5 Step 5:
Determine factor [gamab]: = ( Gc - Gs ) / Do (config d)
= (680.0920 - 678.2908 )/639.0500 = 0.00282
Calculate Parameter [OmegaS]: = rhos * ks * Betas * deltaS( 1 + h * Betas )
= 1.0614 * 0.00 * 0.0000 * 0.000000 ( 1 + 54.0000 * 0.0000 )
= 0.0000 mm ²
Calculate Parameter [Omega*S]: = Ao² * ( Rhos² - 1 ) * ( Rhos - 1 ) / 4 - OmegaS
= 319.525² * ( 1.061² - 1 ) * ( 1.061 - 1 ) / 4 - 0.000
= 198.3907 mm ²
Calculate Parameter [OmegaC]: = rhoc * kc * Betac * deltaC( 1 + h * Betac )
= 1.0642 * 0.00 * 0.0000 * 0.000000 ( 1 + 54.0000 * 0.0000 )
= 0.0000 mm ²
Calculate Parameter [Omega*C]: = ao²[( Rhoc²+1 )*( Rhoc-1 )/4 -(Rhos-1)/2]- OmegaC
= 319.52499²[( 1.06422²+1 )*( 1.06422 -1 )/4 -(1.06141 -1)/2]- 0.00000
= 361.1879 mm ²
Compute the Pressure [P*S]:= 0 For Pressure only cases or Configurations d,e,f,A,B,C,D
Compute the Pressure [P*C]:= 0 For Pressure only cases or Configurations b,c,d,B,C,D
UHX-14.5.6 Step 6:
Pe = Ps - Pt
= 2.000 - 0.500 = 1.500 MPa
UHX-14.5.7 Step 7:
Determine Factor [Q2]: = [((Omega*S*Ps - Omega*C*Pt) - (Omegas*P*s - Omegac P*c))CNV_FAC +
W* * gamab/(2*pi)]/(1 + Phi*Zm)
= [( ( 198.391 * 2.000 - 361.188 * 0.500 ) -
( 0.000 * 0.000 - 0.000 * 0.000 )) * 1.000 +
865039 * 0.003 /(2*3.141)]/(1 + 0.22189 * 0.41467 )
= 553.285156250 N
Calculate Factor [Q3]: = Q1 + 2 * Q2 / ( Pe * ao^(2)
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 85 of 94
ASME TS Calc : NORMAL OPERATIO Case: 1 9:50a Jul 11,2013
= 0.041 + 2 * 553.285 / ( 1.500 * 319.525 ^(2) = 0.047785
Fm Value from Table UHX-13.1 = 0.084143
The Tubesheet Bending Stress - Original Thickness [Sigma]: = (1.5 * Fm / mu* ) * (2 * ao/(H - h'g)^(2) * Pe
= (1.5 * 0.0841 /0.3424 ) * (2 * 319.5250 /(54.000 - 5.000 ))^(2) * 1.50
= 94.0485 MPa
The Allowable Tubesheet Bending Stress [Sigma allowed]: = 1.5 * S = 1.5 * 137.90 = 206.85 MPa
The Tubesheet Bending Stress - Final Thickness [Sigmaf]: = (1.5 * Fm/mu*) * (2 * ao/( h - h'g)² * Pe
= (1.5 * 0.0698 /0.3424 ) * (2 * 319.5250 /(35.090 - 5.000 ))² * 1.50
= 206.8376 MPa
Reqd Tubesheet Thickness, for Bending Stress (Including CA ) [HReqB]: = h + Cats + Catc = 35.0899 + 0.0000 + 0.0000 = 35.0899 mm
UHX-14.5.8 Step 8:
Shear Stress check [Tau_limit]: = 3.2 * S * MU * h / Do
= 3.2 * 20000.00 * 0.200 * 54.000 / 639.05 = 7.46 MPa
The Tubesheet Average Shear Stress - Original Thickness [Tau]: = ( 1 / ( 2*mu ) ) * ( ao/h ) * Pe
= ( 1 / (2*0.200 ) ) * ( 319.5250 /54.000 ) * 1.500
= 22.1911 MPa
The Allowable Tubesheet Shear Stress [Tau allowed]: = 0.8 * S = 0.8 * 137.90 = 110.32 MPa
The Tubesheet Shear Stress - Final Thickness [Tauf]: = ( 1/(2*mu) ) * ( ao/h ) * Pe
= ( 1/(2*0.200 ) ) * ( 319.5250 /10.862 ) * 1.500 = 110.32 MPa
Reqd Tubesheet Thickness, for Shear Stress (Including CA) [HreqS]: = H + Cats + Catc = 10.8622 + 0.0000 + 0.0000 = 10.8622 mm
Reqd Tubesheet Thickness for Given Loadings (Including CA) [Hreqd] : = Max( HreqB, HreqS ) = Max( 35.0899 , 10.8622 ) = 35.0899 mm
UHX-14.5.9 Step 9:
The Ftmin and Ftmax Coefficients from Table UHX-13.2: Ftmin = -0.8353 , Ftmax = 3.1109
First Extreme Tube Axial Stress from among all the tubes [Sigmat1]: = ( (Ps * xs - Pt * xt) - Pe * Ftmin ) / ( Xt - Xs )
= ( (2.00 * 0.5841 - 0.50 * 0.7480 ) - (1.500 ) * -0.835 ) /
(0.7480 - 0.5841 ) )
= 12.4951 MPa
Second Extreme value of Tube Axial Stress from among all the tubes [Sigmat2]: = ( (Ps * xs - Pt * xt) - Pe * Ftmax ) / ( Xt - Xs )
= ( (2.00 * 0.5841 - 0.50 * 0.7480 ) - (1.500 ) * 3.111 ) /
(0.7480 - 0.5841 ) )
= -23.6327 MPa
Maximum Tube Axial Stress [Sigmat,max]: = MAX( |Sigmat1|, |Sigmat2| ) = 23.633 MPa
The Allowable Tube Stress, [SigmatA] = Sot = 92.3930 MPa
Check for Buckling as some of the Tubes are in Compression
Determine the Factor of Safety [Fs]: = Max( (3.25 - 0.25*(Zd + Q3*Zw)*Xa^4 ), 1.25 )
= Max((3.25 - 0.25*(0.032 + 0.048 *0.077 )*3.633 ^4), 1.25 )
= 1.6945 (Should be <= 2 )
Determine the Factor [rt]: = ( ( dt^(2) + (dt - 2*tt)^(2) )^(.5) )/4
= ( (19.0500 ^(2) + (19.0500 - 2*2.1100 )^(2) )^(.5) )/4 = 6.0355 mm
Determine the Factor [Ct]: = ( 2 * PI^(2) * Et/Syt )^(0.5)
= ( 2 * 3.14 ^(2) * 198162 /163 )^(0.5) = 154.7023
Determine the Factor [Ft]: = k * L/r = 0.8 * 380.00 /6.035 = 50.3689
The Buckling Allowable Stress [Stb]: = Sy,t/Fs*( 1 - Ft/(2*Ct) )
= 163 /1.69 *( 1 - 50.369 /(2*154.702 ) )
= 80.749 MPa (Never greater than Sot)
Note: The Axial Compressive stress in Tubes is within limits.
The Largest tube-to-tubesheet Joint Load [Wt]: = Sigmat,max * Tube Area = 23.63 * 112.2912 = 2653.52 N
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 86 of 94
ASME TS Calc : NORMAL OPERATIO Case: 1 9:50a Jul 11,2013
Tube Weld Size Results per UW-20:Tube Strength [Ft]:
= 3.1415 * t * ( do - t ) * Sa
= 3.1415 * 2.110 * ( 19.050 - 2.110 ) * 92.39 = 10374.039 N
Fillet Weld Strength [Ff]: = .55 * 3.1415 * af * (do + 0.67*af) * Sw (but not > Ft)
= .55 * 3.1415 * 2.000 * (19.050 + 0.67*2.000 ) * 92.39
= 6509.7148 N
Groove Weld Strength, Fg = 0.0
Max. Allow. Tube-Tubesheet Joint load, Lmax
= Ff + Fg (but not > Ft) = 6509.7148 N
Design Strength Ratio [fd]: = Fd / Ft = 0.2558
Weld Strength Factor [fw]: = Sot / ( Min(Sot, S) ) = 1.0000
Min Weld Length [ar]: = ( (0.75 * do)² + 2.73*t*(do - t)* fw * fd ) )½ - .75 * do
= 0.8483 mm
Minimum Required Fillet Weld Leg afr 0.8483 mm
Note: Computations completed for ASME Tubesheet Configuration d.
Stress/Force summary for loadcase 3 un-corr. (Ps + Pt - Th): ------------------------------------------------------------------------
Stress Description Actual Allowable Pass/Fail
------------------------------------------------------------------------
Tubesheet Bend. Stress 94.0 <= 206.9 MPa Ok
Tubesheet Shear Stress 22.2 <= 110.3 MPa Ok
Maximum Stress in the Tubes 23.6 <= 92.4 MPa Ok
Minmum Tube Stress (Buckling) -23.6 <= -80.7 MPa Ok
Maximum Force on any one Tube 2653.5 <= 6509.7 N Ok
------------------------------------------------------------------------
Thickness results for loadcase 3 un-corr. (Ps + Pt - Th): ----------------------------------------------------------------------------
Thickness (mm) Required Actual P/F
----------------------------------------------------------------------------
Tubesheet Thickness : 35.090 54.000 Ok
Tube-Tubesheet Fillet Weld Leg : 0.848 2.000 Ok
----------------------------------------------------------------------------
Stationary Tubesheet results per ASME UHX-14 2010, 2011a
Results for 6 Load Cases:
--Reqd. Thk. + CA -------- Tubesheet Stresses Case Pass/
Case# Tbsht Extnsn Bend Allwd Shear Allwd Type Fail
----------------------------------------------------------------------------
1uc 20.611 ... 31 207 7 110 Fvs+Pt-Th Ok
2uc 40.743 ... 125 207 30 110 Ps+Fvt-Th Ok
3uc 35.090 ... 94 207 22 110 Ps+Pt-Th Ok
1c 23.101 ... 33 207 8 110 Fvs+Pt-Th-Ca Ok
2c 43.078 ... 134 207 33 110 Ps+Fvt-Th-Ca Ok
3c 37.446 ... 100 207 25 110 Ps+Pt-Th-Ca Ok
----------------------------------------------------------------------------
Max: 43.0782 ... mm 0.646 0.302 (Str. Ratio)
Load Case Definitions:Fvs,Fvt - User-defined Shell-side and Tube-side vacuum pressures or 0.0.Ps, Pt - Shell-side and Tube-side Design Pressures.(+-)Th - With or Without Thermal Expansion.Ca - With or Without Corrosion Allowance.
Tube, Shell and Channel Stress Summary: --------- Tube Stresses Tube Loads Shell Stress Channel Stress Pass
Case# Ten Allwd Cmp Allwd Ld Allwd Stress Allwd Stress Allwd Fail
------------------------------------------------------------------------------
1uc 7 92 -5 -80 808 6509 ... ... ... ... Ok
2uc 31 92 -31 -80 3461 6509 ... ... ... ... Ok
3uc 24 92 -24 -80 2654 6509 ... ... ... ... Ok
1c 8 92 -5 -89 928 6509 ... ... ... ... Ok
2c 35 92 -35 -90 3943 6509 ... ... ... ... Ok
3c 27 92 -27 -90 3015 6509 ... ... ... ... Ok
------------------------------------------------------------------------------
Max RATIO 0.380 0.390 0.606 ... ...
Summary of Thickness Comparisons for 6 Load Cases: ----------------------------------------------------------------------------
Thickness (mm) Required Actual P/F
----------------------------------------------------------------------------
Tubesheet Thickness : 43.078 54.000 Ok
Tube Thickness : 0.451 2.110 Ok
Tube-Tubesheet Fillet Weld Leg : 1.244 2.000 Ok
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 87 of 94
ASME TS Calc : NORMAL OPERATIO Case: 1 9:50a Jul 11,2013
----------------------------------------------------------------------------
Tubesheet MAWP used to Compute Hydrotest Pressure:
Stress / Force | Tubeside (0 shellside) | Shellside (0 tubeside) |
Condition | MAWP |Stress Rat.| MAWP |Stress Rat.|
------------------------------------------------------------------------------
Tubesheet Bending Stress | 3.103 | 1.000 | 3.094 | 1.000 |
Tubesheet Shear Stress | 6.628 | 1.000 | 6.628 | 1.000 |
Tube Tensile Stress | 5.588 | 1.000 | 5.261 | 1.000 |
Tube Compressive Stress | 8.359 | 1.000 | 5.129 | 1.000 |
Tube-Tubesheet Joint load | 3.507 | 1.000 | 3.302 | 1.000 |
Tube Pressure Stress | 22.457 | 1.000 | 15.020 | 1.000 |
------------------------------------------------------------------------------
Minimum MAWP | 3.103 | | 3.094 | |
Tubesheet MAPnc used to Compute Hydrotest Pressure:
Stress / Force | Tubeside (0 shellside) | Shellside (0 tubeside) |
Condition | MAPnc |Stress Rat.| MAPnc |Stress Rat.|
------------------------------------------------------------------------------
Tubesheet Bending Stress | 3.309 | 1.000 | 3.302 | 1.000 |
Tubesheet Shear Stress | 7.457 | 1.000 | 7.457 | 1.000 |
Tube Tensile Stress | 6.420 | 1.000 | 5.994 | 1.000 |
Tube Compressive Stress | 9.105 | 1.000 | 5.704 | 1.000 |
Tube-Tubesheet Joint load | 4.028 | 1.000 | 3.761 | 1.000 |
Tube Pressure Stress | 22.457 | 1.000 | 15.020 | 1.000 |
------------------------------------------------------------------------------
Minimum MAPnc | 3.309 | | 3.302 | |
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 88 of 94
ASME Fl-TS Calc : NORMAL OPERATIO Case: 1 9:50a Jul 11,2013
Input Echo, Tubesheet Number 1, Description: FLOATING TUBESH
Shell Data:Main Shell Description: SHELL
Shell Design Pressure Ps 2.00 MPa
Shell Thickness ts 10.0000 mm
Shell Corrosion Allowance cas 3.0000 mm
Inside Diameter of Shell Ds 635.000 mm
Shell Temperature for Internal Pressure Ts 100.00 C
Shell Material SA-516 70
Note: Using 2 * Yield for Discontinuity Stress Allowable (UG-23(e)), Sps.Make sure that material properties at this temperature are nottime-dependent for Material: SA-516 70
Shell Material UNS Number K02700
Shell Allowable Stress at Temperature Ss 137.90 MPa
Shell Allowable Stress at Ambient 137.90 MPa
Channel Description: FC SHELL Channel Type: Cylinder
Channel Design Pressure Pt 0.50 MPa
Channel Thickness tc 10.0000 mm
Channel Corrosion Allowance cac 3.0000 mm
Inside Diameter of Channel Dc 635.000 mm
Channel Design Temperature TEMPC 15.00 C
Channel Material SA-516 70
Note: Using 2 * Yield for Discontinuity Stress Allowable (UG-23(e)), Sps.Make sure that material properties at this temperature are nottime-dependent for Material: SA-516 70
Channel Material UNS Number K02700
Channel Allowable Stress at Temperature Sc 137.90 MPa
Channel Allowable Stress at Ambient 137.90 MPa
Tube Data: Number of Tube Holes Nt 468
Tube Wall Thickness et 2.1100 mm
Tube Outside Diameter D 19.0500 mm
Straight Tube Length (bet. inner tubsht faces) L 3952.00 mm
Design Temperature of the Tubes 100.00 C
Tube Material SA-179
Tube Material UNS Number K01200
Is this a Welded Tube No
Tube Material Specification used Smls. tube
Tube Allowable Stress at Temperature 92.39 MPa
Tube Allowable Stress At Ambient 92.39 MPa
Tube Yield Stress At design Temperature Syt 163.44 MPa
Tube Pitch (Center to Center Spacing) P 23.8120 mm
Tube Layout Pattern Triangular
Fillet Weld Leg af 2.0000 mm
Groove Weld Leg ag 0.0000 mm
Tube-Tubesheet Joint Weld Type Partial Strength
Method for Tube-Tubesheet Jt. Allow. UW-20
Tube-Tubesheet Joint Classification i
Radius to Outermost Tube Hole Center ro 310.000 mm
Largest Center-to-Center Tube Distance Ul 38.0000 mm
Length of Expanded Portion of Tube ltx 40.0000 mm
Tube-side pass partition groove depth hg 5.0000 mm
Tubesheet Data:
Tubesheet TYPE: UNKNOWN Exchanger TYPE: With an Immersed Floating Head, Conf. a
Tubesheet Design Metal Temperature T 100.00 C
Tubesheet Material Specification SA-266 4
Note: Using 2 * Yield for Discontinuity Stress Allowable (UG-23(e)), Sps.Make sure that material properties at this temperature are nottime-dependent for Material: SA-266 4
Tubesheet Material UNS Number K03017
Tubesheet Allowable Stress at Temperature S 137.90 MPa
Tubesheet Allowable Stress at Ambient Tt 137.90 MPa
Thickness of Tubesheet h 54.0000 mm
Tubesheet Corr. Allowance (Shell side) Cats 3.0000 mm
Tubesheet Corr. Allowance (Channel side) Catc 3.0000 mm
Tubesheet Outside Diameter A 625.000 mm
Area of the Untubed Lanes AL 47182.0 mm²
Additional Data for Fixed/Floating Tubesheet Exchangers: Unsupported Tube Span under consideration l 380.000 mm
Tube End condition corresponding to Span (l) k 0.80
Ignore Radial Thermal Exp. effects (UHX-13.8/14.6) YES
Note: The Metal temperatures at the Rim are set to ambient (21 C)
Tubesheet Metal Temp. at Rim T' 21.11 C
Shell Metal Temp. at Tubesheet T'S 21.11 C
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 89 of 94
ASME Fl-TS Calc : NORMAL OPERATIO Case: 1 9:50a Jul 11,2013
Channel Metal Temp. at Tubesheet T'C 21.11 C
Perform Differential Pressure Design N
Run Multiple Load Cases YES
Junction Stress Reduction option None
Additional Data for Gasketed Tubesheets: Tubesheet Gasket on which Side Channel
Flange Outside Diameter A 708.000 mm
Flange Inside Diameter B 593.000 mm
Flange Face Outside Diameter Fod 628.000 mm
Flange Face Inside Diameter Fid 593.000 mm
Gasket Outside Diameter Go 625.000 mm
Gasket Inside Diameter Gi 599.000 mm
Gasket Factor, m 2.00
Gasket Design Seating Stress y 11.03 MPa
Flange Facing Sketch Code Sketch 1a
Column for Gasket Seating Code Column I
Gasket Thickness tg 3.0000 mm
Full face Gasket Flange Option Program Selects
Length of Partition Gasket lp 890.000 mm
Width of Partition Gasket wp 10.0000 mm
Partition Gasket Factor, mPart 2.0000
Partition Gasket Design Seating Stress yPart 11.03 MPa
Partition Gasket Facing Sketch Code Sketch 1a
Partition Gasket Column for Gasket Seating Code Column I
Bolting Information: Diameter of Bolt Circle C 660.000 mm
Nominal Bolt Diameter dB 20.0000 mm
Type of Thread Series TEMA Metric Thread
Number of Bolts n 24
Bolt Material SA-193 B7
Bolt Material UNS Number G41400
Bolt Allowable Stress At Temperature Sb 172.38 MPa
Bolt Allowable Stress At Ambient Sa 172.38 MPa
Weld between Flange and Shell/Channel 0.0000 mm
Tubesheet Extended as Flange Yes
Thickness of Extended Portion of Tubesheet Tf 0.0000 mm
Is Bolt Load Transferred to the Tubesheet No
Is Exchanger in Creep range (skip EP, Use 3S for Sps) NO
Notes/Error Messages/Warnings for Tubesheet number 1
ERROR - The selected Tubesheet Type is not a valid per ASME, check the input.
Warning: Bolt load is not transferred to tubesheet which is extended for
bolting. Req. Tubesheet extension thk. can't be computed. Please check input
Number of fatal errors: 1. Analysis of this tubesheet will be halted.
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 90 of 94
Flohead Analysis : FLOATING COVER Case: 1 9:50a Jul 11,2013
Input Echo, Floating Head Item 1, Description: FLOATING COVER
Floating Head Type Appendix 1-6 type (d)
Tube Side ( Internal ) Design Pressure Pts 0.50 MPa
Shell Side ( External ) Design Pressure Pss 2.00 MPa
Design Temperature for Spherical Head Temp 150.00 C
Head Material SA-516 70
Head Material UNS Number K02700
Head Allowable Stress at Temperature Sho 137.90 MPa
Head Allowable Stress at Ambient Sha 137.90 MPa
Crown Radius for Spherical Head L 445.000 mm
Head Thickness Th 16.000 mm
Tube Side ( Internal ) Corrosion Allowance Cats 3.0000 mm
Shell Side ( External ) Corrosion Allowance Cass 3.0000 mm
Flange Material SA-105
Flange Material UNS Number K03504
Flange Allowable Stress at Temperature Sfo 137.90 MPa
Flange Allowable Stress at Ambient Sfa 137.90 MPa
Flange Outside Diameter Fod 708.000 mm
Flange Inside Diameter Fid 593.000 mm
Flange Thickness Tf 65.0000 mm
Bolt Material SA-193 B7
Bolt Material UNS Number G41400
Bolt Allowable Stress At Temperature Sb 172.38 MPa
Bolt Allowable Stress At Ambient Sa 172.38 MPa
Diameter of Bolt Circle C 660.000 mm
Nominal Bolt Diameter dB 20.0000 mm
Type of Threads TEMA Metric Thread
Number of Bolts 24
Full face Gasket Flange Option Not a Full Face
Flange Face Outside Diameter Ffod 628.000 mm
Flange Face Inside Diameter Ffid 593.000 mm
Gasket Outside Diameter Go 625.000 mm
Gasket Inside Diameter Gi 599.000 mm
Gasket Factor, m 2.0000
Gasket Design Seating Stress y 11.03 MPa
Flange Facing Sketch Code Sketch 1a
Column for Gasket Seating Code Column I
Gasket Thickness 3.0000 mm
Flange Face Nubbin Width 0.0000 mm
Length of Partition Gasket 890.000 mm
Width of Partition Gasket 10.0000 mm
Partition Gasket Factor, mPart 2.0000
Partition Gasket Design Seating Stress yPart 11.03 MPa
Partition Gasket Facing Sketch Code Sketch 1a
Partition Gasket Column for Gasket Seating Code Column I
Dist. from Head Centerline to Flange Centroid hr 23.2296 mm
The Flange is not Slotted.
Backing Ring Material Specification SA-105
Backing Ring Material UNS Number K03504
Backing Ring Allowable Stress, Temperature Sots 137.90 MPa
Backing Ring Allowable Stress, Ambient Sats 137.90 MPa
Backing Ring Inside Diameter Dr 599.000 mm
Backing Ring Thickness Tr 79.0000 mm
Number of Splits in Backing Ring nsp 1
Internal Pressure results for Spherical headsASME Code, Section VIII, Div. 1, 2010, 2011a Appendix 1-6
Thickness Due to Internal Pressure[thr]: = 5PL / 6Sho
= ( 5 * 0.50 * 448.0000 ) / ( 6 * 137 )
= 1.3536 mm
Maximum Allowable Working Pressure at Given Thickness[Pa]: = 6Sho* (Th-Cass-Cats) / 5L
= ( 6 * 137 * 10.0000 ) / ( 5 * 448.0000 )
= 3.69 MPa
Maximum Allowable Pressure, New and Cold[Pnc]: = 6Sha / 5L
= ( 6 * 137 * 16.0000 ) / ( 5 * 445.0000 )
= 5.95 MPa
Actual Stress at given Pressure and Thickness[Sact]: = 5PL / 6(Th-Cass-Cats)
= ( 5 * 0.50 * 448.0000 ) / ( 6 * 10.0000 )
= 19. MPa
External Pressure results, Spherical headASME Code, Section VIII, Division 1, 2010, 2011a
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 91 of 94
Flohead Analysis : FLOATING COVER Case: 1 9:50a Jul 11,2013
External Pressure Chart CS-2 at 150.00 C
Elastic Modulus for Material 199818.77 MPa
Results for Maximum Allowable External Pressure: Corroded Thickness of Shell TCA 10.0000 mm
Outside Crown Radius of Shell OD/2 458.0000 mm
Crown Radius / Thickness Ratio (0D/2)/T 45.8000
Geometry Factor, A f(D/T,LD) A 0.0027293
Materials Factor, B, f(A, Chart) B 109.9170 MPa
Maximum Allowable Working Pressure 2.40 MPa
EMAWP = B/( (0D/T)/ 2 ) = 109.9170 /(91.6000 /2.0) = 2.3999
Results for Reqd Thickness for Ext. Pressure (Tca): Corroded Thickness of Head TCA 8.5711 mm
Outside Diameter of Shell ODCA 916.000 mm
Diameter / Thickness Ratio (D/T) 106.8710
Geometry Factor, A f(DT,LD) A 0.0023393
Materials Factor, B, f(A, Chart) B 106.8824 MPa
Maximum Allowable Working Pressure 2.00 MPa
EMAWP = B/((D/T)/2) = 106.8824 /(106.8710 / 2 ) = 2.0002
Intermediate Calculations for Flanged portion:
ASME Code, Section VIII, Div. 1, 2010, 2011a Appendix 2
Gasket Contact Width, N = (Goc-Gic) / 2 13.000 mm
Basic Gasket Width, b0 = N / 2.0 6.500 mm
Effective Gasket Width, b = SQRT(b0) * 2.5 6.422 mm
Gasket Reaction Diameter, G = Go-2.0*b 612.156 mm
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]: = 2a + 6t/(m + 0.5)
= 2 * 20.000 + 6 * 65.000 /(2.00 + 0.5)
= 196.000 mm
Actual Circumferential Bolt Spacing [Bs]: = C * sin( pi / n ) )
= 660.000 * sin( 3.142 / 24 )
= 86.147 mm
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]: = max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 86.147 /( 2 * 20.000 + 65.000 )), 1 )
= 1.0000
Bolting Information for TEMA Metric Thread Series (Non Mandatory): Total Area of Bolts 5209.224 mm²
-----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Radial distance bet. bolts and the edge 23.810 24.000
Circumferential spacing between bolts 52.390 86.147 196.000
-----------------------------------------------------------------------------
Results for the Internal Pressure case:
Basic Flange and Bolt loads: Hydrostatic End Load due to Pressure H 147145.4 N
Contact Load on Gasket Surfaces Hp 33598.8 N
Hydrostatic End Load at Flange ID Hd 140888.8 N
Pressure Force on Flange Face Ht 6256.5 N
Radial Component of Head Membrane Force Hr 159429.2 N
Operating Bolt Load: Wm1 180744.2 N
Gasket Seating Bolt Load Wm2 185331.1 N
Required Bolt Area Am 1075.254 mm²
Min. Gasket Contact Width (Brownell Young) [Not an ASME Calculation]: = Ab * Sb/(y * PI * (Go+Gi) )
= 5209.224 * 172.38 /(11.03 * 3.14 * (625.00 + 599.00 ) )
= 21.167 mm[Note: Exceeds actual gasket width, 13.000 ]
Flange Design Bolt Load (Seating) W 541597.4 N
Gasket Seating Force (Operating) Hg 33598.8 N
Distance to Gasket Load Reaction hg 23.9222 mm
Distance to Face Pressure Reaction ht 27.2111 mm
Distance to End Pressure Reaction hd 30.5000 mm
Summary of Moments for Internal Pressure: Loading Force Distance Bolt Corr Moment
End Pressure, Md 140889. 30.5000 1.0000 4298852. N-mm
Face Pressure, Mt 6257. 27.2111 1.0000 170316. N-mm
Gasket Load, Mg 33599. 23.9222 1.0000 804084. N-mm
Floating Hd. Load, Mh 159429. 23.2296 1.0000 -3704978. N-mm
Gasket Seating, Ma 541597. 23.9222 1.0000 12961458. N-mm
Total Moment for Operation ( Internal Pressure ) 1568274.000 N-mm
Total Moment for Gasket Seating ( Int. Pressure ) 12961458.000 N-mm
Results for the External Pressure case:
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 92 of 94
Flohead Analysis : FLOATING COVER Case: 1 9:50a Jul 11,2013
Basic Flange and Bolt loads: Hydrostatic End Load due to Pressure H 588581.4 N
Hydrostatic End Load at Flange ID Hd 563555.4 N
Pressure Force on Flange Face Ht 25026.1 N
Radial Component of Head Membrane Force Hr 637716.8 N
Gasket Seating Bolt Load Wm2 185331.1 N
Required Bolt Area Am 1075.254 mm²
Flange Design Bolt Load (Seating) W 541597.4 N
Distance to Gasket Load Reaction hg 23.9222 mm
Distance to Face Pressure Reaction ht 27.2111 mm
Distance to End Pressure Reaction hd 30.5000 mm
Summary of Moments for External Pressure: Loading Force Distance Bolt Corr Moment
End Pressure, Md 563555. 6.5778 1.0000 3708456. N-mm
Face Pressure, Mt 25026. 3.2889 1.0000 82342. N-mm
Floating Hd. Load, Mh 637717. 23.2296 1.0000 -14819914. N-mm
Gasket Seating, Ma 541597. 23.9222 1.0000 12961458. N-mm
Total Moment for Operation ( External Pressure ) 11029118.000 N-mm
Total Moment for Gasket Seating ( Ext. Pressure ) 12961458.000 N-mm
Required thickness for Main Flange, internal operating conditions: [T] = F + SQRT( F * F + J ) per 1-6(g)
= 1.756+SQRT(1.756*1.756+239.735)
= 17.3390 mm
Required thickness for Main Flange, internal bolt-up conditions: [T] = F + SQRT( F * F + J ) per 1-6(g)
= 0.000+SQRT(0.000*0.000+1981.362)
= 44.5125 mm
Required thickness for Main Flange, external operating conditions: [T] = F + SQRT( F * F + J ) per 1-6(g)
= 7.025+SQRT(7.025*7.025+1685.974)
= 48.6826 mm
Required thickness for Main Flange, external bolt-up conditions: [T] = F + SQRT( F * F + J ) per 1-6(g)
= 0.000+SQRT(0.000*0.000+1981.362)
= 44.5125 mm
Required thickness for Backing Ring, internal operating conditions: [T] = SQRT( WM1 * h * Split_fac * Y / S B ) Per TEMA 8th ed. RCB-5.141
= SQRT(180744.2*30.50*2.00*11.699/(137.9*599.000))
= 39.5187 mm
Required thickness for Backing Ring, internal bolt-up conditions: [T] = SQRT( W * h * Split_fac * Y / S B ) Per TEMA 8th ed. RCB-5.141
= SQRT(541597*30.50*2.00*11.699/(137.9*599.000))
= 68.4083 mm
Summary of Required Thicknesses: Head Flange Backing Ring
Tubeside (Internal) Pressure 1.3536 17.3390 39.5187 mm
Shellside (External) Pressure 8.5711 48.6826 mm
Tubeside Gasket Seating Load 44.5125 68.4083 mm
Shellside Gasket Seating Load 44.5125 mm
Maximum + Corrosion Allowance 14.5711 54.6826 68.4083 mm
Actual Thickness as Given 16.0000 65.0000 79.0000 mm
Floating Head MAWP and MAPnc (MPa):
Stress | Tubeside | Shellside |
Condition | MAWP | MAPnc | MAWP | MAPnc |
------------------------------------------------------------------------------
Flange Stress | 2.00 | 2.00 | 2.75 | 4.02 |
Floating head Stress | 3.69 | 5.95 | 2.40 | 4.08 |
Bolt Stress | 2.48 | 2.48 | ---- | ---- |
------------------------------------------------------------------------------
Minimum MAWP & MAPnc | 2.00 | 2.00 | 2.40 | 4.02 |
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 93 of 94
Vessel Design Summary : Step: 26 9:50a Jul 11,2013
Design Code: ASME Code Section VIII Division 1, 2010, 2011a
Diameter Spec : 635.000 x 724.000 mm ID
Vessel Design Length, Tangent to Tangent 4923.00 mm
Specified Datum Line Distance 0.00 mm
Shell Material Specification SA-516 70
Nozzle Material Specification SA-106 B
Re-Pad Material Specification SA-516 70
Shell Side Design Temperature 100 C
Channel Side Design Temperature 15 C
Shell Side Design Pressure 2.000 MPa
Channel Side Design Pressure 0.500 MPa
Shell Side Hydrostatic Test Pressure 2.732 MPa
Channel Side Hydrostatic Test Pressure 0.672 MPa
Required Minimum Design Metal Temperature 0 C
Warmest Computed Minimum Design Metal Temperature -29 C
Wind Design Code ASCE-93
Earthquake Design Code UBC-94
Element Pressures and MAWP: MPa
Element Desc | Design Pres. | External | M.A.W.P | Corrosion
| + Stat. head | Pressure | | Allowance
---------------------------------------------------------------------
FC COVER 0.500 0.103 0.841 3.1750
FC#CV FLANGE 0.500 0.103 1.013 3.0000
FC SHELL 0.500 0.103 2.527 3.0000
FC#SH FLANGE 0.500 0.103 0.517 3.0000
SH#FC FLANGE 2.000 0.103 2.102 3.0000
SHELL 2.000 0.103 2.527 3.0000
SH#RC FLANGE 2.000 0.103 2.243 3.0000
RC#SH FLANGE 2.000 0.103 2.285 3.0000
RC SHELL 2.000 0.103 2.222 3.0000
RC HEAD 2.000 0.103 2.268 3.0000
Element "To" Elev Length Element Thk R e q d T h k Joint Eff
Type mm mm mm Int. Ext. Long Circ
-----------------------------------------------------------------------
Body Flg 43.0 43.0 43.0 35.3 28.8 1.00 1.00
Body Flg 90.0 47.0 47.0 42.8 42.8 1.00 1.00
Cylinder 693.0 650.0 10.0 4.5 5.1 0.85 0.85
Body Flg 693.0 76.0 76.0 72.6 62.5 1.00 1.00
Body Flg 840.0 93.0 60.0 58.6 38.4 1.00 1.00
Cylinder 4465.0 3625.0 10.0 8.5 7.3 0.85 0.85
Body Flg 4573.0 108.0 75.0 69.7 28.4 1.00 1.00
Body Flg 4663.0 90.0 80.0 66.8 46.7 1.00 1.00
Cylinder 4873.0 300.0 10.0 9.3 4.9 0.85 0.85
Ellipse 4923.0 50.0 12.0 9.2 4.9 0.85 0.85
Element thicknesses are shown as Nominal if specified, otherwise are Minimum
Saddle Parameters: Saddle Width 101.600 mm
Saddle Bearing Angle 120.000 deg.
Centerline Dimension 609.600 mm
Wear Pad Width 152.400 mm
Wear Pad Thickness 9.525 mm
Wear Pad Bearing Angle 130.000 deg.
Distance from Saddle to Tangent 209.550 mm
Baseplate Length 685.800 mm
Baseplate Thickness 12.700 mm
Baseplate Width 101.600 mm
Number of Ribs (including outside ribs) 4
Rib Thickness 6.350 mm
Web Thickness 6.350 mm
Height of Center Web 228.600 mm
Summary of Maximum Saddle Loads, Operating Case : Maximum Vertical Saddle Load 21594.77 N
Maximum Transverse Saddle Shear Load 788.75 N
Maximum Longitudinal Saddle Shear Load 194.49 N
Summary of Maximum Saddle Loads, Hydrotest Case : Maximum Vertical Saddle Load 26318.06 N
Maximum Transverse Saddle Shear Load 260.29 N
Maximum Longitudinal Saddle Shear Load 64.18 N
Weights: Fabricated - Bare W/O Removable Internals 3625.9 kgm
Shop Test - Fabricated + Water ( Full ) 5065.9 kgm
Shipping - Fab. + Rem. Intls.+ Shipping App. 3625.9 kgm
Erected - Fab. + Rem. Intls.+ Insul. (etc) 3625.9 kgm
Empty - Fab. + Intls. + Details + Wghts. 3625.9 kgm
Operating - Empty + Operating Liquid (No CA) 3954.0 kgm
Field Test - Empty Weight + Water (Full) 5065.9 kgm
PV Elite 2012 Licensee: JACOBS H&G
FileName : Floating Head HE ------------------------------ Page 94 of 94
Vessel Design Summary : Step: 26 9:50a Jul 11,2013
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012