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Transcript of E-6012_DC ad adasd ad adqwe adas da
MSET ENGINEERING CORPORATION SDN BHD
DOCUMENT TITLE: DESIGN CALCULATION DATE: 11.01.2015
DOC. REF. NO.: MSET/M2-251/E-6012/DC REVISION: 02
SUBJECT: TITLE PAGE JOB NO: M2-251
SERIAL NO.: MSET/003
DESIGN CALCULATION
Fuel Gas Super Heater TAG NO: E-6012
PROJECT NAME: E6 Development Project
CLIENT NAME: VME Process
02 11.01.15 Issued for Approval Mohd Faizal Yahasliza Azahar 01 11.12.14 Issued for Review Muhd Faizal Yahasliza Azahar
Rev. No.
Date Description of Revision Prepared
by Reviewed
by Approved
by
MSET ENGINEERING CORPORATION SDN BHD
DOCUMENT TITLE: DESIGN CALCULATION DATE: 11.01.2015
DOC. REF. NO.: MSET/M2-251/E-6012/DC REVISION: 02
SUBJECT: TITLE PAGE JOB NO: M2-251
SERIAL NO.: M2-234/003
DESIGN DATA
ITEM NO. FUEL GAS SUPER HEATER
DESIGN CODE ASME SEC.VIII DIV.1, 2013 EDITION +
DEP 31.22. 20.31
DESIGN PRESSURE (barg) (Int./Ext.) 18/FV
TEMPERATURE (⁰C) (Max./Min) 50/0
OPERATING PRESSURE (barg) (In / Out) 6.8 / 6.0
TEMPERATURE (⁰C) (In / Out) 24.7-38.8 / 39.7-48.8
TEST PRESSURE
HYDROTEST (barg) (1.3xMAPxLSR)(note1) (UG-99c)
24.647 (Horizontal Position)
PNEUMATIC NO
MAWP (hot & corroded) (barg) 18.398
MAP (new & cold) (barg) 18.998
OUTSIDE DIAMETER / SEAM TO SEAM (mm) 114.3/1050
TYPE OF HEAD CAP / BODY FLANGE
MATERIAL OF CONSTRUCTION (SHELL & HEAD) SA 312 TP 316 & SA 182 F 316/SA 403 GR 316
HEAT TREATMENT
NORMALISED NO
PWHT NO
IMPACT TEST YES
MDMT (⁰C) 0
RADIOGRAPHY HEAD: 100%, SHELL: 100%
JOINT EFFICIENCY HEAD:1.0 , SHELL: 1.0
CORROSION ALLOWANCE (mm) 0
CONTENTS HC LIQUID/GAS
ERECTION WEIGHT (kg) 80
CAPACITY (m3) 0.01
PRESSURE VESSEL DESIGN CALCULATION Note: 1.MAP will be used in lieu of MAWP for determining hydro test pressure (As per DEP 31.22.20.31-Gen, Jan 09)
MSET ENGINEERING CORPORATION SDN BHD
DOCUMENT TITLE: DESIGN CALCULATION DATE: 11.01.2015
DOC. REF. NO.: MSET/M2-251/E-6012/DC REVISION: 02
SUBJECT: TITLE PAGE JOB NO: M2-251
SERIAL NO.: M2-251/003
TABLE OF CONTENT
NO CONTENT PAGE NO.
1 Input Echo 4
2 Flg Calc [Int P] : H1 (flange) 13
3 Internal Pressure Calculations 19
4 External Pressure Calculations 24
5 Element and Detail Weights 28
6 Nozzle Flange MAWP 31
7 Wind Load Calculation 32
8 Earthquake Load Calculation 33
9 Center of Gravity Calculation 34
10 Lifting Lug Calc : Left Side 37
11 Lifting Lug Calc : Right Side 49
12 Horizontal Vessel Analysis (Ope.) 61
13 Horizontal Vessel Analysis (Test) 85
14 Nozzle Calculation 104
15 Nozzle Schedule 149
16 Nozzle Summary 151
17 MDMT Summary 153
18 Vessel Design Summary 155
19 Attachment 1 : Wind Pressure Calc 158
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Input Echo : Step: 1 12:36p Jan 11,2015
PV Elite Vessel Analysis Program: Input Data
Design Internal Pressure (for test) 18.000 bar
Design Internal Temperature 50 °C
Type of Test UG-99(c)
Test Position Horizontal
Projection of Nozzle from Vessel Top 200.00 mm
Projection of Nozzle from Vessel Bottom 200.00 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 Pressure test N
Is this a Heat Exchanger No
User Defined Test Press. (Used if > 0) 0.0000 bar
User defined MAWP 0.0000 bar
User defined MAPnc 0.0000 bar
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
4
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Input Echo : Step: 1 12:36p Jan 11,2015 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 User Defined
Wind Profile Height mm Pressure kPa
10000.0000 0.7500
0.0000 0.0000
0.0000 0.0000
0.0000 0.0000
0.0000 0.0000
0.0000 0.0000
0.0000 0.0000
0.0000 0.0000
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 G Loading
5
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Input Echo : Step: 1 12:36p Jan 11,2015 Seismic Importance Factor 1.000
G Loading Coefficient Gx 0.500
G Loading Coefficient Gz 0.500
G Loading Coefficient Gy -2.000
Percent Seismic for Test 0.000
Design Nozzle for M.A.W.P. (maximum) 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 20
Element To Node 30
Element Type Flange
Description Body flange
Distance "FROM" to "TO" 75.000 mm
Flange Inside Diameter (OD for Blinds) 102.36 mm
6
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Input Echo : Step: 1 12:36p Jan 11,2015 Element Thickness 22.300 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 24.300 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 18.000 bar
Design Temperature Internal Pressure 50 °C
Design External Pressure 1.0341 bar
Design Temperature External Pressure 50 °C
Effective Diameter Multiplier 1.2
Material Name SA-182 F316
Allowable Stress, Ambient 137.90 MPa
Allowable Stress, Operating 137.90 MPa
Allowable Stress, Hydrotest 186.17 MPa
Material Density 8027.2 kg/m³
P Number Thickness 0.0000 mm
Yield Stress, Operating 217.74 MPa
External Pressure Chart Name HA-2
UNS Number S31600
Class / Thickness / Grade :: > 5
Product Form Forgings
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
Detail Type Insulation
Detail ID Ins: 20
Dist. from "FROM" Node / Offset dist 0.0000 mm
Height/Length of Insulation 75.000 mm
Thickness of Insulation 40.000 mm
Density 8940.0 kg/m³
7
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Input Echo : Step: 1 12:36p Jan 11,2015
--------------------------------------------------------------------
Element From Node 30
Element To Node 40
Element Type Cylinder
Description Shell
Distance "FROM" to "TO" 1050.0 mm
Element Outside Diameter 114.30 mm
Element Thickness 7.4898 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 8.5598 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 18.000 bar
Design Temperature Internal Pressure 50 °C
Design External Pressure 1.0341 bar
Design Temperature External Pressure 50 °C
Effective Diameter Multiplier 1.2
Material Name SA-312 TP316
Allowable Stress, Ambient 137.90 MPa
Allowable Stress, Operating 137.90 MPa
Allowable Stress, Hydrotest 186.17 MPa
Material Density 8027.2 kg/m³
P Number Thickness 0.0000 mm
Yield Stress, Operating 198.97 MPa
External Pressure Chart Name HA-2
UNS Number S31600
Product Form Smls. & wld. pipe
Efficiency, Longitudinal Seam 1.0
Efficiency, Circumferential Seam 1.0
Element From Node 30
8
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Input Echo : Step: 1 12:36p Jan 11,2015 Detail Type Saddle
Detail ID Fixed
Dist. from "FROM" Node / Offset dist 164.00 mm
Width of Saddle 70.000 mm
Height of Saddle at Bottom 255.00 mm
Saddle Contact Angle 120.0
Height of Composite Ring Stiffener 0.0000 mm
Width of Wear Plate 102.00 mm
Thickness of Wear Plate 8.0000 mm
Contact Angle, Wear Plate (degrees) 132.0
Element From Node 30
Detail Type Saddle
Detail ID Sliding
Dist. from "FROM" Node / Offset dist 804.00 mm
Width of Saddle 70.000 mm
Height of Saddle at Bottom 255.00 mm
Saddle Contact Angle 120.0
Height of Composite Ring Stiffener 0.0000 mm
Width of Wear Plate 102.00 mm
Thickness of Wear Plate 8.0000 mm
Contact Angle, Wear Plate (degrees) 132.0
Element From Node 30
Detail Type Insulation
Detail ID Insulation
Dist. from "FROM" Node / Offset dist 0.0000 mm
Height/Length of Insulation 1050.0 mm
Thickness of Insulation 40.000 mm
Density 8940.0 kg/m³
Element From Node 30
9
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Input Echo : Step: 1 12:36p Jan 11,2015 Detail Type Nozzle
Detail ID N1
Dist. from "FROM" Node / Offset dist 123.65 mm
Nozzle Diameter 2.0 in.
Nozzle Schedule None
Nozzle Class 150
Layout Angle 0.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 67.101 N
Grade of Attached Flange GR 2.2
Nozzle Matl SA-182 F316
Element From Node 30
Detail Type Nozzle
Detail ID N2
Dist. from "FROM" Node / Offset dist 931.65 mm
Nozzle Diameter 2.0 in.
Nozzle Schedule None
Nozzle Class 150
Layout Angle 180.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 67.101 N
Grade of Attached Flange GR 2.2
Nozzle Matl SA-182 F316
Element From Node 30
Detail Type Nozzle
Detail ID N3
Dist. from "FROM" Node / Offset dist 427.65 mm
Nozzle Diameter 2.0 in.
Nozzle Schedule None
Nozzle Class 150
10
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Input Echo : Step: 1 12:36p Jan 11,2015 Layout Angle 180.0
Blind Flange (Y/N) N
Weight of Nozzle ( Used if > 0 ) 67.101 N
Grade of Attached Flange GR 2.2
Nozzle Matl SA-182 F316
Element From Node 30
Detail Type Weight
Detail ID HEATER
Dist. from "FROM" Node / Offset dist 155.00 mm
Miscellaneous Weight 980.60 N
Offset from Element Centerline 0.0000 mm
--------------------------------------------------------------------
Element From Node 40
Element To Node 50
Element Type Elliptical
Description Head
Distance "FROM" to "TO" 39.700 mm
Element Outside Diameter 114.30 mm
Element Thickness 7.4898 mm
Internal Corrosion Allowance 0.0000 mm
Nominal Thickness 8.5598 mm
External Corrosion Allowance 0.0000 mm
Design Internal Pressure 18.000 bar
Design Temperature Internal Pressure 50 °C
Design External Pressure 1.0341 bar
Design Temperature External Pressure 50 °C
Effective Diameter Multiplier 1.2
Material Name SA-403 316
Allowable Stress, Ambient 137.90 MPa
11
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Input Echo : Step: 1 12:36p Jan 11,2015 Allowable Stress, Operating 137.90 MPa
Allowable Stress, Hydrotest 186.17 MPa
Material Density 8027.2 kg/m³
P Number Thickness 0.0000 mm
Yield Stress, Operating 198.97 MPa
External Pressure Chart Name HA-2
UNS Number S31600
Product Form Smls. & wld. fittings
Efficiency, Longitudinal Seam 1.0
Efficiency, Circumferential Seam 1.0
Elliptical Head Factor 2.0
Element From Node 40
Detail Type Insulation
Detail ID Ins: 40
Dist. from "FROM" Node / Offset dist 0.0000 mm
Height/Length of Insulation 68.275 mm
Thickness of Insulation 40.000 mm
Density 8940.0 kg/m³
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
12
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Flg Calc [Int P] : H1 (flange) Flng: 2 12:36p Jan 11,2015
Flange Input Data Values Description: H1 (flange) :
Body flange
Description of Flange Geometry (Type) Integral Weld Neck
Design Pressure P 18.00 bar
Design Temperature 50 °C
Internal Corrosion Allowance ci 0.0000 mm
External Corrosion Allowance ce 0.0000 mm
Use Corrosion Allowance in Thickness Calcs. No
Flange Inside Diameter B 102.362 mm
Flange Outside Diameter A 230.000 mm
Flange Thickness t 22.3000 mm
Thickness of Hub at Small End go 7.4898 mm
Thickness of Hub at Large End g1 17.7768 mm
Length of Hub h 52.7000 mm
Flange Material SA-182 F316
Flange Material UNS number S31600
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 190.500 mm
Nominal Bolt Diameter a 15.8750 mm
Type of Threads TEMA Thread Series
Number of Bolts 8
13
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Flg Calc [Int P] : H1 (flange) Flng: 2 12:36p Jan 11,2015
Flange Face Outside Diameter Fod 157.200 mm
Flange Face Inside Diameter Fid 102.362 mm
Flange Facing Sketch 1, Code Sketch 1a
Gasket Outside Diameter Go 149.352 mm
Gasket Inside Diameter Gi 127.000 mm
Gasket Factor m 0.0000
Gasket Design Seating Stress y 0.00 MPa
Column for Gasket Seating 2, Code Column II
Gasket Thickness tg 3.1750 mm
ANSI Flange Class 150
ANSI Flange Grade GR 2.2
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)
= (18.00*(102.3620/2+0.0000))/(137.90*1.00-0.6*18.00)+Ca
= 0.6734 mm
Hub Small End Hub MAWP:
= (S*E*t)/(R+0.6*t) per UG-27 (c)(1)
= (137.90 * 1.00 * 7.4898 )/(51.1810 + 0.6 * 7.4898 )
= 185.487 bar
Corroded Flange ID, Bcor = B+2*Fcor 102.362 mm
Corroded Large Hub, g1Cor = g1-ci 17.777 mm
Corroded Small Hub, g0Cor = go-ci 7.490 mm
14
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Flg Calc [Int P] : H1 (flange) Flng: 2 12:36p Jan 11,2015 Code R Dimension, R = (C-B)/2 - g1 26.292 mm
Gasket Contact Width, N = (Go - Gi) / 2 11.176 mm
Basic Gasket Width, bo = N / 2 5.588 mm
Effective Gasket Width, b = bo 5.588 mm
Gasket Reaction Diameter, G = Go (Self-Energizing) 149.352 mm
Basic Flange and Bolt Loads:
Hydrostatic End Load due to Pressure [H]:
= 0.785 * G² * Peq
= 0.785 * 149.3520² * 18.000
= 31536.289 N
Contact Load on Gasket Surfaces [Hp]:
= 2 * b * Pi * G * m * P
= 2 * 5.5880 * 3.1416 * 149.3520 * 0.0000 * 18.00
= 0.000 N
Hydrostatic End Load at Flange ID [Hd]:
= Pi * Bcor² * P / 4
= 3.1416 * 102.3620² *18.0000/4
= 14813.786 N
Pressure Force on Flange Face [Ht]:
= H - Hd
= 31536 - 14813
= 16722.504 N
Operating Bolt Load [Wm1]:
= max( H + Hp + H'p, 0 )
= max( 31536 + 0 + 0 , 0 )
= 31536.289 N
Gasket Seating Bolt Load [Wm2]:
= y * b * Pi * G + yPart * bPart * lp
15
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Flg Calc [Int P] : H1 (flange) Flng: 2 12:36p Jan 11,2015 = 0.00*5.5880*3.141*149.352+0.00*0.0000*0.00
= 0.000 N
Required Bolt Area [Am]:
= Maximum of Wm1/Sb, Wm2/Sa
= Maximum of 31536/172 , 0/172
= 182.967 mm²
ASME Maximum Circumferential Spacing between Bolts per App. 2 eq. (3) [Bsmax]:
= 2a + 6t/(m + 0.5)
= 2 * 15.875 + 6 * 22.300/(0.00 + 0.5)
= 299.350 mm
Actual Circumferential Bolt Spacing [Bs]:
= C * sin( pi / n )
= 190.500 * sin( 3.142/8 )
= 72.901 mm
ASME Moment Multiplier for Bolt Spacing per App. 2 eq. (7) [Bsc]:
= max( sqrt( Bs/( 2a + t )), 1 )
= max( sqrt( 72.901/( 2 * 15.875 + 22.300 )), 1 )
= 1.1614
Bolting Information for TEMA Imperial Thread Series (Non Mandatory):
-----------------------------------------------------------------------------
Minimum Actual Maximum
-----------------------------------------------------------------------------
Bolt Area, mm² 182.967 1042.579
Radial distance bet. hub and bolts 23.812 26.292
Radial distance bet. bolts and the edge 19.050 19.750
Circumferential spacing between bolts 38.100 72.901 299.350
-----------------------------------------------------------------------------
16
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Flg Calc [Int P] : H1 (flange) Flng: 2 12:36p Jan 11,2015
Flange Design Bolt Load, Gasket Seating [W]:
= Sa * ( Am + Ab ) / 2
= 172.38 * ( 182.9672 + 1042.5786 )/2
= 105617.75 N
Gasket Load for the Operating Condition [HG]:
= Wm1 - H
= 31536 - 31536
= 0.00 N
Moment Arm Calculations:
Distance to Gasket Load Reaction [hg]:
= (C - G ) / 2
= ( 190.5000 - 149.3520 )/2
= 20.5740 mm
Distance to Face Pressure Reaction [ht]:
= ( R + g1 + hg ) / 2
= ( 26.2922 + 17.7768 + 20.5740 )/2
= 32.3215 mm
Distance to End Pressure Reaction [hd]:
= R + ( g1 / 2 )
= 26.2922 + ( 17.7768/2.0 )
= 35.1806 mm
Summary of Moments for Internal Pressure:
Loading Force Distance Bolt Corr Moment
End Pressure, Md 14814. 35.1806 1.1614 606. N-m
Face Pressure, Mt 16723. 32.3215 1.1614 628. N-m
Gasket Load, Mg 0. 20.5740 1.1614 0. N-m
Gasket Seating, Matm 105618. 20.5740 1.1614 2525. N-m
17
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Flg Calc [Int P] : H1 (flange) Flng: 2 12:36p Jan 11,2015 Total Moment for Operation, Mop 1233. N-m
Total Moment for Gasket seating, Matm 2525. N-m
Note: User choose not to perform Stress Calculations on this ANSI Flange.
Pressure rating of the flange will be used to check code compliance.
Estimated Finished Weight of Flange at given Thk. 7.9 kgm
Estimated Unfinished Weight of Forging at given Thk 20.1 kgm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
18
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Internal Pressure Calculations : Step: 4 12:36p Jan 11,2015
Element Thickness, Pressure, Diameter and Allowable Stress :
| | Int. Press | Nominal | Total Corr| Element | Allowable |
From| To | + Liq. Hd | Thickness | Allowance | Diameter | Stress(SE)|
| | bar | mm | mm | mm | MPa |
---------------------------------------------------------------------------
Body flang| 18.000 | 24.300 | ... | 102.36 | 137.90 |
Shell| 18.000 | 8.5598 | ... | 114.30 | 137.90 |
Head| 18.000 | 8.5598 | ... | 114.30 | 137.90 |
Element Required Thickness and MAWP :
| | Design | M.A.W.P. | M.A.P. | Minimum | Required |
From| To | Pressure | Corroded | New & Cold | Thickness | Thickness |
| | bar | bar | bar | mm | mm |
----------------------------------------------------------------------------
Body flang| 18.0000 | 18.3984 | 18.9983 | 22.3000 | No Calc |
Shell| 18.0000 | 190.696 | 190.696 | 7.48983 | 1.50000 |
Head| 18.0000 | 204.863 | 204.863 | 7.48983 | 1.50000 |
Minimum 18.398 18.998
Note : The M.A.W.P is Governed by a Standard Flange !
Internal Pressure Calculation Results :
ASME Code, Section VIII, Division 1, 2010, 2011a
Cylindrical Shell From 30 To 40 SA-312 TP316 at 50 °C
Shell
19
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Internal Pressure Calculations : Step: 4 12:36p Jan 11,2015
Longitudinal Joint: Seamless
Circumferential Joint: Full Radiography per UW-11(a) Type 1
Material UNS Number: S31600
Required Thickness due to Internal Pressure [tr]:
= (P*Ro) / (S*E+0.4*P) per Appendix 1-1 (a)(1)
= (18.000*57.1500)/(137.90*1.00+0.4*18.000)
= 0.7422 + 0.0000 = 0.7422 mm
Note: The thickness required was less than the Code Minimum, therefore
the 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)/(Ro-0.4*t) per Appendix 1-1 (a)(1)
= (137.90*1.00*7.4898)/(57.1500-0.4*7.4898)
= 190.696 bar
Maximum Allowable Pressure, New and Cold [MAPNC]:
= (S*E*t)/(Ro-0.4*t) per Appendix 1-1 (a)(1)
= (137.90*1.00*7.4898)/(57.1500-0.4*7.4898)
= 190.696 bar
Actual stress at given pressure and thickness, corroded [Sact]:
= (P*(Ro-0.4*t))/(E*t)
= (18.000*((57.1500-0.4*7.4898))/(1.00*7.4898)
= 13.017 MPa
SA-312 TP316, Min Metal Temp without impact per UHA-51: -196 °C
20
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Internal Pressure Calculations : Step: 4 12:36p Jan 11,2015 Elliptical Head From 40 To 50 SA-403 316 at 50 °C
Head
Longitudinal Joint: Seamless
Circumferential Joint: Full Radiography per UW-11(a) Type 1
Material UNS Number: S31600
Required Thickness due to Internal Pressure [tr]:
= (P*Do*Kcor)/(2*S*E+2*P*(Kcor-0.1)) per Appendix 1-4 (c)
= (18.000*114.3000*1.000)/(2*137.90*1.00+2*18.000*(1.000-0.1))
= 0.7374 + 0.0000 = 0.7374 mm
Note: The thickness required was less than the Code Minimum, therefore
the Code Minimum value of 1.5000 mm per UG-16 will be used.
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]:
= (2*S*E*t)/(Kcor*Do-2*t*(Kcor-0.1)) per Appendix 1-4 (c)
= (2*137.90*1.00*7.4898)/(1.000*114.3000-2*7.4898*(1.00-0.1))
= 204.863 bar
Maximum Allowable Pressure, New and Cold [MAPNC]:
= (2*S*E*t)/(K*Do-2*t*(K-0.1)) per Appendix 1-4 (c)
= (2*137.90*1.00*7.4898)/(1.000*114.3000-2*7.4898*(1.000-0.1))
= 204.863 bar
Actual stress at given pressure and thickness, corroded [Sact]:
= (P*(Kcor*Do-2*t*(Kcor-0.1)))/(2*E*t)
= (18.000*(1.000*114.3000-2*7.4898*(1.000-0.1)))/(2*1.00*7.4898)
= 12.116 MPa
21
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Internal Pressure Calculations : Step: 4 12:36p Jan 11,2015
Straight Flange Required Thickness:
= (P*Ro)/(S*E+0.4*P) + ca per Appendix 1-1 (a)(1)
= (18.000*57.1500)/(137.90*1.00+0.4*18.000)+0.000
= 0.742 mm
Straight Flange Maximum Allowable Working Pressure:
= (S*E*t)/(Ro-0.4*t) per Appendix 1-1 (a)(1)
= (137.90 * 1.00 * 8.5598 )/(57.1500 - 0.4 * 8.5598 )
= 219.675 bar
SA-403 316, Min Metal Temp without impact per UHA-51: -196 °C
Hydrostatic Test Pressure Results:
Pressure per UG99b = 1.3 * M.A.W.P. * Sa/S 23.918 bar
Pressure per UG99b[34] = 1.3 * Design Pres * Sa/S 23.400 bar
Pressure per UG99c = 1.3 * M.A.P. - Head(Hyd) 24.647 bar
Pressure per UG100 = 1.1 * M.A.W.P. * Sa/S 20.238 bar
Pressure per PED = 1.43 * MAWP 26.310 bar
Horizontal Test performed per: UG-99c
Please note that Nozzle, Shell, Head, Flange, etc MAWPs are all considered
when determining the hydrotest pressure for those test types that are based
on the MAWP of the vessel.
Stresses on Elements due to Test Pressure:
From To Stress Allowable Ratio Pressure
----------------------------------------------------------------------
22
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Internal Pressure Calculations : Step: 4 12:36p Jan 11,2015 Shell 17.8 186.2 0.096 24.66
Head 16.6 186.2 0.089 24.66
----------------------------------------------------------------------
Elements Suitable for Internal Pressure.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
23
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- External Pressure Calculations : Step: 5 12:36p Jan 11,2015
External Pressure Calculation Results :
ASME Code, Section VIII, Division 1, 2010, 2011a
Cylindrical Shell From 30 to 40 Ext. Chart: HA-2 at 50 °C
Shell
Elastic Modulus from Chart: HA-2 at 50 °C : 0.192E+06 MPa
Results for Maximum Allowable External Pressure (MAEP):
Tca OD SLEN D/t L/D Factor A B
7.490 114.30 1097.98 15.26 9.6061 0.0048437 91.55
EMAP = (4*B)/(3*(D/t)) = (4*91.5548 )/(3*15.2607 ) = 79.9802 bar
Results for Required Thickness (Tca):
Tca OD SLEN D/t L/D Factor A B
0.965 114.30 1097.98 118.48 9.6061 0.0000957 9.19
EMAP = (4*B)/(3*(D/t)) = (4*9.1905 )/(3*118.4784 ) = 1.0341 bar
Results for Maximum Stiffened Length (Slen):
Tca OD SLEN D/t L/D Factor A B
7.490 114.30 84831.01 15.26 50.0000 0.0047606 91.36
EMAP = (4*B)/(3*(D/t)) = (4*91.3618 )/(3*15.2607 ) = 79.8115 bar
Elliptical Head From 40 to 50 Ext. Chart: HA-2 at 50 °C
Head
Elastic Modulus from Chart: HA-2 at 50 °C : 0.192E+06 MPa
24
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- External Pressure Calculations : Step: 5 12:36p Jan 11,2015
Results for Maximum Allowable External Pressure (MAEP):
Tca OD D/t Factor A B
7.490 114.30 15.26 0.0091011 97.82
EMAP = B/(K0*D/t) = 97.8199/(0.9000 *15.2607 ) = 71.2110 bar
Results for Required Thickness (Tca):
Tca OD D/t Factor A B
0.302 114.30 378.45 0.0003670 35.23
EMAP = B/(K0*D/t) = 35.2308/(0.9000 *378.4536 ) = 1.0342 bar
Check the requirements of UG-33(a)(1) using P = 1.67 * External Design
pressure for this head.
Material UNS Number: S31600
Required Thickness due to Internal Pressure [tr]:
= (P*Do*Kcor)/(2*S*E+2*P*(Kcor-0.1)) per Appendix 1-4 (c)
= (1.727*114.3000*1.000)/(2*137.90*1.00+2*1.727*(1.000-0.1))
= 0.0715 + 0.0000 = 0.0715 mm
Max. Allowable Working Pressure at given Thickness, corroded [MAWP]:
= ((2*S*E*t)/(Kcor*Do-2*t*(Kcor-0.1)))/1.67 per Appendix 1-4 (c)
= ((2*137.90*1.00*7.4898)/(1.000*114.3000-2*7.4898*(1.00-0.1)))/1.67
= 122.672 bar
Maximum Allowable External Pressure [MAEP]:
= min( MAEP, MAWP )
= min( 71.21 , 122.6725 )
= 71.211 bar
25
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- External Pressure Calculations : Step: 5 12:36p Jan 11,2015 Thickness requirements per UG-33(a)(1) govern the required
thickness of this head.
External Pressure Calculations
| | Section | Outside | Corroded | Factor | Factor |
From| To | Length | Diameter | Thickness | A | B |
| | mm | mm | mm | | MPa |
---------------------------------------------------------------------------
20| 30| No Calc | ... | 22.3000 | No Calc | No Calc |
30| 40| 1097.98 | 114.300 | 7.48983 | 0.0048437 | 91.5548 |
40| 50| No Calc | 114.300 | 7.48983 | 0.0091011 | 97.8199 |
External Pressure Calculations
| | External | External | External | External |
From| To | Actual T. | Required T.|Des. Press. | M.A.W.P. |
| | mm | mm | bar | bar |
----------------------------------------------------------------
20| 30| 22.3000 | No Calc | 1.03410 | No Calc |
30| 40| 7.48983 | 0.96473 | 1.03410 | 79.9802 |
40| 50| 7.48983 | 1.50000 | 1.03410 | 71.2110 |
Minimum 71.211
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 |
-------------------------------------------------------------------
20| 30| No Calc | No Calc | No Calc | No Calc |
26
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- External Pressure Calculations : Step: 5 12:36p Jan 11,2015 30| 40| 1097.98 | 84831.0 | No Calc | No Calc |
40| 50| No Calc | No Calc | No Calc | No Calc |
Elements Suitable for External Pressure.
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
27
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Element and Detail Weights : Step: 6 12:36p Jan 11,2015
Element and Detail Weights
| | Element | Element | Corroded | Corroded | Extra due |
From| To | Metal Wgt. | ID Volume |Metal Wgt. | ID Volume | Misc % |
| | kgm | m³ | kgm | m³ | kgm |
---------------------------------------------------------------------------
20| 30| 8.42992 | 0.00063378 | 8.42992 | 0.00063378 | 0.42150 |
30| 40| 24.4520 | 0.0081364 | 24.4520 | 0.0081364 | 1.22260 |
40| 50| 1.88162 | 0.00043591 | 1.88162 | 0.00043591 | 0.094081 |
---------------------------------------------------------------------------
Total 34 0.01 34 0.01 1
Weight of Details
| | Weight of | X Offset, | Y Offset, |
From|Type| Detail | Dtl. Cent. |Dtl. Cent. | Description
| | kgm | mm | mm |
-------------------------------------------------
20|Insl| 26.7406 | 37.5000 | ... | Ins: 20
30|Sadl| 5.26371 | 164.000 | 144.585 | Fixed
30|Sadl| 5.26371 | 804.000 | 144.585 | Sliding
30|Insl| 182.018 | 525.000 | ... | Insulation
30|Nozl| 7.18497 | 123.650 | 75.0602 | N1
30|Nozl| 7.18497 | 931.650 | 75.0602 | N2
30|Nozl| 7.18497 | 427.650 | 75.0602 | N3
30|Wght| 100.000 | 155.000 | ... | HEATER
40|Insl| 16.1679 | 34.1375 | ... | Ins: 40
Total Weight of Each Detail Type
28
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Element and Detail Weights : Step: 6 12:36p Jan 11,2015 Total Weight of Saddles 10.5
Total Weight of Insulation 224.9
Total Weight of Nozzles 21.6
Total Weight of Weights 100.0
---------------------------------------------------------------
Sum of the Detail Weights 357.0 kgm
Weight Summation
Fabricated Shop Test Shipping Erected Empty Operating
------------------------------------------------------------------------------
36.5 68.6 36.5 68.6 36.5 293.5
10.5 9.2 10.5 ... 10.5 ...
21.6 ... 21.6 ... ... ...
... ... ... 224.9 ... ...
... ... ... ... 224.9 ...
... ... ... ... ... 100.0
... ... ... ... ... ...
... ... ... ... 21.6 ...
------------------------------------------------------------------------------
68.6 77.8 293.5 293.5 293.5 393.5 kgm
Miscellaneous Weight Percent: 5.0 %
Note that the above value for the miscellaneous weight percent has
been applied to the shells/heads/flange/tubesheets/tubes etc. in the
weight calculations for metallic components.
Note: The shipping total has been modified because some items have
29
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Element and Detail Weights : Step: 6 12:36p Jan 11,2015 been specified as being installed in the shop.
Weight Summary
Fabricated Wt. - Bare Weight W/O Removable Internals 68.6 kgm
Shop Test Wt. - Fabricated Weight + Water ( Full ) 77.8 kgm
Shipping Wt. - Fab. Wt + Rem. Intls.+ Shipping App. 293.5 kgm
Erected Wt. - Fab. Wt + Rem. Intls.+ Insul. (etc) 293.5 kgm
Ope. Wt. no Liq - Fab. Wt + Intls. + Details + Wghts. 293.5 kgm
Operating Wt. - Empty Wt + Operating Liq. Uncorroded 393.5 kgm
Oper. Wt. + CA - Corr Wt. + Operating Liquid 393.5 kgm
Field Test Wt. - Empty Weight + Water (Full) 302.7 kgm
Note: The Corroded Weight and thickness are used in the Horizontal
Vessel Analysis (Ope Case) and Earthquake Load Calculations.
Outside Surface Areas of Elements
| | Surface |
From| To | Area |
| | mm² |
----------------------------
20| 30| 73710.1 |
30| 40| 384097. |
40| 50| 29219.5 |
----------------------------
Total 487026.844 mm²
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
30
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Flange MAWP : Step: 7 12:36p Jan 11,2015
Nozzle Flange MAWP Results :
Nozzle ----- Flange Rating
Description Operating Ambient Temperature Class Grade|Group
bar bar °C
----------------------------------------------------------------------------
N1 18.4 19.0 50 150 GR 2.2
N2 18.4 19.0 50 150 GR 2.2
N3 18.4 19.0 50 150 GR 2.2
----------------------------------------------------------------------------
Minimum Rating 18.4 19.0 bar
Note: ANSI Ratings are per ANSI/ASME B16.5 2009 Metric Edition
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
31
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Wind Load Calculation : Step: 8 12:36p Jan 11,2015
Note: Using the User Defined Wind Profile ...
Wind Loads on Masses/Equipment/Piping
ID Wind Area Elevation Pressure Force
mm² mm kPa N
-------------------------------------------------------------------------
HEATER 0.00 155.00 0.75 0.00
Wind Load Calculation
| | Wind | Wind | Wind | Wind | Element |
From| To | Height | Diameter | Area | Pressure | Wind Load |
| | mm | mm | mm² | kPa | N |
---------------------------------------------------------------------------
20| 30| 255.000 | 215.184 | 16138.8 | 0.75000 | 12.1038 |
30| 40| 255.000 | 233.160 | 244818. | 0.75000 | 183.609 |
40| 50| 255.000 | 233.160 | 20292.7 | 0.75000 | 15.2192 |
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
32
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Earthquake Load Calculation : Step: 9 12:36p Jan 11,2015
Earthquake Loading Specified in G's
Horizontal Acceleration factor (GX) 0.500
Horizontal Acceleration factor (GZ) 0.500
Vertical Acceleration factor (GY) -2.000
Note: Loads are distributed evenly among all elements for horizontal
geometries.
Earthquake Load Calculation
| | Earthquake | Earthquake | Element |
From| To | Height | Weight | Ope Load |
| | mm | N | N |
-------------------------------------------------
20| 30| 49.6602 | 771.753 | 385.876 |
30|Sadl| 49.6602 | 771.753 | 385.876 |
Sadl| 40| 49.6602 | 771.753 | 385.876 |
30| 40| 49.6602 | 771.753 | 385.876 |
40| 50| 49.6602 | 771.753 | 385.876 |
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
33
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Center of Gravity Calculation : Step: 10 12:36p Jan 11,2015
Shop/Field Installation Options :
Insulation is installed in the Shop.
Note : The CG is computed from the first Element From Node
Center of Gravity of Saddles 559.000 mm
Center of Gravity of Insulation 573.318 mm
Center of Gravity of Nozzles 569.317 mm
Center of Gravity of Added Weights (Operating) 230.000 mm
Center of Gravity of Bare Shell New and Cold 493.697 mm
Center of Gravity of Bare Shell Corroded 493.697 mm
Vessel CG in the Operating Condition 478.085 mm
Vessel CG in the Fabricated (Shop/Empty) Condition 562.609 mm
Vessel CG in the Test Condition 576.310 mm
Rigging Analysis Results:
Total Effective Length of Vessel for this analysis 1164.70 mm
Total vessel weight (No Liquid) Twt 2878.16 N
Impact weight multiplication factor Imp 2.00
Design lifting weight, DWT = Imp * Twt 5756.33 N
Elevation of the Tailing Lug (bottom) 329.00 mm
Elevation of the Lifting Lug (top ) 882.00 mm
Design Reaction force at the tailing lug 3324.63 N
Design Reaction force at the lifting lug 2431.69 N
CG Distance from Tailing Lug 233.61 mm
34
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Center of Gravity Calculation : Step: 10 12:36p Jan 11,2015 CG Distance from the Nearer Lifting Lug 233.61 mm
Critical Values:
Max Stress Elevation Allowables
MPa mm MPa
-----------|-----------|---------------|------------------------
Bending | 8.28 | 285.00 | 102.99 (UG-23)
Shear | -1.15 | 285.00 | 96.53 (0.7*S)
-----------|-----------|---------------|------------------------
Forces and Moments at selected elevations (not all analysis points shown):
Distance Bending Moment Bending Stress Shear Force Shear Stress
mm N-m MPa N MPa
------------------------------------------------------------------------------
0.00 0.0 0.0 -1036.1 -0.4
30.00 24.2 0.4 -1496.6 -0.6
60.00 62.2 1.0 -1957.2 -0.8
285.00 521.7 8.3 -2878.2 -1.1
705.00 278.0 4.4 -139.5 -0.1
1125.00 35.6 0.6 115.1 0.0
Unity Check (Actual Stress / Allowable Stress):
Maximum Unity Check is 0.0804 at elevation 285.0000 mm - Must be <=1
Note: The rigging analysis is performed using a uniformly distributed load.
--- Plot data successfully generated ...----
35
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Center of Gravity Calculation : Step: 10 12:36p Jan 11,2015
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
36
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015
Lifting Lug Calculations: Lug(s) on Left End of Vessel
Input Values:
Lifting Lug Material SA-240 316
Lifting Lug Yield Stress Yield 206.85 MPa
Total Height of Lifting Lug w 80.0000 mm
Thickness of Lifting Lug t 8.0000 mm
Diameter of Hole in Lifting Lug dh 14.0000 mm
Radius of Semi-Circular Arc of Lifting Lug r 21.0000 mm
Height of Lug from bottom to Center of Hole h 40.0000 mm
Offset from Vessel OD to Center of Hole off 51.0000 mm
Lug Fillet Weld Size tw 7.0000 mm
Length of weld along side of Lifting Lug wl 80.0000 mm
Length of Weld along Bottom of Lifting Lug wb 8.0000 mm
Thickness of Collar (if any) tc 0.0000 mm
Diameter of Collar (if any) dc 0.0000 mm
Impact Factor Impfac 2.00
Sling Angle from Horizontal 60.0000 deg
Number of Lugs in Group 2
Lifting Lug Orientation to Vessel: Perpendicular
Lift Orientation : Horizontal Lift
PV Elite does not compute weak axis bending forces on the lugs. It is
assumed that a spreader bar is used.
Computed Results:
37
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 Force Along Vessel Axis Fax 959.74 N
Force Normal to Vessel Fn 1662.32 N
Force Tangential to Vessel Ft 0.00 N
Converting the weld leg dimension (tw) to the weld throat dimension.
Weld Group Inertia Calculations:
Weld Group Inertia about the Circumferential Axis Ilc 565330.250 mm**4
Weld Group Centroid distance in the Long. Direction Yll 44.949 mm
Dist. of Weld Group Centroid from Lug bottom Yll_b 40.000 mm
Weld Group Inertia about the Longitudinal Axis Ill 3881.227 mm**4
Weld Group Centroid Distance in the Circ. Direction Ylc 4.000 mm
Note: The Impact Factor is applied to the Forces acting on the Lug.
Primary Shear Stress in the Welds due to Shear Loads [Ssll]:
= sqrt( Fax2 + Ft2 + Fn2 )/(( 2 * (wl + wb) ) * tw )
= sqrt(9592+02+16622)/((2*(80.0+8.0))*4.9490)
= 2.20 MPa
Shear Stress in the Welds due to Bending Loads [Sblf]:
= (Fn*(h-Yll_b)) *Yll/Ilc + (Fax*off *Yll/Ilc) + (Ft*off *Ylc/Ill)
= (1662 *(40.000 -40.000 )) * 44.949/565330 +
(959 *0.000 * 44.949/565330 ) +
(0 *0.000 * 4.000/3881.227 )
= 3.89 MPa
Total Shear Stress for Combined Loads [St]:
= Ssll + Sblf
= 2.204 + 3.892
38
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 = 6.10 MPa
Allowable Shear Stress for Combined Loads [Sta]:
= 0.4 * Yield * Occfac (AISC Shear Allowable)
= 0.4 * 206 * 1.00
= 82.74 MPa
Shear Stress in Lug above Hole [Shs]:
= sqrt( Pl2 + Fax2 ) / Sha
= sqrt( 16622 + 9592 )/224.000
= 8.57 MPa
Allowable Shear Stress in Lug above Hole [Sas]:
= 0.4 * Yield * Occfac
= 0.4 * 206 * 1.00
= 82.74 MPa
Pin Hole Bearing Stress [Pbs]:
= sqrt( Fax2 + Fn2 ) / ( t * dh )
= sqrt( 9592 + 16622 )/( 8.000 * 14.000 )
= 17.14 MPa
Allowable Bearing Stress [Pba]:
= min( 0.75 * Yield * Occfac, 0.9 * Yield ) AISC Bearing All.
= min( 0.75 * 206 * 1.00 , 186.2 )
= 155.14 MPa
Bending Stress at the Base of the Lug [Fbs]:
= Ft * off/(w * t2/6) + Fax * off/(w2 * t/6)
= 0 * 51.000/(80.000 * 8.0002/6) +
959 * 51.000/(80.0002 * 8.000/6)
39
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 = 5.74 MPa
Tensile Stress at the Base of the Lug [Fa]:
= Fn / (w * t)
= 959/(80.000 * 8.000 )
= 2.60 MPa
Total Combined Stress at the Base of the Lug:
= Fbs + Fa
= 5.7 + 2.6
= 8.33 MPa
Lug Allowable Stress for Bending and Tension:
= min( 0.66 * Yield * Occfac, 0.75 * Yield )
= min( 0.66 * 206 * 1.00 , 155.1 )
= 136.52 MPa
Required Shackle Pin Diameter [Spd]:
= sqrt[(2 * sqrt(Fn2 + Fax2)/( Pi * Sta))]
= sqrt[2 * sqrt(16622 + 9592)/( Pi * 82 )]
= 3.8432 mm
WRC 107/537 Stress Analysis for the Lifting Lug to Shell Junction in
the new and Cold Condition (no corrosion applied).
Note: Since Beta1/Beta2 >= 0.25, C22 (C22p) is adjusted per table 6
in paragraph 4.3 of WRC Bulletin 107.
Input Echo, WRC107/537 Item 1, Description: Lift Lug
Diameter Basis for Vessel Vbasis ID
40
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 Cylindrical or Spherical Vessel Cylsph Cylindrical
Internal Corrosion Allowance Cas 0.0000 mm
Vessel Diameter Dv 99.320 mm
Vessel Thickness Tv 7.490 mm
Design Temperature 37.78 °C
Attachment Type Type Rectangular
Parameter C11 C11 22.00 mm
Parameter C22 C22 88.00 mm
Thickness of Reinforcing Pad Tpad 8.000 mm
Pad Parameter C11P C11p 62.000 mm
Pad Parameter C22P C22p 100.000 mm
Design Internal Pressure Dp 0.000 bar
Include Pressure Thrust No
External Forces and Moments in WRC 107/537 Convention:
Radial Load (SUS) P -1662.3 N
Longitudinal Shear (SUS) Vl -959.7 N
Circumferential Shear (SUS) Vc 0.0 N
Circumferential Moment (SUS) Mc 0.0 N-m
Longitudinal Moment (SUS) Ml -38.4 N-m
Torsional Moment (SUS) Mt 0.0 N-m
Use Interactive Control No
WRC107 Version Version March 1979
Include Pressure Stress Indices per Div. 2 No
Compute Pressure Stress per WRC-368 No
41
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015
WRC 107 Stress Calculation for SUStained loads:
Radial Load P -1662.3 N
Circumferential Shear VC 0.0 N
Longitudinal Shear VL -959.7 N
Circumferential Moment MC 0.0 N-m
Longitudinal Moment ML -38.4 N-m
Torsional Moment MT 0.0 N-m
Dimensionless Parameters used : Gamma = 5.00 ( 3.71)
Dimensionless Loads for Cylindrical Shells at Attachment Junction:
-------------------------------------------------------------------
Curves read for 1979 Beta Figure Value Location
-------------------------------------------------------------------
N(PHI) / ( P/Rm ) 0.567 4C ! 0.749 (A,B)
N(PHI) / ( P/Rm ) 0.567 3C ! 0.603 (C,D)
M(PHI) / ( P ) 0.337 2C1 ! 0.067 (A,B)
M(PHI) / ( P ) 0.337 1C ! 0.092 (C,D)
N(PHI) / ( MC/(Rm**2 * Beta) ) 0.304 3A ! 0.175 (A,B,C,D)
M(PHI) / ( MC/(Rm * Beta) ) 0.398 1A ! 0.091 (A,B,C,D)
N(PHI) / ( ML/(Rm**2 * Beta) ) 0.483 3B ! 0.594 (A,B,C,D)
M(PHI) / ( ML/(Rm * Beta) ) 0.435 1B ! 0.033 (A,B,C,D)
N(x) / ( P/Rm ) 0.460 3C ! 0.644 (A,B)
N(x) / ( P/Rm ) 0.460 4C ! 0.779 (C,D)
M(x) / ( P ) 0.479 1C1 ! 0.063 (A,B)
M(x) / ( P ) 0.479 2C ! 0.042 (C,D)
N(x) / ( MC/(Rm**2 * Beta) ) 0.304 4A ! 0.281 (A,B,C,D)
M(x) / ( MC/(Rm * Beta) ) 0.560 2A ! 0.051 (A,B,C,D)
N(x) / ( ML/(Rm**2 * Beta) ) 0.483 4B ! 0.214 (A,B,C,D)
42
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 M(x) / ( ML/(Rm * Beta) ) 0.599 2B ! 0.053 (A,B,C,D)
Note - The ! mark next to the figure name denotes curve value exceeded.
Stress Concentration Factors Kn = 1.00, Kb = 1.00
Stresses in the Vessel at the Attachment Junction
------------------------------------------------------------------------
| Stress Values at
Type of | (MPa )
---------------|--------------------------------------------------------
Stress Load| Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Memb. P | 1 1 1 1 1 1 1 1
Circ. Bend. P | 2 -2 2 -2 3 -3 3 -3
Circ. Memb. MC | 0 0 0 0 0 0 0 0
Circ. Bend. MC | 0 0 0 0 0 0 0 0
Circ. Memb. ML | 0 0 0 0 0 0 0 0
Circ. Bend. ML | 1 -1 -1 1 0 0 0 0
|
Tot. Circ. Str.| 6.1 -2.0 2.3 -0.8 5.0 -2.7 5.0 -2.7
------------------------------------------------------------------------
Long. Memb. P | 1 1 1 1 1 1 1 1
Long. Bend. P | 2 -2 2 -2 1 -1 1 -1
Long. Memb. MC | 0 0 0 0 0 0 0 0
Long. Bend. MC | 0 0 0 0 0 0 0 0
Long. Memb. ML | 0 0 0 0 0 0 0 0
Long. Bend. ML | 1 -1 -1 1 0 0 0 0
|
43
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 Tot. Long. Str.| 5.7 -2.5 1.9 -0.3 3.2 -0.3 3.2 -0.3
------------------------------------------------------------------------
Shear VC | 0 0 0 0 0 0 0 0
Shear VL | 0 0 0 0 0 0 0 0
Shear MT | 0 0 0 0 0 0 0 0
|
Tot. Shear| 0.0 0.0 0.0 0.0 0.4 0.4 -0.4 -0.4
------------------------------------------------------------------------
Str. Int. | 6.09 2.50 2.29 0.75 5.03 2.76 5.03 2.76
------------------------------------------------------------------------
WARNING: Ratio of Pad Radius/Rm (0.580) is not between 0.01 and 0.571.
Dimensionless Parameters used : Gamma = 7.13
Dimensionless Loads for Cylindrical Shells at Pad edge:
-------------------------------------------------------------------
Curves read for 1979 Beta Figure Value Location
-------------------------------------------------------------------
N(PHI) / ( P/Rm ) 0.916 4C ! 0.961 (A,B)
N(PHI) / ( P/Rm ) 0.916 3C ! 0.664 (C,D)
M(PHI) / ( P ) 0.692 2C1 ! 0.032 (A,B)
M(PHI) / ( P ) 0.692 1C ! 0.054 (C,D)
N(PHI) / ( MC/(Rm**2 * Beta) ) 0.681 3A ! 0.325 (A,B,C,D)
M(PHI) / ( MC/(Rm * Beta) ) 0.748 1A ! 0.081 (A,B,C,D)
N(PHI) / ( ML/(Rm**2 * Beta) ) 0.798 3B ! 0.750 (A,B,C,D)
M(PHI) / ( ML/(Rm * Beta) ) 0.779 1B ! 0.023 (A,B,C,D)
N(x) / ( P/Rm ) 0.812 3C ! 0.664 (A,B)
N(x) / ( P/Rm ) 0.812 4C ! 0.961 (C,D)
M(x) / ( P ) 0.831 1C1 ! 0.053 (A,B)
M(x) / ( P ) 0.831 2C ! 0.034 (C,D)
44
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 N(x) / ( MC/(Rm**2 * Beta) ) 0.681 4A ! 0.711 (A,B,C,D)
M(x) / ( MC/(Rm * Beta) ) 0.905 2A ! 0.043 (A,B,C,D)
N(x) / ( ML/(Rm**2 * Beta) ) 0.798 4B ! 0.324 (A,B,C,D)
M(x) / ( ML/(Rm * Beta) ) 0.878 2B ! 0.041 (A,B,C,D)
Note - The ! mark next to the figure name denotes curve value exceeded.
Stress Concentration Factors Kn = 1.00, Kb = 1.00
Stresses in the Vessel at the Edge of Reinforcing Pad
------------------------------------------------------------------------
| Stress Values at
Type of | (MPa )
---------------|--------------------------------------------------------
Stress Load| Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Memb. P | 3 3 3 3 2 2 2 2
Circ. Bend. P | 5 -5 5 -5 9 -9 9 -9
Circ. Memb. MC | 0 0 0 0 0 0 0 0
Circ. Bend. MC | 0 0 0 0 0 0 0 0
Circ. Memb. ML | 1 1 -1 -1 0 0 0 0
Circ. Bend. ML | 2 -2 -2 2 0 0 0 0
|
Tot. Circ. Str.| 13.5 -2.5 6.0 -1.0 12.4 -6.9 12.4 -6.9
------------------------------------------------------------------------
Long. Memb. P | 2 2 2 2 3 3 3 3
Long. Bend. P | 9 -9 9 -9 6 -6 6 -6
Long. Memb. MC | 0 0 0 0 0 0 0 0
Long. Bend. MC | 0 0 0 0 0 0 0 0
45
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 Long. Memb. ML | 0 0 0 0 0 0 0 0
Long. Bend. ML | 3 -3 -3 3 0 0 0 0
|
Tot. Long. Str.| 16.5 -9.3 7.7 -3.8 10.1 -2.1 10.1 -2.1
------------------------------------------------------------------------
Shear VC | 0 0 0 0 0 0 0 0
Shear VL | 0 0 0 0 0 0 0 0
Shear MT | 0 0 0 0 0 0 0 0
|
Tot. Shear| 0.0 0.0 0.0 0.0 0.6 0.6 -0.6 -0.6
------------------------------------------------------------------------
Str. Int. | 16.55 9.33 7.66 3.83 12.58 6.98 12.58 6.98
------------------------------------------------------------------------
WRC 107/537 Stress Summations:
Vessel Stress Summation at Attachment Junction
------------------------------------------------------------------------
Type of | Stress Values at
Stress Int. | (MPa )
---------------|--------------------------------------------------------
Location | Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Pm (SUS) | 0 0 0 0 0 0 0 0
Circ. Pl (SUS) | 2 2 0 0 1 1 1 1
Circ. Q (SUS) | 4 -4 1 -1 3 -3 3 -3
------------------------------------------------------------------------
Long. Pm (SUS) | 0 0 0 0 0 0 0 0
Long. Pl (SUS) | 1 1 0 0 1 1 1 1
Long. Q (SUS) | 4 -4 1 -1 1 -1 1 -1
------------------------------------------------------------------------
46
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 Shear Pm (SUS) | 0 0 0 0 0 0 0 0
Shear Pl (SUS) | 0 0 0 0 0 0 0 0
Shear Q (SUS) | 0 0 0 0 0 0 0 0
------------------------------------------------------------------------
Pm (SUS) | 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
------------------------------------------------------------------------
Pm+Pl (SUS) | 2.0 2.0 0.8 0.8 1.7 1.7 1.7 1.7
------------------------------------------------------------------------
Pm+Pl+Q (Total)| 6.1 2.5 2.3 0.8 5.0 2.8 5.0 2.8
------------------------------------------------------------------------
------------------------------------------------------------------------
Type of | Max. S.I. S.I. Allowable | Result
Stress Int. | MPa |
---------------|--------------------------------------------------------
Pm (SUS) | 0.00 137.90 | Passed
Pm+Pl (SUS) | 2.03 206.85 | Passed
Pm+Pl+Q (TOTAL)| 6.09 413.70 | Passed
------------------------------------------------------------------------
WRC 107/537 Stress Summations:
Vessel Stress Summation at Reinforcing Pad Edge
------------------------------------------------------------------------
Type of | Stress Values at
Stress Int. | (MPa )
---------------|--------------------------------------------------------
Location | Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Pm (SUS) | 0 0 0 0 0 0 0 0
Circ. Pl (SUS) | 5 5 2 2 2 2 2 2
47
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Left Side Step: 11 12:36p Jan 11,2015 Circ. Q (SUS) | 7 -7 3 -3 9 -9 9 -9
------------------------------------------------------------------------
Long. Pm (SUS) | 0 0 0 0 0 0 0 0
Long. Pl (SUS) | 3 3 1 1 3 3 3 3
Long. Q (SUS) | 12 -12 5 -5 6 -6 6 -6
------------------------------------------------------------------------
Shear Pm (SUS) | 0 0 0 0 0 0 0 0
Shear Pl (SUS) | 0 0 0 0 0 0 0 0
Shear Q (SUS) | 0 0 0 0 0 0 0 0
------------------------------------------------------------------------
Pm (SUS) | 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
------------------------------------------------------------------------
Pm+Pl (SUS) | 5.5 5.5 2.5 2.5 4.3 4.3 4.3 4.3
------------------------------------------------------------------------
Pm+Pl+Q (Total)| 16.5 9.3 7.7 3.8 12.6 7.0 12.6 7.0
------------------------------------------------------------------------
------------------------------------------------------------------------
Type of | Max. S.I. S.I. Allowable | Result
Stress Int. | MPa |
---------------|--------------------------------------------------------
Pm (SUS) | 0.00 137.90 | Passed
Pm+Pl (SUS) | 5.48 206.85 | Passed
Pm+Pl+Q (TOTAL)| 16.55 413.70 | Passed
------------------------------------------------------------------------
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
48
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015
Lifting Lug Calculations: Lug(s) on Right End of Vessel
Input Values:
Lifting Lug Material SA-240 316
Lifting Lug Yield Stress Yield 206.85 MPa
Total Height of Lifting Lug w 80.0000 mm
Thickness of Lifting Lug t 8.0000 mm
Diameter of Hole in Lifting Lug dh 14.0000 mm
Radius of Semi-Circular Arc of Lifting Lug r 21.0000 mm
Height of Lug from bottom to Center of Hole h 40.0000 mm
Offset from Vessel OD to Center of Hole off 51.0000 mm
Lug Fillet Weld Size tw 7.0000 mm
Length of weld along side of Lifting Lug wl 80.0000 mm
Length of Weld along Bottom of Lifting Lug wb 8.0000 mm
Thickness of Collar (if any) tc 0.0000 mm
Diameter of Collar (if any) dc 0.0000 mm
Impact Factor Impfac 2.00
Sling Angle from Horizontal 60.0000 deg
Number of Lugs in Group 2
Lifting Lug Orientation to Vessel: Perpendicular
Lift Orientation : Horizontal Lift
PV Elite does not compute weak axis bending forces on the lugs. It is
assumed that a spreader bar is used.
Computed Results:
49
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 Force Along Vessel Axis Fax 701.97 N
Force Normal to Vessel Fn 1215.85 N
Force Tangential to Vessel Ft 0.00 N
Converting the weld leg dimension (tw) to the weld throat dimension.
Weld Group Inertia Calculations:
Weld Group Inertia about the Circumferential Axis Ilc 565330.250 mm**4
Weld Group Centroid distance in the Long. Direction Yll 44.949 mm
Dist. of Weld Group Centroid from Lug bottom Yll_b 40.000 mm
Weld Group Inertia about the Longitudinal Axis Ill 3881.227 mm**4
Weld Group Centroid Distance in the Circ. Direction Ylc 4.000 mm
Note: The Impact Factor is applied to the Forces acting on the Lug.
Primary Shear Stress in the Welds due to Shear Loads [Ssll]:
= sqrt( Fax2 + Ft2 + Fn2 )/(( 2 * (wl + wb) ) * tw )
= sqrt(7012+02+12152)/((2*(80.0+8.0))*4.9490)
= 1.61 MPa
Shear Stress in the Welds due to Bending Loads [Sblf]:
= (Fn*(h-Yll_b)) *Yll/Ilc + (Fax*off *Yll/Ilc) + (Ft*off *Ylc/Ill)
= (1215 *(40.000 -40.000 )) * 44.949/565330 +
(701 *0.000 * 44.949/565330 ) +
(0 *0.000 * 4.000/3881.227 )
= 2.85 MPa
Total Shear Stress for Combined Loads [St]:
= Ssll + Sblf
= 1.612 + 2.847
50
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 = 4.46 MPa
Allowable Shear Stress for Combined Loads [Sta]:
= 0.4 * Yield * Occfac (AISC Shear Allowable)
= 0.4 * 206 * 1.00
= 82.74 MPa
Shear Stress in Lug above Hole [Shs]:
= sqrt( Pl2 + Fax2 ) / Sha
= sqrt( 12152 + 7012 )/224.000
= 6.27 MPa
Allowable Shear Stress in Lug above Hole [Sas]:
= 0.4 * Yield * Occfac
= 0.4 * 206 * 1.00
= 82.74 MPa
Pin Hole Bearing Stress [Pbs]:
= sqrt( Fax2 + Fn2 ) / ( t * dh )
= sqrt( 7012 + 12152 )/( 8.000 * 14.000 )
= 12.54 MPa
Allowable Bearing Stress [Pba]:
= min( 0.75 * Yield * Occfac, 0.9 * Yield ) AISC Bearing All.
= min( 0.75 * 206 * 1.00 , 186.2 )
= 155.14 MPa
Bending Stress at the Base of the Lug [Fbs]:
= Ft * off/(w * t2/6) + Fax * off/(w2 * t/6)
= 0 * 51.000/(80.000 * 8.0002/6) +
701 * 51.000/(80.0002 * 8.000/6)
51
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 = 4.20 MPa
Tensile Stress at the Base of the Lug [Fa]:
= Fn / (w * t)
= 701/(80.000 * 8.000 )
= 1.90 MPa
Total Combined Stress at the Base of the Lug:
= Fbs + Fa
= 4.2 + 1.9
= 6.10 MPa
Lug Allowable Stress for Bending and Tension:
= min( 0.66 * Yield * Occfac, 0.75 * Yield )
= min( 0.66 * 206 * 1.00 , 155.1 )
= 136.52 MPa
Required Shackle Pin Diameter [Spd]:
= sqrt[(2 * sqrt(Fn2 + Fax2)/( Pi * Sta))]
= sqrt[2 * sqrt(12152 + 7012)/( Pi * 82 )]
= 3.2868 mm
WRC 107/537 Stress Analysis for the Lifting Lug to Shell Junction in
the new and Cold Condition (no corrosion applied).
Note: Since Beta1/Beta2 >= 0.25, C22 (C22p) is adjusted per table 6
in paragraph 4.3 of WRC Bulletin 107.
Input Echo, WRC107/537 Item 1, Description: Lift Lug
Diameter Basis for Vessel Vbasis ID
52
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 Cylindrical or Spherical Vessel Cylsph Cylindrical
Internal Corrosion Allowance Cas 0.0000 mm
Vessel Diameter Dv 99.320 mm
Vessel Thickness Tv 7.490 mm
Design Temperature 37.78 °C
Attachment Type Type Rectangular
Parameter C11 C11 22.00 mm
Parameter C22 C22 88.00 mm
Thickness of Reinforcing Pad Tpad 8.000 mm
Pad Parameter C11P C11p 62.000 mm
Pad Parameter C22P C22p 100.000 mm
Design Internal Pressure Dp 0.000 bar
Include Pressure Thrust No
External Forces and Moments in WRC 107/537 Convention:
Radial Load (SUS) P -1215.8 N
Longitudinal Shear (SUS) Vl -702.0 N
Circumferential Shear (SUS) Vc 0.0 N
Circumferential Moment (SUS) Mc 0.0 N-m
Longitudinal Moment (SUS) Ml -28.1 N-m
Torsional Moment (SUS) Mt 0.0 N-m
Use Interactive Control No
WRC107 Version Version March 1979
Include Pressure Stress Indices per Div. 2 No
Compute Pressure Stress per WRC-368 No
53
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015
WRC 107 Stress Calculation for SUStained loads:
Radial Load P -1215.8 N
Circumferential Shear VC 0.0 N
Longitudinal Shear VL -702.0 N
Circumferential Moment MC 0.0 N-m
Longitudinal Moment ML -28.1 N-m
Torsional Moment MT 0.0 N-m
Dimensionless Parameters used : Gamma = 5.00 ( 3.71)
Dimensionless Loads for Cylindrical Shells at Attachment Junction:
-------------------------------------------------------------------
Curves read for 1979 Beta Figure Value Location
-------------------------------------------------------------------
N(PHI) / ( P/Rm ) 0.567 4C ! 0.749 (A,B)
N(PHI) / ( P/Rm ) 0.567 3C ! 0.603 (C,D)
M(PHI) / ( P ) 0.337 2C1 ! 0.067 (A,B)
M(PHI) / ( P ) 0.337 1C ! 0.092 (C,D)
N(PHI) / ( MC/(Rm**2 * Beta) ) 0.304 3A ! 0.175 (A,B,C,D)
M(PHI) / ( MC/(Rm * Beta) ) 0.398 1A ! 0.091 (A,B,C,D)
N(PHI) / ( ML/(Rm**2 * Beta) ) 0.483 3B ! 0.594 (A,B,C,D)
M(PHI) / ( ML/(Rm * Beta) ) 0.435 1B ! 0.033 (A,B,C,D)
N(x) / ( P/Rm ) 0.460 3C ! 0.644 (A,B)
N(x) / ( P/Rm ) 0.460 4C ! 0.779 (C,D)
M(x) / ( P ) 0.479 1C1 ! 0.063 (A,B)
M(x) / ( P ) 0.479 2C ! 0.042 (C,D)
N(x) / ( MC/(Rm**2 * Beta) ) 0.304 4A ! 0.281 (A,B,C,D)
M(x) / ( MC/(Rm * Beta) ) 0.560 2A ! 0.051 (A,B,C,D)
N(x) / ( ML/(Rm**2 * Beta) ) 0.483 4B ! 0.214 (A,B,C,D)
54
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 M(x) / ( ML/(Rm * Beta) ) 0.599 2B ! 0.053 (A,B,C,D)
Note - The ! mark next to the figure name denotes curve value exceeded.
Stress Concentration Factors Kn = 1.00, Kb = 1.00
Stresses in the Vessel at the Attachment Junction
------------------------------------------------------------------------
| Stress Values at
Type of | (MPa )
---------------|--------------------------------------------------------
Stress Load| Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Memb. P | 1 1 1 1 0 0 0 0
Circ. Bend. P | 2 -2 2 -2 2 -2 2 -2
Circ. Memb. MC | 0 0 0 0 0 0 0 0
Circ. Bend. MC | 0 0 0 0 0 0 0 0
Circ. Memb. ML | 0 0 0 0 0 0 0 0
Circ. Bend. ML | 0 0 0 0 0 0 0 0
|
Tot. Circ. Str.| 4.5 -1.5 1.7 -0.6 3.6 -2.0 3.6 -2.0
------------------------------------------------------------------------
Long. Memb. P | 0 0 0 0 1 1 1 1
Long. Bend. P | 1 -1 1 -1 1 -1 1 -1
Long. Memb. MC | 0 0 0 0 0 0 0 0
Long. Bend. MC | 0 0 0 0 0 0 0 0
Long. Memb. ML | 0 0 0 0 0 0 0 0
Long. Bend. ML | 1 -1 -1 1 0 0 0 0
|
55
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 Tot. Long. Str.| 4.2 -1.8 1.4 -0.2 2.3 -0.2 2.3 -0.2
------------------------------------------------------------------------
Shear VC | 0 0 0 0 0 0 0 0
Shear VL | 0 0 0 0 0 0 0 0
Shear MT | 0 0 0 0 0 0 0 0
|
Tot. Shear| 0.0 0.0 0.0 0.0 0.3 0.3 -0.3 -0.3
------------------------------------------------------------------------
Str. Int. | 4.45 1.83 1.68 0.55 3.68 2.02 3.68 2.02
------------------------------------------------------------------------
WARNING: Ratio of Pad Radius/Rm (0.580) is not between 0.01 and 0.571.
Dimensionless Parameters used : Gamma = 7.13
Dimensionless Loads for Cylindrical Shells at Pad edge:
-------------------------------------------------------------------
Curves read for 1979 Beta Figure Value Location
-------------------------------------------------------------------
N(PHI) / ( P/Rm ) 0.916 4C ! 0.961 (A,B)
N(PHI) / ( P/Rm ) 0.916 3C ! 0.664 (C,D)
M(PHI) / ( P ) 0.692 2C1 ! 0.032 (A,B)
M(PHI) / ( P ) 0.692 1C ! 0.054 (C,D)
N(PHI) / ( MC/(Rm**2 * Beta) ) 0.681 3A ! 0.325 (A,B,C,D)
M(PHI) / ( MC/(Rm * Beta) ) 0.748 1A ! 0.081 (A,B,C,D)
N(PHI) / ( ML/(Rm**2 * Beta) ) 0.798 3B ! 0.750 (A,B,C,D)
M(PHI) / ( ML/(Rm * Beta) ) 0.779 1B ! 0.023 (A,B,C,D)
N(x) / ( P/Rm ) 0.812 3C ! 0.664 (A,B)
N(x) / ( P/Rm ) 0.812 4C ! 0.961 (C,D)
M(x) / ( P ) 0.831 1C1 ! 0.053 (A,B)
M(x) / ( P ) 0.831 2C ! 0.034 (C,D)
56
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 N(x) / ( MC/(Rm**2 * Beta) ) 0.681 4A ! 0.711 (A,B,C,D)
M(x) / ( MC/(Rm * Beta) ) 0.905 2A ! 0.043 (A,B,C,D)
N(x) / ( ML/(Rm**2 * Beta) ) 0.798 4B ! 0.324 (A,B,C,D)
M(x) / ( ML/(Rm * Beta) ) 0.878 2B ! 0.041 (A,B,C,D)
Note - The ! mark next to the figure name denotes curve value exceeded.
Stress Concentration Factors Kn = 1.00, Kb = 1.00
Stresses in the Vessel at the Edge of Reinforcing Pad
------------------------------------------------------------------------
| Stress Values at
Type of | (MPa )
---------------|--------------------------------------------------------
Stress Load| Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Memb. P | 2 2 2 2 2 2 2 2
Circ. Bend. P | 4 -4 4 -4 7 -7 7 -7
Circ. Memb. MC | 0 0 0 0 0 0 0 0
Circ. Bend. MC | 0 0 0 0 0 0 0 0
Circ. Memb. ML | 1 1 -1 -1 0 0 0 0
Circ. Bend. ML | 1 -1 -1 1 0 0 0 0
|
Tot. Circ. Str.| 9.8 -1.8 4.4 -0.7 9.1 -5.0 9.1 -5.0
------------------------------------------------------------------------
Long. Memb. P | 2 2 2 2 2 2 2 2
Long. Bend. P | 6 -6 6 -6 4 -4 4 -4
Long. Memb. MC | 0 0 0 0 0 0 0 0
Long. Bend. MC | 0 0 0 0 0 0 0 0
57
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 Long. Memb. ML | 0 0 0 0 0 0 0 0
Long. Bend. ML | 2 -2 -2 2 0 0 0 0
|
Tot. Long. Str.| 12.1 -6.8 5.6 -2.8 7.4 -1.5 7.4 -1.5
------------------------------------------------------------------------
Shear VC | 0 0 0 0 0 0 0 0
Shear VL | 0 0 0 0 0 0 0 0
Shear MT | 0 0 0 0 0 0 0 0
|
Tot. Shear| 0.0 0.0 0.0 0.0 0.5 0.5 -0.5 -0.5
------------------------------------------------------------------------
Str. Int. | 12.10 6.82 5.60 2.80 9.20 5.11 9.20 5.11
------------------------------------------------------------------------
WRC 107/537 Stress Summations:
Vessel Stress Summation at Attachment Junction
------------------------------------------------------------------------
Type of | Stress Values at
Stress Int. | (MPa )
---------------|--------------------------------------------------------
Location | Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Pm (SUS) | 0 0 0 0 0 0 0 0
Circ. Pl (SUS) | 1 1 0 0 0 0 0 0
Circ. Q (SUS) | 2 -2 1 -1 2 -2 2 -2
------------------------------------------------------------------------
Long. Pm (SUS) | 0 0 0 0 0 0 0 0
Long. Pl (SUS) | 1 1 0 0 1 1 1 1
Long. Q (SUS) | 3 -3 0 0 1 -1 1 -1
------------------------------------------------------------------------
58
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 Shear Pm (SUS) | 0 0 0 0 0 0 0 0
Shear Pl (SUS) | 0 0 0 0 0 0 0 0
Shear Q (SUS) | 0 0 0 0 0 0 0 0
------------------------------------------------------------------------
Pm (SUS) | 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
------------------------------------------------------------------------
Pm+Pl (SUS) | 1.5 1.5 0.6 0.6 1.2 1.2 1.2 1.2
------------------------------------------------------------------------
Pm+Pl+Q (Total)| 4.5 1.8 1.7 0.6 3.7 2.0 3.7 2.0
------------------------------------------------------------------------
------------------------------------------------------------------------
Type of | Max. S.I. S.I. Allowable | Result
Stress Int. | MPa |
---------------|--------------------------------------------------------
Pm (SUS) | 0.00 137.90 | Passed
Pm+Pl (SUS) | 1.48 206.85 | Passed
Pm+Pl+Q (TOTAL)| 4.45 413.70 | Passed
------------------------------------------------------------------------
WRC 107/537 Stress Summations:
Vessel Stress Summation at Reinforcing Pad Edge
------------------------------------------------------------------------
Type of | Stress Values at
Stress Int. | (MPa )
---------------|--------------------------------------------------------
Location | Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Pm (SUS) | 0 0 0 0 0 0 0 0
Circ. Pl (SUS) | 4 4 1 1 2 2 2 2
59
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Lifting Lug Calcs : Right Side Step: 12 12:36p Jan 11,2015 Circ. Q (SUS) | 5 -5 2 -2 7 -7 7 -7
------------------------------------------------------------------------
Long. Pm (SUS) | 0 0 0 0 0 0 0 0
Long. Pl (SUS) | 2 2 1 1 2 2 2 2
Long. Q (SUS) | 9 -9 4 -4 4 -4 4 -4
------------------------------------------------------------------------
Shear Pm (SUS) | 0 0 0 0 0 0 0 0
Shear Pl (SUS) | 0 0 0 0 0 0 0 0
Shear Q (SUS) | 0 0 0 0 0 0 0 0
------------------------------------------------------------------------
Pm (SUS) | 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
------------------------------------------------------------------------
Pm+Pl (SUS) | 4.0 4.0 1.8 1.8 3.1 3.1 3.1 3.1
------------------------------------------------------------------------
Pm+Pl+Q (Total)| 12.1 6.8 5.6 2.8 9.2 5.1 9.2 5.1
------------------------------------------------------------------------
------------------------------------------------------------------------
Type of | Max. S.I. S.I. Allowable | Result
Stress Int. | MPa |
---------------|--------------------------------------------------------
Pm (SUS) | 0.00 137.90 | Passed
Pm+Pl (SUS) | 4.01 206.85 | Passed
Pm+Pl+Q (TOTAL)| 12.10 413.70 | Passed
------------------------------------------------------------------------
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
60
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015
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
Input and Calculated Values:
Vessel Mean Radius Rm 53.41 mm
Stiffened Vessel Length per 4.15.6 L 1089.70 mm
Distance from Saddle to Vessel tangent a 164.00 mm
Saddle Width b 70.00 mm
Saddle Bearing Angle theta 120.00 degrees
Wear Plate Width b1 102.00 mm
Wear Plate Bearing Angle theta1 132.00 degrees
Wear Plate Thickness tr 8.0 mm
Wear Plate Allowable Stress Sr 115.15 MPa
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 14201.79 N
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan -16.81 -2029.24 MPa
Long. Stress at Top of Midspan 16.81 137.90 MPa
61
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 Long. Stress at Bottom of Midspan 29.64 137.90 MPa
Long. Stress at Top of Saddles 52.82 137.90 MPa
Long. Stress at Bottom of Saddles -19.30 -2029.24 MPa
Long. Stress at Bottom of Saddles 19.30 137.90 MPa
Tangential Shear in Shell 29.06 82.74 MPa
Circ. Stress at Horn of Saddle 8.08 172.38 MPa
Circ. Compressive Stress in Shell 1.42 137.90 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 * ( 210.9/2 + 0 ) * 255.0000/92.5003
= 872.2 N
Saddle Reaction Force due to Wind Fl or Friction [Fwl]:
= max( Fl, Friction Load, Sum of X Forces) * B / Ls
= max( 9.23 , 0.00 , 0 ) * 255.0000/640.0000
= 3.7 N
Saddle Reaction Force due to Earthquake Fl or Friction [Fsl]:
= max( Fl, Friction Force, Sum of X Forces ) * B / Ls
= max( 1929.38 , 0.00 , 0 ) * 255.0000/640.0000
= 768.7 N
Saddle Reaction Force due to Earthquake Ft [Fst]:
= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 1929/2 + 0 ) * 255.0000/92.5003
= 7978.2 N
62
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 Load Combination Results for Q + Wind or Seismic [Q]:
= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 6223 + Max( 3 , 872 , 768 , 7978 )
= 14201.8 N
Summary of Loads at the base of this Saddle:
Vertical Load (including saddle weight) 14253.41 N
Transverse Shear Load Saddle 964.69 N
Longitudinal Shear Load Saddle 1929.38 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 = 0.0529 K8 = 0.3405
K9 = 0.2711 K10 = 0.0581 K1* = 0.1923 K6p = 0.0434
K7P = 0.0434
The suffix 'p' denotes the values for a wear plate if it exists.
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)]
= -14201*164.00[1-(1-164.00/1089.70+(53.405²-0.000²)/
(2*164.00*1089.70))/(1+(4*0.00)/(3*1089.70))]
= -332.1 N-m
Moment per Equation 4.15.4 [M2]:
63
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = Q*L/4(1+2(R²-h2²)/(L²))/(1+(4h2)/( 3L))-4a/L
= 14201*1089/4(1+2(53²-0²)/(1089²))/(1+(4*0)/
(3*1089))-4*164/1089
= 1559.0 N-m
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]:
= P * Rm/(2t) - M2/(pi*Rm²t)
= 18.000 * 53.405/(2*7.490 ) - 1559.0/(pi*53.4²*7.490 )
= -16.81 MPa
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:
= P * Rm/(2t) + M2/(pi * Rm² * t)
= 18.000 * 53.405/(2 * 7.490 ) + 1559.0/(pi * 53.4² * 7.490 )
= 29.64 MPa
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:
= P * Rm/(2t) - M1/(K1*pi*Rm²t)
= 18.000*53.405/(2*7.490)--332.1/(0.1066*pi*53.4²*7.490)
= 52.82 MPa
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]:
= P * Rm/(2t) + M1/(K1* * pi * Rm² * t)
= 18.000*53.405/(2*7.490)+-332.1/(0.1923*pi*53.4²*7.490)
= -19.30 MPa
Maximum Shear Force in the Saddle (4.15.5) [T]:
= Q(L-2a)/(L+(4*h2/3))
= 14201 ( 1089.70 - 2 * 164.00 )/(1089.70 + ( 4 * 0.00/3))
= 9927.0 N
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:
64
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = K2 * T / ( Rm * t )
= 1.1707 * 9927.05/( 53.4051 * 7.4898 )
= 29.06 MPa
Decay Length (4.15.22) [x1,x2]:
= 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 53.405 * 7.490 )
= 15.600 mm
Circumferential Stress in shell, no rings (4.15.23) [sigma6]:
= -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7603 * 14201 * 0.1/( 7.490 * ( 70.00 + 15.60 + 15.60 ) )
= -1.42 MPa
Effective reinforcing plate width (4.15.1) [B1]:
= min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 70.00 + 1.56 * sqrt( 53.405 * 7.490 ), 2 * 164.000 )
= 101.20 mm
Wear Plate/Shell Stress ratio (4.15.29) [eta]:
= min( Sr/S, 1 )
= min( 115.146/137.900 , 1 )
= 0.8350
Circumferential Stress at wear plate (4.15.26) [sigma6,r]:
= -K5 * Q * k / ( B1( t + eta * tr ) )
= -0.7603 * 14201 * 0.1/( 101.200 ( 7.490 + 0.835 * 8.000 ) )
= -0.75 MPa
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.27) [sigma7,r]:
= -Q/(4(t+eta*tr)b1) - 3*K7*Q/(2(t+eta*tr)²)
65
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = -14201/(4(7.490 + 0.835 * 8.000 )101.200 ) -
3 * 0.053 * 14201/(2(7.490 + 0.835 * 8.000 )²)
= -8.08 MPa
Free Un-Restrained Thermal Expansion between the Saddles [Exp]:
= Alpha * Ls * ( Design Temperature - Ambient Temperature )
= 0.156E-04 * 640.000 * ( 50.0 - 21.1 )
= 0.289 mm
Results for Vessel Ribs, Web and Base:
Baseplate Length Bplen 132.0000 mm
Baseplate Thickness Bpthk 8.0000 mm
Baseplate Width Bpwid 90.0000 mm
Number of Ribs ( inc. outside ribs ) Nribs 2
Rib Thickness Ribtk 8.0000 mm
Web Thickness Webtk 8.0000 mm
Web Location Webloc Center
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 4. 989. 3705. 18499.
Wearplate 11. 816. 9376. 112077.
Web 97. 1300. 125776. 15029416.
BasePlate 182. 720. 131040. 23853098.
Totals 294. 3825. 269897. 39013088.
Value C1 = Sumof(Ay)/Sumof(A) = 71. mm
Value I = Sumof(Io) - C1*Sumof(Ay) = 19970750. mm**4
Value As = Sumof(A) - Ashell = 2836. mm²
66
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035
Fh = K1 * Q = 0.2035 * 14201.791 = 2890.3728 N
Tension Stress, St = ( Fh/As ) = 1.0192 MPa
Allowed Stress, Sa = 0.6 * Yield Str = 103.4250 MPa
d = B - R*Sin(theta) / theta = 194.5916 mm
Bending Moment, M = Fh * d = 562.6701 N-m
Bending Stress, Sb = ( M * C1 / I ) = 1.9872 MPa
Allowed Stress, Sa = 2/3 * Yield Str = 114.9167 MPa
Minimum Thickness of Baseplate per Moss :
= ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 4 * BasePlateLength *
AllStress ))½
= ( 3 * (14201 + 51 ) * 90.00/( 4 * 132.000 * 114.917 ))½
= 7.964 mm
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]:
= ( Bplen - Clearance ) / ( Nribs - 1)
= ( 132.0000 - 25.4 )/( 2 - 1 ) = 106.6000 mm
Baseplate Pressure Area [Ap]:
= e * Bpwid / 2
= 106.6000 * 90.0000/2 = 4796.9995 mm²
Axial Load [P]:
= Ap * Bp
67
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = 4797.0 * 1.20 = 5734.5 N
Area of the Rib and Web [Ar]:
= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 90.000 - 25.4 - 8.000 ) * 8.000 + 106.6000/2 * 8.000
= 879.200 mm²
Compressive Stress [Sc]:
= P/Ar
= 5734.5/879.2000 = 6.5230 MPa
Check of Outside Ribs:
Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay² Io
Rib 35.0 474.4 16604.0 0.0 203213.9
Web 35.0 426.4 14924.0 0.0 4548.3
Values 35.0 900.8 31528.0 0.0 207762.2
Bending Moment [Rm]:
= Fl /( 2 * Bplen ) * e * rl / 2
= 1929.4/( 2 * 132.00 ) * 106.600 * 207.09/2
= 80.699 N-m
KL/R < Cc ( 13.4713 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 13.47 )²/(2 * 151.32² )) * 172/
( 5/3+3*(13.47 )/(8* 151.32 )-( 13.47³)/(8*151.32³)
Sca = 101.00 MPa
AISC Unity Check on Outside Ribs ( must be <= 1.0 )
68
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 Check = Sc/Sca + (Rm/Z)/Sba
Check = 6.52/101.00 + (80.70/5936.062 )/114.92
Check = 0.18
Input Data for Base Plate Bolting Calculations:
Total Number of Bolts per BasePlate Nbolts 2
Total Number of Bolts in Tension/Baseplate Nbt 2
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 32.9946 mm
Nominal Bolt Diameter Bnd 12.0000 mm
Thread Series Series TEMA Metric
BasePlate Allowable Stress S 115.15 MPa
Area Available in a Single Bolt BltArea 72.3980 mm²
Saddle Load QO (Weight) QO 6275.2 N
Saddle Load QL (Wind/Seismic contribution) QL 768.7 N
Maximum Transverse Force Ft 964.7 N
Maximum Longitudinal Force Fl 1929.4 N
Saddle Bolted to Steel Foundation Yes
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)
= 1929.38/(172.38 * 2.00 )
= 5.5969 mm²
69
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015
Bolt Area due to Transverse Load
Moment on Baseplate Due to Transverse Load [Rmom]:
= B * Ft + Sum of X Moments
= 255.00 * 964.69 + 0.00
= 246.10 N-m
Eccentricity (e):
= Rmom / QO
= 246.10/6275.18
= 39.20 mm > Bplen/6 --> Uplift in Transverse direction
f = Bplen / 2 - Edgedis
= 132.00/2 - 32.99
= 33.01 mm
K1 = 3 (e - 0.5 * Bplen)
= 3 (39.20 - 0.5*132.00 )
= -80.40 mm
K2 = 6 * n1 * At / Bpwid * (f + e)
= 6 * 1.00 * 144.80/90.00 * (33.01 + 39.20 )
= 697.02 mm ²
K3 = -K2 * (0.5 * Bplen + f)
= -697.02 * (0.5 * 132.00 + 33.01 )
= -69008.49 mm ³
Iteratively Solving for the Effective Bearing Length:
Y³ + K1 * Y² + K2 * Y + K3 = 0
70
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 Y³ + -80.40 * Y² + 697.02 * Y + -69008.48 = 0
Y = 82.14 mm
Num = (Bplen / 2 - Y / 3 - e)
= (132.00/2 - 82.14/3 - 39.20 )
= -0.58
Denom = (Bplen / 2 - Y / 3 + f)
= (132.00/2 - 82.14/3 + 33.01 )
= 71.63
Total Bolt Tension Force [Tforce]:
= - QO * Num / Denom
= - 6275.18 * -0.58/71.63
= 50.89 N
Bolt Area Required due to Transverse Load [Bltareart]
= Tforce / (Stba * Nbt)
= 50.89/( 172.38 * 2.00 )
= 0.1476 mm²
Required of a Single Bolt [Bltarear]
= max[Bltarearl, Bltarears, Bltareart]
= max[0.0000 , 5.5969 , 0.1476 ]
= 5.5969 mm²
Baseplate Thickness Calculation per D. Moss:
Bearing Pressure (fc)
= 2 * (QO + Tforce) / (Y * Bplen)
71
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = 2 * (6275.18 + 50.89 )/(82.14 * 132.00 )
= 11.67 bar
Distance from Baseplate Edge to the Web [ADIST]:
= (Bplen - Weblngth) / 2
= (132.00 - 81.20 )/2
= 25.4000 mm
Overturning Moment due To Bolt Tension [Mt]:
= Tforce * Adist
= 50.89 * 25.40
= 1.29 N-m
Equivalent Bearing Pressure (f1):
= fc * (Y - Adist) / Y
= 11.67 * (82.14 - 25.40 )/82.14
= 8.06 bar
Overturning Moment due to Bearing Pressure [Mc]:
= (Adist² * Bpwid / 6) * (f1 + 2 * fc)
= (25.40² * 90.00/6) * (8.06 + 2 * 11.67 )
= 30.40 N-m
Baseplate Required Thickness [Treq]:
= (6 * max(Mt,Mc) / (Bpwid * Sba))½
= (6 *max(1.29 ,30.40/(90.00 * 172.72 ))½
= 3.4249 mm
ASME Horizontal Vessel Analysis: Stresses for the Right Saddle
(per ASME Sec. VIII Div. 2 based on the Zick method.)
72
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015
Input and Calculated Values:
Vessel Mean Radius Rm 53.41 mm
Stiffened Vessel Length per 4.15.6 L 1089.70 mm
Distance from Saddle to Vessel tangent a 246.00 mm
Saddle Width b 70.00 mm
Saddle Bearing Angle theta 120.00 degrees
Wear Plate Width b1 102.00 mm
Wear Plate Bearing Angle theta1 132.00 degrees
Wear Plate Thickness tr 8.0 mm
Wear Plate Allowable Stress Sr 115.15 MPa
Inside Depth of Head h2 24.83 mm
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 13227.72 N
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 2.60 137.90 MPa
Long. Stress at Bottom of Midspan 10.24 137.90 MPa
Long. Stress at Top of Saddles 117.64 137.90 MPa
Long. Stress at Bottom of Saddles -55.23 -2029.24 MPa
Long. Stress at Bottom of Saddles 55.23 137.90 MPa
73
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 Tangential Shear in Shell 20.61 82.74 MPa
Circ. Stress at Horn of Saddle 7.53 172.38 MPa
Circ. Compressive Stress in Shell 1.33 137.90 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 * ( 210.9/2 + 0 ) * 255.0000/92.5003
= 872.2 N
Saddle Reaction Force due to Wind Fl or Friction [Fwl]:
= max( Fl, Friction Load, Sum of X Forces) * B / Ls
= max( 9.23 , 0.00 , 0 ) * 255.0000/640.0000
= 3.7 N
Saddle Reaction Force due to Earthquake Fl or Friction [Fsl]:
= max( Fl, Friction Force, Sum of X Forces ) * B / Ls
= max( 1929.38 , 0.00 , 0 ) * 255.0000/640.0000
= 768.7 N
Saddle Reaction Force due to Earthquake Ft [Fst]:
= Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E
= 3.00 * ( 1929/2 + 0 ) * 255.0000/92.5003
= 7978.2 N
Load Combination Results for Q + Wind or Seismic [Q]:
= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 5249 + Max( 3 , 872 , 768 , 7978 )
= 13227.7 N
74
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 Summary of Loads at the base of this Saddle:
Vertical Load (including saddle weight) 13279.33 N
Transverse Shear Load Saddle 964.69 N
Longitudinal Shear Load Saddle 1929.38 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 = 0.0529 K8 = 0.3405
K9 = 0.2711 K10 = 0.0581 K1* = 0.1923 K6p = 0.0434
K7P = 0.0434
The suffix 'p' denotes the values for a wear plate if it exists.
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)]
= -13227*246.00[1-(1-246.00/1089.70+(53.405²-24.830²)/
(2*246.00*1089.70))/(1+(4*24.83)/(3*1089.70))]
= -796.0 N-m
Moment per Equation 4.15.4 [M2]:
= Q*L/4(1+2(R²-h2²)/(L²))/(1+(4h2)/( 3L))-4a/L
= 13227*1089/4(1+2(53²-24²)/(1089²))/(1+(4*24)/
(3*1089))-4*246/1089
= 256.6 N-m
75
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]:
= P * Rm/(2t) - M2/(pi*Rm²t)
= 18.000 * 53.405/(2*7.490 ) - 256.6/(pi*53.4²*7.490 )
= 2.60 MPa
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:
= P * Rm/(2t) + M2/(pi * Rm² * t)
= 18.000 * 53.405/(2 * 7.490 ) + 256.6/(pi * 53.4² * 7.490 )
= 10.24 MPa
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:
= P * Rm/(2t) - M1/(K1*pi*Rm²t)
= 18.000*53.405/(2*7.490)--796.0/(0.1066*pi*53.4²*7.490)
= 117.64 MPa
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]:
= P * Rm/(2t) + M1/(K1* * pi * Rm² * t)
= 18.000*53.405/(2*7.490)+-796.0/(0.1923*pi*53.4²*7.490)
= -55.23 MPa
Maximum Shear Force in the Saddle (4.15.5) [T]:
= Q(L-2a)/(L+(4*h2/3))
= 13227 ( 1089.70 - 2 * 246.00 )/(1089.70 + ( 4 * 24.83/3))
= 7041.5 N
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:
= K2 * T / ( Rm * t )
= 1.1707 * 7041.47/( 53.4051 * 7.4898 )
= 20.61 MPa
Decay Length (4.15.22) [x1,x2]:
76
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 53.405 * 7.490 )
= 15.600 mm
Circumferential Stress in shell, no rings (4.15.23) [sigma6]:
= -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7603 * 13227 * 0.1/( 7.490 * ( 70.00 + 15.60 + 15.60 ) )
= -1.33 MPa
Effective reinforcing plate width (4.15.1) [B1]:
= min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 70.00 + 1.56 * sqrt( 53.405 * 7.490 ), 2 * 246.000 )
= 101.20 mm
Wear Plate/Shell Stress ratio (4.15.29) [eta]:
= min( Sr/S, 1 )
= min( 115.146/137.900 , 1 )
= 0.8350
Circumferential Stress at wear plate (4.15.26) [sigma6,r]:
= -K5 * Q * k / ( B1( t + eta * tr ) )
= -0.7603 * 13227 * 0.1/( 101.200 ( 7.490 + 0.835 * 8.000 ) )
= -0.70 MPa
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.27) [sigma7,r]:
= -Q/(4(t+eta*tr)b1) - 3*K7*Q/(2(t+eta*tr)²)
= -13227/(4(7.490 + 0.835 * 8.000 )101.200 ) -
3 * 0.053 * 13227/(2(7.490 + 0.835 * 8.000 )²)
= -7.53 MPa
Results for Vessel Ribs, Web and Base
77
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015
Baseplate Length Bplen 132.0000 mm
Baseplate Thickness Bpthk 8.0000 mm
Baseplate Width Bpwid 90.0000 mm
Number of Ribs ( inc. outside ribs ) Nribs 2
Rib Thickness Ribtk 8.0000 mm
Web Thickness Webtk 8.0000 mm
Web Location Webloc Center
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 4. 989. 3705. 18499.
Wearplate 11. 816. 9376. 112077.
Web 97. 1300. 125776. 15029416.
BasePlate 182. 720. 131040. 23853098.
Totals 294. 3825. 269897. 39013088.
Value C1 = Sumof(Ay)/Sumof(A) = 71. mm
Value I = Sumof(Io) - C1*Sumof(Ay) = 19970750. mm**4
Value As = Sumof(A) - Ashell = 2836. mm²
K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035
Fh = K1 * Q = 0.2035 * 13227.716 = 2692.1272 N
Tension Stress, St = ( Fh/As ) = 0.9493 MPa
Allowed Stress, Sa = 0.6 * Yield Str = 103.4250 MPa
d = B - R*Sin(theta) / theta = 194.5916 mm
Bending Moment, M = Fh * d = 524.0776 N-m
78
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015
Bending Stress, Sb = ( M * C1 / I ) = 1.8509 MPa
Allowed Stress, Sa = 2/3 * Yield Str = 114.9167 MPa
Minimum Thickness of Baseplate per Moss :
= ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 4 * BasePlateLength *
AllStress ))½
= ( 3 * (13227 + 51 ) * 90.00/( 4 * 132.000 * 114.917 ))½
= 7.687 mm
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]:
= ( Bplen - Clearance ) / ( Nribs - 1)
= ( 132.0000 - 25.4 )/( 2 - 1 ) = 106.6000 mm
Baseplate Pressure Area [Ap]:
= e * Bpwid / 2
= 106.6000 * 90.0000/2 = 4796.9995 mm²
Axial Load [P]:
= Ap * Bp
= 4797.0 * 1.11 = 5341.2 N
Area of the Rib and Web [Ar]:
= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 90.000 - 25.4 - 8.000 ) * 8.000 + 106.6000/2 * 8.000
= 879.200 mm²
Compressive Stress [Sc]:
= P/Ar
79
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = 5341.2/879.2000 = 6.0756 MPa
Check of Outside Ribs:
Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay² Io
Rib 35.0 474.4 16604.0 0.0 203213.9
Web 35.0 426.4 14924.0 0.0 4548.3
Values 35.0 900.8 31528.0 0.0 207762.2
Bending Moment [Rm]:
= Fl /( 2 * Bplen ) * e * rl / 2
= 1929.4/( 2 * 132.00 ) * 106.600 * 207.09/2
= 80.699 N-m
KL/R < Cc ( 13.4713 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 13.47 )²/(2 * 151.32² )) * 172/
( 5/3+3*(13.47 )/(8* 151.32 )-( 13.47³)/(8*151.32³)
Sca = 101.00 MPa
AISC Unity Check on Outside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 6.08/101.00 + (80.70/5936.062 )/114.92
Check = 0.18
Input Data for Base Plate Bolting Calculations:
Total Number of Bolts per BasePlate Nbolts 2
Total Number of Bolts in Tension/Baseplate Nbt 2
Bolt Material Specification SA-193 B7
80
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 Bolt Allowable Stress Stba 172.38 MPa
Bolt Corrosion Allowance Bca 0.0000 mm
Distance from Bolts to Edge Edgedis 32.9946 mm
Nominal Bolt Diameter Bnd 12.0000 mm
Thread Series Series TEMA Metric
BasePlate Allowable Stress S 115.15 MPa
Area Available in a Single Bolt BltArea 72.3980 mm²
Saddle Load QO (Weight) QO 5301.1 N
Saddle Load QL (Wind/Seismic contribution) QL 768.7 N
Maximum Transverse Force Ft 964.7 N
Maximum Longitudinal Force Fl 1929.4 N
Saddle Bolted to Steel Foundation Yes
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)
= 1929.38/(172.38 * 2.00 )
= 5.5969 mm²
Bolt Area due to Transverse Load
Moment on Baseplate Due to Transverse Load [Rmom]:
= B * Ft + Sum of X Moments
= 255.00 * 964.69 + 0.00
= 246.10 N-m
Eccentricity (e):
81
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = Rmom / QO
= 246.10/5301.11
= 46.40 mm > Bplen/6 --> Uplift in Transverse direction
f = Bplen / 2 - Edgedis
= 132.00/2 - 32.99
= 33.01 mm
K1 = 3 (e - 0.5 * Bplen)
= 3 (46.40 - 0.5*132.00 )
= -58.79 mm
K2 = 6 * n1 * At / Bpwid * (f + e)
= 6 * 1.00 * 144.80/90.00 * (33.01 + 46.40 )
= 766.55 mm ²
K3 = -K2 * (0.5 * Bplen + f)
= -766.55 * (0.5 * 132.00 + 33.01 )
= -75892.66 mm ³
Iteratively Solving for the Effective Bearing Length:
Y³ + K1 * Y² + K2 * Y + K3 = 0
Y³ + -58.79 * Y² + 766.55 * Y + -75892.66 = 0
Y = 64.97 mm
Num = (Bplen / 2 - Y / 3 - e)
= (132.00/2 - 64.97/3 - 46.40 )
= -2.06
Denom = (Bplen / 2 - Y / 3 + f)
= (132.00/2 - 64.97/3 + 33.01 )
82
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = 77.35
Total Bolt Tension Force [Tforce]:
= - QO * Num / Denom
= - 5301.11 * -2.06/77.35
= 141.22 N
Bolt Area Required due to Transverse Load [Bltareart]
= Tforce / (Stba * Nbt)
= 141.22/( 172.38 * 2.00 )
= 0.4097 mm²
Required of a Single Bolt [Bltarear]
= max[Bltarearl, Bltarears, Bltareart]
= max[0.0000 , 5.5969 , 0.4097 ]
= 5.5969 mm²
Baseplate Thickness Calculation per D. Moss:
Bearing Pressure (fc)
= 2 * (QO + Tforce) / (Y * Bplen)
= 2 * (5301.11 + 141.22 )/(64.97 * 132.00 )
= 12.69 bar
Distance from Baseplate Edge to the Web [ADIST]:
= (Bplen - Weblngth) / 2
= (132.00 - 81.20 )/2
= 25.4000 mm
Overturning Moment due To Bolt Tension [Mt]:
83
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 13 12:36p Jan 11,2015 = Tforce * Adist
= 141.22 * 25.40
= 3.59 N-m
Equivalent Bearing Pressure (f1):
= fc * (Y - Adist) / Y
= 12.69 * (64.97 - 25.40 )/64.97
= 7.73 bar
Overturning Moment due to Bearing Pressure [Mc]:
= (Adist² * Bpwid / 6) * (f1 + 2 * fc)
= (25.40² * 90.00/6) * (7.73 + 2 * 12.69 )
= 32.06 N-m
Baseplate Required Thickness [Treq]:
= (6 * max(Mt,Mc) / (Bpwid * Sba))½
= (6 *max(3.59 ,32.06/(90.00 * 172.72 ))½
= 3.5172 mm
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
84
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015
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
Input and Calculated Values:
Vessel Mean Radius Rm 53.41 mm
Stiffened Vessel Length per 4.15.6 L 1089.70 mm
Distance from Saddle to Vessel tangent a 164.00 mm
Saddle Width b 70.00 mm
Saddle Bearing Angle theta 120.00 degrees
Wear Plate Width b1 102.00 mm
Wear Plate Bearing Angle theta1 132.00 degrees
Wear Plate Thickness tr 8.0 mm
Wear Plate Allowable Stress Sr 115.15 MPa
Shell Allowable Stress used in Calculation 186.17 MPa
Head Allowable Stress used in Calculation 186.17 MPa
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
Saddle Force Q, Test Case, no Ext. Forces 1699.14 N
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 6.01 186.17 MPa
Long. Stress at Bottom of Midspan 11.57 186.17 MPa
85
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Long. Stress at Top of Saddles 14.34 186.17 MPa
Long. Stress at Bottom of Saddles 5.71 186.17 MPa
Tangential Shear in Shell 3.48 111.70 MPa
Circ. Stress at Horn of Saddle 1.21 279.25 MPa
Circ. Compressive Stress in Shell 0.17 186.17 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 * ( 69.6/2 + 0 ) * 255.0000/92.5003
= 287.8 N
Saddle Reaction Force due to Wind Fl or Friction [Fwl]:
= max( Fl, Friction Load, Sum of X Forces) * B / Ls
= max( 9.23 , 0.00 , 0 ) * 255.0000/640.0000
= 1.2 N
Load Combination Results for Q + Wind or Seismic [Q]:
= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 1411 + Max( 1 , 287 , 0 , 0 )
= 1699.1 N
Summary of Loads at the base of this Saddle:
Vertical Load (including saddle weight) 1750.76 N
Transverse Shear Load Saddle 34.80 N
Longitudinal Shear Load Saddle 3.05 N
Hydrostatic Test Pressure at center of Vessel: 24.653 bar
86
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 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 = 0.0529 K8 = 0.3405
K9 = 0.2711 K10 = 0.0581 K1* = 0.1923 K6p = 0.0434
K7P = 0.0434
The suffix 'p' denotes the values for a wear plate if it exists.
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)]
= -1699*164.00[1-(1-164.00/1089.70+(53.405²-0.000²)/
(2*164.00*1089.70))/(1+(4*0.00)/(3*1089.70))]
= -39.7 N-m
Moment per Equation 4.15.4 [M2]:
= Q*L/4(1+2(R²-h2²)/(L²))/(1+(4h2)/( 3L))-4a/L
= 1699*1089/4(1+2(53²-0²)/(1089²))/(1+(4*0)/
(3*1089))-4*164/1089
= 186.5 N-m
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]:
= P * Rm/(2t) - M2/(pi*Rm²t)
= 24.653 * 53.405/(2*7.490 ) - 186.5/(pi*53.4²*7.490 )
= 6.01 MPa
87
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:
= P * Rm/(2t) + M2/(pi * Rm² * t)
= 24.653 * 53.405/(2 * 7.490 ) + 186.5/(pi * 53.4² * 7.490 )
= 11.57 MPa
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:
= P * Rm/(2t) - M1/(K1*pi*Rm²t)
= 24.653*53.405/(2*7.490)--39.7/(0.1066*pi*53.4²*7.490)
= 14.34 MPa
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]:
= P * Rm/(2t) + M1/(K1* * pi * Rm² * t)
= 24.653*53.405/(2*7.490)+-39.7/(0.1923*pi*53.4²*7.490)
= 5.71 MPa
Maximum Shear Force in the Saddle (4.15.5) [T]:
= Q(L-2a)/(L+(4*h2/3))
= 1699 ( 1089.70 - 2 * 164.00 )/(1089.70 + ( 4 * 0.00/3))
= 1187.7 N
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:
= K2 * T / ( Rm * t )
= 1.1707 * 1187.70/( 53.4051 * 7.4898 )
= 3.48 MPa
Decay Length (4.15.22) [x1,x2]:
= 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 53.405 * 7.490 )
= 15.600 mm
Circumferential Stress in shell, no rings (4.15.23) [sigma6]:
88
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 = -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7603 * 1699 * 0.1/( 7.490 * ( 70.00 + 15.60 + 15.60 ) )
= -0.17 MPa
Effective reinforcing plate width (4.15.1) [B1]:
= min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 70.00 + 1.56 * sqrt( 53.405 * 7.490 ), 2 * 164.000 )
= 101.20 mm
Wear Plate/Shell Stress ratio (4.15.29) [eta]:
= min( Sr/S, 1 )
= min( 115.146/186.165 , 1 )
= 0.6185
Circumferential Stress at wear plate (4.15.26) [sigma6,r]:
= -K5 * Q * k / ( B1( t + eta * tr ) )
= -0.7603 * 1699 * 0.1/( 101.200 ( 7.490 + 0.619 * 8.000 ) )
= -0.10 MPa
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.27) [sigma7,r]:
= -Q/(4(t+eta*tr)b1) - 3*K7*Q/(2(t+eta*tr)²)
= -1699/(4(7.490 + 0.619 * 8.000 )101.200 ) -
3 * 0.053 * 1699/(2(7.490 + 0.619 * 8.000 )²)
= -1.21 MPa
Results for Vessel Ribs, Web and Base:
Baseplate Length Bplen 132.0000 mm
Baseplate Thickness Bpthk 8.0000 mm
Baseplate Width Bpwid 90.0000 mm
Number of Ribs ( inc. outside ribs ) Nribs 2
Rib Thickness Ribtk 8.0000 mm
89
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Web Thickness Webtk 8.0000 mm
Web Location Webloc Center
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 4. 989. 3705. 18499.
Wearplate 11. 816. 9376. 112077.
Web 97. 1300. 125776. 15029416.
BasePlate 182. 720. 131040. 23853098.
Totals 294. 3825. 269897. 39013088.
Value C1 = Sumof(Ay)/Sumof(A) = 71. mm
Value I = Sumof(Io) - C1*Sumof(Ay) = 19970750. mm**4
Value As = Sumof(A) - Ashell = 2836. mm²
K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035
Fh = K1 * Q = 0.2035 * 1699.144 = 345.8128 N
Tension Stress, St = ( Fh/As ) = 0.1219 MPa
Allowed Stress, Sa = 0.6 * Yield Str = 103.4250 MPa
d = B - R*Sin(theta) / theta = 194.5916 mm
Bending Moment, M = Fh * d = 67.3195 N-m
Bending Stress, Sb = ( M * C1 / I ) = 0.2378 MPa
Allowed Stress, Sa = 2/3 * Yield Str = 114.9167 MPa
Minimum Thickness of Baseplate per Moss :
= ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 4 * BasePlateLength *
90
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 AllStress ))½
= ( 3 * (1699 + 51 ) * 90.00/( 4 * 132.000 * 114.917 ))½
= 2.791 mm
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]:
= ( Bplen - Clearance ) / ( Nribs - 1)
= ( 132.0000 - 25.4 )/( 2 - 1 ) = 106.6000 mm
Baseplate Pressure Area [Ap]:
= e * Bpwid / 2
= 106.6000 * 90.0000/2 = 4796.9995 mm²
Axial Load [P]:
= Ap * Bp
= 4797.0 * 0.14 = 686.1 N
Area of the Rib and Web [Ar]:
= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 90.000 - 25.4 - 8.000 ) * 8.000 + 106.6000/2 * 8.000
= 879.200 mm²
Compressive Stress [Sc]:
= P/Ar
= 686.1/879.2000 = 0.7804 MPa
Check of Outside Ribs:
Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay² Io
Rib 35.0 474.4 16604.0 0.0 203213.9
91
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Web 35.0 426.4 14924.0 0.0 4548.3
Values 35.0 900.8 31528.0 0.0 207762.2
Bending Moment [Rm]:
= Fl /( 2 * Bplen ) * e * rl / 2
= 3.0/( 2 * 132.00 ) * 106.600 * 207.09/2
= 0.127 N-m
KL/R < Cc ( 13.4713 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 13.47 )²/(2 * 151.32² )) * 172/
( 5/3+3*(13.47 )/(8* 151.32 )-( 13.47³)/(8*151.32³)
Sca = 101.00 MPa
AISC Unity Check on Outside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 0.78/101.00 + (0.13/5936.062 )/114.92
Check = 0.01
Input Data for Base Plate Bolting Calculations:
Total Number of Bolts per BasePlate Nbolts 2
Total Number of Bolts in Tension/Baseplate Nbt 2
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 32.9946 mm
Nominal Bolt Diameter Bnd 12.0000 mm
Thread Series Series TEMA Metric
BasePlate Allowable Stress S 115.15 MPa
92
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Area Available in a Single Bolt BltArea 72.3980 mm²
Saddle Load QO (Weight) QO 1462.9 N
Saddle Load QL (Wind/Seismic contribution) QL 1.2 N
Maximum Transverse Force Ft 34.8 N
Maximum Longitudinal Force Fl 3.0 N
Saddle Bolted to Steel Foundation Yes
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)
= 3.05/(172.38 * 2.00 )
= 0.0088 mm²
Bolt Area due to Transverse Load
Moment on Baseplate Due to Transverse Load [Rmom]:
= B * Ft + Sum of X Moments
= 255.00 * 34.84 + 0.00
= 8.89 N-m
Eccentricity (e):
= Rmom / QO
= 8.89/1462.92
= 6.07 mm < Bplen/6 --> No Uplift in Transverse direction
Bolt Area due to Transverse Load [Bltareart]:
= 0 (No Uplift)
93
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015
Required of a Single Bolt [Bltarear]
= max[Bltarearl, Bltarears, Bltareart]
= max[0.0000 , 0.0088 , 0.0000 ]
= 0.0088 mm²
ASME Horizontal Vessel Analysis: Stresses for the Right Saddle
(per ASME Sec. VIII Div. 2 based on the Zick method.)
Input and Calculated Values:
Vessel Mean Radius Rm 53.41 mm
Stiffened Vessel Length per 4.15.6 L 1089.70 mm
Distance from Saddle to Vessel tangent a 246.00 mm
Saddle Width b 70.00 mm
Saddle Bearing Angle theta 120.00 degrees
Wear Plate Width b1 102.00 mm
Wear Plate Bearing Angle theta1 132.00 degrees
Wear Plate Thickness tr 8.0 mm
Wear Plate Allowable Stress Sr 115.15 MPa
Inside Depth of Head h2 24.83 mm
Shell Allowable Stress used in Calculation 186.17 MPa
Head Allowable Stress used in Calculation 186.17 MPa
Circumferential Efficiency in Plane of Saddle 1.00
Circumferential Efficiency at Mid-Span 1.00
94
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Saddle Force Q, Test Case, no Ext. Forces 1741.68 N
Horizontal Vessel Analysis Results: Actual Allowable
-------------------------------------------------------------------
Long. Stress at Top of Midspan 8.29 186.17 MPa
Long. Stress at Bottom of Midspan 9.29 186.17 MPa
Long. Stress at Top of Saddles 23.44 186.17 MPa
Long. Stress at Bottom of Saddles 0.67 186.17 MPa
Tangential Shear in Shell 2.71 111.70 MPa
Circ. Stress at Horn of Saddle 1.24 279.25 MPa
Circ. Compressive Stress in Shell 0.17 186.17 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 * ( 69.6/2 + 0 ) * 255.0000/92.5003
= 287.8 N
Saddle Reaction Force due to Wind Fl or Friction [Fwl]:
= max( Fl, Friction Load, Sum of X Forces) * B / Ls
= max( 9.23 , 0.00 , 0 ) * 255.0000/640.0000
= 1.2 N
Load Combination Results for Q + Wind or Seismic [Q]:
= Saddle Load + Max( Fwl, Fwt, Fsl, Fst )
= 1453 + Max( 1 , 287 , 0 , 0 )
= 1741.7 N
Summary of Loads at the base of this Saddle:
95
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Vertical Load (including saddle weight) 1793.29 N
Transverse Shear Load Saddle 34.80 N
Longitudinal Shear Load Saddle 3.05 N
Hydrostatic Test Pressure at center of Vessel: 24.653 bar
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 = 0.0529 K8 = 0.3405
K9 = 0.2711 K10 = 0.0581 K1* = 0.1923 K6p = 0.0434
K7P = 0.0434
The suffix 'p' denotes the values for a wear plate if it exists.
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)]
= -1741*246.00[1-(1-246.00/1089.70+(53.405²-24.830²)/
(2*246.00*1089.70))/(1+(4*24.83)/(3*1089.70))]
= -104.8 N-m
Moment per Equation 4.15.4 [M2]:
= Q*L/4(1+2(R²-h2²)/(L²))/(1+(4h2)/( 3L))-4a/L
= 1741*1089/4(1+2(53²-24²)/(1089²))/(1+(4*24)/
(3*1089))-4*246/1089
= 33.8 N-m
96
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015
Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]:
= P * Rm/(2t) - M2/(pi*Rm²t)
= 24.653 * 53.405/(2*7.490 ) - 33.8/(pi*53.4²*7.490 )
= 8.29 MPa
Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]:
= P * Rm/(2t) + M2/(pi * Rm² * t)
= 24.653 * 53.405/(2 * 7.490 ) + 33.8/(pi * 53.4² * 7.490 )
= 9.29 MPa
Longitudinal Stress at Top of Shell at Support (4.15.10) [Sigma*3]:
= P * Rm/(2t) - M1/(K1*pi*Rm²t)
= 24.653*53.405/(2*7.490)--104.8/(0.1066*pi*53.4²*7.490)
= 23.44 MPa
Longitudinal Stress at Bottom of Shell at Support (4.15.11) [Sigma*4]:
= P * Rm/(2t) + M1/(K1* * pi * Rm² * t)
= 24.653*53.405/(2*7.490)+-104.8/(0.1923*pi*53.4²*7.490)
= 0.67 MPa
Maximum Shear Force in the Saddle (4.15.5) [T]:
= Q(L-2a)/(L+(4*h2/3))
= 1741 ( 1089.70 - 2 * 246.00 )/(1089.70 + ( 4 * 24.83/3))
= 927.1 N
Shear Stress in the shell no rings, not stiffened (4.15.14) [tau2]:
= K2 * T / ( Rm * t )
= 1.1707 * 927.14/( 53.4051 * 7.4898 )
= 2.71 MPa
97
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Decay Length (4.15.22) [x1,x2]:
= 0.78 * sqrt( Rm * t )
= 0.78 * sqrt( 53.405 * 7.490 )
= 15.600 mm
Circumferential Stress in shell, no rings (4.15.23) [sigma6]:
= -K5 * Q * k / ( t * ( b + X1 + X2 ) )
= -0.7603 * 1741 * 0.1/( 7.490 * ( 70.00 + 15.60 + 15.60 ) )
= -0.17 MPa
Effective reinforcing plate width (4.15.1) [B1]:
= min( b + 1.56 * sqrt( Rm * t ), 2a )
= min( 70.00 + 1.56 * sqrt( 53.405 * 7.490 ), 2 * 246.000 )
= 101.20 mm
Wear Plate/Shell Stress ratio (4.15.29) [eta]:
= min( Sr/S, 1 )
= min( 115.146/186.165 , 1 )
= 0.6185
Circumferential Stress at wear plate (4.15.26) [sigma6,r]:
= -K5 * Q * k / ( B1( t + eta * tr ) )
= -0.7603 * 1741 * 0.1/( 101.200 ( 7.490 + 0.619 * 8.000 ) )
= -0.11 MPa
Circ. Comp. Stress at Horn of Saddle, L>=8Rm (4.15.27) [sigma7,r]:
= -Q/(4(t+eta*tr)b1) - 3*K7*Q/(2(t+eta*tr)²)
= -1741/(4(7.490 + 0.619 * 8.000 )101.200 ) -
3 * 0.053 * 1741/(2(7.490 + 0.619 * 8.000 )²)
= -1.24 MPa
98
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Results for Vessel Ribs, Web and Base
Baseplate Length Bplen 132.0000 mm
Baseplate Thickness Bpthk 8.0000 mm
Baseplate Width Bpwid 90.0000 mm
Number of Ribs ( inc. outside ribs ) Nribs 2
Rib Thickness Ribtk 8.0000 mm
Web Thickness Webtk 8.0000 mm
Web Location Webloc Center
Moment of Inertia of Saddle - Lateral Direction
Y A AY Io
Shell 4. 989. 3705. 18499.
Wearplate 11. 816. 9376. 112077.
Web 97. 1300. 125776. 15029416.
BasePlate 182. 720. 131040. 23853098.
Totals 294. 3825. 269897. 39013088.
Value C1 = Sumof(Ay)/Sumof(A) = 71. mm
Value I = Sumof(Io) - C1*Sumof(Ay) = 19970750. mm**4
Value As = Sumof(A) - Ashell = 2836. mm²
K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2035
Fh = K1 * Q = 0.2035 * 1741.678 = 354.4694 N
Tension Stress, St = ( Fh/As ) = 0.1250 MPa
Allowed Stress, Sa = 0.6 * Yield Str = 103.4250 MPa
d = B - R*Sin(theta) / theta = 194.5916 mm
99
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Bending Moment, M = Fh * d = 69.0047 N-m
Bending Stress, Sb = ( M * C1 / I ) = 0.2437 MPa
Allowed Stress, Sa = 2/3 * Yield Str = 114.9167 MPa
Minimum Thickness of Baseplate per Moss :
= ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 4 * BasePlateLength *
AllStress ))½
= ( 3 * (1741 + 51 ) * 90.00/( 4 * 132.000 * 114.917 ))½
= 2.825 mm
Calculation of Axial Load, Intermediate Values and Compressive Stress
Effective Baseplate Length [e]:
= ( Bplen - Clearance ) / ( Nribs - 1)
= ( 132.0000 - 25.4 )/( 2 - 1 ) = 106.6000 mm
Baseplate Pressure Area [Ap]:
= e * Bpwid / 2
= 106.6000 * 90.0000/2 = 4796.9995 mm²
Axial Load [P]:
= Ap * Bp
= 4797.0 * 0.15 = 703.3 N
Area of the Rib and Web [Ar]:
= ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk
= ( 90.000 - 25.4 - 8.000 ) * 8.000 + 106.6000/2 * 8.000
= 879.200 mm²
Compressive Stress [Sc]:
100
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 = P/Ar
= 703.3/879.2000 = 0.8000 MPa
Check of Outside Ribs:
Inertia of Saddle, Outer Ribs - Longitudinal Direction
Y A AY Ay² Io
Rib 35.0 474.4 16604.0 0.0 203213.9
Web 35.0 426.4 14924.0 0.0 4548.3
Values 35.0 900.8 31528.0 0.0 207762.2
Bending Moment [Rm]:
= Fl /( 2 * Bplen ) * e * rl / 2
= 3.0/( 2 * 132.00 ) * 106.600 * 207.09/2
= 0.127 N-m
KL/R < Cc ( 13.4713 < 151.3192 ) per AISC E2-1
Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³)
Sca = ( 1-( 13.47 )²/(2 * 151.32² )) * 172/
( 5/3+3*(13.47 )/(8* 151.32 )-( 13.47³)/(8*151.32³)
Sca = 101.00 MPa
AISC Unity Check on Outside Ribs ( must be <= 1.0 )
Check = Sc/Sca + (Rm/Z)/Sba
Check = 0.80/101.00 + (0.13/5936.062 )/114.92
Check = 0.01
Input Data for Base Plate Bolting Calculations:
Total Number of Bolts per BasePlate Nbolts 2
Total Number of Bolts in Tension/Baseplate Nbt 2
101
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 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 32.9946 mm
Nominal Bolt Diameter Bnd 12.0000 mm
Thread Series Series TEMA Metric
BasePlate Allowable Stress S 115.15 MPa
Area Available in a Single Bolt BltArea 72.3980 mm²
Saddle Load QO (Weight) QO 1505.5 N
Saddle Load QL (Wind/Seismic contribution) QL 1.2 N
Maximum Transverse Force Ft 34.8 N
Maximum Longitudinal Force Fl 3.0 N
Saddle Bolted to Steel Foundation Yes
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)
= 3.05/(172.38 * 2.00 )
= 0.0088 mm²
Bolt Area due to Transverse Load
Moment on Baseplate Due to Transverse Load [Rmom]:
= B * Ft + Sum of X Moments
= 255.00 * 34.80 + 0.00
= 8.88 N-m
102
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Horizontal Vessel Analysis (Test) : Step: 14 12:36p Jan 11,2015 Eccentricity (e):
= Rmom / QO
= 8.88/1505.46
= 5.90 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 , 0.0088 , 0.0000 ]
= 0.0088 mm²
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
103
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015
INPUT VALUES, Nozzle Description: N1 From : 30
Pressure for Reinforcement Calculations P 18.398 bar
Temperature for Internal Pressure Temp 50 °C
Design External Pressure Pext 1.03 bar
Temperature for External Pressure Tempex 50 °C
Shell Material SA-312 TP316
Shell Allowable Stress at Temperature S 137.90 MPa
Shell Allowable Stress At Ambient Sa 137.90 MPa
Inside Diameter of Cylindrical Shell D 97.18 mm
Design Length of Section L 1097.9767 mm
Shell Finished (Minimum) Thickness t 7.4898 mm
Shell Internal Corrosion Allowance c 0.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Distance from Bottom/Left Tangent 198.6500 mm
User Entered Minimum Design Metal Temperature 0.00 °C
Type of Element Connected to the Shell : Nozzle
Material SA-182 F316
Material UNS Number S31600
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 137.90 MPa
Allowable Stress At Ambient Sna 137.90 MPa
Diameter Basis (for tr calc only) ID
104
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015 Layout Angle 0.00 deg
Diameter 2.0000 in.
Size and Thickness Basis Actual
Actual Thickness tn 13.4620 mm
Flange Material SA-182 F316
Flange Type Long Weld Neck
Corrosion Allowance can 0.0000 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 9.0000 mm
Groove weld depth between Nozzle and Vessel Wgnv 7.4898 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
ASME Code Weld Type per UW-16 None
Class of attached Flange 150
Grade of attached Flange GR 2.2
The Pressure Design option was Overall MAWP.
Nozzle Sketch (may not represent actual weld type/configuration)
| |
| |
| |
| |
____________/| |
105
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015 | \ | |
| \ | |
|____________\|__|
Insert Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: N1
ASME Code, Section VIII, Division 1, 2010, 2011a, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 2.000 in.
Actual Thickness Used in Calculation 0.530 in.
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)
= (18.40*48.5902)/(137*1.00-0.6*18.40)
= 0.6536 mm
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= R( exp([P/(SE)] - 1 ) per Appendix 1-2 (a)(1)
= 25.400(exp([18.40/(137.90*1.00]-1)
= 0.3412 mm
Required Nozzle thickness under External Pressure per UG-28 : 0.3761 mm
UG-40, Limits of Reinforcement : [Internal Pressure]
Parallel to Vessel Wall (Diameter Limit) Dl 101.6000 mm
Parallel to Vessel Wall, opening length d 50.8000 mm
Normal to Vessel Wall (Thickness Limit), no pad Tlnp 18.7246 mm
106
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: N1.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.3761 mm
Wall Thickness per UG16(b), tr16b = 1.5000 mm
Wall Thickness, shell/head, internal pressure trb1 = 0.6536 mm
Wall Thickness tb1 = max(trb1, tr16b) = 1.5000 mm
Wall Thickness tb2 = max(trb2, tr16b) = 1.5000 mm
Wall Thickness per table UG-45 tb3 = 4.8000 mm
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 4.800 , max( 1.500 , 1.500 ) ]
= 1.5000 mm
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.3761 , 1.5000 )
= 1.5000 mm
Available Nozzle Neck Thickness = 13.4620 mm --> OK
107
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015 Stresses on Nozzle due to External and Pressure Loads per the ASME
B31.3 Piping Code (see 319.4.4 and 302.3.5):
Sustained : 15.2, Allowable : 137.9 MPa Passed
Expansion : 0.0, Allowable : 329.5 MPa Passed
Occasional : 1.4, Allowable : 183.4 MPa Passed
Shear : 8.3, Allowable : 96.5 MPa Passed
Note : The number of cycles on this nozzle was assumed to be 7000 or less for
the determination of the expansion stress allowable.
SA-312 TP316, Min Metal Temp without impact per UHA-51: -196 °C
SA-182 F316, Min Metal Temp without impact per UHA-51: -196 °C
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]:
= thickness - corrosion allowance
= 13.462 - 0.000
= 13.462 mm
Effective Pressure Radius [Reff]:
= Di/2 + corrosion allowance
= 97.180/2 + 0.000
= 48.590 mm
Effective Length of Vessel Wall [LR]:
= 8 * t
= 8 * 7.490
= 59.919 mm
108
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015 Thickness Limit Candidate [LH1]:
= t + 0.78 * sqrt( Rn * tn )
= 7.490 + 0.78 * sqrt( 25.400 * 13.462 )
= 21.913 mm
Thickness Limit Candidate [LH2]:
= Lpr1 + T
= 200.000 + 7.490
= 207.490 mm
Thickness Limit Candidate [LH3]:
= 8( t + te )
= 8( 7.490 + 0.000 )
= 59.919 mm
Effective Nozzle Wall Length Outside the Vessel [LH]:
= min[ LH1, LH2, LH3 ]
= min[ 21.913 , 207.490 , 59.919 )
= 21.913 mm
Effective Vessel Thickness [teff]:
= t
= 7.490 mm
Determine Parameter [Lamda]:
= min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (50.80 + 13.462 )/( sqrt((97.18 + 7.490 ) * 7.490 )) )
= 2.295
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
109
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015 Area Contributed by the Vessel Wall [A1]:
= t * LR * max( Lamda/4, 1 )
= 7.490 * 59.919 * max( 2.295/4, 1 )
= 448.780 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]:
= tn * LH
= 13.462 * 21.913
= 294.995 mm²
Area Contributed by the Outside Fillet Weld [A41]:
= 0.5 * Leg412
= 0.5 * 9.0002
= 40.500 mm²
The total area contributed by A1 through A43 [AT]:
= A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 448.780+1.000(294.995+0.000)+40.500+0.000+0.000
= 784.275 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 )
= 18.398 * 25.400 ( 21.913 - 7.490 )
= 674.1 N
Determine Force acting on the Shell [fS]:
110
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015 = P * Reff * ( LR + tn )
= 18.398 * 48.590 * ( 59.919 + 13.462 )
= 6560.5 N
Discontinuity Force from Internal Pressure [fY]:
= P * Reff * Rnc
= 18.398 * 48.590 * 25.400
= 2270.8 N
Area Resisting Internal Pressure [Ap]:
= Rn( LH - t ) + Reff( LR + tn + Rnc )
= 25.400 ( 21.913 - 7.490 ) + 48.590 ( 59.919 + 13.462 + 25.400 )
= 5166.1 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]:
= Sallow /( 2 * Ap/AT - Rxs/teff )
= 206.850/( 2 * 5166.123/784.275 - 48.590/7.490 )
= 309.3 bar
Maximum Allowable Working Pressure Candidate [Pmax2]:
= S[t/Reff]
= 137.900 [7.490/48.590 ]
= 212.5 bar
Maximum Allowable Working Pressure [Pmax]:
= min( Pmax1, Pmax2 )
= min( 309.297 , 212.532 )
= 212.532 bar
Average Primary Membrane Stress [SigmaAvg]:
= ( fN + fS + fY ) / AT
111
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015 = ( 674.071 + 6560.483 + 2270.849 )/784.275
= 12.121 MPa
General Primary Membrane Stress [SigmaCirc]:
= P * Reff / teff
= 18.398 * 48.590/7.490
= 11.9 MPa
Maximum Local Primary Membrane Stress [PL]:
= max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 12.121 - 11.938 , 11.938 )
= 12.3 MPa
Summary of Nozzle Pressure/Stress Results:
Allowed Local Primary Membrane Stress Sallow 206.85 MPa
Local Primary Membrane Stress PL 12.30 MPa
Maximum Allowable Working Pressure Pmax 212.53 bar
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]:
= ( Rnc + tn ) / Rnc
= ( 25.400 + 13.462 )/25.400
= 1.530 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]:
= pi/2 * ( Rn + tn )
= pi/2 * ( 25.400 + 13.462 )
= 61.044 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]:
112
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015 = 6.364, 0.000, 0.000, mm
Weld Load Value [fwelds]:
= min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(2270*1.53,1.5*137.9(294.995+0.000),pi/4*18.4*25.40^2*1.53^2)
= 2182.458 N
Weld Stress Value [tau]:
= fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 2182.458/(61.044 (0.49*6.364 + 0.6*7.490 + 0.49*0.000 ) )
= 4.697 < or = to 137.900 Weld Size is OK
Weld Size Calculations, Description: N1
Intermediate Calc. for nozzle/shell Welds Tmin 8.5598 mm
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 5.9919 = 0.7 * tmin. 6.3630 = 0.7 * Wo mm
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 190.696 bar
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 19.4225 mm
The Cut Length for this Nozzle is, Drop + Ho + H + T : 226.9124 mm
113
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015
Input Echo, WRC107/537 Item 1, Description: N1 :
Diameter Basis for Vessel Vbasis ID
Cylindrical or Spherical Vessel Cylsph Cylindrical
Internal Corrosion Allowance Cas 0.0000 mm
Vessel Diameter Dv 97.180 mm
Vessel Thickness Tv 7.490 mm
Design Temperature -195.57 °C
Vessel Material SA-312 TP316
Vessel Cold S.I. Allowable Smc 137.90 MPa
Vessel Hot S.I. Allowable Smh 137.90 MPa
Attachment Type Type Round
Diameter Basis for Nozzle Nbasis ID
Corrosion Allowance for Nozzle Can 0.0000 mm
Nozzle Diameter Dn 50.800 mm
Nozzle Thickness Tn 13.462 mm
Nozzle Material SA-182 F316
Nozzle Cold S.I. Allowable SNmc 137.90 MPa
Nozzle Hot S.I. Allowable SNmh 137.90 MPa
Design Internal Pressure Dp 18.398 bar
Include Pressure Thrust No
External Forces and Moments in WRC 107/537 Convention:
Radial Load (SUS) P -1040.0 N
Longitudinal Shear (SUS) Vl 1040.0 N
Circumferential Shear (SUS) Vc 1040.0 N
114
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015
Circumferential Moment (SUS) Mc 380.0 N-m
Longitudinal Moment (SUS) Ml 380.0 N-m
Torsional Moment (SUS) Mt 380.0 N-m
Use Interactive Control No
WRC107 Version Version March 1979
Include Pressure Stress Indices per Div. 2 No
Compute Pressure Stress per WRC-368 No
WRC 107 Stress Calculation for SUStained loads:
Radial Load P -1040.0 N
Circumferential Shear VC 1040.0 N
Longitudinal Shear VL 1040.0 N
Circumferential Moment MC 380.0 N-m
Longitudinal Moment ML 380.0 N-m
Torsional Moment MT 380.0 N-m
Dimensionless Parameters used : Gamma = 6.99
Dimensionless Loads for Cylindrical Shells at Attachment Junction:
-------------------------------------------------------------------
Curves read for 1979 Beta Figure Value Location
-------------------------------------------------------------------
N(PHI) / ( P/Rm ) 0.650 4C ! 0.947 (A,B)
N(PHI) / ( P/Rm ) 0.650 3C ! 0.660 (C,D)
115
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015
M(PHI) / ( P ) 0.650 2C1 ! 0.033 (A,B)
M(PHI) / ( P ) 0.650 1C ! 0.055 (C,D)
N(PHI) / ( MC/(Rm**2 * Beta) ) 0.650 3A ! 0.319 (A,B,C,D)
M(PHI) / ( MC/(Rm * Beta) ) 0.650 1A ! 0.082 (A,B,C,D)
N(PHI) / ( ML/(Rm**2 * Beta) ) 0.650 3B ! 0.739 (A,B,C,D)
M(PHI) / ( ML/(Rm * Beta) ) 0.650 1B ! 0.023 (A,B,C,D)
N(x) / ( P/Rm ) 0.650 3C ! 0.660 (A,B)
N(x) / ( P/Rm ) 0.650 4C ! 0.947 (C,D)
M(x) / ( P ) 0.650 1C1 ! 0.053 (A,B)
M(x) / ( P ) 0.650 2C ! 0.034 (C,D)
N(x) / ( MC/(Rm**2 * Beta) ) 0.650 4A ! 0.696 (A,B,C,D)
M(x) / ( MC/(Rm * Beta) ) 0.650 2A ! 0.043 (A,B,C,D)
N(x) / ( ML/(Rm**2 * Beta) ) 0.650 4B ! 0.317 (A,B,C,D)
M(x) / ( ML/(Rm * Beta) ) 0.650 2B ! 0.042 (A,B,C,D)
Note - The ! mark next to the figure name denotes curve value exceeded.
Stress Concentration Factors Kn = 1.00, Kb = 1.00
Stresses in the Vessel at the Attachment Junction
------------------------------------------------------------------------
| Stress Values at
Type of | (MPa )
---------------|--------------------------------------------------------
Stress Load| Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Memb. P | 2 2 2 2 1 1 1 1
Circ. Bend. P | 3 -3 3 -3 6 -6 6 -6
116
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015
Circ. Memb. MC | 0 0 0 0 -9 -9 9 9
Circ. Bend. MC | 0 0 0 0 -97 97 97 -97
Circ. Memb. ML | -21 -21 21 21 0 0 0 0
Circ. Bend. ML | -27 27 27 -27 0 0 0 0
|
Tot. Circ. Str.| -42.3 5.2 54.7 -7.5 -99.0 84.3 114.6 -92.9
------------------------------------------------------------------------
Long. Memb. P | 1 1 1 1 2 2 2 2
Long. Bend. P | 5 -5 5 -5 3 -3 3 -3
Long. Memb. MC | 0 0 0 0 -19 -19 19 19
Long. Bend. MC | 0 0 0 0 -51 51 51 -51
Long. Memb. ML | -9 -9 9 9 0 0 0 0
Long. Bend. ML | -50 50 50 -50 0 0 0 0
|
Tot. Long. Str.| -51.4 36.9 66.7 -45.2 -65.3 30.7 78.0 -33.3
------------------------------------------------------------------------
Shear VC | 1 1 -1 -1 0 0 0 0
Shear VL | 0 0 0 0 -1 -1 1 1
Shear MT | 5 5 5 5 5 5 5 5
|
Tot. Shear| 6.5 6.5 4.2 4.2 4.2 4.2 6.5 6.5
------------------------------------------------------------------------
Str. Int. | 54.80 38.15 68.05 45.62 99.51 84.62 115.75 93.62
------------------------------------------------------------------------
WRC 107/537 Stress Summations:
Vessel Stress Summation at Attachment Junction
------------------------------------------------------------------------
Type of | Stress Values at
Stress Int. | (MPa )
117
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N1 Nozl: 4 12:36p Jan 11,2015
---------------|--------------------------------------------------------
Location | Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Pm (SUS) | 11 12 11 12 11 12 11 12
Circ. Pl (SUS) | -18 -18 23 23 -7 -7 10 10
Circ. Q (SUS) | -23 23 31 -31 -91 91 103 -103
------------------------------------------------------------------------
Long. Pm (SUS) | 5 5 5 5 5 5 5 5
Long. Pl (SUS) | -7 -7 10 10 -17 -17 22 22
Long. Q (SUS) | -44 44 55 -55 -47 47 55 -55
------------------------------------------------------------------------
Shear Pm (SUS) | 0 0 0 0 0 0 0 0
Shear Pl (SUS) | 1 1 -1 -1 -1 -1 1 1
Shear Q (SUS) | 5 5 5 5 5 5 5 5
------------------------------------------------------------------------
Pm (SUS) | 11.1 12.9 11.1 12.9 11.1 12.9 11.1 12.9
------------------------------------------------------------------------
Pm+Pl (SUS) | 7.7 5.9 34.7 36.6 15.7 17.5 28.1 28.2
------------------------------------------------------------------------
Pm+Pl+Q (Total)| 48.3 44.0 74.3 45.8 88.5 97.5 126.7 80.8
------------------------------------------------------------------------
------------------------------------------------------------------------
Type of | Max. S.I. S.I. Allowable | Result
Stress Int. | MPa |
---------------|--------------------------------------------------------
Pm (SUS) | 12.92 137.90 | Passed
Pm+Pl (SUS) | 36.57 206.85 | Passed
Pm+Pl+Q (TOTAL)| 126.69 413.70 | Passed
------------------------------------------------------------------------
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
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PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015
INPUT VALUES, Nozzle Description: N2 From : 30
Pressure for Reinforcement Calculations P 18.398 bar
Temperature for Internal Pressure Temp 50 °C
Design External Pressure Pext 1.03 bar
Temperature for External Pressure Tempex 50 °C
Shell Material SA-312 TP316
Shell Allowable Stress at Temperature S 137.90 MPa
Shell Allowable Stress At Ambient Sa 137.90 MPa
Inside Diameter of Cylindrical Shell D 97.18 mm
Design Length of Section L 1097.9767 mm
Shell Finished (Minimum) Thickness t 7.4898 mm
Shell Internal Corrosion Allowance c 0.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Distance from Bottom/Left Tangent 1006.6500 mm
User Entered Minimum Design Metal Temperature 0.00 °C
Type of Element Connected to the Shell : Nozzle
Material SA-182 F316
Material UNS Number S31600
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 137.90 MPa
Allowable Stress At Ambient Sna 137.90 MPa
Diameter Basis (for tr calc only) ID
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PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015
Layout Angle 180.00 deg
Diameter 2.0000 in.
Size and Thickness Basis Actual
Actual Thickness tn 13.4620 mm
Flange Material SA-182 F316
Flange Type Long Weld Neck
Corrosion Allowance can 0.0000 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 9.0000 mm
Groove weld depth between Nozzle and Vessel Wgnv 7.4898 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
ASME Code Weld Type per UW-16 None
Class of attached Flange 150
Grade of attached Flange GR 2.2
The Pressure Design option was Overall MAWP.
Nozzle Sketch (may not represent actual weld type/configuration)
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Insert Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: N2
ASME Code, Section VIII, Division 1, 2010, 2011a, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 2.000 in.
Actual Thickness Used in Calculation 0.530 in.
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)
= (18.40*48.5902)/(137*1.00-0.6*18.40)
= 0.6536 mm
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= R( exp([P/(SE)] - 1 ) per Appendix 1-2 (a)(1)
= 25.400(exp([18.40/(137.90*1.00]-1)
= 0.3412 mm
Required Nozzle thickness under External Pressure per UG-28 : 0.3761 mm
UG-40, Limits of Reinforcement : [Internal Pressure]
Parallel to Vessel Wall (Diameter Limit) Dl 101.6000 mm
Parallel to Vessel Wall, opening length d 50.8000 mm
Normal to Vessel Wall (Thickness Limit), no pad Tlnp 18.7246 mm
121
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: N2.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.3761 mm
Wall Thickness per UG16(b), tr16b = 1.5000 mm
Wall Thickness, shell/head, internal pressure trb1 = 0.6536 mm
Wall Thickness tb1 = max(trb1, tr16b) = 1.5000 mm
Wall Thickness tb2 = max(trb2, tr16b) = 1.5000 mm
Wall Thickness per table UG-45 tb3 = 4.8000 mm
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 4.800 , max( 1.500 , 1.500 ) ]
= 1.5000 mm
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.3761 , 1.5000 )
= 1.5000 mm
Available Nozzle Neck Thickness = 13.4620 mm --> OK
122
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015
Stresses on Nozzle due to External and Pressure Loads per the ASME
B31.3 Piping Code (see 319.4.4 and 302.3.5):
Sustained : 15.2, Allowable : 137.9 MPa Passed
Expansion : 0.0, Allowable : 329.5 MPa Passed
Occasional : 1.4, Allowable : 183.4 MPa Passed
Shear : 8.3, Allowable : 96.5 MPa Passed
Note : The number of cycles on this nozzle was assumed to be 7000 or less for
the determination of the expansion stress allowable.
SA-312 TP316, Min Metal Temp without impact per UHA-51: -196 °C
SA-182 F316, Min Metal Temp without impact per UHA-51: -196 °C
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]:
= thickness - corrosion allowance
= 13.462 - 0.000
= 13.462 mm
Effective Pressure Radius [Reff]:
= Di/2 + corrosion allowance
= 97.180/2 + 0.000
= 48.590 mm
Effective Length of Vessel Wall [LR]:
= 8 * t
= 8 * 7.490
= 59.919 mm
123
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015 Thickness Limit Candidate [LH1]:
= t + 0.78 * sqrt( Rn * tn )
= 7.490 + 0.78 * sqrt( 25.400 * 13.462 )
= 21.913 mm
Thickness Limit Candidate [LH2]:
= Lpr1 + T
= 200.000 + 7.490
= 207.490 mm
Thickness Limit Candidate [LH3]:
= 8( t + te )
= 8( 7.490 + 0.000 )
= 59.919 mm
Effective Nozzle Wall Length Outside the Vessel [LH]:
= min[ LH1, LH2, LH3 ]
= min[ 21.913 , 207.490 , 59.919 )
= 21.913 mm
Effective Vessel Thickness [teff]:
= t
= 7.490 mm
Determine Parameter [Lamda]:
= min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (50.80 + 13.462 )/( sqrt((97.18 + 7.490 ) * 7.490 )) )
= 2.295
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
124
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015
Area Contributed by the Vessel Wall [A1]:
= t * LR * max( Lamda/4, 1 )
= 7.490 * 59.919 * max( 2.295/4, 1 )
= 448.780 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]:
= tn * LH
= 13.462 * 21.913
= 294.995 mm²
Area Contributed by the Outside Fillet Weld [A41]:
= 0.5 * Leg412
= 0.5 * 9.0002
= 40.500 mm²
The total area contributed by A1 through A43 [AT]:
= A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 448.780+1.000(294.995+0.000)+40.500+0.000+0.000
= 784.275 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 )
= 18.398 * 25.400 ( 21.913 - 7.490 )
= 674.1 N
Determine Force acting on the Shell [fS]:
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PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015 = P * Reff * ( LR + tn )
= 18.398 * 48.590 * ( 59.919 + 13.462 )
= 6560.5 N
Discontinuity Force from Internal Pressure [fY]:
= P * Reff * Rnc
= 18.398 * 48.590 * 25.400
= 2270.8 N
Area Resisting Internal Pressure [Ap]:
= Rn( LH - t ) + Reff( LR + tn + Rnc )
= 25.400 ( 21.913 - 7.490 ) + 48.590 ( 59.919 + 13.462 + 25.400 )
= 5166.1 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]:
= Sallow /( 2 * Ap/AT - Rxs/teff )
= 206.850/( 2 * 5166.123/784.275 - 48.590/7.490 )
= 309.3 bar
Maximum Allowable Working Pressure Candidate [Pmax2]:
= S[t/Reff]
= 137.900 [7.490/48.590 ]
= 212.5 bar
Maximum Allowable Working Pressure [Pmax]:
= min( Pmax1, Pmax2 )
= min( 309.297 , 212.532 )
= 212.532 bar
Average Primary Membrane Stress [SigmaAvg]:
= ( fN + fS + fY ) / AT
126
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015
= ( 674.071 + 6560.483 + 2270.849 )/784.275
= 12.121 MPa
General Primary Membrane Stress [SigmaCirc]:
= P * Reff / teff
= 18.398 * 48.590/7.490
= 11.9 MPa
Maximum Local Primary Membrane Stress [PL]:
= max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 12.121 - 11.938 , 11.938 )
= 12.3 MPa
Summary of Nozzle Pressure/Stress Results:
Allowed Local Primary Membrane Stress Sallow 206.85 MPa
Local Primary Membrane Stress PL 12.30 MPa
Maximum Allowable Working Pressure Pmax 212.53 bar
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]:
= ( Rnc + tn ) / Rnc
= ( 25.400 + 13.462 )/25.400
= 1.530 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]:
= pi/2 * ( Rn + tn )
= pi/2 * ( 25.400 + 13.462 )
= 61.044 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]:
127
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015 = 6.364, 0.000, 0.000, mm
Weld Load Value [fwelds]:
= min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(2270*1.53,1.5*137.9(294.995+0.000),pi/4*18.4*25.40^2*1.53^2)
= 2182.458 N
Weld Stress Value [tau]:
= fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 2182.458/(61.044 (0.49*6.364 + 0.6*7.490 + 0.49*0.000 ) )
= 4.697 < or = to 137.900 Weld Size is OK
Weld Size Calculations, Description: N2
Intermediate Calc. for nozzle/shell Welds Tmin 8.5598 mm
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 5.9919 = 0.7 * tmin. 6.3630 = 0.7 * Wo mm
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 190.696 bar
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 19.4225 mm
The Cut Length for this Nozzle is, Drop + Ho + H + T : 226.9124 mm
128
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015
Input Echo, WRC107/537 Item 1, Description: N2 :
Diameter Basis for Vessel Vbasis ID
Cylindrical or Spherical Vessel Cylsph Cylindrical
Internal Corrosion Allowance Cas 0.0000 mm
Vessel Diameter Dv 97.180 mm
Vessel Thickness Tv 7.490 mm
Design Temperature -195.57 °C
Vessel Material SA-312 TP316
Vessel Cold S.I. Allowable Smc 137.90 MPa
Vessel Hot S.I. Allowable Smh 137.90 MPa
Attachment Type Type Round
Diameter Basis for Nozzle Nbasis ID
Corrosion Allowance for Nozzle Can 0.0000 mm
Nozzle Diameter Dn 50.800 mm
Nozzle Thickness Tn 13.462 mm
Nozzle Material SA-182 F316
Nozzle Cold S.I. Allowable SNmc 137.90 MPa
Nozzle Hot S.I. Allowable SNmh 137.90 MPa
Design Internal Pressure Dp 18.398 bar
Include Pressure Thrust No
External Forces and Moments in WRC 107/537 Convention:
Radial Load (SUS) P -1040.0 N
Longitudinal Shear (SUS) Vl 1040.0 N
Circumferential Shear (SUS) Vc 1040.0 N
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Circumferential Moment (SUS) Mc 380.0 N-m
Longitudinal Moment (SUS) Ml 380.0 N-m
Torsional Moment (SUS) Mt 380.0 N-m
Use Interactive Control No
WRC107 Version Version March 1979
Include Pressure Stress Indices per Div. 2 No
Compute Pressure Stress per WRC-368 No
WRC 107 Stress Calculation for SUStained loads:
Radial Load P -1040.0 N
Circumferential Shear VC 1040.0 N
Longitudinal Shear VL 1040.0 N
Circumferential Moment MC 380.0 N-m
Longitudinal Moment ML 380.0 N-m
Torsional Moment MT 380.0 N-m
Dimensionless Parameters used : Gamma = 6.99
Dimensionless Loads for Cylindrical Shells at Attachment Junction:
-------------------------------------------------------------------
Curves read for 1979 Beta Figure Value Location
-------------------------------------------------------------------
N(PHI) / ( P/Rm ) 0.650 4C ! 0.947 (A,B)
N(PHI) / ( P/Rm ) 0.650 3C ! 0.660 (C,D)
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PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015
M(PHI) / ( P ) 0.650 2C1 ! 0.033 (A,B)
M(PHI) / ( P ) 0.650 1C ! 0.055 (C,D)
N(PHI) / ( MC/(Rm**2 * Beta) ) 0.650 3A ! 0.319 (A,B,C,D)
M(PHI) / ( MC/(Rm * Beta) ) 0.650 1A ! 0.082 (A,B,C,D)
N(PHI) / ( ML/(Rm**2 * Beta) ) 0.650 3B ! 0.739 (A,B,C,D)
M(PHI) / ( ML/(Rm * Beta) ) 0.650 1B ! 0.023 (A,B,C,D)
N(x) / ( P/Rm ) 0.650 3C ! 0.660 (A,B)
N(x) / ( P/Rm ) 0.650 4C ! 0.947 (C,D)
M(x) / ( P ) 0.650 1C1 ! 0.053 (A,B)
M(x) / ( P ) 0.650 2C ! 0.034 (C,D)
N(x) / ( MC/(Rm**2 * Beta) ) 0.650 4A ! 0.696 (A,B,C,D)
M(x) / ( MC/(Rm * Beta) ) 0.650 2A ! 0.043 (A,B,C,D)
N(x) / ( ML/(Rm**2 * Beta) ) 0.650 4B ! 0.317 (A,B,C,D)
M(x) / ( ML/(Rm * Beta) ) 0.650 2B ! 0.042 (A,B,C,D)
Note - The ! mark next to the figure name denotes curve value exceeded.
Stress Concentration Factors Kn = 1.00, Kb = 1.00
Stresses in the Vessel at the Attachment Junction
------------------------------------------------------------------------
| Stress Values at
Type of | (MPa )
---------------|--------------------------------------------------------
Stress Load| Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Memb. P | 2 2 2 2 1 1 1 1
Circ. Bend. P | 3 -3 3 -3 6 -6 6 -6
131
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015 Circ. Memb. MC | 0 0 0 0 -9 -9 9 9
Circ. Bend. MC | 0 0 0 0 -97 97 97 -97
Circ. Memb. ML | -21 -21 21 21 0 0 0 0
Circ. Bend. ML | -27 27 27 -27 0 0 0 0
|
Tot. Circ. Str.| -42.3 5.2 54.7 -7.5 -99.0 84.3 114.6 -92.9
------------------------------------------------------------------------
Long. Memb. P | 1 1 1 1 2 2 2 2
Long. Bend. P | 5 -5 5 -5 3 -3 3 -3
Long. Memb. MC | 0 0 0 0 -19 -19 19 19
Long. Bend. MC | 0 0 0 0 -51 51 51 -51
Long. Memb. ML | -9 -9 9 9 0 0 0 0
Long. Bend. ML | -50 50 50 -50 0 0 0 0
|
Tot. Long. Str.| -51.4 36.9 66.7 -45.2 -65.3 30.7 78.0 -33.3
------------------------------------------------------------------------
Shear VC | 1 1 -1 -1 0 0 0 0
Shear VL | 0 0 0 0 -1 -1 1 1
Shear MT | 5 5 5 5 5 5 5 5
|
Tot. Shear| 6.5 6.5 4.2 4.2 4.2 4.2 6.5 6.5
------------------------------------------------------------------------
Str. Int. | 54.80 38.15 68.05 45.62 99.51 84.62 115.75 93.62
------------------------------------------------------------------------
WRC 107/537 Stress Summations:
Vessel Stress Summation at Attachment Junction
------------------------------------------------------------------------
Type of | Stress Values at
Stress Int. | (MPa )
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PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N2 Nozl: 5 12:36p Jan 11,2015
---------------|--------------------------------------------------------
Location | Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Pm (SUS) | 11 12 11 12 11 12 11 12
Circ. Pl (SUS) | -18 -18 23 23 -7 -7 10 10
Circ. Q (SUS) | -23 23 31 -31 -91 91 103 -103
------------------------------------------------------------------------
Long. Pm (SUS) | 5 5 5 5 5 5 5 5
Long. Pl (SUS) | -7 -7 10 10 -17 -17 22 22
Long. Q (SUS) | -44 44 55 -55 -47 47 55 -55
------------------------------------------------------------------------
Shear Pm (SUS) | 0 0 0 0 0 0 0 0
Shear Pl (SUS) | 1 1 -1 -1 -1 -1 1 1
Shear Q (SUS) | 5 5 5 5 5 5 5 5
------------------------------------------------------------------------
Pm (SUS) | 11.1 12.9 11.1 12.9 11.1 12.9 11.1 12.9
------------------------------------------------------------------------
Pm+Pl (SUS) | 7.7 5.9 34.7 36.6 15.7 17.5 28.1 28.2
------------------------------------------------------------------------
Pm+Pl+Q (Total)| 48.3 44.0 74.3 45.8 88.5 97.5 126.7 80.8
------------------------------------------------------------------------
------------------------------------------------------------------------
Type of | Max. S.I. S.I. Allowable | Result
Stress Int. | MPa |
---------------|--------------------------------------------------------
Pm (SUS) | 12.92 137.90 | Passed
Pm+Pl (SUS) | 36.57 206.85 | Passed
Pm+Pl+Q (TOTAL)| 126.69 413.70 | Passed
------------------------------------------------------------------------
PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013
133
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N3 Nozl: 6 12:36p Jan 11,2015
INPUT VALUES, Nozzle Description: N3 From : 30
Pressure for Reinforcement Calculations P 18.398 bar
Temperature for Internal Pressure Temp 50 °C
Design External Pressure Pext 1.03 bar
Temperature for External Pressure Tempex 50 °C
Shell Material SA-312 TP316
Shell Allowable Stress at Temperature S 137.90 MPa
Shell Allowable Stress At Ambient Sa 137.90 MPa
Inside Diameter of Cylindrical Shell D 97.18 mm
Design Length of Section L 1097.9767 mm
Shell Finished (Minimum) Thickness t 7.4898 mm
Shell Internal Corrosion Allowance c 0.0000 mm
Shell External Corrosion Allowance co 0.0000 mm
Distance from Bottom/Left Tangent 502.6500 mm
User Entered Minimum Design Metal Temperature 0.00 °C
Type of Element Connected to the Shell : Nozzle
Material SA-182 F316
Material UNS Number S31600
Material Specification/Type Forgings
Allowable Stress at Temperature Sn 137.90 MPa
Allowable Stress At Ambient Sna 137.90 MPa
Diameter Basis (for tr calc only) ID
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Layout Angle 180.00 deg
Diameter 2.0000 in.
Size and Thickness Basis Actual
Actual Thickness tn 13.4620 mm
Flange Material SA-182 F316
Flange Type Long Weld Neck
Corrosion Allowance can 0.0000 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 9.0000 mm
Groove weld depth between Nozzle and Vessel Wgnv 7.4898 mm
Inside Projection h 0.0000 mm
Weld leg size, Inside Element to Shell Wi 0.0000 mm
ASME Code Weld Type per UW-16 None
Class of attached Flange 150
Grade of attached Flange GR 2.2
The Pressure Design option was Overall MAWP.
Nozzle Sketch (may not represent actual weld type/configuration)
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Insert Nozzle No Pad, no Inside projection
Reinforcement CALCULATION, Description: N3
ASME Code, Section VIII, Division 1, 2010, 2011a, UG-37 to UG-45
Actual Inside Diameter Used in Calculation 2.000 in.
Actual Thickness Used in Calculation 0.530 in.
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)
= (18.40*48.5902)/(137*1.00-0.6*18.40)
= 0.6536 mm
Reqd thk per App. 1 of Nozzle Wall, Trn [Int. Press]
= R( exp([P/(SE)] - 1 ) per Appendix 1-2 (a)(1)
= 25.400(exp([18.40/(137.90*1.00]-1)
= 0.3412 mm
Required Nozzle thickness under External Pressure per UG-28 : 0.3761 mm
UG-40, Limits of Reinforcement : [Internal Pressure]
Parallel to Vessel Wall (Diameter Limit) Dl 101.6000 mm
Parallel to Vessel Wall, opening length d 50.8000 mm
Normal to Vessel Wall (Thickness Limit), no pad Tlnp 18.7246 mm
136
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N3 Nozl: 6 12:36p Jan 11,2015
Note:
Taking a UG-36(c)(3)(a) exemption for nozzle: N3.
This calculation is valid for nozzles that meet all the requirements of
paragraph UG-36. Please check the Code carefully, especially for nozzles
that are not isolated or do not meet Code spacing requirements. To force
the computation of areas for small nozzles go to Tools->Configuration
and check the box to force the UG-37 small nozzle area calculation or
force the Appendix 1-10 computation in Nozzle Design Options.
UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]
Wall Thickness for Internal/External pressures ta = 0.3761 mm
Wall Thickness per UG16(b), tr16b = 1.5000 mm
Wall Thickness, shell/head, internal pressure trb1 = 0.6536 mm
Wall Thickness tb1 = max(trb1, tr16b) = 1.5000 mm
Wall Thickness tb2 = max(trb2, tr16b) = 1.5000 mm
Wall Thickness per table UG-45 tb3 = 4.8000 mm
Determine Nozzle Thickness candidate [tb]:
= min[ tb3, max( tb1,tb2) ]
= min[ 4.800 , max( 1.500 , 1.500 ) ]
= 1.5000 mm
Minimum Wall Thickness of Nozzle Necks [tUG-45]:
= max( ta, tb )
= max( 0.3761 , 1.5000 )
= 1.5000 mm
Available Nozzle Neck Thickness = 13.4620 mm --> OK
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PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N3 Nozl: 6 12:36p Jan 11,2015
Stresses on Nozzle due to External and Pressure Loads per the ASME
B31.3 Piping Code (see 319.4.4 and 302.3.5):
Sustained : 15.2, Allowable : 137.9 MPa Passed
Expansion : 0.0, Allowable : 329.5 MPa Passed
Occasional : 1.4, Allowable : 183.4 MPa Passed
Shear : 8.3, Allowable : 96.5 MPa Passed
Note : The number of cycles on this nozzle was assumed to be 7000 or less for
the determination of the expansion stress allowable.
SA-312 TP316, Min Metal Temp without impact per UHA-51: -196 °C
SA-182 F316, Min Metal Temp without impact per UHA-51: -196 °C
Nozzle Calculations per App. 1-10: Internal Pressure Case:
Thickness of Nozzle [tn]:
= thickness - corrosion allowance
= 13.462 - 0.000
= 13.462 mm
Effective Pressure Radius [Reff]:
= Di/2 + corrosion allowance
= 97.180/2 + 0.000
= 48.590 mm
Effective Length of Vessel Wall [LR]:
= 8 * t
= 8 * 7.490
= 59.919 mm
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Thickness Limit Candidate [LH1]:
= t + 0.78 * sqrt( Rn * tn )
= 7.490 + 0.78 * sqrt( 25.400 * 13.462 )
= 21.913 mm
Thickness Limit Candidate [LH2]:
= Lpr1 + T
= 200.000 + 7.490
= 207.490 mm
Thickness Limit Candidate [LH3]:
= 8( t + te )
= 8( 7.490 + 0.000 )
= 59.919 mm
Effective Nozzle Wall Length Outside the Vessel [LH]:
= min[ LH1, LH2, LH3 ]
= min[ 21.913 , 207.490 , 59.919 )
= 21.913 mm
Effective Vessel Thickness [teff]:
= t
= 7.490 mm
Determine Parameter [Lamda]:
= min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )
= min( 10, (50.80 + 13.462 )/( sqrt((97.18 + 7.490 ) * 7.490 )) )
= 2.295
Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :
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Area Contributed by the Vessel Wall [A1]:
= t * LR * max( Lamda/4, 1 )
= 7.490 * 59.919 * max( 2.295/4, 1 )
= 448.780 mm²
Area Contributed by the Nozzle Outside the Vessel Wall [A2]:
= tn * LH
= 13.462 * 21.913
= 294.995 mm²
Area Contributed by the Outside Fillet Weld [A41]:
= 0.5 * Leg412
= 0.5 * 9.0002
= 40.500 mm²
The total area contributed by A1 through A43 [AT]:
= A1 + frn( A2 + A3 ) + A41 + A42 + A43
= 448.780+1.000(294.995+0.000)+40.500+0.000+0.000
= 784.275 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 )
= 18.398 * 25.400 ( 21.913 - 7.490 )
= 674.1 N
Determine Force acting on the Shell [fS]:
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= P * Reff * ( LR + tn )
= 18.398 * 48.590 * ( 59.919 + 13.462 )
= 6560.5 N
Discontinuity Force from Internal Pressure [fY]:
= P * Reff * Rnc
= 18.398 * 48.590 * 25.400
= 2270.8 N
Area Resisting Internal Pressure [Ap]:
= Rn( LH - t ) + Reff( LR + tn + Rnc )
= 25.400 ( 21.913 - 7.490 ) + 48.590 ( 59.919 + 13.462 + 25.400 )
= 5166.1 mm²
Maximum Allowable Working Pressure Candidate [Pmax1]:
= Sallow /( 2 * Ap/AT - Rxs/teff )
= 206.850/( 2 * 5166.123/784.275 - 48.590/7.490 )
= 309.3 bar
Maximum Allowable Working Pressure Candidate [Pmax2]:
= S[t/Reff]
= 137.900 [7.490/48.590 ]
= 212.5 bar
Maximum Allowable Working Pressure [Pmax]:
= min( Pmax1, Pmax2 )
= min( 309.297 , 212.532 )
= 212.532 bar
Average Primary Membrane Stress [SigmaAvg]:
= ( fN + fS + fY ) / AT
141
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Nozzle Calcs. : N3 Nozl: 6 12:36p Jan 11,2015 = ( 674.071 + 6560.483 + 2270.849 )/784.275
= 12.121 MPa
General Primary Membrane Stress [SigmaCirc]:
= P * Reff / teff
= 18.398 * 48.590/7.490
= 11.9 MPa
Maximum Local Primary Membrane Stress [PL]:
= max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )
= max( 2 * 12.121 - 11.938 , 11.938 )
= 12.3 MPa
Summary of Nozzle Pressure/Stress Results:
Allowed Local Primary Membrane Stress Sallow 206.85 MPa
Local Primary Membrane Stress PL 12.30 MPa
Maximum Allowable Working Pressure Pmax 212.53 bar
Strength of Nozzle Attachment Welds per 1-10 and U-2(g)
Discontinuity Force Factor [ky]:
= ( Rnc + tn ) / Rnc
= ( 25.400 + 13.462 )/25.400
= 1.530 For set-in Nozzles
Weld Length of Nozzle to Shell Weld [Ltau]:
= pi/2 * ( Rn + tn )
= pi/2 * ( 25.400 + 13.462 )
= 61.044 mm
Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]:
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= 6.364, 0.000, 0.000, mm
Weld Load Value [fwelds]:
= min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )
= min(2270*1.53,1.5*137.9(294.995+0.000),pi/4*18.4*25.40^2*1.53^2)
= 2182.458 N
Weld Stress Value [tau]:
= fwelds/(Ltau(0.49*L41T + 0.6*tw1 + 0.49*L43T ) )
= 2182.458/(61.044 (0.49*6.364 + 0.6*7.490 + 0.49*0.000 ) )
= 4.697 < or = to 137.900 Weld Size is OK
Weld Size Calculations, Description: N3
Intermediate Calc. for nozzle/shell Welds Tmin 8.5598 mm
Results Per UW-16.1:
Required Thickness Actual Thickness
Nozzle Weld 5.9919 = 0.7 * tmin. 6.3630 = 0.7 * Wo mm
NOTE : Skipping the nozzle attachment weld strength calculations.
Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)
(small nozzles) do not require a weld strength check.
Maximum Allowable Pressure for this Nozzle at this Location:
Converged Max. Allow. Pressure in Operating case 190.696 bar
Note: The MAWP of this junction was limited by the parent Shell/Head.
The Drop for this Nozzle is : 19.4225 mm
The Cut Length for this Nozzle is, Drop + Ho + H + T : 226.9124 mm
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Input Echo, WRC107/537 Item 1, Description: N3 :
Diameter Basis for Vessel Vbasis ID
Cylindrical or Spherical Vessel Cylsph Cylindrical
Internal Corrosion Allowance Cas 0.0000 mm
Vessel Diameter Dv 97.180 mm
Vessel Thickness Tv 7.490 mm
Design Temperature -195.57 °C
Vessel Material SA-312 TP316
Vessel Cold S.I. Allowable Smc 137.90 MPa
Vessel Hot S.I. Allowable Smh 137.90 MPa
Attachment Type Type Round
Diameter Basis for Nozzle Nbasis ID
Corrosion Allowance for Nozzle Can 0.0000 mm
Nozzle Diameter Dn 50.800 mm
Nozzle Thickness Tn 13.462 mm
Nozzle Material SA-182 F316
Nozzle Cold S.I. Allowable SNmc 137.90 MPa
Nozzle Hot S.I. Allowable SNmh 137.90 MPa
Design Internal Pressure Dp 18.398 bar
Include Pressure Thrust No
External Forces and Moments in WRC 107/537 Convention:
Radial Load (SUS) P -1040.0 N
Longitudinal Shear (SUS) Vl 1040.0 N
Circumferential Shear (SUS) Vc 1040.0 N
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Circumferential Moment (SUS) Mc 380.0 N-m
Longitudinal Moment (SUS) Ml 380.0 N-m
Torsional Moment (SUS) Mt 380.0 N-m
Use Interactive Control No
WRC107 Version Version March 1979
Include Pressure Stress Indices per Div. 2 No
Compute Pressure Stress per WRC-368 No
WRC 107 Stress Calculation for SUStained loads:
Radial Load P -1040.0 N
Circumferential Shear VC 1040.0 N
Longitudinal Shear VL 1040.0 N
Circumferential Moment MC 380.0 N-m
Longitudinal Moment ML 380.0 N-m
Torsional Moment MT 380.0 N-m
Dimensionless Parameters used : Gamma = 6.99
Dimensionless Loads for Cylindrical Shells at Attachment Junction:
-------------------------------------------------------------------
Curves read for 1979 Beta Figure Value Location
-------------------------------------------------------------------
N(PHI) / ( P/Rm ) 0.650 4C ! 0.947 (A,B)
N(PHI) / ( P/Rm ) 0.650 3C ! 0.660 (C,D)
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M(PHI) / ( P ) 0.650 2C1 ! 0.033 (A,B)
M(PHI) / ( P ) 0.650 1C ! 0.055 (C,D)
N(PHI) / ( MC/(Rm**2 * Beta) ) 0.650 3A ! 0.319 (A,B,C,D)
M(PHI) / ( MC/(Rm * Beta) ) 0.650 1A ! 0.082 (A,B,C,D)
N(PHI) / ( ML/(Rm**2 * Beta) ) 0.650 3B ! 0.739 (A,B,C,D)
M(PHI) / ( ML/(Rm * Beta) ) 0.650 1B ! 0.023 (A,B,C,D)
N(x) / ( P/Rm ) 0.650 3C ! 0.660 (A,B)
N(x) / ( P/Rm ) 0.650 4C ! 0.947 (C,D)
M(x) / ( P ) 0.650 1C1 ! 0.053 (A,B)
M(x) / ( P ) 0.650 2C ! 0.034 (C,D)
N(x) / ( MC/(Rm**2 * Beta) ) 0.650 4A ! 0.696 (A,B,C,D)
M(x) / ( MC/(Rm * Beta) ) 0.650 2A ! 0.043 (A,B,C,D)
N(x) / ( ML/(Rm**2 * Beta) ) 0.650 4B ! 0.317 (A,B,C,D)
M(x) / ( ML/(Rm * Beta) ) 0.650 2B ! 0.042 (A,B,C,D)
Note - The ! mark next to the figure name denotes curve value exceeded.
Stress Concentration Factors Kn = 1.00, Kb = 1.00
Stresses in the Vessel at the Attachment Junction
------------------------------------------------------------------------
| Stress Values at
Type of | (MPa )
---------------|--------------------------------------------------------
Stress Load| Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Memb. P | 2 2 2 2 1 1 1 1
Circ. Bend. P | 3 -3 3 -3 6 -6 6 -6
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Circ. Memb. MC | 0 0 0 0 -9 -9 9 9
Circ. Bend. MC | 0 0 0 0 -97 97 97 -97
Circ. Memb. ML | -21 -21 21 21 0 0 0 0
Circ. Bend. ML | -27 27 27 -27 0 0 0 0
|
Tot. Circ. Str.| -42.3 5.2 54.7 -7.5 -99.0 84.3 114.6 -92.9
------------------------------------------------------------------------
Long. Memb. P | 1 1 1 1 2 2 2 2
Long. Bend. P | 5 -5 5 -5 3 -3 3 -3
Long. Memb. MC | 0 0 0 0 -19 -19 19 19
Long. Bend. MC | 0 0 0 0 -51 51 51 -51
Long. Memb. ML | -9 -9 9 9 0 0 0 0
Long. Bend. ML | -50 50 50 -50 0 0 0 0
|
Tot. Long. Str.| -51.4 36.9 66.7 -45.2 -65.3 30.7 78.0 -33.3
------------------------------------------------------------------------
Shear VC | 1 1 -1 -1 0 0 0 0
Shear VL | 0 0 0 0 -1 -1 1 1
Shear MT | 5 5 5 5 5 5 5 5
|
Tot. Shear| 6.5 6.5 4.2 4.2 4.2 4.2 6.5 6.5
------------------------------------------------------------------------
Str. Int. | 54.80 38.15 68.05 45.62 99.51 84.62 115.75 93.62
------------------------------------------------------------------------
WRC 107/537 Stress Summations:
Vessel Stress Summation at Attachment Junction
------------------------------------------------------------------------
Type of | Stress Values at
Stress Int. | (MPa )
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---------------|--------------------------------------------------------
Location | Au Al Bu Bl Cu Cl Du Dl
---------------|--------------------------------------------------------
Circ. Pm (SUS) | 11 12 11 12 11 12 11 12
Circ. Pl (SUS) | -18 -18 23 23 -7 -7 10 10
Circ. Q (SUS) | -23 23 31 -31 -91 91 103 -103
------------------------------------------------------------------------
Long. Pm (SUS) | 5 5 5 5 5 5 5 5
Long. Pl (SUS) | -7 -7 10 10 -17 -17 22 22
Long. Q (SUS) | -44 44 55 -55 -47 47 55 -55
------------------------------------------------------------------------
Shear Pm (SUS) | 0 0 0 0 0 0 0 0
Shear Pl (SUS) | 1 1 -1 -1 -1 -1 1 1
Shear Q (SUS) | 5 5 5 5 5 5 5 5
------------------------------------------------------------------------
Pm (SUS) | 11.1 12.9 11.1 12.9 11.1 12.9 11.1 12.9
------------------------------------------------------------------------
Pm+Pl (SUS) | 7.7 5.9 34.7 36.6 15.7 17.5 28.1 28.2
------------------------------------------------------------------------
Pm+Pl+Q (Total)| 48.3 44.0 74.3 45.8 88.5 97.5 126.7 80.8
------------------------------------------------------------------------
------------------------------------------------------------------------
Type of | Max. S.I. S.I. Allowable | Result
Stress Int. | MPa |
---------------|--------------------------------------------------------
Pm (SUS) | 12.92 137.90 | Passed
Pm+Pl (SUS) | 36.57 206.85 | Passed
Pm+Pl+Q (TOTAL)| 126.69 413.70 | Passed
------------------------------------------------------------------------
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Nozzle Schedule:
Nominal Flange Noz. Wall Re-Pad Cut
Description Size Sch/Type O/Dia Thk ODia Thick Length
in. Cls in. mm mm mm mm
------------------------------------------------------------------------------
N1 2.000 150 LWN 3.060 13.462 - - 226.91
N2 2.000 150 LWN 3.060 13.462 - - 226.91
N3 2.000 150 LWN 3.060 13.462 - - 226.91
General Notes for the above table:
The Cut Length is the Outside Projection + Inside Projection + Drop +
In Plane Shell Thickness. This value does not include weld gaps,
nor does it account for shrinkage.
In the case of Oblique Nozzles, the Outside Diameter must
be increased. The Re-Pad WIDTH around the nozzle is calculated as follows:
Width of Pad = (Pad Outside Dia. (per above) - Nozzle Outside Dia.)/2
For hub nozzles, the thickness and diameter shown are those of the smaller
and thinner section.
Nozzle Material and Weld Fillet Leg Size Details:
Shl Grve Noz Shl/Pad Pad OD Pad Grve Inside
Nozzle Material Weld Weld Weld Weld Weld
mm mm mm mm mm
------------------------------------------------------------------------------
N1 SA-182 F316 7.490 9.000 - - -
N2 SA-182 F316 7.490 9.000 - - -
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N3 SA-182 F316 7.490 9.000 - - -
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
----------------------------------------------------------------------------
N1 174.350 0.00 200.00 0.00 Shell
N2 982.350 180.00 200.00 0.00 Shell
N3 478.350 180.00 200.00 0.00 Shell
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Nozzle Calculation Summary:
Description MAWP Ext MAPNC UG45 [tr] Weld Areas or
bar bar Path Stresses
---------------------------------------------------------------------------
N1 190.70 ... ... OK 1.50 OK NoCalc[*]
N2 190.70 ... ... OK 1.50 OK NoCalc[*]
N3 190.70 ... ... OK 1.50 OK NoCalc[*]
---------------------------------------------------------------------------
Min. - Nozzles 190.70 N3
Min. Shell&Flgs 18.40
Computed Vessel M.A.W.P. 18.40 bar
[*] - This was a small opening and the areas were not computed or
the MAWP of this connection could not be computed because
the longitudinal bending stress was greater than the hoop stress.
Check the Spatial Relationship between the Nozzles
From Node Nozzle Description X Coordinate, Layout Angle, Dia. Limit
30 N1 198.650 0.000 197.561
30 N2 1006.650 180.000 197.561
30 N3 502.650 180.000 197.561
The nozzle spacing is computed by the following:
= Sqrt( ll² + lc² ) where
ll - Arc length along the inside vessel surface in the long. direction.
lc - Arc length along the inside vessel surface in the circ. direction
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If any interferences/violations are found, they will be noted below.
No interference violations have been detected !
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152
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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
----------------------------------------------------------------------------
Shell [16] -196
Head [16] -196
N1 [15] -196
N2 [15] -196
N3 [15] -196
----------------------------------------------------------------------------
Required Minimum Design Metal Temperature 0 °C
Warmest Computed Minimum Design Metal Temperature -196 °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
[13] - Tubesheet MDMT, shell side, if applicable
[14] - Tubesheet MDMT, tube side, if applicable
[15] - Nozzle Material
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UG-84(b)(2) was not considered.
UCS-66(g) was not considered.
UCS-66(i) was not considered.
Notes:
Impact test temps were not entered in and not considered in the analysis.
UCS-66(i) applies to impact tested materials not by specification and
UCS-66(g) applies to materials impact tested per UG-84.1 General Note (c).
The Basic MDMT includes the (30F) PWHT credit if applicable.
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154
PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Vessel Design Summary : Step: 21 12:36p Jan 11,2015
Design Code: ASME Code Section VIII Division 1, 2010, 2011a
Diameter Spec : 114.300 mm OD
Vessel Design Length, Tangent to Tangent 1164.70 mm
Specified Datum Line Distance 24.30 mm
Shell Material SA-312 TP316
Head Material SA-403 316
Nozzle Material SA-182 F316
Internal Design Temperature 50 °C
Internal Design Pressure 18.000 bar
External Design Temperature 50 °C
External Design Pressure 1.034 bar
Maximum Allowable Working Pressure 18.398 bar
External Max. Allowable Working Pressure 71.211 bar
Hydrostatic Test Pressure 24.647 bar
Required Minimum Design Metal Temperature 0 °C
Warmest Computed Minimum Design Metal Temperature -196 °C
Wind Design Code User Defined
Earthquake Design Code G-Loading
Element Pressures and MAWP: bar
Element Desc | Design Pres. | External | M.A.W.P | Corrosion
| + Stat. head | Pressure | | Allowance
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Body flange 18.000 1.034 18.398 0.0000
Shell 18.000 1.034 190.696 0.0000
Head 18.000 1.034 204.863 0.0000
Element "To" Elev Length Element Thk R e q d T h k Joint Eff
Type mm mm mm Int. Ext. Long Circ
-----------------------------------------------------------------------
Body Flg 50.7 75.0 24.3 No Calc No Calc 1.00 1.00
Cylinder 1100.7 1050.0 8.6 1.5 1.0 1.00 1.00
Ellipse 1140.4 39.7 8.6 1.5 1.5 1.00 1.00
Element thicknesses are shown as Nominal if specified, otherwise are Minimum
Saddle Parameters:
Saddle Width 70.000 mm
Saddle Bearing Angle 120.000 deg.
Centerline Dimension 255.000 mm
Wear Pad Width 102.000 mm
Wear Pad Thickness 8.000 mm
Wear Pad Bearing Angle 132.000 deg.
Distance from Saddle to Tangent 164.000 mm
Baseplate Length 132.000 mm
Baseplate Thickness 8.000 mm
Baseplate Width 90.000 mm
Number of Ribs (including outside ribs) 2
Rib Thickness 8.000 mm
Web Thickness 8.000 mm
Height of Center Web 186.000 mm
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PV Elite 2013 Licensee: MSET ENGINEERING SDN BHD FileName : E-6012 ---------------------------------------- Vessel Design Summary : Step: 21 12:36p Jan 11,2015 Summary of Maximum Saddle Loads, Operating Case :
Maximum Vertical Saddle Load 14253.41 N
Maximum Transverse Saddle Shear Load 964.69 N
Maximum Longitudinal Saddle Shear Load 1929.38 N
Summary of Maximum Saddle Loads, Hydrotest Case :
Maximum Vertical Saddle Load 1793.29 N
Maximum Transverse Saddle Shear Load 34.80 N
Maximum Longitudinal Saddle Shear Load 3.05 N
Weights:
Fabricated - Bare W/O Removable Internals 68.6 kgm
Shop Test - Fabricated + Water ( Full ) 77.8 kgm
Shipping - Fab. + Rem. Intls.+ Shipping App. 293.5 kgm
Erected - Fab. + Rem. Intls.+ Insul. (etc) 293.5 kgm
Empty - Fab. + Intls. + Details + Wghts. 293.5 kgm
Operating - Empty + Operating Liquid (No CA) 393.5 kgm
Field Test - Empty Weight + Water (Full) 302.7 kgm
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157
Attachment 1
158
(Ref :Recommended Practice for Plannning,Design & Construction Fixed Offshore(API RP 2A‐WSD,
:Design and Engineering Practice‐Shell (DEP) or Petronas Technical Spec.(PTS) 37.81.10.31)
Density of air, ρ = kg/m3
Max. wind Speed at 10m above MSL, μ = m/sShape coefficient, Cs =
Pressure, p = F/A = (ρ/2)μ2 Cs = kg/ms2
= N/m2
= kg/m2
76.336
MSET ENGINEERING CORPORATION SDN BHDDATE : 08.12.2014
DOC. REF. NO.: MSET/M2-251/E-6012/DC
SUBJECT: WIND FORCE CALC.
DOCUMENT TITLE: DESIGN CALCULATION
REVISION: 01
JOB NO: M2-251
1.225
41.80.7
749.129
749.129
WIND FORCE CALCULATION
159