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TRANSCRIPT
REV. PREP'D CHK'D REV'D APP'D
PROJECT :
CLIENT :
VENDOR :
MANUFACTURER :
Total page : 206
STRENGTH CALCULATION SHEET
FOR APPROVAL
DATE DESCRIPTION
SS PROJECT
DOCUMENT No.
HS E&C
HS ENGINEERING
W/O No. CLIENT P.O. No.
2
*** TABLE OF CONTENTS ***
N O. S U B J E C T PAGE
1 Cover Sheet 1
2 This Contents 2
3 Design Data 3
4 Setting Summary 4 ∼ 5
5 Pressure Summary 6 ∼ 8
6 Nozzle Schedule 9 ∼ 10
7 Nozzle Summary 11 ∼ 12
8 Thickness Summary 13
9 Weight Summary 14
10 Hydrostatic Test 15 ∼ 18
11 Shell & Head Calculation by Int'l & Ext'l Pressure 19 ∼ 51
12 Stiffener Ring Calculation 52 ∼ 53
13 Flange Calculation 54 ∼ 115
14 Nozzle Opening Calculation 116 ∼ 175
15 Wind Code 176 ∼ 186
16 Seismicd Code 187 ∼ 189
17 Support Lug Calculation 190 ∼ 198
18 Lifting Lug Calculation 199 ∼ 207
19 Setting Bolt Calculation 208
3
DESIGN DATA
ITEM NO. : C-6211
SERVICE : HBM COLUMN
CODE
CODE STAMP NO
CORROSION ALLOWANCE mm
JOINT EFFICIENCY %
POST WELD HEAT TREATMENT
HEAD NORMALIZING AFTER COLD FORMING
RADIOGRAPHY
PNEUMATIC TEST PRESS [kg/cm2 g] --- [MPa g]
HYDROSTATIC TEST PRESSURE (AT SHOP) [kg/cm2 g] 0.415 [MPa g]
HYDROSTATIC TEST PRESSURE (AT FIELD) [kg/cm2 g] 0.233 [MPa g]
M.A.W. P. (CORR. & HOT) [kg/cm2 g] 0.177 [MPa g]
M.A.P. (NEW & COLD) [kg/cm2 g] 0.727 [MPa g]
DESIGN TEMPERATURE ˚C
MIN. DESIGN METAL TEMPERATURE ˚C
DESIGN INTERNAL PRESSURE [kg/cm2 g] 0.177 [MPa g]
DESIGN EXTERNAL PRESSURE [kg/cm2 g] 0.103 [MPa g]
OPERATING TEMPERATURE ˚C
OPERATING PRESSURE [kg/cm2 g] 0.011 [MPa g]
PRESSURE DROP [kg/cm2 g] --- [MPa g]
KIND FO FLUID HBM
SP. & GR. 1.00
SHELL INSIDE DIAMETER mm
SHELL LENGTH (T.L to T.L) mm
TYPE OF HEADS 2:1 ELLIP.
WIND LOAD ASCE 7-05, 162km/hr, I=1.15,"D"
SEISMIC LOAD UBC 1997, I=1.0, Zone:2A, "SD"
INSULATION THICKNESS mm
FIRE PROOFING THICKNESS mm
VOLUME m3
IMPACT TEST
LETHAL/TOXIC
NOTES
1. THE THERMAL OR MECHANICAL SHOCK LOADINGS : NO
2. CYCLIC LOADING : NO
3. CYCLIC & DYNAMIC REACTION DUE TO PRESSURE OR THERMAL VARIATIONS,
OR FROM EQUIPMENT MOUNTED ON A VESSEL, & MECHANICAL LOADING; NO
4. IMPACT REACTIONS DUE TO FLUID SHOCK ; NO
NO
8.726
50
1.80
-10.0
---
72/76
NO
7.41
ASME SEC. VIII DIV.1 2010 EDITION + A11 ADDENDA
0.0
2.38
---
NO
4.23
(SHELL / HEAD)
(SHELL/HEAD / SHELL to HEAD)
85 / 100
NO
SPOT/SEAMLESS / SPOT
1.80
1.05
180
---
18000
0.109
780
Settings Summary
COMPRESS 2014 Build 7400
Units: SI
Datum Line Location: -20.00 mm from bottom seam
Design
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Butt welds are tapered per Figure UCS-66.3(a).
Hydro/Pneumatic Test
Required Marking - UG-116
Code Cases\Interpretations
UG-22 Loadings
Design or Rating: Get Thickness from Pressure
Minimum thickness: 2.5 mm per UG-16(b)
Design for cold shut down only: No
Design for lethal service (full radiography required): No
Design nozzles for: Design P only
Corrosion weight loss: 100% of theoretical loss
UG-23 Stress Increase: 1.20
Skirt/legs stress increase: 1.0
Minimum nozzle projection: 30 mm
Juncture calculations for > 30 only: Yes
Preheat P-No 1 Materials > 1.25" and <= 1.50" thick: No
UG-37(a) shell tr calculation considers longitudinal stress: No
Shop Hydrotest at user defined pressure
Test liquid specific gravity: 1.00
Field Hydrotest Pressure: 1.3 times vessel MAWP
Wind load present @ field: 33% of design
Maximum stress during test: 90% of yield
UG-116(e) Radiography: RT4
UG-116(f) Postweld heat treatment: None
Use Code Case 2547: No
Use Code Case 2695: No
Apply interpretation VIII-1-83-66: Yes
Apply interpretation VIII-1-86-175: Yes
Apply interpretation VIII-1-01-37: Yes
No UCS-66.1 MDMT reduction: No
No UCS-68(c) MDMT reduction: No
Disallow UG-20(f) exemptions: No
ITEM NO.: C-6211 4
Note: UG-22(b),(c) and (f) loads only considered when supports are present.
UG-22(a) Internal or External Design Pressure : Yes
UG-22(b) Weight of the vessel and normal contents under operating or test conditions: Yes
UG-22(c) Superimposed static reactions from weight of attached equipment (external loads): Yes
UG-22(d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: Yes
UG-22(f) Wind reactions: Yes
UG-22(f) Seismic reactions: Yes
UG-22(j) Test pressure and coincident static head acting during the test: Yes
ITEM NO.: C-6211 5
Pressure Summary
Pressure Summary for Chamber bounded by Ellipsoidal Head (Bottom) and Ellipsoidal Head (Top)
Identifier P
Design ( kPa)
T Design
( °C)
MAWP
( kPa)
MAP ( kPa)
MAEP
( kPa)
Te
external ( °C)
MDMT ( °C)
MDMT Exemption
Impact
Tested
Ellipsoidal Head (Top) 176.52 180 1,671.66 1,802.26 337.64 180 -196 Note 1 No
Straight Flange on Ellipsoidal Head (Top) 176.52 180 1,951.22 2,103.66 418.45 180 -196 Note 2 No
Shell #1 176.52 180 1,658.54 1,788.11 418.45 180 -196 Note 2 No
Shell #2 176.52 180 1,658.54 1,788.11 110.48 180 -196 Note 2 No
Shell #3 176.52 180 1,658.54 1,788.11 146.5 180 -196 Note 2 No
Shell #4 176.52 180 1,658.54 1,788.11 137.89 180 -196 Note 2 No
Shell #5 176.52 180 1,741.72 1,788.11 137.16 180 -196 Note 3 No
Straight Flange on Ellipsoidal Head (Bottom) 176.52 180 2,052.48 2,103.66 137.16 180 -196 Note 5 No
Ellipsoidal Head (Bottom) 176.52 180 1,753.34 1,802.26 431.8 180 -196 Note 4 No
Flange #1 176.52 180 857.56 910.42 2,575.23 180 -196 Note 6 No
Flange #3 176.52 180 555.61 712.73 2,314.39 180 -196 Note 7 No
Flange #2 176.52 180 857.56 910.42 2,575.23 180 -196 Note 6 No
Flange #4 176.52 180 555.61 712.73 2,314.39 180 -196 Note 7 No
Flange #5 176.52 180 591.39 810.9 2,462.39 180 -196 Note 7 No
Rings #1 N/A N/A N/A N/A 102.97 180 N/A N/A No
Support Lugs 176.52 180 176.52 N/A N/A N/A N/A N/A N/A
Flange #6 176.52 180 591.39 810.9 2,462.39 180 -196 Note 7 No
Handhole (H1 (150A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 2 No
Handhole (H2 (150A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 2 No
Handhole (H3 (150A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 2 No
Handhole (H4 (150A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 2 No
Manhole (M1 (300A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 8 No
Manhole (M2 (300A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 2 No
Manhole (M3 (300A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 2 No
LG (N10A/B (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
LG (N10C/D (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 9 No
LT (N11A/B (50A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 9 No
Reflux (N12 (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
ITEM NO.: C-6211 6
Chamber design MDMT is -10 °C
Chamber rated MDMT is -196 °C @ 176.52 kPa
Chamber MAWP was used in the MDMT determination
Chamber MAWP hot & corroded is 176.52 kPa @ 180 °C
Chamber MAP cold & new is 176.52 kPa @ 17 °C
Chamber MAEP is 102.97 kPa @ 180 °C
Vacuum rings did not govern the external pressure rating.
Notes for MDMT Rating:
PG (N13A (20A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 10 No
PG (N13B (20A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
PT (N14(15A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
Feed Inlet (N1A (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
Feed Inlet (N1B (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 10 No
Overhaed Outlet (N2 (300A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 11 No
Reboiler Inlet (N3 (150A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 12 No
Reboiler Return (N4 (300A)) 176.52 180 176.52 176.52 102.97 180 -196Nozzle N/A No
Pad Note 13 No
Bottom Return (N5 (15A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 14 No
N2 Inlet (N6 (15A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
Side Out (N7 (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
TE (N8A (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 9 No
TE (N8B (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
TE (N8C (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
TE (N8D (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
TG (N9A (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 11 No
TG (N9B (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
TG (N9C (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
TG (N9D (25A)) 176.52 180 176.52 176.52 102.97 180 -196 Note 2 No
Note # Exemption Details
1. Straight Flange governs MDMT
2. Impact test exempt per UHA-51(g)(coincident ratio = 0.0832)
3. Impact test exempt per UHA-51(g)(coincident ratio = 0.0929)
4. Straight Flange governs MDMT
5. Impact test exempt per UHA-51(g)(coincident ratio = 0.093)
6. Impact test exempt per UHA-51(g)(coincident ratio = 0.2019)
7. Rated MDMT per UHA-51(d)(1)(a) = -196 °C
8. Impact test exempt per UHA-51(g)(coincident ratio = 0.0859)
ITEM NO.: C-6211 7
Design notes are available on the Settings Summary page.
9. Impact test exempt per UHA-51(g)(coincident ratio = 0.0923)
10. Impact test exempt per UHA-51(g)(coincident ratio = 0.084)
11. Impact test exempt per UHA-51(g)(coincident ratio = 0.0881)
12. Impact test exempt per UHA-51(g)(coincident ratio = 0.1003)
13. Impact test exempt per UHA-51(g)(coincident ratio = 0.0888)
14. Impact test exempt per UHA-51(g)(coincident ratio = 0.0922)
ITEM NO.: C-6211 8
Nozzle Schedule
Nozzle
markService Size Materials
Impact
Tested
Normalized Fine Grain Flange Blind
H1 (150A) Handhole 151 ID x 7.1Nozzle STS 304-TP-E (user defined) No No No
N/A NoPad SA-240 304 No No No
H2 (150A) Handhole 151 ID x 7.1Nozzle STS 304-TP-E (user defined) No No No
N/A NoPad SA-240 304 No No No
H3 (150A) Handhole 151 ID x 7.1Nozzle STS 304-TP-E (user defined) No No No
N/A NoPad SA-240 304 No No No
H4 (150A) Handhole 151 ID x 7.1Nozzle STS 304-TP-E (user defined) No No No
N/A NoPad SA-240 304 No No No
M1 (300A) Manhole 297.9 ID x 10.3Nozzle STS 316-TP-E (user defined) No No No
N/A NoPad SA-240 316 No No No
M2 (300A) Manhole 297.9 ID x 10.3Nozzle STS 304-TP-E (user defined) No No No
N/A NoPad SA-240 304 No No No
M3 (300A) Manhole 297.9 ID x 10.3Nozzle STS 304-TP-E (user defined) No No No
N/A NoPad SA-240 304 No No No
N10A/B (25A) LG 27.2 ID x 13.9 Nozzle SA-182 F304 <= 125 No No No N/A No
N10C/D (25A) LG 27.2 ID x 13.9 Nozzle SA-182 F316 <= 125 No No No N/A No
N11A/B (50A) LT 52.7 ID x 3.9Nozzle STS 316-TP-E (user defined) No No No
N/A NoPad SA-240 316 No No No
N12 (25A) Reflux 27.2 ID x 13.9 Nozzle SA-182 F304 <= 125 No No No N/A No
N13A (20A) PG 21.4 ID x 11.8 Nozzle SA-182 F316 <= 125 No No No N/A No
N13B (20A) PG 21.4 ID x 11.8 Nozzle SA-182 F304 <= 125 No No No N/A No
N14(15A) PT 16.1 ID x 11.95 Nozzle SA-182 F304 <= 125 No No No N/A No
N1A (25A) Feed Inlet 27.2 ID x 13.9 Nozzle SA-182 F304 <= 125 No No No N/A No
N1B (25A) Feed Inlet 27.2 ID x 13.9 Nozzle SA-182 F316 <= 125 No No No N/A No
N2 (300A) Overhaed Outlet 297.9 ID x 10.3Nozzle STS 304-TP-E (user defined) No No No
N/A NoPad SA-240 304 No No No
N3 (150A) Reboiler Inlet 151 ID x 7.1Nozzle STS 316-TP-E (user defined) No No No
N/A NoPad SA-240 316 No No No
N4 (300A) Reboiler Return 297.9 ID x 10.3Nozzle STS 316-TP-E (user defined) No No No
N/A NoPad SA-240 316 No No No
N5 (15A) Bottom Return 16.1 ID x 11.95 Nozzle SA-182 F316L <= 125 No No No N/A No
N6 (15A) N2 Inlet 16.1 ID x 11.95 Nozzle SA-182 F304 <= 125 No No No N/A No
N7 (25A) Side Out 27.2 ID x 13.9 Nozzle SA-182 F316 <= 125 No No No N/A No
N8A (25A) TE 27.2 ID x 13.9 Nozzle SA-182 F316 <= 125 No No No N/A No
N8B (25A) TE 27.2 ID x 13.9 Nozzle SA-182 F304 <= 125 No No No N/A No
N8C (25A) TE 27.2 ID x 13.9 Nozzle SA-182 F304 <= 125 No No No N/A No
N8D (25A) TE 27.2 ID x 13.9 Nozzle SA-182 F304 <= 125 No No No N/A No
ITEM NO.: C-6211 9
N9A (25A) TG 27.2 ID x 13.9 Nozzle SA-182 F316 <= 125 No No No N/A No
N9B (25A) TG 27.2 ID x 13.9 Nozzle SA-182 F304 <= 125 No No No N/A No
N9C (25A) TG 27.2 ID x 13.9 Nozzle SA-182 F304 <= 125 No No No N/A No
N9D (25A) TG 27.2 ID x 13.9 Nozzle SA-182 F304 <= 125 No No No N/A No
ITEM NO.: C-6211 10
Nozzle Summary
Nozzle mark
OD (mm)
tn
(mm)
Req tn
(mm) A1? A2?
Shell Reinforcement
Pad Corr (mm)
Aa/Ar
(%) Nom t
(mm) Design t
(mm) User t
(mm) Width
(mm) tpad
(mm)
H1 (150A) 165.2 7.1 2.86 Yes Yes 6 5.35 67.4 6 0 262.9
H2 (150A) 165.2 7.1 2.86 Yes Yes 6 5.35 67.4 6 0 262.9
H3 (150A) 165.2 7.1 2.86 Yes Yes 6 5.2 67.4 6 0 275.5
H4 (150A) 165.2 7.1 2.86 Yes Yes 6 5.82 67.4 6 0 225.7
M1 (300A) 318.5 10.3 2.86 Yes Yes 6 5.36 145.75 6 0 259.3
M2 (300A) 318.5 10.3 2.86 Yes Yes 6 5.22 145.75 6 0 269.3
M3 (300A) 318.5 10.3 2.86 Yes Yes 6 5.82 145.75 6 0 221.2
N10A/B (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N10C/D (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N11A/B (50A) 60.5 3.9 2.86 Yes Yes 6 N/A 44.75 6 0 Exempt
N12 (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N13A (20A) 45 11.8 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N13B (20A) 45 11.8 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N14(15A) 40 11.95 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N1A (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N1B (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N2 (300A) 318.5 10.3 2.86 Yes Yes 5.1* 2.13 145.75 6 0 848.4
N3 (150A) 165.2 7.1 2.86 Yes Yes 5.1* 2.13 67.4 6 0 861.5
N4 (300A) 318.5 10.3 2.86 Yes Yes 6 5.36 70.75 6 0 161.8
N5 (15A) 40 11.95 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N6 (15A) 40 11.95 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N7 (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N8A (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N8B (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N8C (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N8D (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N9A (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N9B (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N9C (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
N9D (25A) 55 13.9 2.5 Yes Yes 6 N/A N/A N/A 0 Exempt
tn: Nozzle thickness
Req tn: Nozzle thickness required per UG-45/UG-16
Nom t: Vessel wall thickness
Design t: Required vessel wall thickness due to pressure + corrosion allowance per UG-37
User t: Local vessel wall thickness (near opening)
Area available per UG-37, governing condition
ITEM NO.: C-6211 11
Aa:
Ar: Area required per UG-37, governing condition
Corr: Corrosion allowance on nozzle wall
* Head minimum thickness after forming
ITEM NO.: C-6211 12
Thickness Summary
Component Identifier
Material Diameter
(mm) Length
(mm) Nominal t
(mm) Design t
(mm) Total Corrosion
(mm) Joint
E Load
Ellipsoidal Head (Top) SA-240 304 780 ID 200.1 5.1* 2.13 0 1.00 External
Straight Flange on Ellipsoidal Head (Top) SA-240 304 780 ID 20 6 3.03 0 1.00 External
Shell #1 SA-240 304 780 ID 1,000 6 3.03 0 0.85 External
Shell #2 SA-240 304 780 ID 5,048 6 5.82 0 0.85 External
Shell #3 SA-240 304 780 ID 7,801 6 5.22 0 0.85 External
Shell #4 SA-240 304 780 ID 2,048 6 5.35 0 0.85 External
Shell #5 SA-240 316 780 ID 2,000 6 5.36 0 0.85 External
Straight Flange on Ellipsoidal Head (Bottom) SA-240 316 780 ID 20 6 5.36 0 1.00 External
Ellipsoidal Head (Bottom) SA-240 316 780 ID 200.1 5.1* 2.14 0 1.00 External
Nominal t: Vessel wall nominal thickness
Design t: Required vessel thickness due to governing loading + corrosion
Joint E: Longitudinal seam joint efficiency
* Head minimum thickness after forming
Load
internal: Circumferential stress due to internal pressure governs
external: External pressure governs
Wind: Combined longitudinal stress of pressure + weight + wind governs
Seismic: Combined longitudinal stress of pressure + weight + seismic governs
ITEM NO.: C-6211 13
Weight Summary
* Shells with attached nozzles have weight reduced by material cut out for opening.
Vessel center of gravity location - from datum - lift condition
Note: Vessel lift weight includes weight of insulation supports as they are assumed to be shop installed.
Vessel Capacity
**The vessel capacity does not include volume of nozzle, piping or other attachments.
Component
Weight ( kg) Contributed by Vessel Elements
Metal New*
Metal
Corroded* Insulation
Insulation
Supports Lining
Piping
+ Liquid
Operating Liquid Test Liquid
New Corroded New Corroded
Ellipsoidal Head (Top) 28.3 28.3 8.2 0 0 0 0 0 86.2 86.2
Shell #1 118.7 118.7 26.5 10 0 0 0 0 482.7 482.7
Shell #2 595 595 133.5 50 0 0 152.2 152.2 2,438.5 2,438.5
Shell #3 922.3 922.3 206.4 70 0 0 300 300 3,752.9 3,752.9
Shell #4 241.4 241.4 54.2 20 0 0 64.4 64.4 990.3 990.3
Shell #5 229.4 229.4 52.9 20 0 0 1,030.5 1,030.5 983.8 983.8
Ellipsoidal Head (Bottom) 30.7 30.7 8.2 0 0 0 81.9 81.9 74.5 74.5
Support Lugs 124.1 124.1 0 0 0 0 0 0 0 0
TOTAL: 2,289.9 2,289.9 489.8 170 0 0 1,629 1,629 8,808.9 8,808.9
Component
Weight ( kg) Contributed by Attachments
Body Flanges Nozzles &
Flanges Packed
Beds Ladders &
Platforms Trays
Tray
Supports
Rings &
Clips Vertical
Loads New Corroded New Corroded
Ellipsoidal Head (Top) 0 0 28.6 28.6 0 0 0 0 0 0
Shell #1 117.8 117.8 2 2 0 0 0 0 57.7 0
Shell #2 235.7 235.7 41.3 41.3 1,170.7 0 0 0 0 900
Shell #3 235.7 235.7 42.4 42.4 2,307.9 0 0 0 6.4 1,000
Shell #4 117.8 117.8 17.4 17.4 495 0 0 0 0 0
Shell #5 0 0 58.9 58.9 6.7 0 0 0 0 0
Ellipsoidal Head (Bottom) 0 0 7.1 7.1 0 0 0 0 0 0
TOTAL: 707 707 197.7 197.7 3,980.4 0 0 0 64.1 1,900
Vessel operating weight, Corroded: 11,428 kg
Vessel operating weight, New: 11,428 kg
Vessel empty weight, Corroded: 9,799 kg
Vessel empty weight, New: 9,799 kg
Vessel test weight, New: 18,608 kg
Vessel test weight, Corroded: 18,608 kg
Vessel Lift Weight, New: 5,315 kg
Center of Gravity: 10,425.75 mm
Vessel Capacity** (New): 8,726 liters
Vessel Capacity** (Corroded): 8,726 liters
ITEM NO.: C-6211 14
Hydrostatic Test
Shop test pressure determination for Chamber bounded by Ellipsoidal Head (Bottom) and Ellipsoidal Head (Top) based on
user defined pressure
Shop test gauge pressure is 415.15 kPa at 17 °C
The shop test is performed with the vessel in the horizontal position.
Identifier
Local test
pressure
kPa
Test liquid
static head
kPa
Stress
during test
MPa
Allowable
test stress
MPa
Stress
excessive?
Ellipsoidal Head (Top) 424.05 8.9 29.185 186.3 No
Straight Flange on Ellipsoidal Head (Top) 424.05 8.9 27.775 186.3 No
Shell #1 424.05 8.9 27.775 186.3 No
Shell #2 424.05 8.9 27.775 186.3 No
Shell #3 424.05 8.9 27.775 186.3 No
Shell #4 424.05 8.9 27.775 186.3 No
Shell #5 424.05 8.9 27.775 186.3 No
Straight Flange on Ellipsoidal Head (Bottom) 424.05 8.9 27.775 186.3 No
Ellipsoidal Head (Bottom) 424.05 8.9 29.185 186.3 No
Flange #1 424.12 8.97 30.51 279.45 No
Flange #2 424.12 8.97 30.51 279.45 No
Flange #3 424.12 8.97 30.51 279.45 No
Flange #4 424.12 8.97 30.51 279.45 No
Flange #5 424.12 8.97 30.51 279.45 No
Flange #6 424.12 8.97 30.51 279.45 No
Bottom Return (N5 (15A)) 424.5 9.35 27.593 276.75 No
Feed Inlet (N1A (25A)) 420.36 5.21 27.323 276.75 No
Feed Inlet (N1B (25A)) 420.36 5.21 27.323 276.75 No
Handhole (H1 (150A)) 424.91 9.76 22.753 276.75 No
Handhole (H2 (150A)) 424.91 9.76 22.753 276.75 No
Handhole (H3 (150A)) 420.97 5.82 22.542 276.75 No
Handhole (H4 (150A)) 426.11 10.96 22.817 276.75 No
LG (N10A/B (25A)) 422.53 7.38 27.464 276.75 No
LG (N10C/D (25A)) 416.35 1.2 27.063 276.75 No
LT (N11A/B (50A)) 416.74 1.59 13.544 276.75 No
Manhole (M1 (300A)) 425.42 10.27 40.903 276.75 No
Manhole (M2 (300A)) 421.69 6.54 40.544 276.75 No
Manhole (M3 (300A)) 426.11 10.96 40.969 276.75 No
N2 Inlet (N6 (15A)) 417.54 2.39 27.14 276.75 No
Overhaed Outlet (N2 (300A)) 421.69 6.54 35.439 276.75 No
PG (N13A (20A)) 416.92 1.77 27.1 276.75 No
ITEM NO.: C-6211 15
Notes:
(1) PL stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399, pages 77-82.
(2) 1.5*0.9*Sy used as the basis for the maximum local primary membrane stress at the nozzle intersection PL.
(3) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-most flange.
PG (N13B (20A)) 424.38 9.23 27.585 276.75 No
PT (N14(15A)) 424.5 9.35 27.593 276.75 No
Reboiler Inlet (N3 (150A)) 420.97 5.82 19.669 276.75 No
Reboiler Return (N4 (300A)) 421.69 6.54 36.444 276.75 No
Reflux (N12 (25A)) 416.35 1.2 27.063 276.75 No
Side Out (N7 (25A)) 420.36 5.21 27.323 276.75 No
TE (N8A (25A)) 424.08 8.93 27.565 276.75 No
TE (N8B (25A)) 424.08 8.93 27.565 276.75 No
TE (N8C (25A)) 424.08 8.93 27.565 276.75 No
TE (N8D (25A)) 424.08 8.93 27.565 276.75 No
TG (N9A (25A)) 424.08 8.93 27.565 276.75 No
TG (N9B (25A)) 423.41 8.26 27.522 276.75 No
TG (N9C (25A)) 423.41 8.26 27.522 276.75 No
TG (N9D (25A)) 423.41 8.26 27.522 276.75 No
ITEM NO.: C-6211 16
Field test pressure determination for Chamber bounded by Ellipsoidal Head (Bottom) and Ellipsoidal Head (Top) based on
MAWP per UG-99(b)
Field hydrostatic test gauge pressure is 232.85 kPa at 17 °C (the chamber MAWP = 176.52 kPa)
The field test is performed with the vessel in the vertical position.
Identifier
Local test
pressure
kPa
Test liquid
static head
kPa
UG-99(b)
stress
ratio
UG-99(b)
pressure
factor
Stress
during test
MPa
Allowable
test stress
MPa
Stress
excessive?
Ellipsoidal Head (Top) 237.06 4.21 1.0781 1.30 16.315 186.3 No
Straight Flange on Ellipsoidal Head (Top) 237.06 4.21 1.0781 1.30 15.527 186.3 No
Shell #1 246.86 14.01 1.0781 1.30 16.169 186.3 No
Shell #2 296.53 63.68 1.0781 1.30 19.422 186.3 No
Shell #3 (1) 373.17 140.32 1.0781 1.30 25.235 186.3 No
Shell #4 393.45 160.6 1.0781 1.30 25.77 186.3 No
Shell #5 (2) 413.04 180.19 1.0147 1.30 27.054 186.3 No
Straight Flange on Ellipsoidal Head (Bottom) 413.24 180.39 1.0147 1.30 27.067 186.3 No
Ellipsoidal Head (Bottom) 415.15 182.3 1.0147 1.30 28.572 186.3 No
Flange #1 246.95 14.1 1.3996 1.30 17.765 279.45 No
Flange #2 247.71 14.86 1.3996 1.30 17.82 279.45 No
Flange #3 296.62 63.77 1.3996 1.30 21.338 279.45 No
Flange #4 297.38 64.53 1.3996 1.30 21.393 279.45 No
Flange #5 373.26 140.41 1.3996 1.30 26.852 279.45 No
Flange #6 374.03 141.18 1.3996 1.30 26.907 279.45 No
Bottom Return (N5 (15A)) 411.85 179 1.036 1.30 26.77 276.75 No
Feed Inlet (N1A (25A)) 371.24 138.39 1.0781 1.30 24.13 276.75 No
Feed Inlet (N1B (25A)) 395.93 163.08 1.0147 1.30 25.735 276.75 No
Handhole (H1 (150A)) 392.42 159.57 1.0781 1.30 21.013 276.75 No
Handhole (H2 (150A)) 381.15 148.3 1.0781 1.30 20.41 276.75 No
Handhole (H3 (150A)) 303.75 70.9 1.0781 1.30 16.265 276.75 No
Handhole (H4 (150A)) 253.77 20.92 1.0781 1.30 13.589 276.75 No
LG (N10A/B (25A)) 293.9 61.05 1.0781 1.30 19.103 276.75 No
LG (N10C/D (25A)) 411.9 179.05 1.0147 1.30 26.774 276.75 No
LT (N11A/B (50A)) 412.03 179.18 1.0147 1.30 13.391 276.75 No
Manhole (M1 (300A)) 399.51 166.66 1.0147 1.30 38.412 276.75 No
Manhole (M2 (300A)) 364.73 131.88 1.0781 1.30 35.068 276.75 No
Manhole (M3 (300A)) 281.44 48.59 1.0781 1.30 27.06 276.75 No
N2 Inlet (N6 (15A)) 383.92 151.07 1.0781 1.30 24.955 276.75 No
Overhaed Outlet (N2 (300A)) 234.91 2.06 1.0781 1.30 19.742 276.75 No
PG (N13A (20A)) 395.9 163.05 1.0147 1.30 25.734 276.75 No
PG (N13B (20A)) 239.13 6.28 1.0781 1.30 15.543 276.75 No
PT (N14(15A)) 239.1 6.25 1.0781 1.30 15.542 276.75 No
ITEM NO.: C-6211 17
Notes:
(1) Longitudinal stress during the test governs this component.
(2) Shell #5 limits the UG-99(b) stress ratio.
(3) PL stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399, pages 77-82.
(4) 1.5*0.9*Sy used as the basis for the maximum local primary membrane stress at the nozzle intersection PL.
Reboiler Inlet (N3 (150A)) 416.77 183.92 1.0147 1.30 19.473 276.75 No
Reboiler Return (N4 (300A)) 405.19 172.34 1.0147 1.30 35.019 276.75 No
Reflux (N12 (25A)) 244.84 11.99 1.0781 1.30 15.914 276.75 No
Side Out (N7 (25A)) 293.9 61.05 1.0147 1.30 19.103 276.75 No
TE (N8A (25A)) 411.9 179.05 1.0147 1.30 26.774 276.75 No
TE (N8B (25A)) 371.24 138.39 1.0781 1.30 24.13 276.75 No
TE (N8C (25A)) 304.02 71.17 1.0781 1.30 19.761 276.75 No
TE (N8D (25A)) 253.46 20.61 1.0781 1.30 16.475 276.75 No
TG (N9A (25A)) 403.87 171.02 1.0147 1.30 26.251 276.75 No
TG (N9B (25A)) 371.24 138.39 1.0781 1.30 24.13 276.75 No
TG (N9C (25A)) 304.02 71.17 1.0781 1.30 19.761 276.75 No
TG (N9D (25A)) 253.46 20.61 1.0781 1.30 16.475 276.75 No
ITEM NO.: C-6211 18
Ellipsoidal Head (Top)
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Straight Flange governs MDMT
Internal design pressure: P = 176.52 kPa @ 180 °C
External design pressure: Pe = 102.97 kPa @ 180 °C
Static liquid head:
Ps= 0 kPa (SG=1.1, Hs=0 mm Operating head)
Pth= 8.9 kPa (SG=1, Hs=908.22 mm Horizontal test head)
Ptv= 4.02 kPa (SG=1, Hs=410 mm Vertical test head)
* includes straight flange
* includes straight flange if applicable
Results Summary
Design thickness for internal pressure, (Corroded at 180 °C) UG-32(d)(1)
Component: Ellipsoidal Head
Material Specification: SA-240 304 (II-D Metric p.86, ln. 25)
Corrosion allowance: Inner C = 0 mm Outer C = 0 mm
Design MDMT = -10°C No impact test performed
Rated MDMT = -196°C Material is not normalized
Material is not produced to fine grain practice
PWHT is not performed
Do not Optimize MDMT / Find MAWP
Radiography: Category A joints - Seamless No RT
Head to shell seam - Spot UW-11(a)(5)(b) Type 1
Estimated weight*: new = 28.3 kg corr = 28.3 kg
Capacity*: new = 71.7 liters corr = 71.7 liters
Inner diameter = 780 mm
Minimum head thickness = 5.1 mm
Head ratio D/2h = 2 (new)
Head ratio D/2h = 2 (corroded)
Straight flange length Lsf = 20 mm
Nominal straight flange thickness tsf = 6 mm
Insulation thk*: 50 mm density: 200 kg/m3 weight: 8.1984 kg
Insulation support ring
spacing: 0 mm individual weight: 0 kg total weight: 0 kg
The governing condition is UG-16.
Minimum thickness per UG-16 = 2.5 mm + 0 mm = 2.5 mm
Design thickness due to internal pressure (t) = 0.54 mm
Design thickness due to external pressure (te) = 2.13 mm
Maximum allowable working pressure (MAWP) = 1,671.66 kPa
Maximum allowable pressure (MAP) = 1,802.26 kPa
Maximum allowable external pressure (MAEP) = 337.64 kPa
ITEM NO.: C-6211 19
The head internal pressure design thickness is 0.54 mm.
Maximum allowable working pressure, (Corroded at 180 °C) UG-32(d)(1)
The maximum allowable working pressure (MAWP) is 1,671.66 kPa.
Maximum allowable pressure, (New at 17 °C) UG-32(d)(1)
The maximum allowable pressure (MAP) is 1,802.26 kPa.
Design thickness for external pressure, (Corroded at 180 °C) UG-33(d)
Check the external pressure per UG-33(a)(1) UG-32(d)(1)
The head external pressure design thickness (te) is 2.13 mm.
Maximum Allowable External Pressure, (Corroded at 180 °C) UG-33(d)
t = P*D / (2*S*E - 0.2*P) + Corrosion
= 176.52*780 / (2*128,000*1 - 0.2*176.52) + 0
= 0.54 mm
P = 2*S*E*t / (D + 0.2*t) - Ps
= 2*128,000*1*5.1 / (780 +0.2*5.1) - 0
= 1,671.66 kPa
P = 2*S*E*t / (D + 0.2*t) - Ps
= 2*138,000*1*5.1 / (780 +0.2*5.1) - 0
= 1,802.26 kPa
Equivalent outside spherical radius (Ro)
Ro = Ko*Do
= 0.8885*790.2
= 702.12 mm
A = 0.125 / (Ro / t)
= 0.125 / (702.12 / 2.13)
= 0.000379
From Table HA-1 Metric:B = 33.9348 MPa
Pa = B / (Ro / t)
= 33,934.77 / (702.12 / 2.13)
= 102.9698 kPa
t = 2.13 mm + Corrosion = 2.13 mm + 0 mm = 2.13 mm
t = 1.67*Pe*D / (2*S*E - 0.2*1.67*Pe) + Corrosion
= 1.67*102.97*780 / (2*128,000*1 - 0.2*1.67*102.97) + 0
= 0.52 mm
Equivalent outside spherical radius (Ro)
Ro = Ko*Do
= 0.8885*790.2
= 702.12 mm
A = 0.125 / (Ro / t)
ITEM NO.: C-6211 20
Check the Maximum External Pressure, UG-33(a)(1) UG-32(d)(1)
The maximum allowable external pressure (MAEP) is 337.64 kPa.
% Forming strain - UHA-44(a)(2)(b)
= 0.125 / (702.12 / 5.1)
= 0.000908
From Table HA-1 Metric:B = 46.483 MPa
Pa = B / (Ro / t)
= 46,483.03 / (702.12 / 5.1)
= 337.641 kPa
P = 2*S*E*t / ((D + 0.2*t)*1.67) - Ps2
= 2*128,000*1*5.1 / ((780 +0.2*5.1)*1.67) - 0
= 1,000.99 kPa
EFE = (75*t / Rf)*(1 - Rf / Ro)
= (75*6 / 135.6)*(1 - 135.6 / infinity)
= 3.3186%
ITEM NO.: C-6211 21
Straight Flange on Ellipsoidal Head (Top)
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Internal design pressure: P = 176.52 kPa @ 180 °C
External design pressure: Pe = 102.97 kPa @ 180 °C
Static liquid head:
Design thickness, (at 180 °C) UG-27(c)(1)
Maximum allowable working pressure, (at 180 °C) UG-27(c)(1)
Maximum allowable pressure, (at 17 °C) UG-27(c)(1)
External Pressure, (Corroded & at 180 °C) UG-28(c)
Component: Straight Flange
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Impact test exempt per UHA-51(g)(coincident ratio = 0.0832)
Ps = 0 kPa (SG = 1.1, Hs = 0 mm,Operating head)
Pth = 8.9 kPa (SG = 1, Hs = 908.22 mm, Horizontal test head)
Ptv = 4.21 kPa (SG = 1, Hs = 430 mm, Vertical test head)
Corrosion allowance Inner C = 0 mm Outer C = 0 mm
Design MDMT = -10 °C No impact test performed
Rated MDMT = -196 °C Material is not normalized
Material is not produced to Fine Grain Practice
PWHT is not performed
Radiography: Longitudinal joint - Seamless No RT
Circumferential joint - Spot UW-11(a)(5)(b) Type 1
Estimated weight New = 2.4 kg corr = 2.4 kg
Capacity New = 9.56 liters corr = 9.56 liters
ID = 780 mm
Length Lc = 20 mm
t = 6 mm
Insulation thk: 50 mm density: 200 kg/m3 Weight: 0 kg
t = P*R / (S*E - 0.60*P) + Corrosion
= 176.52*390 / (128,000*1.00 - 0.60*176.52) + 0
= 0.54 mm
P = S*E*t / (R + 0.60*t) - Ps
= 128,000*1.00*6 / (390 + 0.60*6) - 0
= 1,951.22 kPa
P = S*E*t / (R + 0.60*t)
= 138,000*1.00*6 / (390 + 0.60*6)
= 2,103.66 kPa
L / Do = 1,094 / 792 = 1.3813
ITEM NO.: C-6211 22
Design thickness for external pressure Pa = 102.97 kPa
Maximum Allowable External Pressure, (Corroded & at 180 °C) UG-28(c)
% Forming strain - UHA-44(a)(2)(a)
Design thickness = 3.03 mm
The governing condition is due to external pressure.
The cylinder thickness of 6 mm is adequate.
Thickness Required Due to Pressure + External Loads
Do / t = 792 / 3.03 = 261.5016
From table G: A = 0.000226
From table HA-1 Metric: B = 20.195 MPa
Pa = 4*B / (3*(Do / t))
= 4*20,195.01 / (3*(792 / 3.03))
= 102.97 kPa
ta = t + Corrosion = 3.03 + 0 = 3.03 mm
L / Do = 1,094 / 792 = 1.3813
Do / t = 792 / 6 = 132.0000
From table G: A = 0.000633
From table HA-1 Metric: B = 41.4263 MPa
Pa = 4*B / (3*(Do / t))
= 4*41,426.31 / (3*(792 / 6))
= 418.45 kPa
EFE = (50*t / Rf)*(1 - Rf / Ro)
= (50*6 / 393)*(1 - 393 / infinity)
= 0.7634%
ConditionPressure P
( kPa)
Allowable Stress Before UG-23 Stress
Increase ( MPa)Temperature
( °C)
Corrosion C
(mm)Load
Req'd Thk
Due to
Tension (mm)
Req'd Thk Due to
Compression (mm)
St Sc
Operating, Hot & Corroded
176.52 128 58.52 180 0Wind 0.26 0.26
Seismic 0.26 0.26
Operating, Hot & New 176.52 128 58.52 180 0Wind 0.26 0.26
Seismic 0.26 0.26
Hot Shut Down,
Corroded0 128 58.52 180 0
Wind 0 0
Seismic 0 0.01
Hot Shut Down, New 0 128 58.52 180 0Wind 0 0
Seismic 0 0.01
Empty, Corroded 0 138 78.09 21.11 0Wind 0 0
Seismic 0 0.01
ITEM NO.: C-6211 23
Empty, New 0 138 78.09 21.11 0Wind 0 0
Seismic 0 0.01
Vacuum -102.97 128 58.52 180 0Wind 0.29 0.29
Seismic 0.29 0.29
Hot Shut Down,
Corroded, Weight &
Eccentric Moments Only
0 128 58.52 180 0 Weight 0 0
Operating, Hot &
Corroded, Vortex
Shedding
176.52 128 58.52 180 0 Wind 0.26 0.26
Empty, Cold &
Corroded, Vortex
Shedding
0 138 78.09 21.11 0 Wind 0 0
Vacuum, Vortex Shedding
-102.97 128 58.52 180 0 Wind 0.29 0.29
ITEM NO.: C-6211 24
Shell #1
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Internal design pressure: P = 176.52 kPa @ 180 °C
External design pressure: Pe = 102.97 kPa @ 180 °C
Static liquid head:
Design thickness, (at 180 °C) UG-27(c)(1)
Maximum allowable working pressure, (at 180 °C) UG-27(c)(1)
Maximum allowable pressure, (at 17 °C) UG-27(c)(1)
External Pressure, (Corroded & at 180 °C) UG-28(c)
Component: Cylinder
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Impact test exempt per UHA-51(g)(coincident ratio = 0.0832)
Ps = 0 kPa (SG = 1.1, Hs = 0 mm,Operating head)
Pth = 8.9 kPa (SG = 1, Hs = 908.22 mm, Horizontal test head)
Ptv = 14.01 kPa (SG = 1, Hs = 1,430 mm, Vertical test head)
Corrosion allowance Inner C = 0 mm Outer C = 0 mm
Design MDMT = -10 °C No impact test performed
Rated MDMT = -196 °C Material is not normalized
Material is not produced to Fine Grain Practice
PWHT is not performed
Radiography: Longitudinal joint - Spot UW-11(b) Type 1
Top circumferential joint - Spot UW-11(a)(5)(b) Type 1
Bottom circumferential joint - N/A
Estimated weight New = 118.7 kg corr = 118.7 kg
Capacity New = 477.84 liters corr = 477.84 liters
ID = 780 mm
Length Lc = 1,000 mm
t = 6 mm
Insulation thk: 50 mm density: 200 kg/m3 Weight: 26.5 kg
Insulation Support
Spacing:1,000 mm
Individual Support
Weight:10 kg
Total Support
Weight:10 kg
t = P*R / (S*E - 0.60*P) + Corrosion
= 176.52*390 / (128,000*0.85 - 0.60*176.52) + 0
= 0.64 mm
P = S*E*t / (R + 0.60*t) - Ps
= 128,000*0.85*6 / (390 + 0.60*6) - 0
= 1,658.54 kPa
P = S*E*t / (R + 0.60*t)
= 138,000*0.85*6 / (390 + 0.60*6)
= 1,788.11 kPa
ITEM NO.: C-6211 25
Design thickness for external pressure Pa = 102.97 kPa
Maximum Allowable External Pressure, (Corroded & at 180 °C) UG-28(c)
% Forming strain - UHA-44(a)(2)(a)
External Pressure + Weight + Wind Loading Check (Bergman, ASME paper 54-A-104)
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
External Pressure + Weight + Seismic Loading Check (Bergman, ASME paper 54-A-104)
L / Do = 1,094 / 792 = 1.3813
Do / t = 792 / 3.03 = 261.5016
From table G: A = 0.000226
From table HA-1 Metric: B = 20.195 MPa
Pa = 4*B / (3*(Do / t))
= 4*20,195.01 / (3*(792 / 3.03))
= 102.97 kPa
ta = t + Corrosion = 3.03 + 0 = 3.03 mm
L / Do = 1,094 / 792 = 1.3813
Do / t = 792 / 6 = 132.0000
From table G: A = 0.000633
From table HA-1 Metric: B = 41.4263 MPa
Pa = 4*B / (3*(Do / t))
= 4*41,426.31 / (3*(792 / 6))
= 418.45 kPa
EFE = (50*t / Rf)*(1 - Rf / Ro)
= (50*6 / 393)*(1 - 393 / infinity)
= 0.7634%
Pv = W / (2**Rm) + M / (*Rm2)
= 98.03*269.9 / (2**393) + 10000*1,290.5 / (*3932)
= 37.3156 N/cm
= Pv / (Pe*Do)
= 100*37.3156 / (102.97*792)
= 0.0458
n = 5
m = 1.23 / (L / Do)2
= 1.23 / (1,094 / 792)2
= 0.6446
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (52 - 1 + 0.6446 + 0.6446*0.0458) / (52 - 1 + 0.6446)
= 1.0012
Pv = (1 + VAccel)*W / (2**Rm) + M / (*Rm2)
ITEM NO.: C-6211 26
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
Design thickness = 3.03 mm
The governing condition is due to external pressure.
The cylinder thickness of 6 mm is adequate.
Thickness Required Due to Pressure + External Loads
= 1.20*98.03*269.9 / (2**393) + 10000*1,222.6 / (*3932)
= 38.0598 N/cm
= Pv / (Pe*Do)
= 100*38.0598 / (102.97*792)
= 0.0467
n = 5
m = 1.23 / (L / Do)2
= 1.23 / (1,094 / 792)2
= 0.6446
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (52 - 1 + 0.6446 + 0.6446*0.0467) / (52 - 1 + 0.6446)
= 1.0012
ConditionPressure P
( kPa)
Allowable Stress Before UG-23 Stress
Increase ( MPa)Temperature
( °C)
Corrosion C
(mm)Load
Req'd Thk
Due to
Tension (mm)
Req'd Thk Due to
Compression (mm)
St Sc
Operating, Hot & Corroded
176.52 128 58.52 180 0Wind 0.24 0.2
Seismic 0.23 0.2
Operating, Hot & New 176.52 128 58.52 180 0Wind 0.24 0.2
Seismic 0.23 0.2
Hot Shut Down,
Corroded0 128 58.52 180 0
Wind 0.01 0.05
Seismic 0.01 0.05
Hot Shut Down, New 0 128 58.52 180 0Wind 0.01 0.05
Seismic 0.01 0.05
Empty, Corroded 0 138 78.09 21.11 0Wind 0.01 0.04
Seismic 0.01 0.04
Empty, New 0 138 78.09 21.11 0Wind 0.01 0.04
Seismic 0.01 0.04
Vacuum -102.97 128 58.52 180 0Wind 0.26 0.34
Seismic 0.27 0.34
Hot Shut Down,
Corroded, Weight &
Eccentric Moments Only
0 128 58.52 180 0 Weight 0.02 0.02
Operating, Hot & Corroded, Vortex
Shedding
176.52 128 58.52 180 0 Wind 0.23 0.21
ITEM NO.: C-6211 27
Empty, Cold &
Corroded, Vortex
Shedding
0 138 78.09 21.11 0 Wind 0.01 0.03
Vacuum, Vortex
Shedding-102.97 128 58.52 180 0 Wind 0.28 0.32
ITEM NO.: C-6211 28
Shell #2
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Internal design pressure: P = 176.52 kPa @ 180 °C
External design pressure: Pe = 102.97 kPa @ 180 °C
Static liquid head:
Design thickness, (at 180 °C) UG-27(c)(1)
Maximum allowable working pressure, (at 180 °C) UG-27(c)(1)
Maximum allowable pressure, (at 17 °C) UG-27(c)(1)
External Pressure, (Corroded & at 180 °C) UG-28(c)
Component: Cylinder
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Impact test exempt per UHA-51(g)(coincident ratio = 0.0832)
Ps = 0 kPa (SG = 1.1, Hs = 0 mm,Operating head)
Pth = 8.9 kPa (SG = 1, Hs = 908.22 mm, Horizontal test head)
Ptv = 63.68 kPa (SG = 1, Hs = 6,499 mm, Vertical test head)
Corrosion allowance Inner C = 0 mm Outer C = 0 mm
Design MDMT = -10 °C No impact test performed
Rated MDMT = -196 °C Material is not normalized
Material is not produced to Fine Grain Practice
PWHT is not performed
Radiography: Longitudinal joint - Spot UW-11(b) Type 1
Top circumferential joint - N/A
Bottom circumferential joint - N/A
Estimated weight New = 595 kg corr = 595 kg
Capacity New = 2,412.12 liters corr = 2,412.12 liters
ID = 780 mm
Length Lc = 5,048 mm
t = 6 mm
Insulation thk: 50 mm density: 200 kg/m3 Weight: 133.5 kg
Insulation Support
Spacing:1,000 mm
Individual Support
Weight:10 kg
Total Support
Weight:50 kg
t = P*R / (S*E - 0.60*P) + Corrosion
= 176.52*390 / (128,000*0.85 - 0.60*176.52) + 0
= 0.64 mm
P = S*E*t / (R + 0.60*t) - Ps
= 128,000*0.85*6 / (390 + 0.60*6) - 0
= 1,658.54 kPa
P = S*E*t / (R + 0.60*t)
= 138,000*0.85*6 / (390 + 0.60*6)
= 1,788.11 kPa
ITEM NO.: C-6211 29
Design thickness for external pressure Pa = 102.97 kPa
Maximum Allowable External Pressure, (Corroded & at 180 °C) UG-28(c)
% Forming strain - UHA-44(a)(2)(a)
External Pressure + Weight + Wind Loading Check (Bergman, ASME paper 54-A-104)
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
External Pressure + Weight + Seismic Loading Check (Bergman, ASME paper 54-A-104)
L / Do = 5,066 / 792 = 6.3965
Do / t = 792 / 5.82 = 135.9685
From table G: A = 0.000118
From table HA-1 Metric: B = 10.5005 MPa
Pa = 4*B / (3*(Do / t))
= 4*10,500.5 / (3*(792 / 5.82))
= 102.97 kPa
ta = t + Corrosion = 5.82 + 0 = 5.82 mm
L / Do = 5,066 / 792 = 6.3965
Do / t = 792 / 6 = 132.0000
From table G: A = 0.000123
From table HA-1 Metric: B = 10.9375 MPa
Pa = 4*B / (3*(Do / t))
= 4*10,937.49 / (3*(792 / 6))
= 110.48 kPa
EFE = (50*t / Rf)*(1 - Rf / Ro)
= (50*6 / 393)*(1 - 393 / infinity)
= 0.7634%
Pv = W / (2**Rm) + M / (*Rm2)
= 98.03*3,498.2 / (2**393) + 10000*34,472.5 / (*3932)
= 849.3876 N/cm
= Pv / (Pe*Do)
= 100*849.3876 / (102.97*792)
= 1.0415
n = 2
m = 1.23 / (L / Do)2
= 1.23 / (5,066 / 792)2
= 0.0301
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (22 - 1 + 0.0301 + 0.0301*1.0415) / (22 - 1 + 0.0301)
= 1.0103
Pv = (1 + VAccel)*W / (2**Rm) + M / (*Rm2)
ITEM NO.: C-6211 30
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
Design thickness = 5.82 mm
The governing condition is due to external pressure.
The cylinder thickness of 6 mm is adequate.
Thickness Required Due to Pressure + External Loads
= 1.20*98.03*3,498.2 / (2**393) + 10000*49,388.7 / (*3932)
= 1184.5879 N/cm
= Pv / (Pe*Do)
= 100*1184.5879 / (102.97*792)
= 1.4526
n = 2
m = 1.23 / (L / Do)2
= 1.23 / (5,066 / 792)2
= 0.0301
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (22 - 1 + 0.0301 + 0.0301*1.4526) / (22 - 1 + 0.0301)
= 1.0144
ConditionPressure P
( kPa)
Allowable Stress Before UG-23 Stress
Increase ( MPa)Temperature
( °C)
Corrosion C
(mm)Load
Req'd Thk
Due to
Tension (mm)
Req'd Thk Due to
Compression (mm)
St Sc
Operating, Hot & Corroded
176.52 128 58.52 180 0Wind 0.63 0.72
Seismic 0.8 1.2
Operating, Hot & New 176.52 128 58.52 180 0Wind 0.63 0.72
Seismic 0.8 1.2
Hot Shut Down,
Corroded0 128 58.52 180 0
Wind 0.41 1.21
Seismic 0.57 1.69
Hot Shut Down, New 0 128 58.52 180 0Wind 0.41 1.21
Seismic 0.57 1.69
Empty, Corroded 0 138 78.09 21.11 0Wind 0.38 0.9
Seismic 0.58 1.33
Empty, New 0 138 78.09 21.11 0Wind 0.38 0.9
Seismic 0.58 1.33
Vacuum -102.97 128 58.52 180 0Wind 0.28 1.5
Seismic 0.44 1.97
Hot Shut Down,
Corroded, Weight &
Eccentric Moments Only
0 128 58.52 180 0 Weight 0.23 0.25
Operating, Hot & Corroded, Vortex
Shedding
176.52 128 58.52 180 0 Wind 0.39 0.19
ITEM NO.: C-6211 31
Empty, Cold &
Corroded, Vortex
Shedding
0 138 78.09 21.11 0 Wind 0.2 0.58
Vacuum, Vortex
Shedding-102.97 128 58.52 180 0 Wind 0.04 0.97
ITEM NO.: C-6211 32
Shell #3
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Internal design pressure: P = 176.52 kPa @ 180 °C
External design pressure: Pe = 102.97 kPa @ 180 °C
Static liquid head:
Design thickness, (at 180 °C) UG-27(c)(1)
Maximum allowable working pressure, (at 180 °C) UG-27(c)(1)
Maximum allowable pressure, (at 17 °C) UG-27(c)(1)
External Pressure, (Corroded & at 180 °C) UG-28(c)
Component: Cylinder
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Impact test exempt per UHA-51(g)(coincident ratio = 0.0832)
Ps = 0 kPa (SG = 1.1, Hs = 0 mm,Operating head)
Pth = 8.9 kPa (SG = 1, Hs = 908.22 mm, Horizontal test head)
Ptv = 140.32 kPa (SG = 1, Hs = 14,321 mm, Vertical test head)
Corrosion allowance Inner C = 0 mm Outer C = 0 mm
Design MDMT = -10 °C No impact test performed
Rated MDMT = -196 °C Material is not normalized
Material is not produced to Fine Grain Practice
PWHT is not performed
Radiography: Longitudinal joint - Spot UW-11(b) Type 1
Top circumferential joint - N/A
Bottom circumferential joint - N/A
Estimated weight New = 922.3 kg corr = 922.3 kg
Capacity New = 3,727.6 liters corr = 3,727.6 liters
ID = 780 mm
Length Lc = 7,801 mm
t = 6 mm
Insulation thk: 50 mm density: 200 kg/m3 Weight: 206.4 kg
Insulation Support
Spacing:1,000 mm
Individual Support
Weight:10 kg
Total Support
Weight:70 kg
t = P*R / (S*E - 0.60*P) + Corrosion
= 176.52*390 / (128,000*0.85 - 0.60*176.52) + 0
= 0.64 mm
P = S*E*t / (R + 0.60*t) - Ps
= 128,000*0.85*6 / (390 + 0.60*6) - 0
= 1,658.54 kPa
P = S*E*t / (R + 0.60*t)
= 138,000*0.85*6 / (390 + 0.60*6)
= 1,788.11 kPa
ITEM NO.: C-6211 33
Design thickness for external pressure Pa = 102.97 kPa
Maximum Allowable External Pressure, (Corroded & at 180 °C) UG-28(c)
% Forming strain - UHA-44(a)(2)(a)
External Pressure + Weight + Wind Loading Check (Bergman, ASME paper 54-A-104)
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
External Pressure + Weight + Wind Loading Check at Bottom Seam (Bergman, ASME paper 54-A-104)
L / Do = 3,920 / 792 = 4.9495
Do / t = 792 / 5.22 = 151.7683
From table G: A = 0.000132
From table HA-1 Metric: B = 11.7207 MPa
Pa = 4*B / (3*(Do / t))
= 4*11,720.72 / (3*(792 / 5.22))
= 102.97 kPa
ta = t + Corrosion = 5.22 + 0 = 5.22 mm
L / Do = 3,920 / 792 = 4.9495
Do / t = 792 / 6 = 132.0000
From table G: A = 0.000163
From table HA-1 Metric: B = 14.504 MPa
Pa = 4*B / (3*(Do / t))
= 4*14,503.99 / (3*(792 / 6))
= 146.5 kPa
EFE = (50*t / Rf)*(1 - Rf / Ro)
= (50*6 / 393)*(1 - 393 / infinity)
= 0.7634%
Pv = W / (2**Rm) + M / (*Rm2)
= 98.03*4,042.5 / (2**393) + 10000*67,470.5 / (*3932)
= 1551.0708 N/cm
= Pv / (Pe*Do)
= 100*1551.0708 / (102.97*792)
= 1.9019
n = 3
m = 1.23 / (L / Do)2
= 1.23 / (3,920 / 792)2
= 0.0502
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (32 - 1 + 0.0502 + 0.0502*1.9019) / (32 - 1 + 0.0502)
= 1.0119
Pv = 0.6*W / (2**Rm) + M / (*Rm2)
ITEM NO.: C-6211 34
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
External Pressure + Weight + Seismic Loading Check (Bergman, ASME paper 54-A-104)
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
External Pressure + Weight + Seismic Loading Check at Bottom Seam(Bergman, ASME paper 54-A-104)
= 0.60*98.03*-6,877 / (2**393) + 10000*66,753.4 / (*3932)
= 1211.8765 N/cm
= Pv / (Pe*Do)
= 100*1211.8765 / (102.97*792)
= 1.4860
n = 3
m = 1.23 / (L / Do)2
= 1.23 / (3,920 / 792)2
= 0.0502
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (32 - 1 + 0.0502 + 0.0502*1.4860) / (32 - 1 + 0.0502)
= 1.0093
Pv = (1 + VAccel)*W / (2**Rm) + M / (*Rm2)
= 1.20*98.03*4,042.5 / (2**393) + 10000*85,919.3 / (*3932)
= 1963.3987 N/cm
= Pv / (Pe*Do)
= 100*1963.3987 / (102.97*792)
= 2.4075
n = 3
m = 1.23 / (L / Do)2
= 1.23 / (3,920 / 792)2
= 0.0502
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (32 - 1 + 0.0502 + 0.0502*2.4075) / (32 - 1 + 0.0502)
= 1.0150
Pv = W / (2**Rm) + M / (*Rm2)
= 98.03*-6,877 / (2**393) + 10000*113,230.1 / (*3932)
= 2060.4854 N/cm
= Pv / (Pe*Do)
= 100*2060.4854 / (102.97*792)
= 2.5266
n = 3
m = 1.23 / (L / Do)2
= 1.23 / (3,920 / 792)2
= 0.0502
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
ITEM NO.: C-6211 35
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
Design thickness = 5.22 mm
The governing condition is due to external pressure.
The cylinder thickness of 6 mm is adequate.
Thickness Required Due to Pressure + External Loads
= (32 - 1 + 0.0502 + 0.0502*2.5266) / (32 - 1 + 0.0502)
= 1.0158
ConditionPressure
P ( kPa)
Allowable Stress
Before UG-23 Stress
Increase ( MPa)Temperature
( °C)
Corrosion
C (mm)Location Load
Req'd Thk
Due to
Tension
(mm)
Req'd Thk Due to
Compression
(mm)St Sc
Operating, Hot &
Corroded176.52 128 58.52 180 0
TopWind 1.07 1.72
Seismic 1.27 2.31
BottomWind 1.3 1.24
Seismic 1.96 2.44
Operating, Hot &
New176.52 128 58.52 180 0
TopWind 1.07 1.72
Seismic 1.27 2.31
BottomWind 1.3 1.24
Seismic 1.96 2.44
Hot Shut Down,
Corroded0 128 58.52 180 0
TopWind 0.84 2.21
Seismic 1.05 2.8
BottomWind 1.07 1.73
Seismic 1.73 2.93
Hot Shut Down, New 0 128 58.52 180 0
TopWind 0.84 2.21
Seismic 1.05 2.8
BottomWind 1.07 1.73
Seismic 1.73 2.93
Empty, Corroded 0 138 78.09 21.11 0
TopWind 0.78 1.65
Seismic 1.05 2.22
BottomWind 0.96 1.33
Seismic 0.97 1.21
Empty, New 0 138 78.09 21.11 0
TopWind 0.78 1.65
Seismic 1.05 2.22
BottomWind 0.96 1.33
Seismic 0.97 1.21
Vacuum -102.97 128 58.52 180 0
TopWind 0.71 2.49
Seismic 0.92 3.08
BottomWind 0.94 2.01
Seismic 1.6 3.22
ITEM NO.: C-6211 36
Hot Shut Down,
Corroded, Weight &
Eccentric Moments
Only
0 128 58.52 180 0
Top Weight 0.27 0.28
Bottom Weight 0.22 0.21
Operating, Hot & Corroded, Vortex
Shedding
176.52 128 58.52 180 0Top Wind 0.58 0.66
Bottom Wind 0.84 0.24
Empty, Cold &
Corroded, Vortex
Shedding
0 138 78.09 21.11 0Top Wind 0.4 0.98
Bottom Wind 0.54 0.58
Vacuum, Vortex
Shedding-102.97 128 58.52 180 0
Top Wind 0.23 1.44
Bottom Wind 0.49 1.01
ITEM NO.: C-6211 37
Shell #4
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Internal design pressure: P = 176.52 kPa @ 180 °C
External design pressure: Pe = 102.97 kPa @ 180 °C
Static liquid head:
Design thickness, (at 180 °C) UG-27(c)(1)
Maximum allowable working pressure, (at 180 °C) UG-27(c)(1)
Maximum allowable pressure, (at 17 °C) UG-27(c)(1)
External Pressure, (Corroded & at 180 °C) UG-28(c)
Component: Cylinder
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Impact test exempt per UHA-51(g)(coincident ratio = 0.0832)
Ps = 0 kPa (SG = 1.1, Hs = 0 mm,Operating head)
Pth = 8.9 kPa (SG = 1, Hs = 908.22 mm, Horizontal test head)
Ptv = 160.6 kPa (SG = 1, Hs = 16,390 mm, Vertical test head)
Corrosion allowance Inner C = 0 mm Outer C = 0 mm
Design MDMT = -10 °C No impact test performed
Rated MDMT = -196 °C Material is not normalized
Material is not produced to Fine Grain Practice
PWHT is not performed
Radiography: Longitudinal joint - Spot UW-11(b) Type 1
Top circumferential joint - N/A
Bottom circumferential joint - Spot UW-11(b) Type 1
Estimated weight New = 241.4 kg corr = 241.4 kg
Capacity New = 978.61 liters corr = 978.61 liters
ID = 780 mm
Length Lc = 2,048 mm
t = 6 mm
Insulation thk: 50 mm density: 200 kg/m3 Weight: 54.2 kg
Insulation Support
Spacing:1,000 mm
Individual Support
Weight:10 kg
Total Support
Weight:20 kg
t = P*R / (S*E - 0.60*P) + Corrosion
= 176.52*390 / (128,000*0.85 - 0.60*176.52) + 0
= 0.64 mm
P = S*E*t / (R + 0.60*t) - Ps
= 128,000*0.85*6 / (390 + 0.60*6) - 0
= 1,658.54 kPa
P = S*E*t / (R + 0.60*t)
= 138,000*0.85*6 / (390 + 0.60*6)
= 1,788.11 kPa
ITEM NO.: C-6211 38
Design thickness for external pressure Pa = 102.97 kPa
Maximum Allowable External Pressure, (Corroded & at 180 °C) UG-28(c)
% Forming strain - UHA-44(a)(2)(a)
External Pressure + Weight + Wind Loading Check (Bergman, ASME paper 54-A-104)
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
External Pressure + Weight + Seismic Loading Check (Bergman, ASME paper 54-A-104)
L / Do = 4,142 / 792 = 5.2298
Do / t = 792 / 5.35 = 148.0792
From table G: A = 0.000128
From table HA-1 Metric: B = 11.4358 MPa
Pa = 4*B / (3*(Do / t))
= 4*11,435.83 / (3*(792 / 5.35))
= 102.97 kPa
ta = t + Corrosion = 5.35 + 0 = 5.35 mm
L / Do = 4,142 / 792 = 5.2298
Do / t = 792 / 6 = 132.0000
From table G: A = 0.000153
From table HA-1 Metric: B = 13.6512 MPa
Pa = 4*B / (3*(Do / t))
= 4*13,651.17 / (3*(792 / 6))
= 137.89 kPa
EFE = (50*t / Rf)*(1 - Rf / Ro)
= (50*6 / 393)*(1 - 393 / infinity)
= 0.7634%
Pv = 0.6*W / (2**Rm) + M / (*Rm2)
= 0.60*98.03*-2,343.8 / (2**393) + 10000*12,948 / (*3932)
= 211.0014 N/cm
= Pv / (Pe*Do)
= 100*211.0014 / (102.97*792)
= 0.2587
n = 3
m = 1.23 / (L / Do)2
= 1.23 / (4,142 / 792)2
= 0.0450
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (32 - 1 + 0.0450 + 0.0450*0.2587) / (32 - 1 + 0.0450)
= 1.0014
Pv = W / (2**Rm) + M / (*Rm2)
ITEM NO.: C-6211 39
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
Design thickness = 5.35 mm
The governing condition is due to external pressure.
The cylinder thickness of 6 mm is adequate.
Thickness Required Due to Pressure + External Loads
= 98.03*-2,343.8 / (2**393) + 10000*31,417.5 / (*3932)
= 554.4130 N/cm
= Pv / (Pe*Do)
= 100*554.4130 / (102.97*792)
= 0.6798
n = 3
m = 1.23 / (L / Do)2
= 1.23 / (4,142 / 792)2
= 0.0450
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (32 - 1 + 0.0450 + 0.0450*0.6798) / (32 - 1 + 0.0450)
= 1.0038
ConditionPressure P
( kPa)
Allowable Stress Before UG-23 Stress
Increase ( MPa)Temperature
( °C)
Corrosion C
(mm)Load
Req'd Thk
Due to
Tension (mm)
Req'd Thk Due to
Compression (mm)
St Sc
Operating, Hot & Corroded
176.52 128 58.52 180 0Wind 0.46 0.09
Seismic 0.72 0.3
Operating, Hot & New 176.52 128 58.52 180 0Wind 0.46 0.09
Seismic 0.72 0.3
Hot Shut Down,
Corroded0 128 58.52 180 0
Wind 0.23 0.3
Seismic 0.49 0.79
Hot Shut Down, New 0 128 58.52 180 0Wind 0.23 0.3
Seismic 0.49 0.79
Empty, Corroded 0 138 78.09 21.11 0Wind 0.19 0.25
Seismic 0.2 0.23
Empty, New 0 138 78.09 21.11 0Wind 0.19 0.25
Seismic 0.2 0.23
Vacuum -102.97 128 58.52 180 0Wind 0.1 0.59
Seismic 0.36 1.08
Hot Shut Down,
Corroded, Weight &
Eccentric Moments Only
0 128 58.52 180 0 Weight 0.08 0.07
Operating, Hot & Corroded, Vortex
Shedding
176.52 128 58.52 180 0 Wind 0.37 0.17
ITEM NO.: C-6211 40
Empty, Cold &
Corroded, Vortex
Shedding
0 138 78.09 21.11 0 Wind 0.11 0.12
Vacuum, Vortex
Shedding-102.97 128 58.52 180 0 Wind 0.02 0.4
ITEM NO.: C-6211 41
Shell #5
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Internal design pressure: P = 176.52 kPa @ 180 °C
External design pressure: Pe = 102.97 kPa @ 180 °C
Static liquid head:
Design thickness, (at 180 °C) UG-27(c)(1)
Maximum allowable working pressure, (at 180 °C) UG-27(c)(1)
Maximum allowable pressure, (at 17 °C) UG-27(c)(1)
External Pressure, (Corroded & at 180 °C) UG-28(c)
Component: Cylinder
Material specification: SA-240 316 (II-D Metric p. 70, ln. 25)
Impact test exempt per UHA-51(g)(coincident ratio = 0.0929)
Ps = 20.48 kPa (SG = 1.1, Hs = 1,900 mm,Operating head)
Pth = 8.9 kPa (SG = 1, Hs = 908.22 mm, Horizontal test head)
Ptv = 180.19 kPa (SG = 1, Hs = 18,390 mm, Vertical test head)
Corrosion allowance Inner C = 0 mm Outer C = 0 mm
Design MDMT = -10 °C No impact test performed
Rated MDMT = -196 °C Material is not normalized
Material is not produced to Fine Grain Practice
PWHT is not performed
Radiography: Longitudinal joint - Spot UW-11(b) Type 1
Top circumferential joint - Spot UW-11(b) Type 1
Bottom circumferential joint - Spot UW-11(a)(5)(b) Type 1
Estimated weight New = 229.4 kg corr = 229.4 kg
Capacity New = 955.67 liters corr = 955.67 liters
ID = 780 mm
Length Lc = 2,000 mm
t = 6 mm
Insulation thk: 50 mm density: 200 kg/m3 Weight: 52.9 kg
Insulation Support
Spacing:1,000 mm
Individual Support
Weight:10 kg
Total Support
Weight:20 kg
t = P*R / (S*E - 0.60*P) + Corrosion
= 197*390 / (136,000*0.85 - 0.60*197) + 0
= 0.67 mm
P = S*E*t / (R + 0.60*t) - Ps
= 136,000*0.85*6 / (390 + 0.60*6) - 20.48
= 1,741.72 kPa
P = S*E*t / (R + 0.60*t)
= 138,000*0.85*6 / (390 + 0.60*6)
= 1,788.11 kPa
ITEM NO.: C-6211 42
Design thickness for external pressure Pa = 102.97 kPa
Maximum Allowable External Pressure, (Corroded & at 180 °C) UG-28(c)
% Forming strain - UHA-44(a)(2)(a)
External Pressure + Weight + Wind Loading Check (Bergman, ASME paper 54-A-104)
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
External Pressure + Weight + Seismic Loading Check (Bergman, ASME paper 54-A-104)
L / Do = 4,142 / 792 = 5.2298
Do / t = 792 / 5.36 = 147.7742
From table G: A = 0.000129
From table HA-2 Metric: B = 11.4123 MPa
Pa = 4*B / (3*(Do / t))
= 4*11,412.27 / (3*(792 / 5.36))
= 102.97 kPa
ta = t + Corrosion = 5.36 + 0 = 5.36 mm
L / Do = 4,142 / 792 = 5.2298
Do / t = 792 / 6 = 132.0000
From table G: A = 0.000153
From table HA-2 Metric: B = 13.5789 MPa
Pa = 4*B / (3*(Do / t))
= 4*13,578.88 / (3*(792 / 6))
= 137.16 kPa
EFE = (50*t / Rf)*(1 - Rf / Ro)
= (50*6 / 393)*(1 - 393 / infinity)
= 0.7634%
Pv = 0.6*W / (2**Rm) + M / (*Rm2)
= 0.60*98.03*-2,030.8 / (2**393) + 10000*3,463.7 / (*3932)
= 22.9926 N/cm
= Pv / (Pe*Do)
= 100*22.9926 / (102.97*792)
= 0.0282
n = 3
m = 1.23 / (L / Do)2
= 1.23 / (4,142 / 792)2
= 0.0450
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (32 - 1 + 0.0450 + 0.0450*0.0282) / (32 - 1 + 0.0450)
= 1.0002
Pv = W / (2**Rm) + M / (*Rm2)
ITEM NO.: C-6211 43
Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.
Design thickness = 5.36 mm
The governing condition is due to external pressure.
The cylinder thickness of 6 mm is adequate.
Thickness Required Due to Pressure + External Loads
= 98.03*-2,030.8 / (2**393) + 10000*9,645.1 / (*3932)
= 118.1270 N/cm
= Pv / (Pe*Do)
= 100*118.1270 / (102.97*792)
= 0.1448
n = 3
m = 1.23 / (L / Do)2
= 1.23 / (4,142 / 792)2
= 0.0450
Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m)
= (32 - 1 + 0.0450 + 0.0450*0.1448) / (32 - 1 + 0.0450)
= 1.0008
ConditionPressure P
( kPa)
Allowable Stress Before UG-23 Stress
Increase ( MPa)Temperature
( °C)
Corrosion C
(mm)Load
Req'd Thk
Due to
Tension (mm)
Req'd Thk Due to
Compression (mm)
St Sc
Operating, Hot & Corroded
176.52 136 72.08 180 0Wind 0.36 0.23
Seismic 0.46 0.16
Operating, Hot & New 176.52 136 72.08 180 0Wind 0.36 0.23
Seismic 0.46 0.16
Hot Shut Down,
Corroded0 136 72.08 180 0
Wind 0.11 0.03
Seismic 0.21 0.14
Hot Shut Down, New 0 136 72.08 180 0Wind 0.11 0.03
Seismic 0.21 0.14
Empty, Corroded 0 138 79.89 21.11 0Wind 0.08 0.05
Seismic 0.07 0.03
Empty, New 0 138 79.89 21.11 0Wind 0.08 0.05
Seismic 0.07 0.03
Vacuum -102.97 136 72.08 180 0Wind 0.06 0.26
Seismic 0.07 0.37
Hot Shut Down,
Corroded, Weight &
Eccentric Moments Only
0 136 72.08 180 0 Weight 0.07 0.07
Operating, Hot & Corroded, Vortex
Shedding
176.52 136 72.08 180 0 Wind 0.33 0.26
ITEM NO.: C-6211 44
Empty, Cold &
Corroded, Vortex
Shedding
0 138 79.89 21.11 0 Wind 0.05 0.02
Vacuum, Vortex
Shedding-102.97 136 72.08 180 0 Wind 0.09 0.22
ITEM NO.: C-6211 45
Straight Flange on Ellipsoidal Head (Bottom)
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Internal design pressure: P = 176.52 kPa @ 180 °C
External design pressure: Pe = 102.97 kPa @ 180 °C
Static liquid head:
Design thickness, (at 180 °C) UG-27(c)(1)
Maximum allowable working pressure, (at 180 °C) UG-27(c)(1)
Maximum allowable pressure, (at 17 °C) UG-27(c)(1)
External Pressure, (Corroded & at 180 °C) UG-28(c)
Component: Straight Flange
Material specification: SA-240 316 (II-D Metric p. 70, ln. 25)
Impact test exempt per UHA-51(g)(coincident ratio = 0.093)
Ps = 20.69 kPa (SG = 1.1, Hs = 1,920 mm,Operating head)
Pth = 8.9 kPa (SG = 1, Hs = 908.22 mm, Horizontal test head)
Ptv = 180.39 kPa (SG = 1, Hs = 18,410 mm, Vertical test head)
Corrosion allowance Inner C = 0 mm Outer C = 0 mm
Design MDMT = -10 °C No impact test performed
Rated MDMT = -196 °C Material is not normalized
Material is not produced to Fine Grain Practice
PWHT is not performed
Radiography: Longitudinal joint - Seamless No RT
Circumferential joint - Spot UW-11(a)(5)(b) Type 1
Estimated weight New = 2.4 kg corr = 2.4 kg
Capacity New = 9.56 liters corr = 9.56 liters
ID = 780 mm
Length Lc = 20 mm
t = 6 mm
Insulation thk: 50 mm density: 200 kg/m3 Weight: 0 kg
t = P*R / (S*E - 0.60*P) + Corrosion
= 197.21*390 / (136,000*1.00 - 0.60*197.21) + 0
= 0.57 mm
P = S*E*t / (R + 0.60*t) - Ps
= 136,000*1.00*6 / (390 + 0.60*6) - 20.69
= 2,052.48 kPa
P = S*E*t / (R + 0.60*t)
= 138,000*1.00*6 / (390 + 0.60*6)
= 2,103.66 kPa
L / Do = 4,142 / 792 = 5.2298
ITEM NO.: C-6211 46
Design thickness for external pressure Pa = 102.97 kPa
Maximum Allowable External Pressure, (Corroded & at 180 °C) UG-28(c)
% Forming strain - UHA-44(a)(2)(a)
Design thickness = 5.36 mm
The governing condition is due to external pressure.
The cylinder thickness of 6 mm is adequate.
Thickness Required Due to Pressure + External Loads
Do / t = 792 / 5.36 = 147.7742
From table G: A = 0.000129
From table HA-2 Metric: B = 11.4123 MPa
Pa = 4*B / (3*(Do / t))
= 4*11,412.27 / (3*(792 / 5.36))
= 102.97 kPa
ta = t + Corrosion = 5.36 + 0 = 5.36 mm
L / Do = 4,142 / 792 = 5.2298
Do / t = 792 / 6 = 132.0000
From table G: A = 0.000153
From table HA-2 Metric: B = 13.5789 MPa
Pa = 4*B / (3*(Do / t))
= 4*13,578.88 / (3*(792 / 6))
= 137.16 kPa
EFE = (50*t / Rf)*(1 - Rf / Ro)
= (50*6 / 393)*(1 - 393 / infinity)
= 0.7634%
ConditionPressure P
( kPa)
Allowable Stress Before UG-23 Stress
Increase ( MPa)Temperature
( °C)
Corrosion C
(mm)Load
Req'd Thk
Due to
Tension (mm)
Req'd Thk Due to
Compression (mm)
St Sc
Operating, Hot & Corroded
176.52 136 72.08 180 0Wind 0.28 0.27
Seismic 0.29 0.28
Operating, Hot & New 176.52 136 72.08 180 0Wind 0.28 0.27
Seismic 0.29 0.28
Hot Shut Down,
Corroded0 136 72.08 180 0
Wind 0.03 0.02
Seismic 0.04 0.03
Hot Shut Down, New 0 136 72.08 180 0Wind 0.03 0.02
Seismic 0.04 0.03
Empty, Corroded 0 138 79.89 21.11 0Wind 0 0
Seismic 0 0
ITEM NO.: C-6211 47
Empty, New 0 138 79.89 21.11 0Wind 0 0
Seismic 0 0
Vacuum -102.97 136 72.08 180 0Wind 0.18 0.2
Seismic 0.17 0.18
Hot Shut Down,
Corroded, Weight &
Eccentric Moments Only
0 136 72.08 180 0 Weight 0.04 0.04
Operating, Hot &
Corroded, Vortex
Shedding
176.52 136 72.08 180 0 Wind 0.28 0.27
Empty, Cold &
Corroded, Vortex
Shedding
0 138 79.89 21.11 0 Wind 0 0
Vacuum, Vortex Shedding
-102.97 136 72.08 180 0 Wind 0.18 0.2
ITEM NO.: C-6211 48
Ellipsoidal Head (Bottom)
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Straight Flange governs MDMT
Internal design pressure: P = 176.52 kPa @ 180 °C
External design pressure: Pe = 102.97 kPa @ 180 °C
Static liquid head:
Ps= 22.8 kPa (SG=1.1, Hs=2115 mm Operating head)
Pth= 8.9 kPa (SG=1, Hs=908.22 mm Horizontal test head)
Ptv= 182.3 kPa (SG=1, Hs=18605 mm Vertical test head)
* includes straight flange
* includes straight flange if applicable
Results Summary
Design thickness for internal pressure, (Corroded at 180 °C) UG-32(d)(1)
Component: Ellipsoidal Head
Material Specification: SA-240 316 (II-D Metric p.70, ln. 25)
Corrosion allowance: Inner C = 0 mm Outer C = 0 mm
Design MDMT = -10°C No impact test performed
Rated MDMT = -196°C Material is not normalized
Material is not produced to fine grain practice
PWHT is not performed
Do not Optimize MDMT / Find MAWP
Radiography: Category A joints - Seamless No RT
Head to shell seam - Spot UW-11(a)(5)(b) Type 1
Estimated weight*: new = 30.7 kg corr = 30.7 kg
Capacity*: new = 71.7 liters corr = 71.7 liters
Inner diameter = 780 mm
Minimum head thickness = 5.1 mm
Head ratio D/2h = 2 (new)
Head ratio D/2h = 2 (corroded)
Straight flange length Lsf = 20 mm
Nominal straight flange thickness tsf = 6 mm
Insulation thk*: 50 mm density: 200 kg/m3 weight: 8.1984 kg
Insulation support ring
spacing: 0 mm individual weight: 0 kg total weight: 0 kg
The governing condition is UG-16.
Minimum thickness per UG-16 = 2.5 mm + 0 mm = 2.5 mm
Design thickness due to internal pressure (t) = 0.57 mm
Design thickness due to external pressure (te) = 2.14 mm
Maximum allowable working pressure (MAWP) = 1,753.34 kPa
Maximum allowable pressure (MAP) = 1,802.26 kPa
Maximum allowable external pressure (MAEP) = 431.8 kPa
ITEM NO.: C-6211 49
The head internal pressure design thickness is 0.57 mm.
Maximum allowable working pressure, (Corroded at 180 °C) UG-32(d)(1)
The maximum allowable working pressure (MAWP) is 1,753.34 kPa.
Maximum allowable pressure, (New at 17 °C) UG-32(d)(1)
The maximum allowable pressure (MAP) is 1,802.26 kPa.
Design thickness for external pressure, (Corroded at 180 °C) UG-33(d)
Check the external pressure per UG-33(a)(1) UG-32(d)(1)
The head external pressure design thickness (te) is 2.13 mm.
Maximum Allowable External Pressure, (Corroded at 180 °C) UG-33(d)
t = P*D / (2*S*E - 0.2*P) + Corrosion
= 199.32*780 / (2*136,000*1 - 0.2*199.32) + 0
= 0.57 mm
P = 2*S*E*t / (D + 0.2*t) - Ps
= 2*136,000*1*5.1 / (780 +0.2*5.1) - 22.8
= 1,753.34 kPa
P = 2*S*E*t / (D + 0.2*t) - Ps
= 2*138,000*1*5.1 / (780 +0.2*5.1) - 0
= 1,802.26 kPa
Equivalent outside spherical radius (Ro)
Ro = Ko*Do
= 0.8885*790.2
= 702.12 mm
A = 0.125 / (Ro / t)
= 0.125 / (702.12 / 2.13)
= 0.00038
From Table HA-2 Metric:B = 33.8822 MPa
Pa = B / (Ro / t)
= 33,882.18 / (702.12 / 2.13)
= 102.9698 kPa
t = 2.13 mm + Corrosion = 2.13 mm + 0 mm = 2.13 mm
t = 1.67*Pe*D / (2*S*E - 0.2*1.67*Pe) + Corrosion
= 1.67*102.97*780 / (2*136,000*1 - 0.2*1.67*102.97) + 0
= 0.49 mm
Equivalent outside spherical radius (Ro)
Ro = Ko*Do
= 0.8885*790.2
= 702.12 mm
A = 0.125 / (Ro / t)
ITEM NO.: C-6211 50
Check the Maximum External Pressure, UG-33(a)(1) UG-32(d)(1)
The maximum allowable external pressure (MAEP) is 431.8 kPa.
% Forming strain - UHA-44(a)(2)(b)
= 0.125 / (702.12 / 5.1)
= 0.000908
From Table HA-2 Metric:B = 59.4461 MPa
Pa = B / (Ro / t)
= 59,446.1 / (702.12 / 5.1)
= 431.8014 kPa
P = 2*S*E*t / ((D + 0.2*t)*1.67) - Ps2
= 2*136,000*1*5.1 / ((780 +0.2*5.1)*1.67) - 0
= 1,063.56 kPa
EFE = (75*t / Rf)*(1 - Rf / Ro)
= (75*6 / 135.6)*(1 - 135.6 / infinity)
= 3.3186%
ITEM NO.: C-6211 51
Rings #1
Stiffener ring calculations per UG-29(a)
L / Do = 3,920 / 792 = 4.9495
Do / t = 792 / 5.22 = 151.7676
From Table HA-1 Metric: A = 0.00012957 (ring, 180°C)
I' for the composite corroded shell-ring cross section is 20.56 cm4
As I' >= Is' a 6tx50w stiffener is adequate for an external pressure of 102.97 kPa.
Check the stiffener ring attachment welds per UG-30
Per UG-30(f)(1) the minimum attachment weld size is 6 mm
The fillet weld size of 7 mm is adequate per UG-30(f)(1).
Ring type: Flat bar
Ring description: 6tx50w
Ring material: SA-240 304 (II-D Metric p. 86, ln. 25)
External pressure: 102.97 kPa
Ring is located: outside the vessel
Distance from ring neutral axis to datum: 8,000 mm
Ring corrosion allowance: 0 mm
Distance to previous support: 3,899 mm
Distance to next support: 3,920 mm
From Table G: A = 0.000132
From Table HA-1 Metric: B = 11.721 MPa
Pa = 4*B / (3*(Do / t))
= 4*11.721 / (3*(792 / 5.22))
= 0.103 MPa
B = 0.75*P*Do / (t + As / Ls)
= 0.75*102.97*792 / (5.22 + 300 / 3,909.5) / 1000
= 11.548 MPa
Is' = [Do2*Ls*(t + As / Ls)*A] / 10.9
= [7922*3,909.5*(5.22 + 300 / 3,909.5)*0.00012957] / 10.9 / 10000
= 15.44 cm4
Fillet weld is: Continuous both sides
Fillet weld leg size: 7 mm
Vessel thickness at weld location, new: 6 mm
Vessel corrosion allowance at weld location: 0 mm
Stiffener thickness at weld location: 6 mm
ITEM NO.: C-6211 52
Radial pressure load, P*Ls = 102.97*3,909.5 / 100 = 4,025.6 N/cm
Radial shear load, V = 0.01*P*Ls*Do = 0.01*102.97 / 1000*3,909.5*792 = 3,188.28 N
First moment of area, Q = 4.55*1.11 = 5.0621 cm3
Weld shear flow, q = V*Q / I' = 784.9762 N/cm
Combined weld load, fw = Sqr(4,025.60442 + 784.97622) = 4,101.42 N/cm
Allowable weld stress per UW-18(d) Sw = 0.55*S = 0.55*128 = 70.4 MPa
Fillet weld size required to resist radial pressure and shear
= fw*(dweld segment + dtoe) / (Sw*dweld total) + corrosion
= 4,101.42*(25.4 + 0) / (10*70.4*50.8) + 0
= 2.91 mm
The fillet weld size of 7 mm is adequate to resist radial pressure and shear.
ITEM NO.: C-6211 53
Flange #1
ASME VIII-1, 2010 Edition, A11 Addenda Metric, Appendix 2 Flange Calculations
Flange dimensions, new
Flange is attached to: Shell #1 (Bottom)
Flange type: Ring type loose
Flange material specification:SA-182 F304 <= 125 (low stress) (II-D Metric
p. 86, ln. 14)
Bolt material specification: SA-193 B8 1 Bolt (II-D Metric p. 342, ln. 20)
Bolt Description: 0.875 in Series 8 Thread
Internal design pressure, P: 176.52 kPa @ 180 °C
Required flange thickness, tr: 68.24 mm
Maximum allowable working pressure,
MAWP:857.56 kPa @ 180 °C (bolting limits)
Maximum allowable pressure, MAP: 910.42 kPa @ 17 °C
External design pressure, Pe 102.97 kPa @ 180 °C
Maximum allowable external pressure,
MAEP:2,575.23 kPa @ 180 °C
Corrosion allowance: Bore = 0 mm Flange = 0 mm
Bolt corrosion (root), Cbolt: 0 mm
Design MDMT: -10 °C No impact test performed
Rated MDMT: -196 °C Flange material is not normalized
Material is not produced to fine grain
practice
PWHT is not performed
Estimated weight: New = 115.53 kg corroded = 115.53 kg
flange OD A = 934 mm
bolt circle C = 886 mm
raised face OD Rf = 855 mm
gasket OD = 845 mm
gasket ID = 805 mm
flange ID B = 795 mm
facing height trf = 3 mm
thickness t = 75 mm
bolting = 28- 0.875 in dia
lower fillet weld h = 6 mm
upper fillet weld h1 = 6 mm
length e = 6 mm
gasket factor m = 2
seating stress y = 14.71 MPa
Gasket thickness T = 3 mm
gasket description PTFE
ITEM NO.: C-6211 54
Note: this flange is calculated as a loose type.
Flange calculations for Internal Pressure + Wind
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*1,290.5/(*829.193)
= 11.5287 kPa
Axial load on flange
Pr = -4*0.6*F/(*G2)
= -4*0.6*3,802.28/(*829.192)
= -4.2244 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 11.5287 + -4.2244
= 183.824 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.1838
= 99,215.86 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
ITEM NO.: C-6211 55
= 99,215.86 - 87,578.42
= 11,637.44 N
Wm1 = H + Hp
= 99,215.86 + 14,531.51
= 113,747.37 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = Wm1/Sb = 113,747.37/(100*98.4) = 11.5597 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 11,637.44*0.037 = 430 N-m
HG = Wm1 - H = 113,747.37 - 99,215.86 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
Mo = MD + MT + MG = 3,984.8 + 430 + 412.8 = 4,827.6 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*4,827.6/(752*795)
= 13.094 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*4,827.6/(184.2E+03*753*0.2*ln(1.1748))
= 0.2109
The flange rigidity index J does not exceed 1; satisfactory.
ITEM NO.: C-6211 56
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Wind per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*1,290.5/(*829.193)
= 11.5287 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*3,802.28/(*829.192)
= 7.0409 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 11.5287 + 7.0409
= 121.5395 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
ITEM NO.: C-6211 57
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.1215
= 65,598.85 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 65,598.85 - 51,087.41
= 14,511.44 N
Wm1 = H + Hp
= 65,598.85 + 8,476.71
= 74,075.57 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 2,422.21/(100*98.4) = 0.2462 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 14,511.44*(0.037 - 0.0284)
= 997.4 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*997.4/(752*795)
= 2.705 MPa
Allowable stress Sfo = 98.6 MPa
ITEM NO.: C-6211 58
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*997.4/(184.2E+03*753*0.2*ln(1.1748))
= 0.0436
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Seismic
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*1,222.6/(*829.193)
= 10.922 kPa
Axial load on flange
Pr = -4*F/(*G2)
= -4*3,802.28/(*829.192)
= -7.0409 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 10.922 + -7.0409
= 180.4007 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
Flange calculations for External Pressure + Seismic per VIII-1, Appendix 2-11
ITEM NO.: C-6211 59
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*1,222.6/(*829.193)
= 10.922 kPa
Axial load on flange
Pr = 4*(1 + VAccel)*F/(*G2)
= 4*(1 + 0.2)*3,802.28/(*829.192)
= 8.4495 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 10.922 + 8.4495
= 122.3413 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.1223
= 66,031.64 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 66,031.64 - 51,087.41
= 14,944.23 N
Wm1 = H + Hp
= 66,031.64 + 8,476.71
= 74,508.36 N
ITEM NO.: C-6211 60
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 1,334.47/(100*98.4) = 0.1356 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 14,944.23*(0.037 - 0.0284)
= 1,001.1 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*1,001.1/(752*795)
= 2.715 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*1,001.1/(184.2E+03*753*0.2*ln(1.1748))
= 0.0437
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
ITEM NO.: C-6211 61
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Vortex shedding
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*642.8/(*829.193)
= 5.7426 kPa
Axial load on flange
Pr = -4*0.6*F/(*G2)
= -4*0.6*3,802.28/(*829.192)
= -4.2244 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 5.7426 + -4.2244
= 178.0379 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
Flange calculations for External Pressure + Vortex shedding per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*642.8/(*829.193)
= 5.7426 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*3,802.28/(*829.192)
= 7.0409 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 5.7426 + 7.0409
= 115.7534 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
ITEM NO.: C-6211 62
Flange #2
ASME VIII-1, 2010 Edition, A11 Addenda Metric, Appendix 2 Flange Calculations
Flange dimensions, new
Flange is attached to: Shell #2 (Top)
Flange type: Ring type loose
Flange material specification:SA-182 F304 <= 125 (low stress) (II-D Metric
p. 86, ln. 14)
Bolt material specification: SA-193 B8 1 Bolt (II-D Metric p. 342, ln. 20)
Bolt Description: 0.875 in Series 8 Thread
Internal design pressure, P: 176.52 kPa @ 180 °C
Required flange thickness, tr: 68.24 mm
Maximum allowable working pressure,
MAWP:857.56 kPa @ 180 °C (bolting limits)
Maximum allowable pressure, MAP: 910.42 kPa @ 17 °C
External design pressure, Pe 102.97 kPa @ 180 °C
Maximum allowable external pressure,
MAEP:2,575.23 kPa @ 180 °C
Corrosion allowance: Bore = 0 mm Flange = 0 mm
Bolt corrosion (root), Cbolt: 0 mm
Design MDMT: -10 °C No impact test performed
Rated MDMT: -196 °C Flange material is not normalized
Material is not produced to fine grain
practice
PWHT is not performed
Estimated weight: New = 115.53 kg corroded = 115.53 kg
flange OD A = 934 mm
bolt circle C = 886 mm
raised face OD Rf = 855 mm
gasket OD = 845 mm
gasket ID = 805 mm
flange ID B = 795 mm
facing height trf = 3 mm
thickness t = 75 mm
bolting = 28- 0.875 in dia
lower fillet weld h = 6 mm
upper fillet weld h1 = 6 mm
length e = 6 mm
gasket factor m = 2
seating stress y = 14.71 MPa
Gasket thickness T = 3 mm
gasket description PTFE
ITEM NO.: C-6211 63
Note: this flange is calculated as a loose type.
Flange calculations for Internal Pressure + Wind
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*1,290.5/(*829.193)
= 11.5287 kPa
Axial load on flange
Pr = -4*0.6*F/(*G2)
= -4*0.6*3,802.28/(*829.192)
= -4.2244 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 11.5287 + -4.2244
= 183.824 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.1838
= 99,215.86 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
ITEM NO.: C-6211 64
= 99,215.86 - 87,578.42
= 11,637.44 N
Wm1 = H + Hp
= 99,215.86 + 14,531.51
= 113,747.37 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = Wm1/Sb = 113,747.37/(100*98.4) = 11.5597 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 11,637.44*0.037 = 430 N-m
HG = Wm1 - H = 113,747.37 - 99,215.86 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
Mo = MD + MT + MG = 3,984.8 + 430 + 412.8 = 4,827.6 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*4,827.6/(752*795)
= 13.094 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*4,827.6/(184.2E+03*753*0.2*ln(1.1748))
= 0.2109
The flange rigidity index J does not exceed 1; satisfactory.
ITEM NO.: C-6211 65
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Wind per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*1,290.5/(*829.193)
= 11.5287 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*3,802.28/(*829.192)
= 7.0409 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 11.5287 + 7.0409
= 121.5395 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
ITEM NO.: C-6211 66
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.1215
= 65,598.85 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 65,598.85 - 51,087.41
= 14,511.44 N
Wm1 = H + Hp
= 65,598.85 + 8,476.71
= 74,075.57 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 2,422.21/(100*98.4) = 0.2462 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 14,511.44*(0.037 - 0.0284)
= 997.4 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*997.4/(752*795)
= 2.705 MPa
Allowable stress Sfo = 98.6 MPa
ITEM NO.: C-6211 67
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*997.4/(184.2E+03*753*0.2*ln(1.1748))
= 0.0436
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Seismic
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*1,222.6/(*829.193)
= 10.922 kPa
Axial load on flange
Pr = -4*F/(*G2)
= -4*3,802.28/(*829.192)
= -7.0409 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 10.922 + -7.0409
= 180.4007 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
Flange calculations for External Pressure + Seismic per VIII-1, Appendix 2-11
ITEM NO.: C-6211 68
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*1,222.6/(*829.193)
= 10.922 kPa
Axial load on flange
Pr = 4*(1 + VAccel)*F/(*G2)
= 4*(1 + 0.2)*3,802.28/(*829.192)
= 8.4495 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 10.922 + 8.4495
= 122.3413 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.1223
= 66,031.64 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 66,031.64 - 51,087.41
= 14,944.23 N
Wm1 = H + Hp
= 66,031.64 + 8,476.71
= 74,508.36 N
ITEM NO.: C-6211 69
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 1,334.47/(100*98.4) = 0.1356 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 14,944.23*(0.037 - 0.0284)
= 1,001.1 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*1,001.1/(752*795)
= 2.715 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*1,001.1/(184.2E+03*753*0.2*ln(1.1748))
= 0.0437
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
ITEM NO.: C-6211 70
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Vortex shedding
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*642.8/(*829.193)
= 5.7426 kPa
Axial load on flange
Pr = -4*0.6*F/(*G2)
= -4*0.6*3,802.28/(*829.192)
= -4.2244 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 5.7426 + -4.2244
= 178.0379 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
Flange calculations for External Pressure + Vortex shedding per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*642.8/(*829.193)
= 5.7426 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*3,802.28/(*829.192)
= 7.0409 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 5.7426 + 7.0409
= 115.7534 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
ITEM NO.: C-6211 71
Flange #3
ASME VIII-1, 2010 Edition, A11 Addenda Metric, Appendix 2 Flange Calculations
Flange dimensions, new
Flange is attached to: Shell #2 (Bottom)
Flange type: Ring type loose
Flange material specification:SA-182 F304 <= 125 (low stress) (II-D Metric
p. 86, ln. 14)
Bolt material specification: SA-193 B8 1 Bolt (II-D Metric p. 342, ln. 20)
Bolt Description: 0.875 in Coarse Thread
Internal design pressure, P: 176.52 kPa @ 180 °C
Required flange thickness, tr: 70.13 mm
Maximum allowable working pressure,
MAWP:555.61 kPa @ 180 °C (bolting limits)
Maximum allowable pressure, MAP: 712.73 kPa @ 17 °C
External design pressure, Pe 102.97 kPa @ 180 °C
Maximum allowable external pressure,
MAEP:2,314.39 kPa @ 180 °C
Corrosion allowance: Bore = 0 mm Flange = 0 mm
Bolt corrosion (root), Cbolt: 0 mm
Design MDMT: -10 °C No impact test performed
Rated MDMT: -196 °C Flange material is not normalized
Material is not produced to fine grain
practice
PWHT is not performed
Estimated weight: New = 115.53 kg corroded = 115.53 kg
flange OD A = 934 mm
bolt circle C = 886 mm
raised face OD Rf = 855 mm
gasket OD = 845 mm
gasket ID = 805 mm
flange ID B = 795 mm
facing height trf = 3 mm
thickness t = 75 mm
bolting = 28- 0.875 in dia
lower fillet weld h = 6 mm
upper fillet weld h1 = 6 mm
length e = 6 mm
gasket factor m = 2
seating stress y = 14.71 MPa
Gasket thickness T = 3 mm
gasket description PTFE
ITEM NO.: C-6211 72
Note: this flange is calculated as a loose type.
Flange calculations for Internal Pressure + Wind
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*34,472.5/(*829.193)
= 307.9495 kPa
Axial load on flange
Pr = -4*0.6*F/(*G2)
= -4*0.6*35,461.53/(*829.192)
= -39.4015 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 307.9495 + -39.4015
= 445.0677 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.4451
= 240,217.7 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
ITEM NO.: C-6211 73
= 240,217.7 - 87,578.42
= 152,639.28 N
Wm1 = H + Hp
= 240,217.7 + 14,531.51
= 254,749.21 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 25.8891 cm2
Am1 = Wm1/Sb = 254,749.21/(100*98.4) = 25.8891 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (2,588.9144 + 7,569.0171)*130/2
= 660,265.63 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 152,639.28*0.037 = 5,640.4 N-m
HG = Wm1 - H = 254,749.21 - 240,217.7 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
Mo = MD + MT + MG = 3,984.8 + 5,640.4 + 412.8 = 10,037.9 N-m
Mg = W*hG = 660,265.63*0.0284 = 18,754.5 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*10,037.9/(752*795)
= 27.225 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*10,037.9/(184.2E+03*753*0.2*ln(1.1748))
= 0.4385
The flange rigidity index J does not exceed 1; satisfactory.
ITEM NO.: C-6211 74
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,754.5/(752*795)
= 50.866 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,754.5/(195.23E+03*753*0.2*ln(1.1748))
= 0.773
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Wind per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*34,472.5/(*829.193)
= 307.9495 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*35,461.53/(*829.192)
= 65.6684 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 307.9495 + 65.6684
= 476.5877 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
ITEM NO.: C-6211 75
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.4766
= 257,230.09 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 257,230.09 - 51,087.41
= 206,142.68 N
Wm1 = H + Hp
= 257,230.09 + 8,476.71
= 265,706.81 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 130,767.07/(100*98.4) = 13.2893 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 206,142.68*(0.037 - 0.0284)
= 2,635.4 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*2,635.4/(752*795)
= 7.148 MPa
Allowable stress Sfo = 98.6 MPa
ITEM NO.: C-6211 76
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*2,635.4/(184.2E+03*753*0.2*ln(1.1748))
= 0.1151
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Seismic
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*49,388.7/(*829.193)
= 441.1983 kPa
Axial load on flange
Pr = -4*F/(*G2)
= -4*35,461.53/(*829.192)
= -65.6684 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 441.1983 + -65.6684
= 552.0495 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
ITEM NO.: C-6211 77
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.5521
= 297,959.31 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
= 297,959.31 - 87,578.42
= 210,380.88 N
Wm1 = H + Hp
= 297,959.31 + 14,531.51
= 312,490.82 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 31.7572 cm2
Am1 = Wm1/Sb = 312,490.82/(100*98.4) = 31.7572 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (3,175.7193 + 7,569.0171)*130/2
= 698,407.95 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 210,380.88*0.037 = 7,774 N-m
HG = Wm1 - H = 312,490.82 - 297,959.31 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
ITEM NO.: C-6211 78
Mo = MD + MT + MG = 3,984.8 + 7,774 + 412.8 = 12,171.6 N-m
Mg = W*hG = 698,407.95*0.0284 = 19,837.9 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*12,171.6/(752*795)
= 33.012 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*12,171.6/(184.2E+03*753*0.2*ln(1.1748))
= 0.5317
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*19,837.9/(752*795)
= 53.805 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*19,837.9/(195.23E+03*753*0.2*ln(1.1748))
= 0.8176
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Seismic per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*49,388.7/(*829.193)
= 441.1983 kPa
Axial load on flange
Pr = 4*(1 + VAccel)*F/(*G2)
ITEM NO.: C-6211 79
= 4*(1 + 0.2)*35,461.53/(*829.192)
= 78.8022 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 441.1983 + 78.8022
= 622.9703 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.623
= 336,237.6 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 336,237.6 - 51,087.41
= 285,150.18 N
Wm1 = H + Hp
= 336,237.6 + 8,476.71
= 344,714.31 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 195,597.06/(100*98.4) = 19.8777 cm2
ITEM NO.: C-6211 80
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 285,150.18*(0.037 - 0.0284)
= 3,310.8 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*3,310.8/(752*795)
= 8.98 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*3,310.8/(184.2E+03*753*0.2*ln(1.1748))
= 0.1446
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Vortex shedding
ITEM NO.: C-6211 81
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*16,481.4/(*829.193)
= 147.2313 kPa
Axial load on flange
Pr = -4*0.6*F/(*G2)
= -4*0.6*35,461.53/(*829.192)
= -39.4015 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 147.2313 + -39.4015
= 284.3496 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
Flange calculations for External Pressure + Vortex shedding per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*16,481.4/(*829.193)
= 147.2313 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*35,461.53/(*829.192)
= 65.6684 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 147.2313 + 65.6684
= 315.8696 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
ITEM NO.: C-6211 82
Flange #4
ASME VIII-1, 2010 Edition, A11 Addenda Metric, Appendix 2 Flange Calculations
Flange dimensions, new
Flange is attached to: Shell #3 (Top)
Flange type: Ring type loose
Flange material specification:SA-182 F304 <= 125 (low stress) (II-D Metric
p. 86, ln. 14)
Bolt material specification: SA-193 B8 1 Bolt (II-D Metric p. 342, ln. 20)
Bolt Description: 0.875 in Coarse Thread
Internal design pressure, P: 176.52 kPa @ 180 °C
Required flange thickness, tr: 70.13 mm
Maximum allowable working pressure,
MAWP:555.61 kPa @ 180 °C (bolting limits)
Maximum allowable pressure, MAP: 712.73 kPa @ 17 °C
External design pressure, Pe 102.97 kPa @ 180 °C
Maximum allowable external pressure,
MAEP:2,314.39 kPa @ 180 °C
Corrosion allowance: Bore = 0 mm Flange = 0 mm
Bolt corrosion (root), Cbolt: 0 mm
Design MDMT: -10 °C No impact test performed
Rated MDMT: -196 °C Flange material is not normalized
Material is not produced to fine grain
practice
PWHT is not performed
Estimated weight: New = 115.53 kg corroded = 115.53 kg
flange OD A = 934 mm
bolt circle C = 886 mm
raised face OD Rf = 855 mm
gasket OD = 845 mm
gasket ID = 805 mm
flange ID B = 795 mm
facing height trf = 3 mm
thickness t = 75 mm
bolting = 28- 0.875 in dia
lower fillet weld h = 6 mm
upper fillet weld h1 = 6 mm
length e = 6 mm
gasket factor m = 2
seating stress y = 14.71 MPa
Gasket thickness T = 3 mm
gasket description PTFE
ITEM NO.: C-6211 83
Note: this flange is calculated as a loose type.
Flange calculations for Internal Pressure + Wind
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*34,472.5/(*829.193)
= 307.9495 kPa
Axial load on flange
Pr = -4*0.6*F/(*G2)
= -4*0.6*35,461.53/(*829.192)
= -39.4015 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 307.9495 + -39.4015
= 445.0677 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.4451
= 240,217.7 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
ITEM NO.: C-6211 84
= 240,217.7 - 87,578.42
= 152,639.28 N
Wm1 = H + Hp
= 240,217.7 + 14,531.51
= 254,749.21 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 25.8891 cm2
Am1 = Wm1/Sb = 254,749.21/(100*98.4) = 25.8891 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (2,588.9144 + 7,569.0171)*130/2
= 660,265.63 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 152,639.28*0.037 = 5,640.4 N-m
HG = Wm1 - H = 254,749.21 - 240,217.7 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
Mo = MD + MT + MG = 3,984.8 + 5,640.4 + 412.8 = 10,037.9 N-m
Mg = W*hG = 660,265.63*0.0284 = 18,754.5 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*10,037.9/(752*795)
= 27.225 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*10,037.9/(184.2E+03*753*0.2*ln(1.1748))
= 0.4385
The flange rigidity index J does not exceed 1; satisfactory.
ITEM NO.: C-6211 85
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,754.5/(752*795)
= 50.866 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,754.5/(195.23E+03*753*0.2*ln(1.1748))
= 0.773
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Wind per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*34,472.5/(*829.193)
= 307.9495 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*35,461.53/(*829.192)
= 65.6684 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 307.9495 + 65.6684
= 476.5877 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
ITEM NO.: C-6211 86
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.4766
= 257,230.09 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 257,230.09 - 51,087.41
= 206,142.68 N
Wm1 = H + Hp
= 257,230.09 + 8,476.71
= 265,706.81 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 130,767.07/(100*98.4) = 13.2893 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 206,142.68*(0.037 - 0.0284)
= 2,635.4 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*2,635.4/(752*795)
= 7.148 MPa
Allowable stress Sfo = 98.6 MPa
ITEM NO.: C-6211 87
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*2,635.4/(184.2E+03*753*0.2*ln(1.1748))
= 0.1151
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Seismic
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*49,388.7/(*829.193)
= 441.1983 kPa
Axial load on flange
Pr = -4*F/(*G2)
= -4*35,461.53/(*829.192)
= -65.6684 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 441.1983 + -65.6684
= 552.0495 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
ITEM NO.: C-6211 88
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.5521
= 297,959.31 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
= 297,959.31 - 87,578.42
= 210,380.88 N
Wm1 = H + Hp
= 297,959.31 + 14,531.51
= 312,490.82 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 31.7572 cm2
Am1 = Wm1/Sb = 312,490.82/(100*98.4) = 31.7572 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (3,175.7193 + 7,569.0171)*130/2
= 698,407.95 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 210,380.88*0.037 = 7,774 N-m
HG = Wm1 - H = 312,490.82 - 297,959.31 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
ITEM NO.: C-6211 89
Mo = MD + MT + MG = 3,984.8 + 7,774 + 412.8 = 12,171.6 N-m
Mg = W*hG = 698,407.95*0.0284 = 19,837.9 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*12,171.6/(752*795)
= 33.012 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*12,171.6/(184.2E+03*753*0.2*ln(1.1748))
= 0.5317
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*19,837.9/(752*795)
= 53.805 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*19,837.9/(195.23E+03*753*0.2*ln(1.1748))
= 0.8176
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Seismic per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*49,388.7/(*829.193)
= 441.1983 kPa
Axial load on flange
Pr = 4*(1 + VAccel)*F/(*G2)
ITEM NO.: C-6211 90
= 4*(1 + 0.2)*35,461.53/(*829.192)
= 78.8022 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 441.1983 + 78.8022
= 622.9703 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.623
= 336,237.6 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 336,237.6 - 51,087.41
= 285,150.18 N
Wm1 = H + Hp
= 336,237.6 + 8,476.71
= 344,714.31 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 195,597.06/(100*98.4) = 19.8777 cm2
ITEM NO.: C-6211 91
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 285,150.18*(0.037 - 0.0284)
= 3,310.8 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*3,310.8/(752*795)
= 8.98 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*3,310.8/(184.2E+03*753*0.2*ln(1.1748))
= 0.1446
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Vortex shedding
ITEM NO.: C-6211 92
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*16,481.4/(*829.193)
= 147.2313 kPa
Axial load on flange
Pr = -4*0.6*F/(*G2)
= -4*0.6*35,461.53/(*829.192)
= -39.4015 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 147.2313 + -39.4015
= 284.3496 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
Flange calculations for External Pressure + Vortex shedding per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*16,481.4/(*829.193)
= 147.2313 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*35,461.53/(*829.192)
= 65.6684 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 147.2313 + 65.6684
= 315.8696 kPa
The static head of liquid has not been included in the total design load because the vessel is supported below the flange.
This load combination does not govern the flange design.
ITEM NO.: C-6211 93
Flange #5
ASME VIII-1, 2010 Edition, A11 Addenda Metric, Appendix 2 Flange Calculations
Flange dimensions, new
Flange is attached to: Shell #3 (Bottom)
Flange type: Ring type loose
Flange material specification:SA-182 F304 <= 125 (low stress) (II-D Metric
p. 86, ln. 14)
Bolt material specification: SA-193 B8 1 Bolt (II-D Metric p. 342, ln. 20)
Bolt Description: 0.875 in Coarse Thread
Internal design pressure, P: 176.52 kPa @ 180 °C
Required flange thickness, tr: 69.64 mm
Maximum allowable working pressure,
MAWP:591.39 kPa @ 180 °C (bolting limits)
Maximum allowable pressure, MAP: 810.9 kPa @ 17 °C
External design pressure, Pe 102.97 kPa @ 180 °C
Maximum allowable external pressure,
MAEP:2,462.39 kPa @ 180 °C
Corrosion allowance: Bore = 0 mm Flange = 0 mm
Bolt corrosion (root), Cbolt: 0 mm
Design MDMT: -10 °C No impact test performed
Rated MDMT: -196 °C Flange material is not normalized
Material is not produced to fine grain
practice
PWHT is not performed
Estimated weight: New = 115.53 kg corroded = 115.53 kg
flange OD A = 934 mm
bolt circle C = 886 mm
raised face OD Rf = 855 mm
gasket OD = 845 mm
gasket ID = 805 mm
flange ID B = 795 mm
facing height trf = 3 mm
thickness t = 75 mm
bolting = 28- 0.875 in dia
lower fillet weld h = 6 mm
upper fillet weld h1 = 6 mm
length e = 6 mm
gasket factor m = 2
seating stress y = 14.71 MPa
Gasket thickness T = 3 mm
gasket description PTFE
ITEM NO.: C-6211 94
Note: this flange is calculated as a loose type.
Flange calculations for Internal Pressure + Wind
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*12,948/(*829.193)
= 115.6671 kPa
Axial load on flange
Pr = -4*F/(*G2)
= -4*-24,140.25/(*829.192)
= 44.7035 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 115.6671 + 44.7035
= 336.8904 kPa
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.3369
= 181,830.82 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
= 181,830.82 - 87,578.42
= 94,252.4 N
ITEM NO.: C-6211 95
Wm1 = H + Hp
= 181,830.82 + 14,531.51
= 196,362.33 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = Wm1/Sb = 196,362.33/(100*98.4) = 19.9555 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 94,252.4*0.037 = 3,482.8 N-m
HG = Wm1 - H = 196,362.33 - 181,830.82 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
Mo = MD + MT + MG = 3,984.8 + 3,482.8 + 412.8 = 7,880.4 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*7,880.4/(752*795)
= 21.373 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*7,880.4/(184.2E+03*753*0.2*ln(1.1748))
= 0.3443
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ITEM NO.: C-6211 96
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Wind per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*12,948/(*829.193)
= 115.6671 kPa
Axial load on flange
Pr = 4*0.6*F/(*G2)
= 4*0.6*-24,140.25/(*829.192)
= -26.822 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 115.6671 + -26.822
= 191.815 kPa
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
ITEM NO.: C-6211 97
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.1918
= 103,528.85 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 103,528.85 - 51,087.41
= 52,441.44 N
Wm1 = H + Hp
= 103,528.85 + 8,476.71
= 112,005.57 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 76,906.07/(100*98.4) = 7.8157 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 52,441.44*(0.037 - 0.0284)
= 1,321.6 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*1,321.6/(752*795)
= 3.585 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
ITEM NO.: C-6211 98
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*1,321.6/(184.2E+03*753*0.2*ln(1.1748))
= 0.0577
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Seismic
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*31,417.5/(*829.193)
= 280.6587 kPa
Axial load on flange
Pr = -4*(1 + VAccel)*F/(*G2)
= -4*(1 + 0.2)*-24,140.25/(*829.192)
= 53.6447 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 280.6587 + 53.6447
= 510.823 kPa
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
ITEM NO.: C-6211 99
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.5108
= 275,708 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
= 275,708 - 87,578.42
= 188,129.58 N
Wm1 = H + Hp
= 275,708 + 14,531.51
= 290,239.51 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 29.4959 cm2
Am1 = Wm1/Sb = 290,239.51/(100*98.4) = 29.4959 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (2,949.5881 + 7,569.0171)*130/2
= 683,709.43 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 188,129.58*0.037 = 6,951.8 N-m
HG = Wm1 - H = 290,239.51 - 275,708 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
Mo = MD + MT + MG = 3,984.8 + 6,951.8 + 412.8 = 11,349.4 N-m
Mg = W*hG = 683,709.43*0.0284 = 19,420.4 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
ITEM NO.: C-6211 100
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*11,349.4/(752*795)
= 30.782 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*11,349.4/(184.2E+03*753*0.2*ln(1.1748))
= 0.4958
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*19,420.4/(752*795)
= 52.672 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*19,420.4/(195.23E+03*753*0.2*ln(1.1748))
= 0.8004
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Seismic per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*31,417.5/(*829.193)
= 280.6587 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*-24,140.25/(*829.192)
= -44.7035 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
ITEM NO.: C-6211 101
= P + Ps + Pm + Pr
= 102.9698 + 0 + 280.6587 + -44.7035
= 338.925 kPa
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.3389
= 182,928.96 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 182,928.96 - 51,087.41
= 131,841.54 N
Wm1 = H + Hp
= 182,928.96 + 8,476.71
= 191,405.67 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 175,608.69/(100*98.4) = 17.8464 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
ITEM NO.: C-6211 102
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 131,841.54*(0.037 - 0.0284)
= 2,000.3 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*2,000.3/(752*795)
= 5.425 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*2,000.3/(184.2E+03*753*0.2*ln(1.1748))
= 0.0874
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Vortex shedding
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*6,663.5/(*829.193)
= 59.5259 kPa
ITEM NO.: C-6211 103
Axial load on flange
Pr = -4*F/(*G2)
= -4*-24,140.25/(*829.192)
= 44.7035 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 59.5259 + 44.7035
= 280.7491 kPa
This load combination does not govern the flange design.
Flange calculations for External Pressure + Vortex shedding per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*6,663.5/(*829.193)
= 59.5259 kPa
Axial load on flange
Pr = 4*0.6*F/(*G2)
= 4*0.6*-24,140.25/(*829.192)
= -26.822 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 59.5259 + -26.822
= 135.6737 kPa
This load combination does not govern the flange design.
ITEM NO.: C-6211 104
Flange #6
ASME VIII-1, 2010 Edition, A11 Addenda Metric, Appendix 2 Flange Calculations
Flange dimensions, new
Flange is attached to: Shell #4 (Top)
Flange type: Ring type loose
Flange material specification:SA-182 F304 <= 125 (low stress) (II-D Metric
p. 86, ln. 14)
Bolt material specification: SA-193 B8 1 Bolt (II-D Metric p. 342, ln. 20)
Bolt Description: 0.875 in Coarse Thread
Internal design pressure, P: 176.52 kPa @ 180 °C
Required flange thickness, tr: 69.64 mm
Maximum allowable working pressure,
MAWP:591.39 kPa @ 180 °C (bolting limits)
Maximum allowable pressure, MAP: 810.9 kPa @ 17 °C
External design pressure, Pe 102.97 kPa @ 180 °C
Maximum allowable external pressure,
MAEP:2,462.39 kPa @ 180 °C
Corrosion allowance: Bore = 0 mm Flange = 0 mm
Bolt corrosion (root), Cbolt: 0 mm
Design MDMT: -10 °C No impact test performed
Rated MDMT: -196 °C Flange material is not normalized
Material is not produced to fine grain
practice
PWHT is not performed
Estimated weight: New = 115.53 kg corroded = 115.53 kg
flange OD A = 934 mm
bolt circle C = 886 mm
raised face OD Rf = 855 mm
gasket OD = 845 mm
gasket ID = 805 mm
flange ID B = 795 mm
facing height trf = 3 mm
thickness t = 75 mm
bolting = 28- 0.875 in dia
lower fillet weld h = 6 mm
upper fillet weld h1 = 6 mm
length e = 6 mm
gasket factor m = 2
seating stress y = 14.71 MPa
Gasket thickness T = 3 mm
gasket description PTFE
ITEM NO.: C-6211 105
Note: this flange is calculated as a loose type.
Flange calculations for Internal Pressure + Wind
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*12,948/(*829.193)
= 115.6671 kPa
Axial load on flange
Pr = -4*F/(*G2)
= -4*-24,140.25/(*829.192)
= 44.7035 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 115.6671 + 44.7035
= 336.8904 kPa
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.3369
= 181,830.82 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
= 181,830.82 - 87,578.42
= 94,252.4 N
ITEM NO.: C-6211 106
Wm1 = H + Hp
= 181,830.82 + 14,531.51
= 196,362.33 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = Wm1/Sb = 196,362.33/(100*98.4) = 19.9555 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 94,252.4*0.037 = 3,482.8 N-m
HG = Wm1 - H = 196,362.33 - 181,830.82 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
Mo = MD + MT + MG = 3,984.8 + 3,482.8 + 412.8 = 7,880.4 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*7,880.4/(752*795)
= 21.373 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*7,880.4/(184.2E+03*753*0.2*ln(1.1748))
= 0.3443
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ITEM NO.: C-6211 107
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Wind per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*12,948/(*829.193)
= 115.6671 kPa
Axial load on flange
Pr = 4*0.6*F/(*G2)
= 4*0.6*-24,140.25/(*829.192)
= -26.822 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 115.6671 + -26.822
= 191.815 kPa
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
ITEM NO.: C-6211 108
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.1918
= 103,528.85 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 103,528.85 - 51,087.41
= 52,441.44 N
Wm1 = H + Hp
= 103,528.85 + 8,476.71
= 112,005.57 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 76,906.07/(100*98.4) = 7.8157 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 52,441.44*(0.037 - 0.0284)
= 1,321.6 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*1,321.6/(752*795)
= 3.585 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
ITEM NO.: C-6211 109
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*1,321.6/(184.2E+03*753*0.2*ln(1.1748))
= 0.0577
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Seismic
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*31,417.5/(*829.193)
= 280.6587 kPa
Axial load on flange
Pr = -4*(1 + VAccel)*F/(*G2)
= -4*(1 + 0.2)*-24,140.25/(*829.192)
= 53.6447 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 280.6587 + 53.6447
= 510.823 kPa
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
ITEM NO.: C-6211 110
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.1765
= 14,531.51 N
H = 0.785*G2*P
= 0.785*829.192*0.5108
= 275,708 N
HD = 0.785*B2*P
= 0.785*7952*0.1765
= 87,578.42 N
HT = H - HD
= 275,708 - 87,578.42
= 188,129.58 N
Wm1 = H + Hp
= 275,708 + 14,531.51
= 290,239.51 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 29.4959 cm2
Am1 = Wm1/Sb = 290,239.51/(100*98.4) = 29.4959 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am + Ab)*Sa/2
= (2,949.5881 + 7,569.0171)*130/2
= 683,709.43 N
MD = HD*hD = 87,578.42*0.0455 = 3,984.8 N-m
MT = HT*hT = 188,129.58*0.037 = 6,951.8 N-m
HG = Wm1 - H = 290,239.51 - 275,708 = 14,531.51 N
MG = HG*hG = 14,531.51*0.0284 = 412.8 N-m
Mo = MD + MT + MG = 3,984.8 + 6,951.8 + 412.8 = 11,349.4 N-m
Mg = W*hG = 683,709.43*0.0284 = 19,420.4 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
ITEM NO.: C-6211 111
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*11,349.4/(752*795)
= 30.782 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*11,349.4/(184.2E+03*753*0.2*ln(1.1748))
= 0.4958
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*19,420.4/(752*795)
= 52.672 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*19,420.4/(195.23E+03*753*0.2*ln(1.1748))
= 0.8004
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for External Pressure + Seismic per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*31,417.5/(*829.193)
= 280.6587 kPa
Axial load on flange
Pr = 4*F/(*G2)
= 4*-24,140.25/(*829.192)
= -44.7035 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
ITEM NO.: C-6211 112
= P + Ps + Pm + Pr
= 102.9698 + 0 + 280.6587 + -44.7035
= 338.925 kPa
Gasket details from facing sketch 1(a) or (b), Column II
Gasket width N = 20 mm
b0 = N/2 = 10 mm
Effective gasket seating width, b = 2.5*b01/2 = 7.9 mm
G = OD of contact face - 2*b = 845 - 2*7.9 = 829.19 mm
hG = (C - G)/2 = (886 - 829.19)/2 = 28.4 mm
hD = (C - B)/2 = (886 - 795)/2 = 45.5 mm
hT = (hD + hG)/2 = (45.5 + 28.4)/2 = 36.95 mm
Hp = 2*b*3.14*G*m*P
= 2*7.9*3.14*829.19*2*0.103
= 8,476.71 N
H = 0.785*G2*P
= 0.785*829.192*0.3389
= 182,928.96 N
HD = 0.785*B2*P
= 0.785*7952*0.103
= 51,087.41 N
HT = H - HD
= 182,928.96 - 51,087.41
= 131,841.54 N
Wm1 = H + Hp
= 182,928.96 + 8,476.71
= 191,405.67 N
Wm2 = 3.14*b*G*y
= 3.14*7.9*829.19*14.71
= 302,739.8 N
Required bolt area, Am = greater of Am1, Am2 = 23.2877 cm2
Am1 = 0.785*G2*(Pm - Pr)/Sb = 175,608.69/(100*98.4) = 17.8464 cm2
Am2 = Wm2/Sa = 302,739.8/(100*130) = 23.2877 cm2
Total area for 28- 0.875 in dia bolts, corroded, Ab = 75.6902 cm2
W = (Am2 + Ab)*Sa/2
= (2,328.7674 + 7,569.0171)*130/2
= 643,356.07 N
ITEM NO.: C-6211 113
Mo = HD*(hD - hG) + HT*(hT - hG)
= 51,087.41*(0.0455 - 0.0284) + 131,841.54*(0.037 - 0.0284)
= 2,000.3 N-m
Mg = W*hG = 643,356.07*0.0284 = 18,274.2 N-m
From FIG. 2-7.1, where K = A/B = 934/795 = 1.1748, Y = 12.1287
Stresses at operating conditions - VIII-1 Appendix 2-7
SR = SH = 0
ST = Y*Mo/(t2*B)
= 1e3*12.1287*2,000.3/(752*795)
= 5.425 MPa
Allowable stress Sfo = 98.6 MPa
ST does not exceed Sfo
Flange rigidity at operating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*2,000.3/(184.2E+03*753*0.2*ln(1.1748))
= 0.0874
The flange rigidity index J does not exceed 1; satisfactory.
Stresses at gasket seating - VIII-1 Appendix 2-7
ST = Y*Mg/(t2*B)
= 1e3*12.1287*18,274.2/(752*795)
= 49.564 MPa
Allowable stress Sfa = 138 MPa
ST does not exceed Sfa
Flange rigidity at gasket seating per VIII-1 Appendix 2-14
J = 109.4*Mo/(E*t3*KL*ln(K))
= 109.4*18,274.2/(195.23E+03*753*0.2*ln(1.1748))
= 0.7532
The flange rigidity index J does not exceed 1; satisfactory.
Flange calculations for Internal Pressure + Vortex shedding
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*6,663.5/(*829.193)
= 59.5259 kPa
ITEM NO.: C-6211 114
Axial load on flange
Pr = -4*F/(*G2)
= -4*-24,140.25/(*829.192)
= 44.7035 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 176.5197 + 0 + 59.5259 + 44.7035
= 280.7491 kPa
This load combination does not govern the flange design.
Flange calculations for External Pressure + Vortex shedding per VIII-1, Appendix 2-11
Longitudinal bending moment on flange
Pm = 16*Mb/(*G3)
= 16*6,663.5/(*829.193)
= 59.5259 kPa
Axial load on flange
Pr = 4*0.6*F/(*G2)
= 4*0.6*-24,140.25/(*829.192)
= -26.822 kPa
Total design load on flange (used for H - ref. III-1 NC-3658.1)
= P + Ps + Pm + Pr
= 102.9698 + 0 + 59.5259 + -26.822
= 135.6737 kPa
This load combination does not govern the flange design.
ITEM NO.: C-6211 115
Feed Inlet (N1A (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Leg43 = 6 mm
hnew = 24 mm
Location and Orientation
Located on: Shell #3
Orientation: 270°
Nozzle center line offset to datum line: 4,300 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Internal projection, hnew: 24 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A required
A available
A1 A2 A3 A5A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 116
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 117
Feed Inlet (N1B (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #5
Orientation: 270°
Nozzle center line offset to datum line: 1,780 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F316 <= 125 (II-D Metric p. 70, ln. 21)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 1.6554 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 178.18 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 118
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 119
Overhaed Outlet (N2 (300A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 5.1 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 610 mm
te = 6 mm
Location and Orientation
Located on: Ellipsoidal Head (Top)
Orientation: 0°
End of nozzle to datum line: 18,410 mm
Calculated as hillside: No
Distance to head center, R: 0 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 304-TP-E (user defined)
Inside diameter, new: 297.9 mm
Nominal wall thickness: 10.3 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 226.87 mm
Local vessel minimum thickness: 5.1 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Diameter: 610 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A A A1 A2 A3 A5 A
treq tmin
ITEM NO.: C-6211 120
Reinforcement Calculations for External Pressure
required available welds
1.4673 32.3328 13.5116 1.9135 -- 16.638 0.2697 2.5 9.01
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-145,058 240,912 634,877 38,009 666,920 250,976 542,167
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 2.55 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
3.2287 27.3909 8.6922 1.791 -- 16.638 0.2697 2.5 9.01
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 2.55 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 121
Reboiler Inlet (N3 (150A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 5.1 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 300 mm
te = 6 mm
Location and Orientation
Located on: Ellipsoidal Head (Bottom)
Orientation: 0°
End of nozzle to datum line: -360 mm
Calculated as hillside: No
Distance to head center, R: 0 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 316-TP-E (user defined)
Inside diameter, new: 151 mm
Nominal wall thickness: 7.1 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 164.32 mm
Local vessel minimum thickness: 5.1 mm
Liquid static head included: 24.5198 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 316 (II-D Metric p. 70, ln. 25)
Diameter: 300 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 201.04 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A A A1 A2 A3 A5 A
treq tmin
ITEM NO.: C-6211 122
Reinforcement Calculations for External Pressure
required available welds
0.7994 16.6325 6.7781 1.3935 -- 8.088 0.3729 2.5 6.21
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-74,362 134,021 288,836 30,530 371,363 141,755 290,207
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 2.55 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
1.6436 14.1602 4.3884 1.311 -- 8.088 0.3729 2.5 6.21
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 2.55 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 123
Reboiler Return (N4 (300A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 460 mm
te = 6 mm
Location and Orientation
Located on: Shell #5
Orientation: 270°
Nozzle center line offset to datum line: 970 mm
End of nozzle to shell center: 600 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 316-TP-E (user defined)
Inside diameter, new: 297.9 mm
Nominal wall thickness: 10.3 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 204 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 11.8445 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 316 (II-D Metric p. 70, ln. 25)
Diameter: 460 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 188.36 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
ITEM NO.: C-6211 124
Reinforcement Calculations for External Pressure
1.6341 27.41 16.0225 2.3645 -- 8.49 0.5329 2.5 9.01
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-183,672 154,869 613,545 49,201 761,291 168,069 542,859
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
8.1013 13.1093 1.88 2.2064 -- 8.49 0.5329 2.5 9.01
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 125
Bottom Return (N5 (15A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #5
Orientation: 180°
Nozzle center line offset to datum line: 150 mm
End of nozzle to shell center: 436 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F316L <= 125 (II-D Metric p. 66, ln. 31)
Inside diameter, new: 16.1 mm
Nominal wall thickness: 11.95 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 40 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 19.1647 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 195.68 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.95
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 126
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.95
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 127
N2 Inlet (N6 (15A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #4
Orientation: 45°
Nozzle center line offset to datum line: 3,000 mm
End of nozzle to shell center: 436 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 16.1 mm
Nominal wall thickness: 11.95 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 40 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.95
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 128
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.95
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 129
Side Out (N7 (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #2
Orientation: 90°
Nozzle center line offset to datum line: 12,193 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F316 <= 125 (II-D Metric p. 70, ln. 21)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 130
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 131
TE (N8A (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #5
Orientation: 210°
Nozzle center line offset to datum line: 150 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F316 <= 125 (II-D Metric p. 70, ln. 21)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 19.224 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 195.74 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 132
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 133
TE (N8B (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #3
Orientation: 210°
Nozzle center line offset to datum line: 4,300 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 134
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 135
TE (N8C (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #3
Orientation: 210°
Nozzle center line offset to datum line: 11,160 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 136
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 137
TE (N8D (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #2
Orientation: 210°
Nozzle center line offset to datum line: 16,320 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 138
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 139
TG (N9A (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #5
Orientation: 210°
Nozzle center line offset to datum line: 970 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F316 <= 125 (II-D Metric p. 70, ln. 21)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 10.3863 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 186.91 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 140
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 141
TG (N9B (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #3
Orientation: 225°
Nozzle center line offset to datum line: 4,300 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 142
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 143
TG (N9C (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #3
Orientation: 225°
Nozzle center line offset to datum line: 11,160 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 144
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 145
TG (N9D (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #2
Orientation: 225°
Nozzle center line offset to datum line: 16,320 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 146
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 147
LG (N10A/B (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #2
Orientation: 120°
Nozzle center line offset to datum line: 12,193 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 148
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 149
LG (N10C/D (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #5
Orientation: 0°
Nozzle center line offset to datum line: 150 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F316 <= 125 (II-D Metric p. 70, ln. 21)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 19.224 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 195.74 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 150
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 151
LT (N11A/B (50A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 150 mm
te = 6 mm
Location and Orientation
Located on: Shell #5
Orientation: 22.5°
Nozzle center line offset to datum line: 150 mm
End of nozzle to shell center: 550 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 316-TP-E (user defined)
Inside diameter, new: 52.7 mm
Nominal wall thickness: 3.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 154 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 19.3619 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 316 (II-D Metric p. 70, ln. 25)
Diameter: 150 mm
Is split: No
UG-37 Area Calculation Summary (cm2)For P = 195.88 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A required
A available
A1 A2 A3 A5A
weldstreq tmin
ITEM NO.: C-6211 152
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 3.41
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 2.73 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 2.73 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 3.41
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 2.73 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 2.73 6 weld size is adequate
ITEM NO.: C-6211 153
Reflux (N12 (25A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Leg43 = 6 mm
hnew = 24 mm
Location and Orientation
Located on: Shell #1
Orientation: 0°
Nozzle center line offset to datum line: 17,200 mm
End of nozzle to shell center: 446 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 27.2 mm
Nominal wall thickness: 13.9 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 50 mm
Internal projection, hnew: 24 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A required
A available
A1 A2 A3 A5A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 154
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 13.9
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 155
PG (N13A (20A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #5
Orientation: 330°
Nozzle center line offset to datum line: 1,780 mm
End of nozzle to shell center: 436 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F316 <= 125 (II-D Metric p. 70, ln. 21)
Inside diameter, new: 21.4 mm
Nominal wall thickness: 11.8 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 40 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 1.6244 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 178.14 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.8
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 156
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.8
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 157
PG (N13B (20A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #1
Orientation: 165°
Nozzle center line offset to datum line: 17,780 mm
End of nozzle to shell center: 436 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 21.4 mm
Nominal wall thickness: 11.8 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 40 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.8
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 158
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.8
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 159
PT (N14(15A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
Location and Orientation
Located on: Shell #1
Orientation: 180°
Nozzle center line offset to datum line: 17,780 mm
End of nozzle to shell center: 436 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: SA-182 F304 <= 125 (II-D Metric p. 86, ln. 15)
Inside diameter, new: 16.1 mm
Nominal wall thickness: 11.95 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 40 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.95
UG-41 Weld Failure Path Analysis Summary
The nozzle is exempt from weld strength calculations per UW-15(b)(2)
ITEM NO.: C-6211 160
This opening does not require reinforcement per UG-36(c)(3)(a)
Reinforcement Calculations for External Pressure
This opening does not require reinforcement per UG-36(c)(3)(a)
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C
UG-45 Nozzle Wall
Thickness Summary (mm) The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
This nozzle is exempt from area calculations per UG-36(c)(3)(a) 2.5 11.95
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
throat size (mm)
Actual weld
throat size (mm)Status
Nozzle to shell fillet (Leg41) 4.2 4.2 weld size is adequate
ITEM NO.: C-6211 161
Manhole (M1 (300A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 610 mm
te = 6 mm
Location and Orientation
Located on: Shell #5
Orientation: 135°
Nozzle center line offset to datum line: 1,550 mm
End of nozzle to shell center: 600 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 316-TP-E (user defined)
Inside diameter, new: 297.9 mm
Nominal wall thickness: 10.3 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 204 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 5.5937 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 316 (II-D Metric p. 70, ln. 25)
Diameter: 610 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 182.11 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
ITEM NO.: C-6211 162
Reinforcement Calculations for External Pressure
1.5803 35.3618 16.0748 2.3664 -- 16.638 0.2826 2.5 9.01
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-185,074 262,304 692,053 49,227 761,291 275,504 621,368
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
8.1013 21.007 1.88 2.2064 -- 16.638 0.2826 2.5 9.01
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 163
Manhole (M2 (300A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 610 mm
te = 6 mm
Location and Orientation
Located on: Shell #3
Orientation: 270°
Nozzle center line offset to datum line: 5,100 mm
End of nozzle to shell center: 600 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 304-TP-E (user defined)
Inside diameter, new: 297.9 mm
Nominal wall thickness: 10.3 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 204 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Diameter: 610 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
ITEM NO.: C-6211 164
Reinforcement Calculations for External Pressure
1.6313 35.1464 15.9877 2.251 -- 16.638 0.2697 2.5 9.01
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-172,984 245,231 634,877 44,104 709,570 257,071 584,817
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
7.9081 21.2986 2.2877 2.1032 -- 16.638 0.2697 2.5 9.01
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 165
Manhole (M3 (300A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 610 mm
te = 6 mm
Location and Orientation
Located on: Shell #2
Orientation: 180°
Nozzle center line offset to datum line: 13,600 mm
End of nozzle to shell center: 600 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 304-TP-E (user defined)
Inside diameter, new: 297.9 mm
Nominal wall thickness: 10.3 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 204 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Diameter: 610 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
ITEM NO.: C-6211 166
Reinforcement Calculations for External Pressure
1.6313 35.1464 15.9877 2.251 -- 16.638 0.2697 2.5 9.01
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-172,984 245,231 634,877 44,104 709,570 257,071 584,817
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
8.8273 19.5232 0.5123 2.1032 -- 16.638 0.2697 2.5 9.01
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 167
Handhole (H1 (150A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 300 mm
te = 6 mm
Location and Orientation
Located on: Shell #4
Orientation: 135°
Nozzle center line offset to datum line: 2,200 mm
End of nozzle to shell center: 600 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 304-TP-E (user defined)
Inside diameter, new: 151 mm
Nominal wall thickness: 7.1 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 204 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Diameter: 300 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
ITEM NO.: C-6211 168
Reinforcement Calculations for External Pressure
0.832 18.0628 8.0522 1.5626 -- 8.088 0.36 2.5 6.21
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-84,990 128,135 266,023 31,615 368,041 136,297 295,257
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
4.1336 10.8654 0.9606 1.4568 -- 8.088 0.36 2.5 6.21
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 169
Handhole (H2 (150A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 300 mm
te = 6 mm
Location and Orientation
Located on: Shell #4
Orientation: 135°
Nozzle center line offset to datum line: 3,350 mm
End of nozzle to shell center: 600 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 304-TP-E (user defined)
Inside diameter, new: 151 mm
Nominal wall thickness: 7.1 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 204 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Diameter: 300 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
ITEM NO.: C-6211 170
Reinforcement Calculations for External Pressure
0.832 18.0628 8.0522 1.5626 -- 8.088 0.36 2.5 6.21
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-84,990 128,135 266,023 31,615 368,041 136,297 295,257
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
4.1336 10.8654 0.9606 1.4568 -- 8.088 0.36 2.5 6.21
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 171
Handhole (H3 (150A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 300 mm
te = 6 mm
Location and Orientation
Located on: Shell #3
Orientation: 270°
Nozzle center line offset to datum line: 11,250 mm
End of nozzle to shell center: 600 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 304-TP-E (user defined)
Inside diameter, new: 151 mm
Nominal wall thickness: 7.1 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 204 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Diameter: 300 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
ITEM NO.: C-6211 172
Reinforcement Calculations for External Pressure
0.832 18.0628 8.0522 1.5626 -- 8.088 0.36 2.5 6.21
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-84,990 128,135 266,023 31,615 368,041 136,297 295,257
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
4.0217 11.079 1.1742 1.4568 -- 8.088 0.36 2.5 6.21
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 173
Handhole (H4 (150A))
ASME Section VIII Division 1, 2010 Edition, A11 Addenda Metric
Note: round inside edges per UG-76(c)
Reinforcement Calculations for Internal Pressure
tw(lower) = 6 mm
Leg41 = 6 mm
tw(upper) = 6 mm
Leg42 = 5 mm
Dp = 300 mm
te = 6 mm
Location and Orientation
Located on: Shell #2
Orientation: 180°
Nozzle center line offset to datum line: 16,350 mm
End of nozzle to shell center: 600 mm
Passes through a Category A joint: No
Nozzle
Access opening: No
Material specification: STS 304-TP-E (user defined)
Inside diameter, new: 151 mm
Nominal wall thickness: 7.1 mm
Corrosion allowance: 0 mm
Projection available outside vessel, Lpr: 204 mm
Local vessel minimum thickness: 6 mm
Liquid static head included: 0 kPa
Longitudinal joint efficiency: 1
Reinforcing Pad
Material specification: SA-240 304 (II-D Metric p. 86, ln. 25)
Diameter: 300 mm
Is split: No
UG-37 Area Calculation Summary (cm2)
For P = 176.52 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
ITEM NO.: C-6211 174
Reinforcement Calculations for External Pressure
0.832 18.0628 8.0522 1.5626 -- 8.088 0.36 2.5 6.21
UG-41 Weld Failure Path Analysis Summary (N)
All failure paths are stronger than the applicable weld loads
Weld load
W
Weld load
W1-1
Path 1-1
strength
Weld load
W2-2
Path 2-2
strength
Weld load
W3-3
Path 3-3
strength
-84,990 128,135 266,023 31,615 368,041 136,297 295,257
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)
Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
UG-37 Area Calculation Summary (cm2)
For Pe = 102.97 kPa @ 180 °C The opening is adequately reinforced
UG-45 Nozzle Wall
Thickness Summary (mm)The nozzle passes UG-45
A
required
A
availableA1 A2 A3 A5
A
weldstreq tmin
4.5019 10.1628 0.2581 1.4568 -- 8.088 0.36 2.5 6.21
UG-41 Weld Failure Path Analysis Summary
Weld strength calculations are not required for external pressure
UW-16 Weld Sizing Summary
Weld descriptionRequired weld
size (mm)Actual weld
size (mm)Status
Nozzle to pad fillet (Leg41) 4.2 4.2 weld size is adequate
Pad to shell fillet (Leg42) 3 3.5 weld size is adequate
Nozzle to pad groove (Upper) 4.2 6 weld size is adequate
ITEM NO.: C-6211 175
Wind Code
Vortex Shedding Calculations
Table Lookup Values
2.4.1 Basic Load Combinations for Allowable Stress Design
The following load combinations are considered in accordance with ASCE section 2.4.1:
Wind Deflection Reports:
Operating, Corroded
Empty, Corroded
Vacuum, Corroded
Hydrotest, New, field
Building Code: ASCE 7-05
Elevation of base above grade: 45.9318 ft (14.0001 m)
Increase effective outer diameter by: 1.9685 ft (0.6000 m)
Wind Force Coefficient Cf: 0.7000
Basic Wind Speed:, V: 100.6621 mph (162.0000 km/h)
Importance Factor:, I: 1.1500
Exposure category: D
Wind Directionality Factor, Kd: 0.9500
Topographic Factor, Kzt: 1.0000
Enforce min. loading of 0.48 kPa: Yes
Vessel Characteristics
Vessel height, h: 29.0358 ft (8.8501 m)
Vessel Minimum Diameter, b
Operating, Corroded: 2.9265 ft (0.8920 m)
Empty, Corroded: 2.9265 ft (0.8920 m)
Hydrotest, New, field: 2.9265 ft (0.8920 m)
Fundamental Frequency, n1
Operating, Corroded: 3.8433 Hz
Empty, Corroded: 4.8531 Hz
Hydrotest, New, field: 3.3608 Hz
Vacuum, Corroded: 3.8433 Hz
Damping coefficient,
Operating, Corroded: 0.0254
Empty, Corroded: 0.0210
Hydrotest, New, field: 0.0260
Vacuum, Corroded: 0.0254
5. D + P + Ps + W
7. 0.6D + P + Ps + W
Where
D = Dead load
P = Internal or external pressure load
Ps = Static head load
W = Wind load
ITEM NO.: C-6211 176
Operating, Corroded,Vortex Shedding
Empty, Corroded, Vortex Shedding
Vacuum, Corroded, Vortex Shedding
Wind Pressure Calculations
Wind Pressures at Critical Speed: Operating, Corroded
Wind Pressures at Critical Speed: Empty, Corroded
Wind Pressures at Critical Speed: Vacuum, Corroded
Wind Deflection Report: Operating, Corroded
Wind Deflection Report: Empty, Corroded
Wind Deflection Report: Vacuum, Corroded
Component
Elevation of
bottom above base (mm)
Effective
OD (m)
Elastic
modulus E (MPa)
Inertia
I (m4)
Platform
wind shear atBottom (N)
Total wind
shear at Bottom (N)
bending
moment at Bottom (N-m)
Deflection
at top (mm)
Ellipsoidal Head (Top) 8,630 1.49 184,200.0 * 0 348 35.7 6.3
Shell #1 7,619.5 1.49 184,200.0 0.001144 0 2,132.4 1,290.5 6.09
Shell #2 2,550.5 1.49 184,200.0 0.001144 0 10,807.4 34,472.5 5.13
Shell #3 (top) 0 1.49 184,200.0 0.001144 0 15,026.1 67,470.5 0.86
Shell #3 (bottom) 0 1.49 184,200.0 0.001144 0 14,413.8 66,753.4 2.98
Shell #4 -5,271.5 1.49 184,200.0 0.001144 0 6,093.2 12,948 4.93
Shell #5 -7,330 1.49 184,200.0 0.001144 0 3,072.9 3,463.7 6.91
Ellipsoidal Head
(Bottom)-9,330 1.49 184,200.0 * 0 266.6 27 7.13
*Moment of Inertia I varies over the length of the component
Component
Elevation of
bottom above
base (mm)
Effective
OD
(m)
Elastic
modulus
E (MPa)
Inertia
I (m4)
Platform
wind shear at
Bottom (N)
Total wind
shear at
Bottom (N)
bending
moment at
Bottom (N-m)
Deflection
at top (mm)
Ellipsoidal Head (Top) 8,630 1.49 195,233.3 * 0 348 35.7 5.95
Shell #1 7,619.5 1.49 195,233.3 0.001144 0 2,132.4 1,290.5 5.75
Shell #2 2,550.5 1.49 195,233.3 0.001144 0 10,807.4 34,472.5 4.84
Shell #3 (top) 0 1.49 195,233.3 0.001144 0 15,026.1 67,470.5 0.81
Shell #3 (bottom) 0 1.49 195,233.3 0.001144 0 14,413.8 66,753.4 2.81
Shell #4 -5,271.5 1.49 195,233.3 0.001144 0 6,093.2 12,948 4.66
Shell #5 -7,330 1.49 195,233.3 0.001144 0 3,072.9 3,463.7 6.52
Ellipsoidal Head
(Bottom)-9,330 1.49 195,233.3 * 0 266.6 27 6.73
*Moment of Inertia I varies over the length of the component
Component Elevation of
bottom above
base (mm)
Effective OD
(m)
Elastic modulus
E (MPa)
Inertia
I (m4)
Platform wind shear at
Bottom (N)
Total wind shear at
Bottom (N)
bending moment at
Bottom (N-m)
Deflection
at top (mm)
Ellipsoidal Head (Top) 8,630 1.49 184,200.0 * 0 348 35.7 6.3
Shell #1 7,619.5 1.49 184,200.0 0.001144 0 2,132.4 1,290.5 6.09
ITEM NO.: C-6211 177
Wind Deflection Report: Hydrotest, New, field
Wind Deflection Report: Operating, Corroded, Vortex Shedding
Wind Deflection Report: Empty, Corroded, Vortex Shedding
Shell #2 2,550.5 1.49 184,200.0 0.001144 0 10,807.4 34,472.5 5.13
Shell #3 (top) 0 1.49 184,200.0 0.001144 0 15,026.1 67,470.5 0.86
Shell #3 (bottom) 0 1.49 184,200.0 0.001144 0 14,413.8 66,753.4 2.98
Shell #4 -5,271.5 1.49 184,200.0 0.001144 0 6,093.2 12,948 4.93
Shell #5 -7,330 1.49 184,200.0 0.001144 0 3,072.9 3,463.7 6.91
Ellipsoidal Head
(Bottom)-9,330 1.49 184,200.0 * 0 266.6 27 7.13
*Moment of Inertia I varies over the length of the component
Component
Elevation of
bottom above
base (mm)
Effective
OD
(m)
Elastic
modulus
E (MPa)
Inertia
I (m4)
Platform
wind shear at
Bottom (N)
Total wind
shear at
Bottom (N)
bending
moment at
Bottom (N-m)
Deflection
at top (mm)
Ellipsoidal Head (Top) 8,630 1.49 195,480.0 * 0 140.8 14.4 2.46
Shell #1 7,619.5 1.49 195,480.0 0.001144 0 862.7 523 2.38
Shell #2 2,550.5 1.49 195,480.0 0.001144 0 4,483.8 14,301.5 2.01
Shell #3 (top) 0 1.49 195,480.0 0.001144 0 6,305.8 28,072.2 0.34
Shell #3 (bottom) 0 1.49 195,480.0 0.001144 0 6,805.9 32,654.1 1.39
Shell #4 -5,271.5 1.49 195,480.0 0.001144 0 3,040.1 6,663.5 2.31
Shell #5 -7,330 1.49 195,480.0 0.001144 0 1,569.5 1,844.3 3.24
Ellipsoidal Head
(Bottom)-9,330 1.49 195,480.0 * 0 140.8 14.4 3.34
*Moment of Inertia I varies over the length of the component
Component
Elevation of
bottom above
base (mm)
Effective
OD
(m)
Elastic
modulus
E (MPa)
Inertia
I (m4)
Platform
wind shear at
Bottom (N)
Total wind
shear at
Bottom (N)
bending
moment at
Bottom (N-m)
Deflection
at top (mm)
Ellipsoidal Head (Top) 8,630 1.49 184,200.0 * 0 177.9 18.8 2.99
Shell #1 7,619.5 1.49 184,200.0 0.001144 0 1,054.1 642.8 2.89
Shell #2 2,550.5 1.49 184,200.0 0.001144 0 4,933.2 16,481.4 2.43
Shell #3 (top) 0 1.49 184,200.0 0.001144 0 6,755.2 31,398.2 0.4
Shell #3 (bottom) 0 1.49 184,200.0 0.001144 0 6,805.9 32,654.1 1.47
Shell #4 -5,271.5 1.49 184,200.0 0.001144 0 3,040.1 6,663.5 2.45
Shell #5 -7,330 1.49 184,200.0 0.001144 0 1,569.5 1,844.3 3.44
Ellipsoidal Head
(Bottom)-9,330 1.49 184,200.0 * 0 140.8 14.4 3.55
*Moment of Inertia I varies over the length of the component
Component
Elevation of
bottom above
base (mm)
Effective
OD
(m)
Elastic
modulus
E (MPa)
Inertia
I (m4)
Platform
wind shear at
Bottom (N)
Total wind
shear at
Bottom (N)
bending
moment at
Bottom (N-m)
Deflection
at top (mm)
ITEM NO.: C-6211 178
Wind Deflection Report: Vacuum, Corroded, Vortex Shedding
Wind Pressure (WP) Calculations
Gust Factor (G¯) Calculations
Design Wind Pressures
Ellipsoidal Head (Top) 8,630 1.49 195,233.3 * 0 237.7 25.5 3.41
Shell #1 7,619.5 1.49 195,233.3 0.001144 0 1,372.9 840.9 3.3
Shell #2 2,550.5 1.49 195,233.3 0.001144 0 5,685.3 20,125.7 2.77
Shell #3 (top) 0 1.49 195,233.3 0.001144 0 7,507.3 36,960.8 0.45
Shell #3 (bottom) 0 1.49 195,233.3 0.001144 0 6,805.9 32,654.1 1.39
Shell #4 -5,271.5 1.49 195,233.3 0.001144 0 3,040.1 6,663.5 2.31
Shell #5 -7,330 1.49 195,233.3 0.001144 0 1,569.5 1,844.3 3.24
Ellipsoidal Head
(Bottom)-9,330 1.49 195,233.3 * 0 140.8 14.4 3.35
*Moment of Inertia I varies over the length of the component
Component Elevation of
bottom above
base (mm)
Effective OD
(m)
Elastic modulus
E (MPa)
Inertia
I (m4)
Platform wind shear at
Bottom (N)
Total wind shear at
Bottom (N)
bending moment at
Bottom (N-m)
Deflectionat top (mm)
Ellipsoidal Head (Top) 8,630 1.49 184,200.0 * 0 177.9 18.8 2.99
Shell #1 7,619.5 1.49 184,200.0 0.001144 0 1,054.1 642.8 2.89
Shell #2 2,550.5 1.49 184,200.0 0.001144 0 4,933.2 16,481.4 2.43
Shell #3 (top) 0 1.49 184,200.0 0.001144 0 6,755.2 31,398.2 0.4
Shell #3 (bottom) 0 1.49 184,200.0 0.001144 0 6,805.9 32,654.1 1.47
Shell #4 -5,271.5 1.49 184,200.0 0.001144 0 3,040.1 6,663.5 2.45
Shell #5 -7,330 1.49 184,200.0 0.001144 0 1,569.5 1,844.3 3.44
Ellipsoidal Head
(Bottom)-9,330 1.49 184,200.0 * 0 140.8 14.4 3.55
*Moment of Inertia I varies over the length of the component
Kz = 2.01 * (Z/Zg)2/
= 2.01 * (Z/213.3600)0.1739
qz = 0.613 * Kz * Kzt * Kd * V2 * I
= 0.613 * Kz * 1.0000 * 0.9500 * 45.00002 * 1.1500
= 1,356.1476 * Kz
WP = qz * G * Cf (Minimum 0.48 kPa)
= qz * G * 0.7000 (Minimum 0.48 kPa)
Height Z
(m)Kz
qz
(kPa)
WP: Operating
(kPa)
WP: Empty
(kPa)
WP: Hydrotest New
(kPa)
WP: Hydrotest Corroded
(kPa)
WP: Vacuum
(kPa)
4.6 1.0302 1.3979 0.8846 0.8846 0.4788 N.A. 0.8846
6.1 1.0831 1.4696 0.9300 0.9300 0.4788 N.A. 0.9300
7.6 1.1259 1.5278 0.9668 0.9668 0.4788 N.A. 0.9668
ITEM NO.: C-6211 179
Design Wind Force determined from: F = Pressure * Af , where Af is the projected area.
Vortex Shedding Calculations
Vortex shedding calculations are based on NBC 1995 building code, Structural Commentaries (Part 4).
Critical wind speed at top of vessel, Vh = (n*D/S)*(3600/5280) mph
Reference wind speed corresponding to critical wind speed, VRef
Corresponding reference wind speed, VRef
Corresponding pressure at top of vessel, qh = 0.00256 * Vh2
9.1 1.1622 1.5770 0.9979 0.9979 0.4788 N.A. 0.9979
12.2 1.2218 1.6579 1.0491 1.0491 0.4788 N.A. 1.0491
15.2 1.2702 1.7235 1.0907 1.0907 0.4788 N.A. 1.0907
18.3 1.3111 1.7791 1.1258 1.1258 0.4788 N.A. 1.1258
21.3 1.3467 1.8274 1.1564 1.1564 0.4788 N.A. 1.1564
24.4 1.3784 1.8703 1.1836 1.1836 0.4788 N.A. 1.1836
Average diameter of vessel (upper third): D = 2.5179 ft (767.46 mm)
Aspect ratio: Ar = 11.5317
Vortex shedding factor, Operating, Corroded: C1 = 2.5469
Vortex shedding factor, Operating, Corroded: C2 = 0.6000
Vortex shedding factor, Empty, Corroded: C1 = 2.5469
Vortex shedding factor, Empty, Corroded: C2 = 0.6000
Vortex shedding factor, Vacuum, Corroded: C1 = 2.5469
Vortex shedding factor, Vacuum, Corroded: C2 = 0.6000
Weight per foot of vessel, Operating, Corroded, (upper third): M = 286.3834 lb/ft (41.7945 N/cm)
Strouhal number, Operating, Corroded: S = 0.2000
Weight per foot of vessel, Empty, Corroded, (upper third): M = 274.1747 lb/ft (40.0128 N/cm)
Strouhal number, Empty, Corroded: S = 0.2000
Weight per foot of vessel, Vacuum, Corroded, (upper third): M = 286.3834 lb/ft (41.7945 N/cm)
Strouhal number, Vacuum, Corroded: S = 0.2000
Operating, Corroded: Vh = (3.8433*2.5179/0.2000)*(3600/5280) = 32.9896 mph (53.0917 km/h)
Empty, Corroded: Vh = (4.8531*2.5179/0.2000)*(3600/5280) = 41.6581 mph (67.0421 km/h)
Vacuum, Corroded: Vh = (3.8433*2.5179/0.2000)*(3600/5280) = 32.9896 mph (53.0917 km/h)
Operating, Corroded: VRef = 33.3588 mph (53.6858 km/h)
Empty, Corroded: VRef = 42.1242 mph (67.7924 km/h)
Vacuum, Corroded: VRef = 33.3588 mph (53.6858 km/h)
Operating, Corroded: VRef = 100.6621 mph (162.0000 km/h)
Empty, Corroded: VRef = 100.6621 mph (162.0000 km/h)
Vacuum, Corroded: VRef = 100.6621 mph (162.0000 km/h)
ITEM NO.: C-6211 180
Equivalent static loading, FL = qh*C1*D / (SQR(Ar)*SQR( - (C2*R0*D2/M)))
Static loading FL is applied throughout the top third of the vessel
Wind Pressures at Critical Wind Speed: Operating, Corroded (Vh = 14.7477 m/sec)
Wind Pressures at Critical Wind Speed: Empty, Corroded (Vh = 18.6228 m/sec)
Operating, Corroded: qh = 0.00256 * (32.9896)2 = 2.7861 psf (0.13 kPa)
Empty, Corroded: qh = 0.00256 * (41.6581)2 = 4.4426 psf (0.21 kPa)
Vacuum, Corroded: qh = 0.00256 * (32.9896)2 = 2.7861 psf (0.13 kPa)
Operating, Corroded: FL = 2.7861*2.5469*2.5179 / (SQR(11.5317)*SQR(0.0254 - (0.6000*0.0765*(2.5179)2/286.3834)))
= 33.6693 lb/ft (4.9137 N/cm)
Empty, Corroded: FL = 4.4426*2.5469*2.5179 / (SQR(11.5317)*SQR(0.0210 - (0.6000*0.0765*(2.5179)2/274.1747)))
= 59.4144 lb/ft (8.6709 N/cm)
Vacuum, Corroded: FL = 2.7861*2.5469*2.5179 / (SQR(11.5317)*SQR(0.0254 - (0.6000*0.0765*(2.5179)2/286.3834)))
= 33.6693 lb/ft (4.9137 N/cm)
Kz = 2.01 * (Z/Zg)2/
= 2.01 * (Z/213.3600)0.1739
qz = 0.613 * Kz * Kd * Kzt * Vh2 * I
= 0.613 * Kz * 0.9500 * 1.0000 * (14.7477)2 * 1.1500
= 145.6564 * Kz
WP = qz * G¯ * Cf
= qz * 0.9040 * 0.7000
Height Z(m) Kz qz(kPa) WP(kPa)
4.6 1.0302 0.1501 0.0950
6.1 1.0831 0.1578 0.0999
7.6 1.1259 0.1641 0.1038
9.1 1.1622 0.1694 0.1072
12.2 1.2218 0.1781 0.1127
15.2 1.2702 0.1851 0.1171
18.3 1.3111 0.1911 0.1209
21.3 1.3467 0.1963 0.1242
24.4 1.3784 0.2009 0.1271
Kz = 2.01 * (Z/Zg)2/
= 2.01 * (Z/213.3600)0.1739
qz = 0.613 * Kz * Kd * Kzt * Vh2 * I
= 0.613 * Kz * 0.9500 * 1.0000 * (18.6228)2 * 1.1500
= 232.2591 * Kz
WP = qz * G¯ * Cf
= qz * 0.9040 * 0.7000
ITEM NO.: C-6211 181
Wind Pressures at Critical Wind Speed: Vacuum, Corroded (Vh = 14.7477 m/sec)
Gust Factor Calculations
Operating, Corroded
Empty, Corroded
Vacuum, Corroded
Hydrotest, New, field
Operating, Corroded, Vortex Shedding
Empty, Corroded, Vortex Shedding
Vacuum, Corroded, Vortex Shedding
Gust Factor Calculations: Operating, Corroded
Height Z(m) Kz qz(kPa) WP(kPa)
4.6 1.0302 0.2394 0.1515
6.1 1.0831 0.2517 0.1593
7.6 1.1259 0.2617 0.1656
9.1 1.1622 0.2701 0.1709
12.2 1.2218 0.2839 0.1797
15.2 1.2702 0.2952 0.1868
18.3 1.3111 0.3047 0.1928
21.3 1.3467 0.3130 0.1980
24.4 1.3784 0.3203 0.2027
Kz = 2.01 * (Z/Zg)2/
= 2.01 * (Z/213.3600)0.1739
qz = 0.613 * Kz * Kd * Kzt * Vh2* I
= 0.613 * Kz * 0.9500 * 1.0000 * (14.7477)2 * 1.1500
= 145.6564 * Kz
WP = qz * G¯ * Cf
= qz * 0.9040 * 0.7000
Height Z(m) Kz qz(kPa) WP(kPa)
4.6 1.0302 0.1501 0.0950
6.1 1.0831 0.1578 0.0999
7.6 1.1259 0.1641 0.1038
9.1 1.1622 0.1694 0.1072
12.2 1.2218 0.1781 0.1127
15.2 1.2702 0.1851 0.1171
18.3 1.3111 0.1911 0.1209
21.3 1.3467 0.1963 0.1242
24.4 1.3784 0.2009 0.1271
ITEM NO.: C-6211 182
Vessel is considered a rigid structure as n1 = 3.8433 Hz ≥ 1 Hz.
Gust Factor Calculations: Empty, Corroded
Vessel is considered a rigid structure as n1 = 4.8531 Hz ≥ 1 Hz.
Gust Factor Calculations: Vacuum, Corroded
Vessel is considered a rigid structure as n1 = 3.8433 Hz ≥ 1 Hz.
z¯ = max ( 0.60 * h , zmin )
= max ( 0.60 * 29.0358 , 7.0000 )
= 17.4215
Iz¯ = c * (33 / z¯)1/6
= 0.1500 * (33 / 17.4215)1/6
= 0.1669
Lz¯ = l * (z¯ / 33)ep
= 650.0000 * (17.4215 / 33)0.1250
= 600.1152
Q = Sqr(1 / (1 + 0.63 * ((b + h) / Lz¯)0.63))
= Sqr(1 / (1 + 0.63 * ((2.9265 + 29.0358) / 600.1152)0.63))
= 0.9538
G = 0.925 * (1 + 1.7 * gQ * Iz¯ * Q) / (1 + 1.7 * gv * Iz¯)
= 0.925 * (1 + 1.7 * 3.40* 0.1669 * 0.9538) / (1 + 1.7 * 3.40 * 0.1669)
= 0.9040
z¯ = max ( 0.60 * h , zmin )
= max ( 0.60 * 29.0358 , 7.0000 )
= 17.4215
Iz¯ = c * (33 / z¯)1/6
= 0.1500 * (33 / 17.4215)1/6
= 0.1669
Lz¯ = l * (z¯ / 33)ep
= 650.0000 * (17.4215 / 33)0.1250
= 600.1152
Q = Sqr(1 / (1 + 0.63 * ((b + h) / Lz¯)0.63))
= Sqr(1 / (1 + 0.63 * ((2.9265 + 29.0358) / 600.1152)0.63))
= 0.9538
G = 0.925 * (1 + 1.7 * gQ * Iz¯ * Q) / (1 + 1.7 * gv * Iz¯)
= 0.925 * (1 + 1.7 * 3.40* 0.1669 * 0.9538) / (1 + 1.7 * 3.40 * 0.1669)
= 0.9040
z¯ = max ( 0.60 * h , zmin )
= max ( 0.60 * 29.0358 , 7.0000 )
= 17.4215
Iz¯ = c * (33 / z¯)1/6
= 0.1500 * (33 / 17.4215)1/6
ITEM NO.: C-6211 183
Gust Factor Calculations: Hydrotest, New, field
Vessel is considered a rigid structure as n1 = 3.3608 Hz ≥ 1 Hz.
Gust Factor Calculations: Operating, Corroded, Vortex Shedding
Vessel is considered a rigid structure as n1 = 3.8433 Hz ≥ 1 Hz.
= 0.1669
Lz¯ = l * (z¯ / 33)ep
= 650.0000 * (17.4215 / 33)0.1250
= 600.1152
Q = Sqr(1 / (1 + 0.63 * ((b + h) / Lz¯)0.63))
= Sqr(1 / (1 + 0.63 * ((2.9265 + 29.0358) / 600.1152)0.63))
= 0.9538
G = 0.925 * (1 + 1.7 * gQ * Iz¯ * Q) / (1 + 1.7 * gv * Iz¯)
= 0.925 * (1 + 1.7 * 3.40* 0.1669 * 0.9538) / (1 + 1.7 * 3.40 * 0.1669)
= 0.9040
z¯ = max ( 0.60 * h , zmin )
= max ( 0.60 * 29.0358 , 7.0000 )
= 17.4215
Iz¯ = c * (33 / z¯)1/6
= 0.1500 * (33 / 17.4215)1/6
= 0.1669
Lz¯ = l * (z¯ / 33)ep
= 650.0000 * (17.4215 / 33)0.1250
= 600.1152
Q = Sqr(1 / (1 + 0.63 * ((b + h) / Lz¯)0.63))
= Sqr(1 / (1 + 0.63 * ((2.9265 + 29.0358) / 600.1152)0.63))
= 0.9538
G = 0.925 * (1 + 1.7 * gQ * Iz¯ * Q) / (1 + 1.7 * gv * Iz¯)
= 0.925 * (1 + 1.7 * 3.40* 0.1669 * 0.9538) / (1 + 1.7 * 3.40 * 0.1669)
= 0.9040
z¯ = max ( 0.60 * h , zmin )
= max ( 0.60 * 29.0358 , 7.0000 )
= 17.4215
Iz¯ = c * (33 / z¯)1/6
= 0.1500 * (33 / 17.4215)1/6
= 0.1669
Lz¯ = l * (z¯ / 33)ep
= 650.0000 * (17.4215 / 33)0.1250
= 600.1152
Q = Sqr(1 / (1 + 0.63 * ((b + h) / Lz¯)0.63))
= Sqr(1 / (1 + 0.63 * ((2.9265 + 29.0358) / 600.1152)0.63))
ITEM NO.: C-6211 184
Gust Factor Calculations: Empty, Corroded, Vortex Shedding
Vessel is considered a rigid structure as n1 = 4.8531 Hz ≥ 1 Hz.
Gust Factor Calculations: Vacuum, Corroded, Vortex Shedding
Vessel is considered a rigid structure as n1 = 3.8433 Hz ≥ 1 Hz.
Table Lookup Values
= 0.9538
G = 0.925 * (1 + 1.7 * gQ * Iz¯ * Q) / (1 + 1.7 * gv * Iz¯)
= 0.925 * (1 + 1.7 * 3.40* 0.1669 * 0.9538) / (1 + 1.7 * 3.40 * 0.1669)
= 0.9040
z¯ = max ( 0.60 * h , zmin )
= max ( 0.60 * 29.0358 , 7.0000 )
= 17.4215
Iz¯ = c * (33 / z¯)1/6
= 0.1500 * (33 / 17.4215)1/6
= 0.1669
Lz¯ = l * (z¯ / 33)ep
= 650.0000 * (17.4215 / 33)0.1250
= 600.1152
Q = Sqr(1 / (1 + 0.63 * ((b + h) / Lz¯)0.63))
= Sqr(1 / (1 + 0.63 * ((2.9265 + 29.0358) / 600.1152)0.63))
= 0.9538
G = 0.925 * (1 + 1.7 * gQ * Iz¯ * Q) / (1 + 1.7 * gv * Iz¯)
= 0.925 * (1 + 1.7 * 3.40* 0.1669 * 0.9538) / (1 + 1.7 * 3.40 * 0.1669)
= 0.9040
z¯ = max ( 0.60 * h , zmin )
= max ( 0.60 * 29.0358 , 7.0000 )
= 17.4215
Iz¯ = c * (33 / z¯)1/6
= 0.1500 * (33 / 17.4215)1/6
= 0.1669
Lz¯ = l * (z¯ / 33)ep
= 650.0000 * (17.4215 / 33)0.1250
= 600.1152
Q = Sqr(1 / (1 + 0.63 * ((b + h) / Lz¯)0.63))
= Sqr(1 / (1 + 0.63 * ((2.9265 + 29.0358) / 600.1152)0.63))
= 0.9538
G = 0.925 * (1 + 1.7 * gQ * Iz¯ * Q) / (1 + 1.7 * gv * Iz¯)
= 0.925 * (1 + 1.7 * 3.40* 0.1669 * 0.9538) / (1 + 1.7 * 3.40 * 0.1669)
= 0.9040
ITEM NO.: C-6211 185
= 11.5000, zg = 213.3600 m [Table 6-2, page 78]
c = 0.1500, l = 650.0000, ep = 0.1250 [Table 6-2, page 78]
a¯ = 0.1111, b¯ = 0.8000 [Table 6-2, page 78]
zmin = 7.0000 ft [Table 6-2, page 78]
gQ = 3.40 [6.5.8.1 page 26]
gv = 3.40 [6.5.8.1 page 26]
ITEM NO.: C-6211 186
Seismic Code
Vessel Characteristics
Period of Vibration Calculation
The fundamental period of vibration T (above) is calculated using the Rayleigh method of approximation:
T = 2 * PI * Sqr( {Sum(Wi * yi2 )} / {g * Sum(Wi * yi )} ), where
Wi is the weight of the ith lumped mass, and
yi is its deflection when the system is treated as a cantilever beam.
Seismic Shear Reports:
Operating, Corroded
Empty, Corroded
Vacuum, Corroded
Base Shear Calculations
Seismic Shear Report: Operating, Corroded
Method of seismic analysis: UBC 1997 building mounted
Seismic Zone: 2A
Rp Factor (Table 16-O): Rp = 2.2000
Soil profile: (Table 16-Q): SD
Importance Factor: Ip = 1.0000
Component Amplification Factor: ap = 1.0000
x/h Ratio 1.0000
Vertical Accelerations Considered: Yes
Force Multiplier: = 0.3333
Minimum Weight Multiplier: = 0.2000
Vessel height: 29.0358 ft (8.85 m)
Vessel Weight:
Operating, Corroded: 25,194 lb (11,428 kg)
Empty, Corroded: 21,603 lb (9,799 kg)
Vacuum, Corroded: 25,194 lb (11,428 kg)
Fundamental Period, T:
Operating, Corroded: 0.260 sec (f = 3.8 Hz)
Empty, Corroded: 0.206 sec (f = 4.9 Hz)
Vacuum, Corroded: 0.260 sec (f = 3.8 Hz)
ComponentElevation of bottom
above base (mm)
Elastic modulus E
(MPa)
Inertia I
(m4)
Seismic shear at
Bottom (N)
Bending Moment at
Bottom (N-m)
Ellipsoidal Head (Top) 8,630 184,200.0 * 588.1 86.9
Shell #1 7,619.5 184,200.0 0.0011 2,087.4 1,222.6
Shell #2 2,550.5 184,200.0 0.0011 13,643.7 49,388.7
ITEM NO.: C-6211 187
Seismic Shear Report: Empty, Corroded
Seismic Shear Report: Vacuum, Corroded
Vertical Acceleration Term, VAccel
Factor is applied to dead load.
Shell #3 (top) 0 184,200.0 0.0011 14,669.9 85,919.3
Shell #3 (bottom) 0 184,200.0 0.0011 17,323.6 113,230.1
Shell #4 -5,271.5 184,200.0 0.0011 12,382.7 31,417.5
Shell #5 -7,330 184,200.0 0.0011 8,266.1 9,645.1
Ellipsoidal Head (Bottom) -9,330 184,200.0 * 774.3 78.4
*Moment of Inertia I varies over the length of the component
ComponentElevation of bottom
above base (mm)
Elastic modulus E
(MPa)
Inertia I
(m4)
Seismic shear at
Bottom (N)
Bending Moment at
Bottom (N-m)
Ellipsoidal Head (Top) 8,630 195,233.3 * 651 96.2
Shell #1 7,619.5 195,233.3 0.0011 2,311 1,353.4
Shell #2 2,550.5 195,233.3 0.0011 14,520.9 52,878.9
Shell #3 (top) 0 195,233.3 0.0011 15,592.1 91,742.3
Shell #3 (bottom) 0 195,233.3 0.0011 11,837.1 65,479.9
Shell #4 -5,271.5 195,233.3 0.0011 6,730.5 12,870.9
Shell #5 -7,330 195,233.3 0.0011 2,474.3 2,925
Ellipsoidal Head (Bottom) -9,330 195,233.3 * 309 38.7
*Moment of Inertia I varies over the length of the component
ComponentElevation of bottom above base (mm)
Elastic modulus E(MPa)
Inertia I
(m4)
Seismic shear atBottom (N)
Bending Moment at Bottom (N-m)
Ellipsoidal Head (Top) 8,630 184,200.0 * 588.1 86.9
Shell #1 7,619.5 184,200.0 0.0011 2,087.4 1,222.6
Shell #2 2,550.5 184,200.0 0.0011 13,643.7 49,388.7
Shell #3 (top) 0 184,200.0 0.0011 14,669.9 85,919.3
Shell #3 (bottom) 0 184,200.0 0.0011 17,323.6 113,230.1
Shell #4 -5,271.5 184,200.0 0.0011 12,382.7 31,417.5
Shell #5 -7,330 184,200.0 0.0011 8,266.1 9,645.1
Ellipsoidal Head (Bottom) -9,330 184,200.0 * 774.3 78.4
*Moment of Inertia I varies over the length of the component
Compressive Side: = 1.0 + VAccel
VAccel Term is:
greater of (Force Mult * Base Shear / Weight) or (Min. Weight Mult.)
Force multiplier = 0.3333 Minimum Weight Multiplier = 0.2000
Condition Base Shear ( N) Weight ( kg) Force Mult * Shear
ITEM NO.: C-6211 188
Base Shear Calculations
Operating, Corroded
Empty, Corroded
Vacuum, Corroded
Base Shear Calculations: Operating, Corroded
V(32-1) = 4 * Ca * Ip * Wp = 4 * 0.2200 * 1.0000 * 25,193.9434 = 22,170.6699
V(32-2) = ap * Ca * Ip * (1 + 3 * (x/h)) * Wp / Rp = 1.0000 * 0.2200 * 1.0000 * (1 + 3 * 1.0000) * 25,193.9434 / 2.2000 =
10,077.5771
V(32-3) = 0.70 * Ca * Ip * Wp = 0.7 * 0.2200 * 1.0000 * 25,193.9434 = 3,879.8672
To obtain V, take the greater of V(32-2) and V(32-3).
Then take the lesser of this and V(32-1), and divide by 1.4, giving 7,198.27 lb (3,265.08 kg)
Base Shear Calculations: Empty, Corroded
V(32-1) = 4 * Ca * Ip * Wp = 4 * 0.2200 * 1.0000 * 21,602.6289 = 19,010.3125
V(32-2) = ap * Ca * Ip * (1 + 3 * (x/h)) * Wp / Rp = 1.0000 * 0.2200 * 1.0000 * (1 + 3 * 1.0000) * 21,602.6289 / 2.2000 =
8,641.0508
V(32-3) = 0.70 * Ca * Ip * Wp = 0.7 * 0.2200 * 1.0000 * 21,602.6289 = 3,326.8047
To obtain V, take the greater of V(32-2) and V(32-3).
Then take the lesser of this and V(32-1), and divide by 1.4, giving 6,172.18 lb (2,799.65 kg)
Base Shear Calculations: Vacuum, Corroded
V(32-1) = 4 * Ca * Ip * Wp = 4 * 0.2200 * 1.0000 * 25,193.9434 = 22,170.6699
V(32-2) = ap * Ca * Ip * (1 + 3 * (x/h)) * Wp / Rp = 1.0000 * 0.2200 * 1.0000 * (1 + 3 * 1.0000) * 25,193.9434 / 2.2000 =
10,077.5771
V(32-3) = 0.70 * Ca * Ip * Wp = 0.7 * 0.2200 * 1.0000 * 25,193.9434 = 3,879.8672
To obtain V, take the greater of V(32-2) and V(32-3).
Then take the lesser of this and V(32-1), and divide by 1.4, giving 7,198.27 lb (3,265.08 kg)
WeightVAccel
Operating, Corroded 32,019.5 11,427.8 0.0952 0.2
Operating, New 32,019.5 11,427.8 0.0952 0.2
Empty, Corroded 27,455.2 9,798.8 0.0952 0.2
Empty, New 27,455.2 9,798.8 0.0952 0.2
Vacuum, Corroded 32,019.5 11,427.8 0.0952 0.2
ITEM NO.: C-6211 189
Support Lugs
Support material: A-516 70
This support is attached to: Shell #3
Distance from baseplate to datum: 9,350 mm
Local shell outer diameter, new: 792 mm
Local shell thickness, new: 6 mm
Local shell inner corrosion: 0 mm
Local shell outer corrosion: 0 mm
Lug allowable stress Sb =165.474MPa
Top plate width Wp = 60mm
Top plate thickness ta =30mm
Base plate width b = 300 mm
Base plate thickness tb =30mm
Base plate load bearing width Lb =75mm
Shell to center of load bearing area d =250 mm
Gusset height h =220 mm
Gusset thickness tg =12mm
Gusset separation Lg =180mm
Lug length, circumferential direction L =220 mm
Lug attachment fillet weld size: 7 mm
Pad width, circumferential direction: 320 mm
Pad length, longitudinal direction: 330 mm
Pad thickness te =6 mm
Pad attachment fillet weld size: 5 mm
Radial/bending lug stiffness ratio: 2
Number of support lugs: 4
ITEM NO.: C-6211 190
Stresses in Shell at Lug Supports
Condition
Total
Weight (kg)
ShearV (N)
Moment
M (N-m)
Lug orient
Lug LoadingStress in Shell
(MPa)
W
(kg)
Pr
(N)
VL
(N)
ML
(N-m)
Vc
(N)
Mc
(N-m)
Primary
Circ
(PL)
Primary
Long
(PL)
Combined
PL+Pb+Q
Wind, operating
Attack angle = 0°11,428 29,440 1,175
0° 1,714 -9,813 15,901 3,975.19 0 0.00 51.531 25.469 125.195
90° 2,857 0 28,017 7,004.27 4,907 1,226.66 50.463 29.806 124.547
180° 2,857 9,813 28,927 7,231.64 0 0.00 -46.712 -25.187 -145.169
270° 2,857 0 28,017 7,004.27-
4,907
-
1,226.6650.463 29.806 124.547
Wind, operating
Attack angle = 45°11,428 29,440 1,175
0° 1,714 -5,204 16,167 4,041.78-
5,204
-
1,301.0743.478 34.832 145.679
90° 1,714 -5,204 16,167 4,041.78 5,204 1,301.07 43.478 34.832 145.679
180° 2,857 5,204 28,660 7,165.04 5,204 1,301.07 41.851 27.138 -130.794
270° 2,857 5,204 28,660 7,165.04-
5,204
-
1,301.0741.851 27.138 -130.794
Wind, operating, new
Attack angle = 0°11,428 29,440 1,175
0° 1,714 -9,813 15,901 3,975.19 0 0.00 51.531 25.469 125.195
90° 2,857 0 28,017 7,004.27 4,907 1,226.66 50.463 29.806 124.547
180° 2,857 9,813 28,927 7,231.64 0 0.00 -46.712 -25.187 -145.169
270° 2,857 0 28,017 7,004.27-
4,907-
1,226.6650.463 29.806 124.547
Wind, operating, new
Attack angle = 45°11,428 29,440 1,175
0° 1,714 -5,204 16,167 4,041.78-
5,204
-
1,301.0743.478 34.832 145.679
90° 1,714 -5,204 16,167 4,041.78 5,204 1,301.07 43.478 34.832 145.679
180° 2,857 5,204 28,660 7,165.04 5,204 1,301.07 41.851 27.138 -130.794
270° 2,857 5,204 28,660 7,165.04-
5,204
-
1,301.0741.851 27.138 -130.794
Wind, empty, new Attack angle = 0°
9,799 29,440 1,175
0° 1,470 -9,813 13,505 3,376.12 0 0.00 36.721 17.706 113.667
90° 2,450 0 24,023 6,005.83 4,907 1,226.66 -33.433 -20.636 101.877
180° 2,450 9,813 24,933 6,233.20 0 0.00 -52.628 -27.496 -133.986
270° 2,450 0 24,023 6,005.83-
4,907
-
1,226.66-33.433 -20.636 101.877
Wind, empty, new
Attack angle = 45°9,799 29,440 1,175
0° 1,470 -5,204 13,771 3,442.72-
5,204-
1,301.0728.675 29.096 134.151
90° 1,470 -5,204 13,771 3,442.72 5,204 1,301.07 28.675 29.096 134.151
180° 2,450 5,204 24,666 6,166.61 5,204 1,301.07 -43.837 -29.096 -134.655
270° 2,450 5,204 24,666 6,166.61-
5,204
-
1,301.07-43.837 -29.096 -134.655
Wind, test, new
Attack angle = 0°18,608 13,112 4,124
0° 2,791 -4,371 24,180 6,045.00 0 0.00 62.404 33.86 125.471
90° 4,652 0 45,620 11,404.92 2,185 546.32 84.254 49.573 203.726
180° 4,652 4,371 48,812 12,202.87 0 0.00 80.717 49.615 -209.09
270° 4,652 0 45,620 11,404.92-
2,185-546.32 84.254 49.573 203.726
Wind, test, new
Attack angle = 45°18,608 13,112 4,124
0° 2,791 -2,318 25,115 6,278.72-
2,318-579.46 59.95 33.391 123.533
90° 2,791 -2,318 25,115 6,278.72 2,318 579.46 59.95 33.391 123.533
180° 4,652 2,318 47,877 11,969.16 2,318 579.46 83.165 50.084 206.615
ITEM NO.: C-6211 191
270° 4,652 2,318 47,877 11,969.16-
2,318-579.46 83.165 50.084 206.615
Wind, vacuum
Attack angle = 0°11,428 29,440 1,175
0° 1,714 -9,813 15,901 3,975.19 0 0.00 33.364 16.382 -108.406
90° 2,857 0 28,017 7,004.27 4,907 1,226.66 -45.685 -27.42 -122.154
180° 2,857 9,813 28,927 7,231.64 0 0.00 -64.88 -34.274 -154.256
270° 2,857 0 28,017 7,004.27-
4,907
-
1,226.66-45.685 -27.42 -122.154
Wind, vacuum
Attack angle = 45°11,428 29,440 1,175
0° 1,714 -5,204 16,167 4,041.78-
5,204
-
1,301.0725.311 25.745 127.567
90° 1,714 -5,204 16,167 4,041.78 5,204 1,301.07 25.311 25.745 127.567
180° 2,857 5,204 28,660 7,165.04 5,204 1,301.07 -56.089 -32.447 -141.542
270° 2,857 5,204 28,660 7,165.04-
5,204
-
1,301.07-56.089 -32.447 -141.542
Seismic, operating,
new
Attack angle = 0°
11,428 31,994 27,311
0° 2,857-
10,6656,879 1,719.66 0 0.00 40.52 24.98 134.793
90° 3,428 0 33,620 8,405.12 5,332 1,333.06 58.261 34.619 148.292
180° 3,428 10,665 54,759 13,689.73 0 0.00 -84.213 -47.905 -257.099
270° 3,428 0 33,620 8,405.12-
5,332
-
1,333.0658.261 34.619 148.292
Seismic, operating,
new
Attack angle = 45°
11,428 31,994 27,311
0° 2,857 -5,656 13,070 3,267.48-
5,656
-
1,413.9339.99 37.356 157.187
90° 2,857 -5,656 13,070 3,267.48 5,656 1,413.93 39.99 37.356 157.187
180° 3,428 5,656 48,568 12,141.90 5,656 1,413.93 68.734 43.961 -216.454
270° 3,428 5,656 48,568 12,141.90-
5,656
-
1,413.9368.734 43.961 -216.454
Seismic, empty, new
Attack angle = 0°9,799 27,429 26,262
0° 2,450 -9,143 3,696 924.08 0 0.00 21.843 16.499 105.697
90° 2,940 0 28,828 7,207.00 4,572 1,142.89 -40.121 -24.766 -122.23
180° 2,940 9,143 49,155 12,288.75 0 0.00 -85.109 -47.891 -234.704
270° 2,940 0 28,828 7,207.00-
4,572
-
1,142.89-40.121 -24.766 -122.23
Seismic, empty, new
Attack angle = 45°9,799 27,429 26,262
0° 2,450 -4,849 9,650 2,412.49-
4,849
-
1,212.2122.291 27.11 124.912
90° 2,450 -4,849 9,650 2,412.49 4,849 1,212.21 22.291 27.11 124.912
180° 2,940 4,849 43,201 10,800.34 4,849 1,212.21 -68.982 -40.114 -197.114
270° 2,940 4,849 43,201 10,800.34-
4,849-
1,212.21-68.982 -40.114 -197.114
Seismic, vacuum
Attack angle = 0°11,428 31,994 27,311
0° 2,857-
10,6656,879 1,719.66 0 0.00 22.353 15.892 -117.025
90° 3,428 0 33,620 8,405.12 5,332 1,333.06 -53.483 -32.233 -145.9
180° 3,428 10,665 54,759 13,689.73 0 0.00 -102.38 -56.992 -266.186
270° 3,428 0 33,620 8,405.12-
5,332-
1,333.06-53.483 -32.233 -145.9
Seismic, vacuum
Attack angle = 45°11,428 31,994 27,311
0° 2,857 -5,656 13,070 3,267.48-
5,656
-
1,413.9321.822 28.269 139.047
90° 2,857 -5,656 13,070 3,267.48 5,656 1,413.93 21.822 28.269 139.047
180° 3,428 5,656 48,568 12,141.90 5,656 1,413.93 -84.612 -48.58 -225.548
270° 3,428 5,656 48,568 12,141.90-
5,656-
1,413.93-84.612 -48.58 -225.548
0° 1,714 -4,520 15,838 3,959.56 0 0.00 41.775 22.139 85.902
ITEM NO.: C-6211 192
Applied Loads (Seismic, vacuum, Attack angle = 0°, lug orientation = 180°)
Maximum stresses due to the applied loads at the pad edge (includes pressure)
Vortex shedding,
operating Attack angle = 0°
11,428 13,561 1,256
90° 2,857 0 28,017 7,004.27 2,260 565.05 50.463 29.806 124.485
180° 2,857 4,520 28,989 7,247.27 0 0.00 43.554 27.841 -130.159
270° 2,857 0 28,017 7,004.27-
2,260-565.05 50.463 29.806 124.485
Vortex shedding,
operating
Attack angle = 45°
11,428 13,561 1,256
0° 1,714 -2,397 16,123 4,030.73-
2,397-599.32 38.287 21.07 81.02
90° 1,714 -2,397 16,123 4,030.73 2,397 599.32 38.287 21.07 81.02
180° 2,857 2,397 28,704 7,176.09 2,397 599.32 47.043 28.917 -122.844
270° 2,857 2,397 28,704 7,176.09-
2,397-599.32 47.043 28.917 -122.844
Vortex shedding, empty
Attack angle = 0°
9,799 14,313 4,307
0° 1,470 -4,771 11,081 2,770.16 0 0.00 24.139 12.473 60.722
90° 2,450 0 24,023 6,005.83 2,386 596.38 -33.433 -20.636 101.822
180° 2,450 4,771 27,357 6,839.16 0 0.00 -46.788 -26.455 -129.704
270° 2,450 0 24,023 6,005.83-
2,386-596.38 -33.433 -20.636 101.822
Vortex shedding,
empty Attack angle = 45°
9,799 14,313 4,307
0° 1,470 -2,530 12,057 3,014.24-
2,530-632.56 21.401 14.141 65.473
90° 1,470 -2,530 12,057 3,014.24 2,530 632.56 21.401 14.141 65.473
180° 2,450 2,530 26,380 6,595.09 2,530 632.56 -41.334 -24.228 -119.121
270° 2,450 2,530 26,380 6,595.09-
2,530-632.56 -41.334 -24.228 -119.121
Vortex shedding,
vacuum
Attack angle = 0°
11,428 13,561 1,256
0° 1,714 -4,520 15,838 3,959.56 0 0.00 23.608 -14.155 76.814
90° 2,857 0 28,017 7,004.27 2,260 565.05 -45.685 -27.42 -122.099
180° 2,857 4,520 28,989 7,247.27 0 0.00 -55.296 -31.054 -139.247
270° 2,857 0 28,017 7,004.27-
2,260-565.05 -45.685 -27.42 -122.099
Vortex shedding,
vacuum
Attack angle = 45°
11,428 13,561 1,256
0° 1,714 -2,397 16,123 4,030.73-
2,397-599.32 -24.752 -15.72 71.912
90° 1,714 -2,397 16,123 4,030.73 2,397 599.32 -24.752 -15.72 71.912
180° 2,857 2,397 28,704 7,176.09 2,397 599.32 -51.021 -29.496 -131.931
270° 2,857 2,397 28,704 7,176.09-
2,397-599.32 -51.021 -29.496 -131.931
Radial load: Pr = 10,664.51 N
Circumferential moment: Mc = 0 N-m
Circumferential shear: Vc = 0 N
Longitudinal moment: ML =13,689.73 N-m
Longitudinal shear: VL =54,758.92 N
Torsion moment: Mt = 0 N-m
Internal pressure: P = -102.97kPa
Mean shell radius: Rm = 393 mm
Local shell thickness: T = 6 mm
Shell yield stress: Sy = 147 MPa
Design factor: 3
ITEM NO.: C-6211 193
= Rm / T = 393 / 6 = 65.5
C1 = 160, C2 = 165 mm
Local circumferential pressure stress = P*Ri / T =-6.695 MPa
Local longitudinal pressure stress = P*Ri / (2*T) =-3.351 MPa
Maximum combined stress (PL+Pb+Q) = -266.19 MPa
Allowable combined stress (PL+Pb+Q) = +-3*S = +-384 MPa
Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material.
The maximum combined stress (PL+Pb+Q) is within allowable limits.
Maximum local primary membrane stress (PL) = -102.38 MPa
Allowable local primary membrane stress (PL) = +-1.5*S = +-192 MPa
The maximum local primary membrane stress (PL) is within allowable limits.
Stresses at the pad edge per WRC Bulletin 107
Figure value Au Al Bu Bl Cu Cl Du Dl
3C* 1.4338 0.4215 0 0 0 0 -6.488 -6.488 -6.488 -6.488
4C* 4.3074 0.4168 -19.478 -19.478 -19.478 -19.478 0 0 0 0
1C 0.0657 0.4114 0 0 0 0 -116.777 116.777 -116.777 116.777
2C-1 0.0058 0.4114 -10.308 10.308 -10.308 10.308 0 0 0 0
3A* 1.368 0.4113 0 0 0 0 0 0 0 0
1A 0.0567 0.4534 0 0 0 0 0 0 0 0
3B* 2.4138 0.4156 -76.208 -76.208 76.208 76.208 0 0 0 0
1B-1 0.0074 0.4119 -104.297 104.297 104.297 -104.297 0 0 0 0
Pressure stress* -6.695 -6.695 -6.695 -6.695 -6.695 -6.695 -6.695 -6.695
Total circumferential stress -216.985 12.224 144.025 -43.954 -129.959 103.594 -129.959 103.594
Primary membrane circumferential stress* -102.38 -102.38 50.035 50.035 -13.183 -13.183 -13.183 -13.183
3C* 1.4594 0.4168 -6.598 -6.598 -6.598 -6.598 0 0 0 0
4C* 4.2548 0.4215 0 0 0 0 -19.243 -19.243 -19.243 -19.243
1C-1 0.0136 0.4176 -24.173 24.173 -24.173 24.173 0 0 0 0
2C 0.03 0.4176 0 0 0 0 -53.324 53.324 -53.324 53.324
4A* 5.8488 0.4113 0 0 0 0 0 0 0 0
2A 0.0224 0.468 0 0 0 0 0 0 0 0
4B* 1.3848 0.4156 -47.043 -47.043 47.043 47.043 0 0 0 0
2B-1 0.0141 0.4424 -185.021 185.021 185.021 -185.021 0 0 0 0
Pressure stress* -3.351 -3.351 -3.351 -3.351 -3.351 -3.351 -3.351 -3.351
Total longitudinal stress -266.186 152.202 197.942 -123.754 -75.918 30.73 -75.918 30.73
Primary membrane longitudinal stress* -56.992 -56.992 37.094 37.094 -22.594 -22.594 -22.594 -22.594
Shear from Mt 0 0 0 0 0 0 0 0
ITEM NO.: C-6211 194
Note: * denotes primary stress.
Maximum stresses due to the applied loads at the lug edge (includes pressure)
= Rm / T = 393 / 12 = 32.75
C1 = 110, C2 = 140 mm
Local circumferential pressure stress = P*Ri / T =-6.695 MPa
Local longitudinal pressure stress = P*Ri / (2*T) =-3.351 MPa
Maximum combined stress (PL+Pb+Q) = -168.38 MPa
Allowable combined stress (PL+Pb+Q) = +-3*S = +-384 MPa
Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material.
The maximum combined stress (PL+Pb+Q) is within allowable limits.
Maximum local primary membrane stress (PL) = -62.34 MPa
Allowable local primary membrane stress (PL) = +-1.5*S = +-192 MPa
The maximum local primary membrane stress (PL) is within allowable limits.
Circ shear from Vc 0 0 0 0 0 0 0 0
Long shear from VL 0 0 0 0 -13.831 -13.831 13.831 13.831
Total Shear stress 0 0 0 0 -13.831 -13.831 13.831 13.831
Combined stress (PL+Pb+Q) -266.186 152.202 197.942 -123.754 -133.296 106.131 -133.296 106.131
Stresses at the lug edge per WRC Bulletin 107
Figure value Au Al Bu Bl Cu Cl Du Dl
3C* 1.5926 0.3591 0 0 0 0 -3.599 -3.599 -3.599 -3.599
4C* 3.4783 0.3338 -7.867 -7.867 -7.867 -7.867 0 0 0 0
1C 0.0613 0.3049 0 0 0 0 -27.241 27.241 -27.241 27.241
2C-1 0.0201 0.3049 -8.929 8.929 -8.929 8.929 0 0 0 0
3A* 1.2632 0.3033 0 0 0 0 0 0 0 0
1A 0.069 0.3377 0 0 0 0 0 0 0 0
3B* 2.4152 0.3287 -47.781 -47.781 47.781 47.781 0 0 0 0
1B-1 0.0167 0.3236 -74.898 74.898 74.898 -74.898 0 0 0 0
Pressure stress* -6.695 -6.695 -6.695 -6.695 -6.695 -6.695 -6.695 -6.695
Total circumferential stress -146.169 21.484 99.188 -32.75 -37.535 16.947 -37.535 16.947
Primary membrane circumferential stress* -62.342 -62.342 33.219 33.219 -10.294 -10.294 -10.294 -10.294
3C* 1.7609 0.3338 -3.985 -3.985 -3.985 -3.985 0 0 0 0
4C* 3.27 0.3591 0 0 0 0 -7.391 -7.391 -7.391 -7.391
1C-1 0.0401 0.3383 -17.816 17.816 -17.816 17.816 0 0 0 0
2C 0.03 0.3383 0 0 0 0 -13.328 13.328 -13.328 13.328
ITEM NO.: C-6211 195
Note: * denotes primary stress.
4A* 3.0483 0.3033 0 0 0 0 0 0 0 0
2A 0.0299 0.3737 0 0 0 0 0 0 0 0
4B* 1.23 0.3287 -29.227 -29.227 29.227 29.227 0 0 0 0
2B-1 0.028 0.3565 -113.998 113.998 113.998 -113.998 0 0 0 0
Pressure stress* -3.351 -3.351 -3.351 -3.351 -3.351 -3.351 -3.351 -3.351
Total longitudinal stress -168.377 95.251 118.073 -74.291 -24.07 2.586 -24.07 2.586
Primary membrane longitudinal stress* -36.563 -36.563 21.891 21.891 -10.742 -10.742 -10.742 -10.742
Shear from Mt 0 0 0 0 0 0 0 0
Circ shear from Vc 0 0 0 0 0 0 0 0
Long shear from VL 0 0 0 0 -8.15 -8.15 8.15 8.15
Total Shear stress 0 0 0 0 -8.15 -8.15 8.15 8.15
Combined stress (PL+Pb+Q) -168.377 95.251 118.073 -74.291 -41.375 21.725 -41.375 21.725
ITEM NO.: C-6211 196
Lug top plate required thickness, Bednar 5.2
ta = 0.75*(VL*d*L)/(Sb*Wp2*h)
= 0.75*(54,758.92*250*220)/(165.474*602*220)
= 17.24 mm
The top plate thickness of 30 mm is adequate.
Gusset plate required thickness, Bednar 5.2
Sc = 18,000 / (1 + (1/18,000)*(h/(0.289*tg))2)
= 18,000 / (1 + (1/18,000)*(8.6614/(0.289*0.4724))2)
= 14,711.043 psi (101.429 MPa)
tg = VL*(3*d - b)/(Sc*b2*Sin()2)
= 54,758.92*(3*250 - 300)/(101.429*3002*Sin(42.51)2)
= 5.91 mm
The gusset thickness of 12 mm is adequate.
Lug base plate required thickness
From Escoe table 4-8 (l/b = 1.6667)
Cx = 0.12567, Cy = -0.12433
fc = VL/(Lb*L)
= 54,758.92/(75*220)
= 3.319 MPa
Mx = Cx*fc*Lg2
= 0.12567*3.319*1802
= 13,512.87 mm-N/mm
My = Cy*fc*Lb2
= -0.12433*3.319*752
= -2,320.97 mm-N/mm
M = Max[Abs(Mx), Abs(My)]
= Max[Abs(13,512.87), Abs(-2,320.97)]
= 13,512.87 mm-N/mm
tb = Sqr(6*M / Sb)
= Sqr(6*13,512.9 / 165.474)
= 22.14 mm
The base plate thickness of 30 mm is adequate.
Support Lug to Pad Fillet Weld Sizing - Bednar chapters 5.2 and 10.3
Note: continuous welding is assumed for all support lug fillet welds.
dh = ta + h + tb
Lw = 2*(b + dh) = 2*(220 + 280) = 1,000 mm
ITEM NO.: C-6211 197
Zw = b*dh + dh2/3 = 220*280 + 2802/3 = 877.33 cm2
Zz = dh*b + b2/3 = 280*220 + 2202/3 = 777.33 cm2
Shear f1 = VL/Lw = 54,758.92/1,000 = 54.76 N/cm
Shear f2 = Vc/Lw = 0/1,000 = 0 N/cm
Bending f3 = larger absolute value of ML/Zw or Mc/Zz
= 100*ML/Zw
= 100*13,689.7/877.33
= 1,560.38 N/cm
Resultant load f = (f12 + f2
2 + f32)1/2
= (547.592 + 02 + 1,560.382)1/2
= 1,653.67 N/cm
Required weld size w = F/(0.707*0.55*Sa)
= 0.1*1,653.67/(0.707*0.55*128)
= 3.32 mm
The support lug fillet weld size of 7 mm is adequate.
Support Lug Pad to Shell Fillet Weld Sizing - Bednar chapters 5.2 and 10.3
Lw = 2*(b + dh) = 2*(320 + 330) = 1,300 mm
Zw = b*dh + dh2/3 = 320*320 + 3302/3 = 1,419 cm2
Zz = dh*b + b2/3 = 330*320 + 3202/3 = 1,397.33 cm2
Shear f1 = VL/Lw = 54,758.92/1,300 = 42.12 N/cm
Shear f2 = Vc/Lw = 0/1,300 = 0 N/cm
Bending f3 = larger absolute value of ML/Zw or Mc/Zz
= 100*ML/Zw
= 100*13,689.7/1,419
= 964.74 N/cm
Resultant load f = (f12 + f2
2 + f32)1/2
= (421.222 + 02 + 964.742)1/2
= 1,052.69 N/cm
Required weld size w = F/(0.707*0.55*Sa)
= 0.1*1,052.69/(0.707*0.55*128)
= 2.12 mm
The support lug pad fillet weld size of 5 mm is adequate.
ITEM NO.: C-6211 198
Lifting Lug
Geometry Inputs
Intermediate Values
Attached To Shell #1
Material A-516 70
Distance of Lift Point From Datum 18,280 mm
Angular Position 0.00 deg and 180.00 deg
Length of Lug, L 300 mm
Width of Lug, B 200 mm
Thickness of Lug, t 25 mm
Hole Diameter, d 70 mm
Pin Diameter, Dp 30 mm
Lug Diameter at Pin, D 200 mm
Weld Size, tw 6 mm
Weld Length, b1 65 mm
Weld Length, d2 90 mm
Width of Pad, Bp 300 mm
Length of Pad, Lp 190 mm
Pad Thickness, tp 6 mm
Pad Weld Size, twp 5 mm
Weld Length, L3 140 mm
Length to Brace Plate, L1 90 mm
Load Angle from Vertical, 0.0000 °
Has Brace Plate Yes
Load Factor 1.5000
Vessel Weight (new, incl. Load Factor), W 7972 kg
Lug Weight (new), Wlug 58 kg (Qty=2)
ITEM NO.: C-6211 199
Summary Values
COMPRESS recommends a spreader beam be used to prevent weak axis bending of the top lugs.
Ear lug brace plate should be removed before vessel is put in service.
Lift Forces
Lug Pin Diameter - Shear stress
Lug Thickness - Tensile stress
Allowable Stress, Tensile, t 137.757 MPa
Allowable Stress, Shear, s 91.838 MPa
Allowable Stress, Bearing, p 206.636 MPa
Allowable Stress, Bending, b 153.071 MPa
Allowable Stress, Weld Shear, allowable 91.838 MPa
Allowable Stress set to 1/3 Sy per ASME B30.20 No
Required Lift Pin Diameter, dreqd 16.46 mm
Required Lug Thickness, treqd 6.31 mm
Estimated Brace Plate Length 178.48 mm
Lug Stress Ratio, ratio 0.06
Weld Shear Stress Ratio, ratio 0.12
Lug Design Acceptable
Local Stresses WRC 107 Acceptable
Maximum Out of Plane Lift Angle - Weak Axis Bending 42.19 deg
Fr = force on vessel at lug
Fr = [W / cos(1)]*(1 - x1 / (x1 + x2))
= (7,972*9.8) / cos(0.0000)*(1 - 396/ (396 + 396))
= 39,089.5 N
where 'x1' is the distance between this lug and the center of gravity
'x2' is the distance between the second lift lug and the center of gravity
dreqd = (2*Fv / (*s))0.5
= (2*39,089.5 / (*91.84))0.5 = 16.46 mm
dreqd / Dp = 16.46 / 30 = 0.55 Acceptable
= Fv / A
= Fv / (2*(0.25**Dp2))
= 39,089.5 / (2*(0.25**302))= 27.65 MPa
/ s = 27.65 / 91.84 = 0.3 Acceptable
ITEM NO.: C-6211 200
Lug Thickness - Bearing stress
Lug Thickness - Shear stress
Shear stress length (per Pressure Vessel and Stacks, A. Keith Escoe)
treqd = Fv / ((D - d)*t)
= 39,089.5 / ((200 - 70)*137.76) = 2.18 mm
treqd / t= 2.18 / 25 = 0.09 Acceptable
= Fv / A
= Fv / ((D - d)*t)
= 39,089.5 / ((200 - 70)*25) = 12.03 MPa
/ t = 12.03 / 137.76 = 0.09 Acceptable
treqd = Fv / (Dp*p)
= 39,089.5 / (30*206.64) = 6.31 mm
treqd / t = 6.31 / 25 = 0.25 Acceptable
= Fv / Abearing
= Fv / (Dp*(t))
= 39,089.5 / (30*(25))= 52.12 MPa
/ p = 52.12 / 206.64 = 0.25 Acceptable
treqd = [Fv / s] / (2*Lshear)
= (39,089.5 / 91.84) / (2*66.07)= 3.22 mm
treqd / t = 3.22 / 25 = 0.13 Acceptable
= Fv / Ashear
= Fv / (2*t*Lshear )
= 39,089.5 / (2*25*66.07) = 11.83 MPa
/ s = 11.83 / 91.84 = 0.13 Acceptable
= 55*Dp / d
= 55*30 / 70
= 23.5714°
Z = 0.5*(D - d) + 0.5*Dp*(1 - cos())
= 0.5*(200 - 70) + 0.5*30*(1 - cos(23.5714))
= 66.25 mm
Z1 = 0.5*D - sqr(0.25*D*D - (0.5*Dp*sin())2)
= 0.5*200 - sqr(0.25*200*200 - (0.5*30*sin(23.5714))2)
= 0.18 mm
Lshear = Z - Z1
= 66.07 mm
ITEM NO.: C-6211 201
Lug Plate Stress
Weak Axis Bending Stress
Maximum lift cable angle from vertical = 42.19 deg
Loading on brace plate and head are not considered.
Weld Stress
Weld stress, direct and torsional shear, during rotational lift:
Direct shear:
Maximum weld shear stress occurs at lift angle 90.00 deg; lift force = 39,089.5 N
Lug stress, tensile + bending, during rotational lift:
ratio = [Ften / (Aten*t)] + [Mbend / (Zbend*b)] ≤ 1
= [(Ftop()*sin() ) / (t*B*t)] + [(6*Ftop() *L*cos() ) / (t*B2 * b)] ≤ 1
= 39,089.5*sin(90.0) / (25*200*137.76) + 6*(39,089.5)*300*cos(90.0) / (25*2002*153.07)
= 0.06 Acceptable
b = M / Z = (F*sin()* L1) / Z
F*cos() = 0.5*W => F = 0.5*W / cos()
= arctan( (2*b*Z ) / (W* L1) )
= arctan( (2*153.07*(200*252/6) ) / (78,178.9*90) ) = 42.19 deg
Aweld = A1 + A2 + A3 + A4 (brace plate)
= 0.707*tw*((d1 + b1) + (2*d2 + b2) + (d3 + b3) + B)
= 0.707*6*((140 + 65) + (2*90 + 70) + (140 + 65) + 200)
= 869.61 + 1,060.5 + 869.61 + 848.4 = 3,648.12 mm2
t = Fr*cos() / Aweld
= 39,089.5*cos(90.0) / 3,648.12 = 0 MPa
s = Fr*sin() / Aweld
= 39,089.5*sin(90.0) / 3,648.12 = 10.71 MPa
ITEM NO.: C-6211 202
Pad Weld Stress
Direct shear:
Maximum weld shear stress occurs at lift angle 90.00 deg; lift force = 39,089.5 N
WRC 107 Analysis
Geometry
Applied Loads
= sqr( t2 + s
2 )
= sqr( 02 + 10.712 ) = 10.71 MPa
/ allowable = 10.71 / 91.84 = 0.12 ≤ 1 Acceptable
Aweld = 0.707*twp*(2*Lp + Bp)
= 0.707*5*(2*190 + 300)= 2,403.8 mm2
t = Fr*cos() / Aweld
= 39,089.5*cos(90.0) / 2,403.8 = 0 MPa
s = Fr*sin() / Aweld
= 39,089.5*sin(90.0) / 2,403.8 = 16.26 MPa
= sqr( t2 + s
2 )
= sqr( 02 + 16.262 ) = 16.26 MPa
/ allowable = 16.26 / 91.84 = 0.18 ≤ 1 Acceptable
Height(radial): 25 mm Pad Thickness: 6 mm
Width (circumferential): 200 mm Pad Width: 300 mm
Length 140 mm Pad Length: 190 mm
Fillet Weld Size: 6 mm Pad Weld Size: 5 mm
Located on: Shell #1 (140 mm from top end)
Location Angle: 0.00° and 180.00°
Radial load: Pr = 0 N
Circumferential moment: Mc = 0 N-m
Circumferential shear: Vc = 0 N
Longitudinal moment: ML = 723.16N-m
Longitudinal shear: VL =39,089.47 N
Torsion moment: Mt = 0 N-m
Internal pressure: P = 0 kPa
ITEM NO.: C-6211 203
Maximum stresses due to the applied loads at the lug edge (includes pressure)
= Rm / T = 393 / 12 = 32.75
C1 = 106, C2 = 76 mm
Local circumferential pressure stress = P*Ri / T =0 MPa
Local longitudinal pressure stress = P*Ri / (2*T) =0 MPa
Maximum combined stress (PL+Pb+Q) = 21.43 MPa
Allowable combined stress (PL+Pb+Q) = +-3*S = +-414 MPa
The maximum combined stress (PL+Pb+Q) is within allowable limits.
Maximum local primary membrane stress (PL) = -5.56 MPa
Allowable local primary membrane stress (PL) = +-1.5*S = +-207 MPa
The maximum local primary membrane stress (PL) is within allowable limits.
Mean shell radius: Rm = 393 mm
Shell yield stress: Sy = 207 MPa
Design factor: 3
Stresses at the lug edge per WRC Bulletin 107
Figure value Au Al Bu Bl Cu Cl Du Dl
3C* 2.8076 0.2257 0 0 0 0 0 0 0 0
4C* 4.2318 0.2488 0 0 0 0 0 0 0 0
1C 0.0613 0.2512 0 0 0 0 0 0 0 0
2C-1 0.0285 0.2512 0 0 0 0 0 0 0 0
3A* 1.3492 0.2414 0 0 0 0 0 0 0 0
1A 0.0728 0.2782 0 0 0 0 0 0 0 0
3B* 3.4048 0.2161 -5.557 -5.557 5.557 5.557 0 0 0 0
1B-1 0.0259 0.2257 -8.798 8.798 8.798 -8.798 0 0 0 0
Pressure stress* 0 0 0 0 0 0 0 0
Total circumferential stress -14.355 3.241 14.355 -3.241 0 0 0 0
Primary membrane circumferential stress* -5.557 -5.557 5.557 5.557 0 0 0 0
3C* 2.4856 0.2488 0 0 0 0 0 0 0 0
4C* 4.4469 0.2257 0 0 0 0 0 0 0 0
1C-1 0.0653 0.2344 0 0 0 0 0 0 0 0
2C 0.0356 0.2344 0 0 0 0 0 0 0 0
4A* 2.7106 0.2414 0 0 0 0 0 0 0 0
2A 0.0356 0.2607 0 0 0 0 0 0 0 0
4B* 1.3328 0.2161 -2.041 -2.041 2.041 2.041 0 0 0 0
2B-1 0.0424 0.2274 -14.3 14.3 14.3 -14.3 0 0 0 0
Pressure stress* 0 0 0 0 0 0 0 0
ITEM NO.: C-6211 204
Note: * denotes primary stress.
Maximum stresses due to the applied loads at the pad edge (includes pressure)
= Rm / T = 393 / 6 = 65.5
C1 = 155, C2 = 100 mm
Local circumferential pressure stress = P*Ri / T =0 MPa
Local longitudinal pressure stress = P*Ri / (2*T) =0 MPa
Maximum combined stress (PL+Pb+Q) = 32.57 MPa
Allowable combined stress (PL+Pb+Q) = +-3*S = +-414 MPa
The maximum combined stress (PL+Pb+Q) is within allowable limits.
Maximum local primary membrane stress (PL) = -9.6 MPa
Allowable local primary membrane stress (PL) = +-1.5*S = +-207 MPa
The maximum local primary membrane stress (PL) is within allowable limits.
Total longitudinal stress -16.341 12.259 16.341 -12.259 0 0 0 0
Primary membrane longitudinal stress* -2.041 -2.041 2.041 2.041 0 0 0 0
Shear from Mt 0 0 0 0 0 0 0 0
Circ shear from Vc 0 0 0 0 0 0 0 0
Long shear from VL 0 0 0 0 -10.714 -10.714 10.714 10.714
Total Shear stress 0 0 0 0 -10.714 -10.714 10.714 10.714
Combined stress (PL+P
b+Q) -16.341 12.259 16.341 -12.259 21.429 21.429 21.429 21.429
Stresses at the pad edge per WRC Bulletin 107
Figure value Au Al Bu Bl Cu Cl Du Dl
3C* 2.3666 0.3116 0 0 0 0 0 0 0 0
4C* 5.1666 0.3563 0 0 0 0 0 0 0 0
1C 0.0657 0.3609 0 0 0 0 0 0 0 0
2C-1 0.0077 0.3609 0 0 0 0 0 0 0 0
3A* 1.6579 0.3408 0 0 0 0 0 0 0 0
1A 0.0567 0.3833 0 0 0 0 0 0 0 0
3B* 3.9084 0.2945 -9.604 -9.604 9.604 9.604 0 0 0 0
1B-1 0.0109 0.3079 -10.852 10.852 10.852 -10.852 0 0 0 0
Pressure stress* 0 0 0 0 0 0 0 0
Total circumferential stress -20.457 1.248 20.457 -1.248 0 0 0 0
Primary membrane circumferential stress* -9.604 -9.604 9.604 9.604 0 0 0 0
3C* 1.8968 0.3563 0 0 0 0 0 0 0 0
4C* 5.911 0.3116 0 0 0 0 0 0 0 0
1C-1 0.0235 0.3284 0 0 0 0 0 0 0 0
ITEM NO.: C-6211 205
Note: * denotes primary stress.
2C 0.03 0.3284 0 0 0 0 0 0 0 0
4A* 6.1514 0.3408 0 0 0 0 0 0 0 0
2A 0.0224 0.3523 0 0 0 0 0 0 0 0
4B* 2.0666 0.2945 -4.282 -4.282 4.282 4.282 0 0 0 0
2B-1 0.0196 0.3056 -19.671 19.671 19.671 -19.671 0 0 0 0
Pressure stress* 0 0 0 0 0 0 0 0
Total longitudinal stress -23.952 15.389 23.952 -15.389 0 0 0 0
Primary membrane longitudinal stress* -4.282 -4.282 4.282 4.282 0 0 0 0
Shear from Mt 0 0 0 0 0 0 0 0
Circ shear from Vc 0 0 0 0 0 0 0 0
Long shear from VL 0 0 0 0 -16.285 -16.285 16.285 16.285
Total Shear stress 0 0 0 0 -16.285 -16.285 16.285 16.285
Combined stress (PL+Pb+Q) -23.952 15.389 23.952 -15.389 32.571 32.571 32.571 32.571
ITEM NO.: C-6211 206
CALCULATION OF LIFTING LUG
DIMENSIONS
a = 120 mm, d = 45 mm, R = 55 mm, b = 155 mm,
c = 9 mm, t = 22 mm, α = 15 ˚ , e = 45 ˚
1) DESIGN CONDITION
LIFTING LUG Q'TY. : EA
MATERIAL OF LIFTING LUG :
ALOWABLE STRESS OF LIFTING LUG Sa = kg/mm2
VESSEL or H/EX ERECTION WEIGHT We = kg
LOAD IMPACT FACTOR C1 =
LOAD PER ONE LUG W = kg
W1 = W * SIN α = kg
W2 = W * COS α = kg
W3 = W * 0.1 = kg (10% ASSUMED)
2) STRENGTH CALCULATION(2-1) TENSILE STRESS DUE TO "W1"ST = W1 / [(2 * R - d) * t)] = 1164.69 / [(2 * 55.00 - 45.00 ) * 22.00) = kg/mm2 < Sa = 14.06 kg/mm2
(2-2) BENDING STRESS DUE TO "W1"M2 = W1 * b = * 155 = kg-mm
Z2 = t * a2 / 6 = 22 * ( 120 ) 2 /6 = mm3
Sb1 = M2 / Z2 = kg/mm2 < Sa = 14.06 kg/mm2
(2-3) BENDING STRESS DUE TO "W3"
M3 = W3 * b = * 155 = kg-mm
Z3 = a * t2 / 6 = 120 * ( 22 ) 2 /6 = mm3
Sb2 = M3 / Z3 = kg/mm2 < Sa = 14.06 kg/mm2
(2-4) LUG STRESS TENSILE + BENDING DURING LIFTSratio = ST/Sa + [MAX.Sb1 or Sb2] / Sa = 0.570 < 1.0 O.K.!!(2-5) SHEAR STRESS DUE TO "W"
SS = W / [(R - d/2) * t] = 4500.00 / [(55.00 - 45.00 / 2) * 22.00]
= kg/mm2 < 0.8*Sa = 11.248 kg/mm2
(2-6) SHEAR STRESS OF WELDMENT
SWS = W / (2 * a *c) = 4500.00 / ( 2 * 120.00 * 9.00)
= 2.0833 kg/mm2 < 0.49*Sa = 6.8894 kg/mm2
** ALL CONDITIONS ARE SATISFACTORY !! **
9680.00
7.206
6.294
0.814
1164.69 180526.3
52800.00
3.419
450.00 69750.0
6000
1.5
4500
1164.69
4346.67
450.00
ITEM NO.: C-6211
2A-240 304
14.06
207
CALCULATION OF SETTING BOLTITEM N0. :
DATA
1) MAX. MOMENT (SEISMC or WIND) 113229.9 N-m M = 11546.23 ㎏-m
2) OPERATION WEIGHT W = 11500 ㎏
3) SETTING BOLT B.C.D. BCD = 1304 ㎜
4) SETTING BOLT Q'TY. PER LUG Ano = 1 EA
5) SETTING BOLT SIZE = M30
6) SETTING BOLT ROOT AREA Ab = 560.574 ㎟
7) ALLOW. STRESS OF SETTING BOLT Sa = 14.06 ㎏/㎟
8) Q'TY. OF LUG SUPPORT No = 4 EA
CALCULATIONS
Sb= 1 / (ANo * Ab) * ( 1000M / BCD - W / No)
= 10.6667 ㎏/㎟
Sb = 10.667 ㎏/㎟ < Sa = 14.06 ㎏/㎟
O.K.!!
C-6211
208