2015 7500 verification manual

Verification Manual

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Table of Contents

1. Introduction .......................................................................................................................................... 6

1.1 Purpose of Document ................................................................................................................................ 6 1.2 Scope of Software ..................................................................................................................................... 6 1.3 Published Examples .................................................................................................................................. 6 1.4 Intellectual Property Statement ................................................................................................................. 6

2. Verification of Published Examples ..................................................................................................... 7

2.1 PTB-4-2013: ASME Section VIII - Division 1 Example Problems ......................................................... 8 E3.1 - Use of MDMT Exemptions Curves ................................................................................................. 9 E3.2 - Use of MDMT Exemptions Curves with Stress Reduction ............................................................ 13 E3.3 - Determine the MDMT for a Nozzle-to-Shell Welded Assembly................................................... 18 E4.1.2 - Determine Required Wall Thickness of Hemispherical Head ................................................... 26 E4.2.1 - Nondestructive Examination Requirement for Vessel Design ..................................................... 32 E4.2.2 - Nozzle Detail and Weld Sizing ................................................................................................... 44 E4.2.3 - Nozzle Detail with Reinforcement Pad and Weld Sizing ........................................................... 53 E4.3.1 - Cylindrical Shell .......................................................................................................................... 64 E4.3.2 - Conical Shell ............................................................................................................................... 70 E4.3.3 - Spherical Shell ............................................................................................................................ 76 E4.3.4 - Torispherical Head ...................................................................................................................... 84 E4.3.5 - Ellipsoidal Head .......................................................................................................................... 89 E4.3.6 - Combined Loadings and Allowable Stresses Cylindrical Shell ................................................... 98 E4.3.7 - Conical Transitions Without a Knuckle .....................................................................................105E4.3.8 - Conical Transitions With a Knuckle ......................................................................................... 144 E4.4.1 - Cylindrical Shell ....................................................................................................................... 149 E4.4.2 - Conical Shell ............................................................................................................................. 156 E4.4.3 - Spherical Shell and Hemispherical Head .................................................................................. 164 E4.4.4 - Torispherical Head .................................................................................................................... 171 E4.4.5 - Ellipsoidal Head ........................................................................................................................ 176 E4.4.6 - Combined Loadings and Allowable Stresses Cylindrical Shell ................................................ 181 E4.4.7 - Conical Transitions Without a Knuckle .................................................................................... 192 E4.4.8 - Conical Transitions With a Knuckle ......................................................................................... 228 E4.5.1 - Radial Nozzle in Cylindrical Shell ........................................................................................... 237E4.5.2 - Hillside Nozzle in Cylindrical Shell ......................................................................................... 249 E4.5.3 - Radial Nozzle in Ellipsoidal Head ............................................................................................ 265 E4.5.4 - Radial Nozzle in Cylindrical Shell ........................................................................................... 277 E4.5.5 - Pad Reinforced Radial Nozzle in Cylindrical Shell .................................................................. 285 E4.5.6 - Radial Nozzle in an Ellipsoidal Head with Inside Projection ................................................... 296 E4.6.1 - Flat Unstayed Circular Heads Attached by Bolts ..................................................................... 303

E4.7.1 - Thickness Calculation for a Type D Head ................................................................................ 315 E4.15.1 - Horizontal Vessel with Zick's Analysis .................................................................................. 325 E4.15.2 - Vertical Vessel, Skirt Design .................................................................................................. 336 E4.16.1 - Integral Type ........................................................................................................................... 341 E4.16.2 - Loose Type ............................................................................................................................. 361 E4.18.1 - U-Tube Tubesheet Integral with Shell and Channel ................................................................ 378 E4.18.2 - U-Tube Tubesheet Gasketed with Shell and Channel .............................................................. 390 E4.18.3 - U-Tube Tubesheet Gasketed with Shell and Channel .............................................................. 401 E4.18.4 - U-Tube Tubesheet Gasketed with Shell and Channel, Extended as Flange ............................. 410 E4.18.5 - Fixed Tubesheet Exchanger, Configuration b, Tubesheet Integral with Shell, Extended as a Flange and Gasketed on the Channel side .............................................................................................. 424 E4.18.6 - Fixed Tubesheet Exchanger, Configuration b, Tubesheet Integral with Shell, Extended as a Flange and Gasketed on the Channel Side ............................................................................................. 444 E4.18.7 - Fixed Tubesheet Exchanger, Configuration a ......................................................................... 471

E4.6.3 - Integral Flat Head with a Centrally Located Opening .............................................................. 309

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E4.18.8 - Stationary Tubesheet Gasketed with Shell and Channel; Floating Tubesheet Gasketed, Not Extended as a Flange .............................................................................................................................. 491 E4.18.9 - Stationary Tubesheet Gasketed with Shell and Channel; Floating Tubesheet Integral .............508 E4.18.10 - Stationary Tubesheet Gasketed with Shell and Channel; Floating Tubesheet Internally Sealed ................................................................................................................................................................ 528 E4.19.1 - U-Shaped Un-reinforced Bellows Expansion Joint and Fatigue Evaluation .......................... 545 E4.19.2 - Toroidal Bellows Expansion Joint and Fatigue Evaluation .................................................... 551 E4.20.1 - Tube-To-Tubesheet Welds - Full Strength Welds .................................................................. 556 E4.20.2 - Tube-To-Tubesheet Welds - Partial Strength Welds .............................................................. 569 E6.1 - Postweld Heat Treatment of a Pressure Vessel ............................................................................ 585 E6.2 - Out-of-Roundness of a Cylindrical Forged Vessel ..................................................................... 592 E7.1 - NDE: Establish Joint Efficiencies, RT-1 ..................................................................................... 595 E7.2 - NDE: Establish Joint Efficiencies, RT-2 ..................................................................................... 597 E7.3 - NDE: Establish Joint Efficiencies, RT-3 ..................................................................................... 599 E7.4 - NDE: Establish Joint Efficiencies, RT-4 ..................................................................................... 601 E8.1 - Determination of a Hydrostatic Test Pressure ............................................................................. 603 E8.2 - Determination of a Pneumatic Test Pressure ............................................................................... 605

2.2 PTB-3-2013: ASME Section VIII - Division 2 Example Problems ..................................................... 607 E3.1 - Use of MDMT Exemptions Curves ............................................................................................. 608 E3.2 - Use of MDMT Exemptions Curves with Stress Reduction ......................................................... 613 E4.1.2 - Determine Required Wall Thickness of Hemispherical Head ................................................. 617 E4.1.3 - Determine Required Wall Thickness of Hemispherical Head - Higher Strength Material ...... 620 E4.2.1 - Nondestructive Examination Requirement for Vessel Design .................................................. 623 E4.2.2 - Nozzle Detail and Weld Sizing ................................................................................................. 628 E4.2.3 - Nozzle Detail with Reinforcement Pad and Weld Sizing ......................................................... 629 E4.3.1 - Cylindrical Shell ....................................................................................................................... 630 E4.3.2 - Conical Shell ............................................................................................................................. 633 E4.3.3 - Spherical Shell .......................................................................................................................... 636 E4.3.4 - Torispherical Head .................................................................................................................... 639 E4.3.5 - Ellipsoidal Head ........................................................................................................................ 643 E4.3.6 - Combined Loadings and Allowable Stresses ........................................................................... 648 E4.3.7 - Conical Transitions Without a Knuckle .................................................................................... 655 E4.3.8 - Conical Transitions With a Knuckle ......................................................................................... 671 E4.4.1 - Cylindrical Shell ....................................................................................................................... 672 E4.4.2 - Conical Shell ............................................................................................................................. 673 E4.4.3 - Spherical Shell and Hemispherical Head .................................................................................. 674 E4.4.4 - Torispherical Head .................................................................................................................... 675 E4.4.5 - Ellipsoidal Head ........................................................................................................................ 676 E4.4.6 - Combined Loadings and Allowable Stresses Cylindrical Shell ................................................ 677 E4.4.7 - Conical Transitions Without a Knuckle .................................................................................... 678 E4.5.1 - Radial Nozzle in Cylindrical Shell ........................................................................................... 702 E4.5.2 - Hillside Nozzle in Cylindrical Shell ......................................................................................... 710 E4.5.3 - Radial Nozzle in Ellipsoidal Head ............................................................................................ 718 E4.6.1 - Flat Unstayed Circular Heads Attached by Bolts ..................................................................... 726 E4.15.1 - Horizontal Vessel with Zick's Analysis .................................................................................. 729 E4.15.2 - Vertical Vessel, Skirt Design .................................................................................................. 738 E4.16.1 - Integral Type ........................................................................................................................... 743 E4.16.2 - Loose Type ............................................................................................................................. 754 E6.1 - Postweld Heat Treatment of a Pressure Vessel ............................................................................ 765 E6.2 - Out-of-Roundness of a Cylindrical Forged Vessel ..................................................................... 772 E8.1 - Determination of a Hydrostatic Test Pressure ............................................................................. 775 E8.2 - Determination of a Pneumatic Test Pressure ............................................................................... 777

2.3 Taylor Forge Examples ......................................................................................................................... 779 Example 1 - Welding Neck Flange Design ............................................................................................ .780

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Example 2 - Slip on Flange Design - Flat Faced .................................................................................... 788 3. References ........................................................................................................................................ 794

Appendix A........................................................................................................................................... 795

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1. Introduction

1.1 Purpose of Document

This document is a validation of calculations performed by COMPRESS against published example problems (see 1.3 below). It shall be used to assess that the software has sufficient coding quality and accurate mathematical calculations. Any discrepancies between COMPRESS and published example calculations are explained at the end of each problem. All COMPRESS files referenced are included in the project file labeled 'SampleProject' and can be accessed in the Window menu by activating the Project Toolbar option.

1.2 Scope of Software

COMPRESS is a software application that is used to model, calculate, and create detailed reports for pressure vessels and heat exchangers using the latest Edition of the ASME Boiler and Pressure Vessel Code. The purpose of this software program is to provide users with a powerful, accurate, and user-friendly tool that will enhance engineering productivity and simplify vessel design.

1.3 Published Examples

Examples from several published manuals are included in this document. These include: ASME Section VIII - Division 1 Example Problem Manual (ASME PTB-4-2013), ASME Section VIII - Division 2 Example Problem Manual (ASME PTB-3-2013), and Taylor Forge Bulletin 502 Edition VII.

1.4 Intellectual Property Statement

This document and its contents are considered to be proprietary. This material shall not be copied or distributed to other parties without the express written consent of Codeware, Inc.

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2. Verification of Published Examples

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2.1 ASME Section VIII - Division 1 Example Problems (PTB-4-2013)

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E3.1 - Use of MDMT Exemptions Curves

a. Division 1

Determine if impact testing is required for the proposed shell section.

i. Comparison of results

Fig E3.1 Division 1 MDMT Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME DifferenceGoverning thickness, tg (in) 1.8125 1.8125 0.00%

MDMT (F) -7 -7 0.00%Impact testing required per

UCS-66(a)?Yes Yes -

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Deficiencies Summary

Deficiencies for Cylinder #1The Rated MDMT of -7 F is warmer than the Design MDMT of -20 F.

Warnings Summary

Warnings for VesselThe vessel does not have a right closure (head or cover). (warning)The vessel does not have a left closure (head or cover). (warning)

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Pressure Summary

Component Summary

IdentifierP

Design(psi)

TDesign

(F)MDMT

(F)MDMT

ExemptionImpactTested

Cylinder #1 100 650 -7 Note 1 No

Chamber Summary

Design MDMT -20 F

Rated MDMT -7 F @ 100 psi

MAWP hot & corroded 100 psi

(1) This pressure chamber is not designedfor external pressure.

Notes for Maximum Pressure Rating

Note # Details

1. Option to calculate MAP was not selected. See the Calculation->General tab of the Set Mode dialog.

2. Option to calculate MAWP was not selected. See the Calculation->General tab of the Set Mode dialog.

Notes for MDMT Rating

Note # Exemption Details

1. Material impact test exemption temperature from Fig UCS-66 Curve D = -7 F UCS-66 governing thickness =1.8125 in

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Cylinder #1

ASME Section VIII Division 1, 2013 Edition

Component Cylinder

Material SA-516 70 (II-D p. 22, ln. 6)ImpactTested Normalized

Fine GrainPractice PWHT

Optimize MDMT/Find MAWP

No Yes No Yes No

DesignPressure (psi)

DesignTemperature (F)

DesignMDMT (F)

Internal 100 650 -20

Static Liquid Head

Condition Ps (psi) Hs (in) SGTest horizontal 0.87 24 1

Dimensions

Inner Diameter 24"

Length 96"

Nominal Thickness 1.8125"

Corrosion Inner 0.125"

Outer 0"

Weight and Capacity

Weight (lb) Capacity (US gal)New 3,993.15 188.01

Corroded 3,735.76 191.94

Radiography

Longitudinal seam Full UW-11(a) Type 1Left Circumferential

seamFull UW-11(a) Type 1

Right Circumferentialseam

Full UW-11(a) Type 1

Results Summary

Governing condition Internal pressure

Minimum thickness per UG-16 0.0625" + 0.125" = 0.1875"

Design thickness due to internal pressure (t) 0.1898"Rated MDMT -7 F

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UCS-66 Material Toughness Requirements

Governing thickness, tg = 1.8125"

Exemption temperature from Fig UCS-66 Curve D = -7F

No UCS-66.1 MDMT Reduction option is active, TR = 0F

MDMT = max[ MDMT - TR, -55] = max[ -7 - 0 , -55] = -7FRated MDMT of -7F > Design MDMT of -20F.

Design thickness, (at 650 F) UG-27(c)(1)

t = P*R / (S*E - 0.60*P) + Corrosion= 100*12.125 / (18,800*1.00 - 0.60*100) + 0.125= 0.1898"

% Extreme fiber elongation - UCS-79(d)

EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*1.8125 / 12.9063)*(1 - 12.9063 / )= 7.0218%

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E3.2 - Use of MDMT Exemptions Curves with Stress Reduction

a. Division 1

Determine if impact testing is required for the proposed shell section.


Fig E3.2 Division 1 MDMT Reduction Comparison

* In COMPRESS, the value of is interpolated from Fig. UCS-66.1, whereas in theexample manual the value of is approximated from Fig. UCS-66.1.

ii. COMPRESS Report


Coincident Ratio, Rts 0.801 0.801 0.00%

TR * (F) 19.9 20 0.50%

MDMT (F) -26.9 -27 0.37%

Impact testing required? No No -

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Pressure Summary

Component Summary

IdentifierP

Design(psi)

TDesign

(F)MDMT

(F)MDMT


Cylinder #1 356 300 -26.9 Note 1 No

Chamber Summary

Design MDMT -20 F

Rated MDMT -26.9 F @ 356 psi


(1) This pressure chamber is not designed forexternal pressure.


Note # Details





1. Material impact test exemption temperature from Fig UCS-66 Curve D = -7 FFig UCS-66.1 MDMT reduction = 19.9 F, (coincident ratio = 0.801)UCS-66 governing thickness =1.8125 in

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Cylinder #1


Component Cylinder




No Yes No Yes Yes



DesignMDMT (F)


Static Liquid Head


Dimensions

Inner Diameter 150"

Length 96"



Outer 0"

Weight and Capacity

Weight (lb) Capacity (US gal)New 23,485.14 7,343.98

Corroded 21,883.48 7,368.48

Radiography





Results Summary



Design thickness due to internal pressure (t) 1.4767"Rated MDMT -26.9 F

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tr = 356*75.125 / (20,000*1 - 0.6*356) = 1.3517"Stress ratio = tr*E* / (tn - c) = 1.3517*1 / (1.8125 - 0.125) = 0.801Reduction in MDMT, TR from Fig UCS-66.1 = 19.9F

MDMT = max[ MDMT - TR, -55] = max[ -7 - 19.9 , -55] = -26.9FMaterial is exempt from impact testing at the Design MDMT of -20F.




EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*1.8125 / 75.9063)*(1 - 75.9063 / )= 1.1939%

The extreme fiber elongation does not exceed 5%.

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E3.3 - Determine the MDMT for a Nozzle-to-Shell Welded Assembly

a. Division 1

Determine if impact testing is required for the proposed nozzle assembly comprised of a shell and integrally reinforced nozzle.


Fig E3.3 Division 1 MDMT Assembly Comparison

* In COMPRESS, the value of is interpolated from Fig. UCS-66.1, whereas in theexample manual the value of is approximated from Fig. UCS-66.1

** In COMPRESS, the MDMT reduction is applied to both the shell and the nozzle assembly. As the final adjusted MDMT of the shell is -26.9 F < -20 F, only the nozzle assembly requires impact testing. The example manual considers the shell and the nozzle assembly as a single welded assembly.

ii. COMPRESS Report


Coincident Ratio, Rts 0.801 0.801 0.00%

TR * (F) 19.9 20 0.50%

MDMTShell **(F) -26.9 N/A N/A

MDMTNozzleAssembly (F) 39.1 39 0.26%

Impact testing required? Yes Yes -

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Deficiencies for Nozzle #1 (N1)Nozzle assembly MDMT is only 39.1F: -20F is required

Warnings Summary


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Pressure Summary

Component Summary

IdentifierP

Design(psi)

TDesign

(F)MDMT

(F)MDMT


Cylinder #1 356 300 -26.9 Note 1 No

Nozzle #1 (N1) 356 300 39.1 Note 2 No

Chamber Summary

Design MDMT -20 F

Rated MDMT 39.1 F @ 356 psi


(1) This pressure chamber is not designed forexternal pressure.


Note # Details





1. Material impact test exemption temperature from Fig UCS-66 Curve D = -7 FFig UCS-66.1 MDMT reduction = 19.9 F, (coincident ratio = 0.801) UCS-66 governing thickness = 1.8125 in

2. Nozzle impact test exemption temperature from Fig UCS-66 Curve B = 59 FFig UCS-66.1 MDMT reduction = 19.9 F, (coincident ratio = 0.801) UCS-66 governing thickness = 1.8125 in.

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Cylinder #1


Component Cylinder




No Yes No Yes No



DesignMDMT (F)


Static Liquid Head


Dimensions

Inner Diameter 150"

Length 636"



Outer 0"

Weight and Capacity


Corroded 144,734.13 48,816.2

Radiography





Results Summary




21





MDMT = max[ MDMT - TR, -55] = max[ -7 - 19.9 , -55] = -26.9FMaterial is exempt from impact testing at the Design MDMT of -20F.




EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*1.8125 / 75.9063)*(1 - 75.9063 / )= 1.1939%


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Nozzle #1 (N1)


Note: Per UW-16(b) minimum inside corner radius r1 = min [1 / 4*t , 0.125 in] = 0.125 inLocation and Orientation

Located on Cylinder #1

Orientation 0

Nozzle center line offset to datum line 564"

End of nozzle to shell center 91"

Passes through a Category A joint NoNozzle

Access opening No

Material specification SA-105 (II-D p. 18, ln. 32)Inside diameter, new 16"

Wall thickness, tn 4.75"

Minimum wall thickness 1.5"

Corrosion allowance 0.125"

Projection available outside vessel, Lpr 14.1875"Heavy barrel length, Lhb 7.1875"

Local vessel minimum thickness 1.8125"

Liquid static head included 0 psi

Longitudinal joint efficiency 1Welds

Inner Fillet, Leg41 0.375"

Nozzle to vessel groove weld 1.8125"

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UCS-66 Material Toughness Requirements Nozzle


Exemption temperature from Fig UCS-66 Curve B = 59F


MDMT = max[ MDMT - TR, -55] = max[ 59 - 19.9 , -55] = 39.1FRated MDMT of 39.1F > Design MDMT of -20F.

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Reinforcement Calculations for Internal Pressure

UG-37 Area Calculation Summary (in2)UG-45

Summary(in)

For P = 356 psi @ 300 FThe opening is adequately reinforced

The nozzlepasses UG-45

Arequired

Aavailable A1 A2 A3 A5

Awelds treq tmin

21.9645 43.3879 5.4574 37.7899 -- -- 0.1406 0.4531 1.5

UG-41 Weld Failure Path Analysis Summary

The nozzle is exempt from weld strength calculations per UW-15(b)(1)

UW-16 Weld Sizing Summary

Weld description Required weldthroat size (in)Actual weld

throat size (in) Status

Nozzle to shell fillet (Leg41) 0.25 0.2625 weld size is adequate

Calculations for internal pressure 356 psi @ 300 F

Parallel Limit of reinforcement per UG-40 and Fig. UG-40 sketch (e-1)

LR = MAX(d, Rn + (tn - Cn) + (t - C))= MAX(16.25, 8.125 + (1.5 - 0.125) + (1.8125 - 0.125))= 16.25 in

Outer Normal Limit of reinforcement per UG-40 and Fig. UG-40 sketch (e-1)

LH = MIN(2.5*(t - C), 2.5*(tn - Cn) + te)= MIN(2.5*(1.8125 - 0.125), 2.5*(1.5 - 0.125) + 5.6292)= 4.2188 in

te = MIN( 7.1875 + 3.25*tan(30) , 3.25*tan(60) )= 5.6292 in

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn / (Sn*E - 0.6*P)= 356*8.125 / (20,000*1 - 0.6*356)= 0.1462 in

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E4.1.2 - Determine Required Wall Thickness of Hemispherical Head

a. Division 1

Determine the required thickness for a hemispherical head at the bottom of a vertical vessel.


Fig E4.1.2a Division 1 Hemispherical Head tr Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME DifferencePadjusted (psig) 1673.13 1673.14 0.00%

t (in) 2.155 2.155 0.00%

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Hemi Head #1


Component Hemispherical Head

Material SA-516 70 (II-D p. 22, ln. 6)Attached To Cylinder #1

ImpactTested Normalized



Yes (-50F) No No Yes NoDesign

Pressure (psi)Design

Temperature (F)Design

MDMT (F)Internal 1,650 300 -20

Static Liquid Head

Condition Ps (psi) Hs (in) SGOperating 23.13 720 0.89

Test horizontal 3.47 96 1

Dimensions

Inner Diameter 96"

Minimum Thickness 2.1814"


Outer 0"

Weight and Capacity


Corroded 8,835.7 1,010.55

Radiography

Category A joints - LongSeam Seamless No RT

Category A joints - CircSeam Full UW-11(a) Type 1

Results Summary




27


Material impact test temperature per UG-84 = -50F

tr = 1,673.13*48.125 / (2*20,000*1 - 0.2*1,673.13) = 2.03"Stress ratio = tr*E* / (tn - c) = 2.03*1 / (2.1814 - 0.125) = 0.9871UCS-66(i) reduction in MDMT, TR from Fig UCS-66.1 = 1.3FMDMT = max[Timpact - TR, -155] = max[ -50 - 1.3 , -155] = -51.3F

Design MDMT of -20F is acceptable.Design thickness, (at 300 F) UG-32(f)

t = P*R / (2*S*E - 0.20*P) + Corrosion= 1,673.13*48.125 / (2*20,000*1.00 - 0.20*1,673.13) + 0.125= 2.155"


EFE = (75*t / Rf)*(1 - Rf / Ro)= (75*2.1814 / 49.0907)*(1 - 49.0907 / )= 3.3327%


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b. Code Case 2695

Determine the required thickness for a hemispherical head at the bottom of a vertical vessel.


Fig E4.1.2b CC 2695 Hemispherical Head tr Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME DifferencePadjusted (psig) 1673.13 1673.14 0.00%

t (in) 2.1807 2.1807 0.00%

29

Hemi Head #1

ASME Section VIII Division 1, 2013 Edition (Code Case 2695)Component Hemispherical Head








Static Liquid Head

Condition Ps (psi) Hs (in) SG

Operating Top 21.58 671.875 0.89Bottom 23.13 720

Test horizontal Bottom 3.47 96 1

Dimensions

Inner Diameter 96"



Outer 0"

Weight and Capacity


Corroded 8,835.7 1,010.55

Radiography



Results Summary

Governing condition Operating Hot & Corroded

Design thickness due to internal pressure (t) 2.1807"Minimum thickness per 4.1.2 0.1875"

Rated MDMT -50F

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Material Toughness Requirements

Material impact test temperature per 3.11.7 = -50F

Stress ratio, Rts = 2.0557*1 / (2.1814 - 0.125 - 0) = 0.9996Reduction in MDMT from Figure UCS-66.1 = 0F

MDMT = max[Timpact - TR, -155] = max[ -50 - 0 , -155] = -50FDesign MDMT of -20F is acceptable.

Division 2 4.3.5.1 Design Thickness for Internal Pressure

td = D / 2 * (exp[0.5*P / (S*E)] - 1) + Corrosion (4.3.4)Operating Hot & Corroded

td = 96.25 / 2 * (exp[0.5*(1,650 + 23.13) / (20,000*1)] - 1) + 0.125 = 2.1807"Operating Cold & Corroded

tr = 96.25 / 2 * (exp[0.5*(1,650 + 23.13) / (20,000*1)] - 1) = 2.0557"

Division 2 6.1.2.3 % Extreme Fiber Elongation

f = 100*ln[Db / (Do - 2*t)] (Table 6.1)Forming strain not calculated.

31

E4.2.1 - Nondestructive Examination Requirement for Vessel Design

a. Division 1

Compare NDE requirements for a cylindrical shell.


Fig E4.2.1a Division 1 NDE Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME Differencet Full RT (in) 1.2414 1.2413 0.01%

t Spot RT (in) 1.4435 1.4435 0.00%

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Cylinder #1


Component Cylinder




Yes (-50F) No No No NoDesign



MDMT (F)Internal 725 300 -20

Static Liquid Head


Dimensions

Inner Diameter 60"

Length 96"



Outer 0"

Weight and Capacity


Corroded 5,893.21 1,184.85

Radiography





Results Summary




33



tr = 725*30.125 / (20,000*1 - 0.6*725) = 1.1163"Stress ratio = tr*E* / (tn - c) = 1.1163*1 / (1.25 - 0.125) = 0.9923UCS-66(i) reduction in MDMT, TR from Fig UCS-66.1 = 0.8FMDMT = max[Timpact - TR, -155] = max[ -50 - 0.8 , -155] = -50.8F

Design MDMT of -20F is acceptable.Design thickness, (at 300 F) UG-27(c)(1)



EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*1.25 / 30.625)*(1 - 30.625 / )= 2.0408%


34


Deficiencies for Cylinder #1UCS-57: Full radiography required on Cylinder longitudinal seam.

Warnings Summary


35

Cylinder #1


Component Cylinder








Static Liquid Head


Dimensions

Inner Diameter 60"

Length 96"



Outer 0"

Weight and Capacity


Corroded 7,232.15 1,184.85

Radiography

Longitudinal seam Spot UW-11(b) Type 1Left Circumferential




Results Summary




36



tr = 725*30.125 / (20,000*0.85 - 0.6*725) = 1.3185"Stress ratio = tr*E* / (tn - c) = 1.3185*0.85 / (1.5 - 0.125) = 0.8151UCS-66(i) reduction in MDMT, TR from Fig UCS-66.1 = 18.5FMDMT = max[Timpact - TR, -155] = max[ -50 - 18.5 , -155] = -68.5F

Design MDMT of -20F is acceptable.Design thickness, (at 300 F) UG-27(c)(1)



EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*1.5 / 30.75)*(1 - 30.75 / )= 2.439%


37

b. Code Case 2695

Compare NDE requirements for a cylindrical shell.


Fig E4.2.1b CC 2695 NDE Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME Differencet Full RT (in) 1.2371 1.2371 0.00%

t Spot RT (in) 1.4375 1.4375 0.00%

38

Cylinder #1

ASME Section VIII Division 1, 2013 Edition (Code Case 2695)Component Cylinder




Yes (-50F) No No No NoDesign




Static Liquid Head


Dimensions

Inner Diameter 60"

Length 96"



Outer 0"

Weight and Capacity


Corroded 5,893.21 1,184.85

Radiography





Results Summary



Rated MDMT -51.1F

39



Stress ratio, Rts = 1.1121*1 / (1.25 - 0.125 - 0) = 0.9885Reduction in MDMT from Figure UCS-66.1 = 1.1F

MDMT = max[Timpact - TR, -155] = max[ -50 - 1.1 , -155] = -51.1FDesign MDMT of -20F is acceptable.


td = D / 2 * (exp[P / (S*E)] - 1) + Corrosion (4.3.1)Operating Hot & Corroded

td = 60.25 / 2 * (exp[(725 + 0) / (20,000*1)] - 1) + 0.125 = 1.2371"Operating Cold & Corroded

tr = 60.25 / 2 * (exp[(725 + 0) / (20,000*1)] - 1) = 1.1121"


f = 50*t / Rf*(1 - Rf / Ro) (Table 6.1)f = 50*1.25 / 30.625*(1 - 30.625 / ) = 2.0408%


40


Deficiencies for Cylinder #1UCS-57: Full radiography required on Cylinder longitudinal seam.

Warnings Summary


41

Cylinder #1









Static Liquid Head


Dimensions

Inner Diameter 60"

Length 96"



Outer 0"

Weight and Capacity


Corroded 7,232.15 1,184.85

Radiography

Longitudinal seam Spot UW-11(b) Type 1Left Circumferential




Results Summary



Rated MDMT -68.9F

42



Stress ratio, Rts = 1.3125*0.85 / (1.5 - 0.125 - 0) = 0.8114Reduction in MDMT from Figure UCS-66.1 = 18.9F



td = D / 2 * (exp[P / (S*E)] - 1) + Corrosion (4.3.1)Operating Hot & Corroded

td = 60.25 / 2 * (exp[(725 + 0) / (20,000*0.85)] - 1) + 0.125 = 1.4375"Operating Cold & Corroded

tr = 60.25 / 2 * (exp[(725 + 0) / (20,000*0.85)] - 1) = 1.3125"


f = 50*t / Rf*(1 - Rf / Ro) (Table 6.1)f = 50*1.5 / 30.75*(1 - 30.75 / ) = 2.439%The extreme fiber elongation does not exceed 5%.

43

E4.2.2 - Nozzle Detail and Weld Sizing

a. Division 1

Determine the required fillet weld size of a set-in type nozzle as shown in Figure UW-16.1(d).


Fig E4.2.2a Division 1 Nozzle Weld Sizing Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME Differencet c (in) 0.25 0.25 0.00%

44

Nozzle #1 (N1)


Note: round inside edges per UG-76(c)Location and Orientation


Orientation 0


End of nozzle to shell center 18.625"


Description NPS 10 Sch 60 (XS)Access opening No

Material specification SA-106 B Smls pipe (II-D p. 14, ln. 19)Inside diameter, new 9.75"

Nominal wall thickness 0.5"


Projection available outside vessel, Lpr 6"Local vessel minimum thickness 0.625"


Longitudinal joint efficiency 1Welds



45


tr = 100*5 / (17,100*1 - 0.6*100) = 0.0293"Stress ratio = tr*E* / (tn - c) = 0.0293*1 / (0.4375 - 0.125) = 0.0939Stress ratio 0.35, MDMT per UCS-66(b)(3) = -155F

Material is exempt from impact testing at the Design MDMT of -20F.

46


UG-37 Area Calculation Summary (in2) UG-45Summary (in)For P = 100 psi @ 650 F

The opening is adequately reinforcedThe nozzle passes

UG-45

Arequired


Awelds treq tmin

0.6514 5.041 4.3235 0.5896 -- -- 0.1279 0.1897 0.4375

UG-41 Weld Failure Path Analysis Summary

The nozzle is exempt from weld strength calculations per UW-15(b)(1)


Weld description Required weldthroat size (in)Actual weld

throat size (in) Status

Nozzle to shell fillet (Leg41) 0.25 0.2625 weld size is adequate


Parallel Limit of reinforcement per UG-40

LR = MAX(d, Rn + (tn - Cn) + (t - C))= MAX(10, 5 + (0.5 - 0.125) + (0.625 - 0.125))= 10 in

Outer Normal Limit of reinforcement per UG-40

LH = MIN(2.5*(t - C), 2.5*(tn - Cn) + te)= MIN(2.5*(0.625 - 0.125), 2.5*(0.5 - 0.125) + 0)= 0.9375 in


trn = P*Rn / (Sn*E - 0.6*P)= 100*5 / (17,100*1 - 0.6*100)= 0.0293 in

Required thickness tr from UG-37(a)

tr = P*R / (S*E - 0.6*P)= 100*12.125 / (18,800*1 - 0.6*100)= 0.0647 in

Area required per UG-37(c)

Allowable stresses: Sn = 17,100, Sv = 18,800 psi

47

fr1 = lesser of 1 or Sn / Sv = 0.9096


A = d*tr*F + 2*tn*tr*F*(1 - fr1)= 10*0.0647*1 + 2*0.375*0.0647*1*(1 - 0.9096)= 0.6514 in2

Area available from FIG. UG-37.1

A1 = larger of the following= 4.3235 in2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 10*(1*0.5 - 1*0.0647) - 2*0.375*(1*0.5 - 1*0.0647)*(1 - 0.9096)= 4.3235 in2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 2*(0.5 + 0.375)*(1*0.5 - 1*0.0647) - 2*0.375*(1*0.5 - 1*0.0647)*(1 - 0.9096)= 0.7323 in2

A2 = smaller of the following= 0.5896 in2

= 5*(tn - trn)*fr2*t= 5*(0.375 - 0.0293)*0.9096*0.5= 0.7861 in2

= 5*(tn - trn)*fr2*tn= 5*(0.375 - 0.0293)*0.9096*0.375= 0.5896 in2

A41 = Leg2*fr2= 0.3752*0.9096= 0.1279 in2

Area = A1 + A2 + A41= 4.3235 + 0.5896 + 0.1279= 5.041 in2

As Area >= A the reinforcement is adequate.

UW-16(c) Weld Check

Fillet weld: tmin = lesser of 0.75 or tn or t = 0.375 intc(min) = lesser of 0.25 or 0.7*tmin = 0.25 intc(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in

The fillet weld size is satisfactory.

48

Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (c-e).

UG-45 Nozzle Neck Thickness Check

ta UG-27 = P*R / (S*E - 0.6*P) + Corrosion= 100*5 / (17,100*1 - 0.6*100) + 0.125= 0.1543 in

ta = max[ ta UG-27 , ta UG-22 ]= max[ 0.1543 , 0 ]= 0.1543 in

tb1 = P*R / (S*E - 0.6*P) + Corrosion= 100*12.125 / (18,800*1 - 0.6*100) + 0.125= 0.1897 in

tb1 = max[ tb1 , tb UG16 ]= max[ 0.1897 , 0.1875 ]= 0.1897 in

tb = min[ tb3 , tb1 ]= min[ 0.4444 , 0.1897 ]= 0.1897 in

tUG-45 = max[ ta , tb ]= max[ 0.1543 , 0.1897 ]= 0.1897 in

Available nozzle wall thickness new, tn = 0.875*0.5 = 0.4375 in

The nozzle neck thickness is adequate.

49

b. Division 2

(Repeated in Division 2 Manual: ASME PTB-3-2013 Division 2 Solution)

Determine the required fillet weld size and inside corner radius of a set-in type nozzle as shown in Table 4.2.10, Detail 4.


Fig E4.2.2b Division 2 Nozzle Weld Sizing Comparison

* In COMPRESS, the calculation for the minimum inside corner radius, 1, is notperformed.

ii. COMPRESS Report

Parameter COMPRESS ASME Differencet c (in) 0.3571 0.357 0.03%

50

Nozzle #1 (N1)


Component Nozzle

Nozzle Material SA-106 B Smls pipe (II-D p. 394, ln. 24)ImpactTested Normalized



Nozzle No No No No No



DesignMDMT (F)


Static Liquid Head


Location and Orientation

Attached to Cylinder #1

Orientation radial

Offset, L 25"

Angle, 0

Distance, r 18.625"

Through aCategory A Joint No

Dimensions

Description NPS 10Sch 60 (XS)Inside Diameter 9.75"

Nominal WallThickness 0.5"

Local VesselMinimumThickness

0.625"

Leg41 0.375"

ExternalProjection

Available, Lpr16"


Outer 0"

51

Summary Tables

4.5.5 Maximum local primary membrane stress

Condition P(psi)PL(psi)

Sallow(psi)Over

stressed

Design P 100 8,485 28,200 No

4.5.4.1 Nozzle Neck Minimum Thickness

Condition P(psi)td1(in)

td,STD(in)t

(in)td(in)

tn(in) Status

Design P 100 0.176 0.49 0.625 0.49 0.5 OKPipe tolerance applied to td1

4.5.14 Strength of Nozzle Attachment Welds Summary

Condition P(psi) kyL(in)

L41T(in)fwelds(lbf)

(psi)

S(psi)

Overstressed

Design P 100 1.075 8.443 0.2652 2,269.06 625 18,800 No

Table 4.2.10 Minimum Fillet Weld Sizes

Fillet Leg RequiredLeg Size (in)Actual

Leg Size (in) Status

Leg41 0.3571 0.375 weld size is adequate

3.11.2 Material Toughness Requirements Nozzle


Exemption temperature from Table 3.14 Curve B = 32.71F

Stress ratio, Rts = 0.0215*1 / (0.875*0.5 - 0.125) = 0.0688Rts 0.24, MDMT = -155F


52

E4.2.3 - Nozzle Detail with Reinforcement Pad and Weld Sizing

a. Division 1

Determine the required fillet weld sizes of a set-in type nozzle with added reinforcement pad as shown in Figure UW-16.1(q).


Fig E4.2.3a Division 1 Nozzle with Pad Weld Sizing Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME DifferenceInner fillet t c (in) 0.25 0.25 0.00%

Outer fillet t w (in) 0.25 0.25 0.00%

Upper groove tw (in) 0.2625 0.2625 0.00%

Lower groove tw (in) 0.2625 0.2625 0.00%

53

Nozzle #1 (N1)


Note: round inside edges per UG-76(c)Location and Orientation


Orientation 0


End of nozzle to shell center 25"


Access opening No

Material specification SA-105 (II-D p. 18, ln. 32)Inside diameter, new 9.75"

Nominal wall thickness 0.5"


Projection available outside vessel, Lpr 12.375"Local vessel minimum thickness 0.625"


Longitudinal joint efficiency 1Reinforcing Pad

Material specification SA-516 70 (II-D p. 22, ln. 6)Diameter, Dp 14.75"

Thickness, te 0.625"

Is split No

Welds

54


Outer Fillet, Leg42 0.375"


Pad groove weld 0.2625"


tr = 100*5 / (20,000*1 - 0.6*100) = 0.0251"Stress ratio = tr*E* / (tn - c) = 0.0251*1 / (0.5 - 0.125) = 0.0669Stress ratio 0.35, MDMT per UCS-66(b)(3) = -155F


UCS-66 Material Toughness Requirements Pad

tr = 100*12.125 / (20,000*1 - 0.6*100) = 0.0608"Stress ratio = tr*E* / (tn - c) = 0.0608*1 / (0.625 - 0.125) = 0.1216Stress ratio 0.35, MDMT per UCS-66(b)(3) = -155F


55


UG-37 Area Calculation Summary (in2)UG-45

Summary(in)

For P = 100 psi @ 650 FThe opening is adequately reinforced

The nozzlepasses UG-45

Arequired


Awelds treq tmin

0.6496 7.9302 4.3356 0.8209 -- 2.5 0.2737 0.1897 0.5

UG-41 Weld Failure Path Analysis Summary (lbf)All failure paths are stronger than the applicable weld loads

Weld loadW

Weld loadW1-1

Path 1-1strength

Weld loadW2-2

Path 2-2strength

Weld loadW3-3

Path 3-3strength

-63,485.94 67,578.48 156,185.95 24,610.14 178,562.49 74,253.42 141,704.36


Weld description Required weldsize (in)

Actual weldsize (in) Status

Nozzle to pad fillet (Leg41) 0.25 0.2625 weld size is adequate

Pad to shell fillet (Leg42) 0.25 0.2625 weld size is adequate

Nozzle to pad groove (Upper) 0.2625 0.2625 weld size is adequate

Nozzle to shell groove (Lower) 0.2625 0.2625 weld size is adequate


Parallel Limit of reinforcement per UG-40

LR = MAX(d, Rn + (tn - Cn) + (t - C))= MAX(10, 5 + (0.5 - 0.125) + (0.625 - 0.125))= 10 in

Outer Normal Limit of reinforcement per UG-40

LH = MIN(2.5*(t - C), 2.5*(tn - Cn) + te)= MIN(2.5*(0.625 - 0.125), 2.5*(0.5 - 0.125) + 0.625)= 1.25 in


trn = P*Rn / (Sn*E - 0.6*P)= 100*5 / (17,800*1 - 0.6*100)= 0.0282 in

56

Required thickness tr from UG-37(a)

tr = P*R / (S*E - 0.6*P)= 100*12.125 / (18,800*1 - 0.6*100)= 0.0647 in

Area required per UG-37(c)

Allowable stresses: Sn = 17,800, Sv = 18,800, Sp = 18,800 psi



fr3 = lesser of fr2 or Sp / Sv = 0.9468

fr4 = lesser of 1 or Sp / Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1)= 10*0.0647*1 + 2*0.375*0.0647*1*(1 - 0.9468)= 0.6496 in2

Area available from FIG. UG-37.1

A1 = larger of the following= 4.3356 in2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 10*(1*0.5 - 1*0.0647) - 2*0.375*(1*0.5 - 1*0.0647)*(1 - 0.9468)= 4.3356 in2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 2*(0.5 + 0.375)*(1*0.5 - 1*0.0647) - 2*0.375*(1*0.5 - 1*0.0647)*(1 - 0.9468)= 0.7444 in2

A2 = smaller of the following= 0.8209 in2

= 5*(tn - trn)*fr2*t= 5*(0.375 - 0.0282)*0.9468*0.5= 0.8209 in2

= 2*(tn - trn)*(2.5*tn + te)*fr2= 2*(0.375 - 0.0282)*(2.5*0.375 + 0.625)*0.9468= 1.0261 in2

A41 = Leg2*fr3= 0.3752*0.9468= 0.1331 in2

57

A42 = Leg2*fr4= 0.3752*1= 0.1406 in2

A5 = (Dp - d - 2*tn)*te*fr4= (14.75 - 10 - 2*0.375)*0.625*1= 2.5 in2

Area = A1 + A2 + A41 + A42 + A5= 4.3356 + 0.8209 + 0.1331 + 0.1406 + 2.5= 7.9302 in2

As Area >= A the reinforcement is adequate.

UW-16(d) Weld Check

Inner fillet: tmin = lesser of 0.75 or tn or te = 0.375 intc(min) = lesser of 0.25 or 0.7*tmin = 0.25 intc(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in

Outer fillet: tmin = lesser of 0.75 or te or t = 0.5 intw(min) = 0.5*tmin = 0.25 intw(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in

Upper groove: tmin = lesser of 0.75 or tn or te = 0.375 intw(min) = 0.7*tmin = 0.2625 intw(actual) = 0.2625 in

Lower groove: tmin = lesser of 0.75 or tn or t = 0.375 intw(min) = 0.7*tmin = 0.2625 intw(actual) = 0.2625 in

UG-45 Nozzle Neck Thickness Check

ta UG-27 = P*R / (S*E - 0.6*P) + Corrosion= 100*5 / (17,800*1 - 0.6*100) + 0.125= 0.1532 in

ta = max[ ta UG-27 , ta UG-22 ]= max[ 0.1532 , 0 ]= 0.1532 in

tb1 = P*R / (S*E - 0.6*P) + Corrosion= 100*12.125 / (18,800*1 - 0.6*100) + 0.125= 0.1897 in

58

b. Division 2

(Repeated in Division 2 Manual: ASME PTB-3-2013 E4.2.3 Division 2 Solution)

Determine the required fillet weld sizes and inside corner radius of a set-in type nozzle with added reinforcement pad as shown in Table 4.2.11, Detail 2.


Fig E4.2.3b Division 2 Nozzle with Pad Weld Sizing Comparison

* In COMPRESS, a deficiency is issued for the 'New' condition as the weld leg size of0.4375 in shown in the problem statement is not sufficient.

* In COMPRESS, the calculation for the minimum inside corner radius, 1, is notperformed.

ii. COMPRESS Report

Parameter COMPRESS ASME Differenceinner fillet t c (in) 0.3571 0.357 0.03%

outer fillet t f1 (in) 0.4286 0.429 0.09%

59


Warnings Summary

Warnings for Nozzle #1 (N1)Leg42 = 0.4375 in is less than minimum required leg size of 0.5357 in. (new condition) (warning)


60

Nozzle #1 (N1)


Component Nozzle

Nozzle Material SA-105 (II-D p. 394, ln. 42)Pad Material SA-516 70 (II-D p. 398, ln. 10)




Nozzle No No No No No

Pad No No No No No



DesignMDMT (F)


Static Liquid Head

Condition Ps (psi) Hs (in) SGTest horizontal 0.45 12.375 1

Location and Orientation

Attached to Cylinder #1

Orientation radial

Offset, L 74"

Angle, 0

Distance, r 25"

Through a Category A Joint No

61

Dimensions

Inside Diameter 9.75"

Nominal WallThickness 0.5"

Local VesselMinimumThickness

0.625"

Nozzle to PadGroove Weld, tw2

0.625"

Leg41 0.375"

Leg42 0.4375"

Pad Width, W 2"

Pad Thickness, te 0.625"

ExternalProjection

Available, Lpr112.375"


Outer 0"

62

Summary Tables

4.5.5 Maximum local primary membrane stress

Condition P(psi)PL(psi)

Sallow(psi)Over

stressed

Design P 100 4,587 28,200 No

4.5.4.1 Nozzle Neck Minimum Thickness

Condition P(psi)td1(in)

td,STD(in)t

(in)td(in)

tn(in) Status

Design P 100 0.1532 0.4444 0.625 0.4444 0.5 OK

4.5.14 Strength of Nozzle Attachment Welds Summary

Condition P(psi) kyL(in)

Lp(in)fwelds(lbf)

1(psi)2(psi)

3(psi)

(psi)S

(psi)Over

stressed

Design P 100 1.075 8.443 11.5846 2,269.06 398 296 718 718 18,800 No

Table 4.2.11 Minimum Fillet Weld Sizes

Fillet Leg RequiredLeg Size (in)Actual

Leg Size (in) Status



3.11.2 Material Toughness Requirements Nozzle



Stress ratio, Rts = 0.0209*1 / (0.5 - 0.125 - 0) = 0.0557Rts 0.24, MDMT = -155F


3.11.2 Material Toughness Requirements Pad



Stress ratio, Rts = 0.048*1 / (0.625 - 0.125 - 0) = 0.096Rts 0.24, MDMT = -155F


63

E4.3.1 - Cylindrical Shell

a. Division 1

Determine the required thickness for a cylindrical shell.


Fig E4.3.1a Division 1 Cylindrical Shell tr Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME Differencet (in) 0.9369 0.9369 0.00%

64

Cylinder #1

ASME Section VIII Division 1, 2013 EditionComponent Cylinder




No Yes No No No



DesignMDMT (F)


Static Liquid HeadCondition Ps (psi) Hs (in) SG


Dimensions

Inner Diameter 90"

Length 144"Nominal Thickness 1"

Corrosion Inner 0.125"Outer 0"

Weight and CapacityWeight (lb) Capacity (US gal)

New 11,650.38 3,965.75

Corroded 10,208.09 3,987.81Radiography





Results SummaryGoverning condition Internal pressureMinimum thickness per UG-16 0.0625" + 0.125" = 0.1875"Design thickness due to internal pressure (t) 0.9369"Maximum allowable working pressure (MAWP) 383.35 psiMaximum allowable pressure (MAP) 438.6 psiRated MDMT -30 F

65

UCS-66 Material Toughness RequirementsGoverning thickness, tg = 1"Exemption temperature from Fig UCS-66 Curve D = -30Ftr = 383.35*45.125 / (20,000*1 - 0.6*383.35) = 0.875"Stress ratio = tr*E* / (tn - c) = 0.875*1 / (1 - 0.125) = 1Reduction in MDMT, TR from Fig UCS-66.1 = 0FMDMT = max[ MDMT - TR, -55] = max[ -30 - 0 , -55] = -30F

Material is exempt from impact testing at the Design MDMT of -20F.Design thickness, (at 300 F) UG-27(c)(1)


Maximum allowable working pressure, (at 300 F) UG-27(c)(1)

P = S*E*t / (R + 0.60*t) - Ps= 20,000*1.00*0.875 / (45.125 + 0.60*0.875) - 0= 383.35 psi

Maximum allowable pressure, (at 70 F) UG-27(c)(1)

P = S*E*t / (R + 0.60*t)= 20,000*1.00*1 / (45 + 0.60*1)= 438.6 psi


EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*1 / 45.5)*(1 - 45.5 / )= 1.0989%


66

b. Code Case 2695

Determine the required thickness for a cylindrical shell.


Fig E4.3.1b CC 2695 Cylindrical Shell tr Comparison

ii. COMPRESS Report


67

Cylinder #1





No Yes No No No



DesignMDMT (F)




Dimensions

Inner Diameter 90"

Length 144"Nominal Thickness 1"


Weight and CapacityWeight (lb) Capacity (US gal)

New 11,650.38 3,965.75

Corroded 10,208.09 3,987.81Radiography





Results SummaryGoverning condition Operating Hot & CorrodedDesign thickness due to internal pressure (t) 0.9354"Minimum thickness per 4.1.2 0.1875"Rated MDMT -37.4F

68

Material Toughness RequirementsGoverning thickness, tg = 1"Exemption temperature from Figure UCS-66 Curve D = -30FStress ratio, Rts = 0.8104*1 / (1 - 0.125 - 0) = 0.9262Reduction in MDMT from Figure UCS-66.1 = 7.4FMDMT = max[ MDMT - TR, -55] = max[ -30 - 7.4 , -55] = -37.4F


Division 2 4.3.3.1 Design Thickness for Internal Pressuretd = D / 2 * (exp[P / (S*E)] - 1) + Corrosion (4.3.1)

Operating Hot & Corrodedtd = 90.25 / 2 * (exp[(356 + 0) / (20,000*1)] - 1) + 0.125 = 0.9354"

Operating Cold & Corrodedtr = 90.25 / 2 * (exp[(356 + 0) / (20,000*1)] - 1) = 0.8104"

Division 2 6.1.2.3 % Extreme Fiber Elongationf = 50*t / Rf*(1 - Rf / Ro) (Table 6.1)f = 50*1 / 45.5*(1 - 45.5 / ) = 1.0989%The extreme fiber elongation does not exceed 5%.

69

E4.3.2 - Conical Shell

a. Division 1

Determine the required thickness for a conical shell.


Fig E4.3.2a Division 1 Conical Shell tr Comparison

* The equation for the required cone thickness at the large end, , uses the large enddiameter, . COMPRESS calculates for a transition using the following equation:

= + 2 () = 150 + 2 0.125(21.0375) = 150.2679 The example manual calculates using:

= + 2( ) = 150 + 2(0.125) = 150.25 COMPRESS takes into account the half apex angle when considering corrosion.

ii. COMPRESS Report

Parameter COMPRESS ASME DifferenceDL * (in) 150.2679 150.25 0.01%

t (in) 1.5734 1.5732 0.01%

70

Transition #1


Component Cone




Yes (-50F) Yes No Yes NoDesign




Static Liquid Head


Test horizontal Large 5.41 150 1Small 4.33 120

Dimensions

Inner Diameter Large 150"

Small 90"

Length 78"



Outer 0"

Weight and Capacity


Corroded 19,348.24 3,915.5

Radiography

Longitudinal seam Full UW-11(a) Type 1Left Circumferential seam Full UW-11(a) Type 1

Right Circumferential seam Full UW-11(a) Type 1

Results Summary




71



tr = 356*150.2679 / (2*0.9333*(20,000*1 - 0.6*356)) = 1.4484"Stress ratio = tr*E* / (tn - c) = 1.4484*1 / (2.25 - 0.125) = 0.6816UCS-66(i) reduction in MDMT, TR from Fig UCS-66.1 = 31.8FMDMT = max[Timpact - TR, -155] = max[ -50 - 31.8 , -155] = -81.8F

Design MDMT of -20F is acceptable.Design thickness, (at 300 F) UG-32(g) (Large End)

t = P*D / (2*cos()*(S*E - 0.60*P)) + Corrosion= 356*150.2679 / (2*cos(21.0375)*(20,000*1.00 - 0.60*356)) + 0.125= 1.5734"

Small End design thickness (t = 0.995") does not govern.


EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*2.4107 / 46.2053)*(1 - 46.2053 / )= 2.6087%


72

b. Code Case 2695

Determine the required thickness for a conical shell.


Fig E4.3.2b CC 2695 Conical Shell tr Comparison

* The equation for the required cone thickness at the large end, , uses the large enddiameter, . COMPRESS calculates for a transition using the following equation:

= + 2 () = 150 + 2 0.125(21.0375) = 150.2679 The example manual calculates using:

= + 2( ) = 150 + 2(0.125) = 150.25 COMPRESS takes into account the half apex angle when considering corrosion.

ii. COMPRESS Report

Parameter COMPRESS ASME DifferenceDL * (in) 150.2679 150.25 0.01%

(degrees) 21.0375 21.0375 0.00%

t (in) 1.5707 1.5705 0.01%

73

Transition #1

ASME Section VIII Division 1, 2013 Edition (Code Case 2695)Component Cone




Yes (-50F) Yes No Yes NoDesign




Static Liquid Head


Test horizontal Left 5.41 150 1Right 4.33 120

Dimensions

Inner Diameter Large 150"

Small 90"

Length 78"



Outer 0"

Weight and Capacity


Corroded 19,348.24 3,915.5

Radiography

Longitudinal seam Full UW-11(a) Type 1Left Circumferential seam Full UW-11(a) Type 1

Right Circumferential seam Full UW-11(a) Type 1

Results Summary



Rated MDMT -82F

74



Stress ratio, Rts = 1.4457*1 / (2.25 - 0.125 - 0) = 0.6803Reduction in MDMT from Figure UCS-66.1 = 32F

MDMT = max[Timpact - TR, -155] = max[ -50 - 32 , -155] = -82FDesign MDMT of -20F is acceptable.

Division 2 4.4.6.1.e Cone Half Apex Angle

= arctan[{(RL - rk) - (RS + rf)} / Lce] (4.4.49) = arcsin[(rf + rk)*cos[] / Lce] (4.4.52) = + (4.4.48)

Results

= arctan[{(75 - 0) - (45 + 0)} / 78] = 21.0375 = arcsin[(0 + 0)*cos[21.0375] / 78] = 0 = 21.0375 + 0 = 21.0375


td = D / (2*cos[]) * (exp[P / (S*E)] - 1) + Corrosion (4.3.2)Operating Hot & Corroded

Left td = 150.2679 / (2*cos[21.0375]) * (exp[(356 + 0) / (20,000*1)] - 1) + 0.125 = 1.5707"Right td = 90.2679 / (2*cos[21.0375]) * (exp[(356 + 0) / (20,000*1)] - 1) + 0.125 = 0.9935"

Operating Cold & Corroded

Left tr = 150.2679 / (2*cos[21.0375]) * (exp[(356 + 0) / (20,000*1)] - 1) = 1.4457"Right tr = 90.2679 / (2*cos[21.0375]) * (exp[(356 + 0) / (20,000*1)] - 1) = 0.8685"


f = 50*t / Rf*(1 - Rf / Ro) (Table 6.1)f = 50*2.4107 / 46.2053*(1 - 46.2053 / ) = 2.6087%


75

E4.3.3 - Spherical Shell

a. Division 1

Determine the required thickness for a spherical shell.


Fig E4.3.3a Division 1 Spherical Shell tr Comparison

ii. COMPRESS Report


76

Hemi Head #1


Component Hemispherical Head

Material SA-542 D 4a (II-D p. 42, ln. 28)Attached To Bottom of vessel








Static Liquid Head


Dimensions

Inner Diameter 149"


Corrosion Inner 0"

Outer 0"

Weight and Capacity

Weight (lb) Capacity (US gal)New 38,647.59 3,749

Corroded 38,647.59 3,749

Radiography



Results Summary


Minimum thickness per UG-16 0.0625" + 0" = 0.0625"


77



tr = 2,080*74.5 / (2*24,300*1 - 0.2*2,080) = 3.216"Stress ratio = tr*E* / (tn - c) = 3.216*1 / (3.7265 - 0) = 0.863UCS-66(i) reduction in MDMT, TR from Fig UCS-66.1 = 13.7FMDMT = max[Timpact - TR, -155] = max[ -50 - 13.7 , -155] = -63.7F

Design MDMT of -20F is acceptable.Design thickness, (at 850 F) UG-32(f)

t = P*R / (2*S*E - 0.20*P) + Corrosion= 2,080*74.5 / (2*21,000*1.00 - 0.20*2,080) + 0= 3.7265"


EFE = (75*t / Rf)*(1 - Rf / Ro)= (75*3.7265 / 76.3633)*(1 - 76.3633 / )= 3.66%


78

b. Code Case 2695

Determine the required thickness for a spherical shell.


Fig E4.3.3b CC 2695 Spherical Shell tr Comparison

ii. COMPRESS Report


79

Hemi Head #1

ASME Section VIII Division 1, 2013 Edition (Code Case 2695)Component Hemispherical Head

Material SA-542 D 4a (II-D p. 42, ln. 28)ImpactTested Normalized







Static Liquid Head


Dimensions

Inner Diameter 149"


Corrosion Inner 0"

Outer 0"

Weight and Capacity

Weight (lb) Capacity (US gal)New 39,256.39 3,749

Corroded 39,256.39 3,749

Radiography



Results Summary



Rated MDMT -63.9F

80



Stress ratio, Rts = 3.2577*1 / (3.7824 - 0 - 0) = 0.8613Reduction in MDMT from Figure UCS-66.1 = 13.9F



td = D / 2 * (exp[0.5*P / (S*E)] - 1) + Corrosion (4.3.4)Operating Hot & Corroded

td = 149 / 2 * (exp[0.5*(2,080 + 0) / (21,000*1)] - 1) + 0 = 3.7824"Operating Cold & Corroded

tr = 149 / 2 * (exp[0.5*(2,080 + 0) / (24,300*1)] - 1) = 3.2577"


f = 100*ln[Db / (Do - 2*t)] (Table 6.1)Forming strain not calculated.

81

E4.3.4 - Torispherical Head

a. Division 1

Determine the maximum allowable working pressure (MAWP) for the proposed seamless torispherical head.


Fig E4.3.4a Division 1 Torispherical Head MAWP Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME DifferenceM 1.750868 1.7509 0.00%

MAWP (psi) 135.3 135.3023 0.00%

82

F&D Head #1

ASME Section VIII Division 1, 2013 EditionComponent F&D Head

Material SA-387 11 1 (II-D p. 38, ln. 27)Attached To Bottom of vessel







MDMT (F)Internal 100 650

-20External 15 650


Test horizontal 2.6 72 1Dimensions

Inner Diameter 72"Crown Radius L 72"

Knuckle Radius r 4.375"Minimum Thickness 0.625"


Length Lsf 2"Nominal Thickness tsf 0.4375"

Weight and CapacityWeight (lb)1 Capacity (US gal)1

New 931.2 166.69Corroded 743.49 169.56

RadiographyCategory A joints Seamless No RT

Head to shell seam Full UW-11(a) Type 11includes straight flange

Results SummaryGoverning condition internal pressureMinimum thickness per UG-16 0.0625" + 0.125" = 0.1875"Design thickness due to internal pressure (t) 0.4945"Design thickness due to external pressure (te) 0.3517"Maximum allowable working pressure (MAWP) 135.3 psiMaximum allowable external pressure (MAEP) 55.75 psiStraight Flange governs MDMT -58.1F

Factor MM = 1/4*[3 + (L / r)1/2]Corroded M = 1/4*[3 + (72.125 / 4.5)1/2] 1.7509New M = 1/4*[3 + (72 / 4.375)1/2] 1.7642Design thickness for internal pressure, (Corroded at 650 F) Appendix 1-4(d)t = P*L*M / (2*S*E - 0.2*P) + Corrosion

=

83

100*72.125*1.7509 / (2*17,100*1 - 0.2*100) +0.125

= 0.4945"

Maximum allowable working pressure, (Corroded at 650 F) Appendix 1-4(d)P = 2*S*E*t / (L*M + 0.2*t) - Ps

= 2*17,100*1*0.5 / (72.125*1.7509 + 0.2*0.5) - 0= 135.3 psi

Design thickness for external pressure, (Corroded at 650 F) UG-33(e)Equivalent outside spherical radius (Ro)

= Outside crown radius= 72.625 in

A = 0.125 / (Ro / t)= 0.125 / (72.625 / 0.226661)= 0.00039

From TableCS-2: B = 4,806.1921 psi

Pa = B / (Ro / t)= 4,806.1921 / (72.625 / 0.2267)= 15 psi

t = 0.2267" + Corrosion = 0.2267" + 0.125" = 0.3517"Check the external pressure per UG-33(a)(1) Appendix 1-4(d)t = 1.67*Pe*L*M / (2*S*E - 0.2*1.67*Pe) + Corrosion

=1.67*15*72.125*1.7509 / (2*17,100*1 -0.2*1.67*15) + 0.125

= 0.2175"

The head external pressure design thickness (te) is 0.3517".Maximum Allowable External Pressure, (Corroded at 650 F) UG-33(e)Equivalent outside spherical radius (Ro)

= Outside crown radius= 72.625 in

A = 0.125 / (Ro / t)= 0.125 / (72.625 / 0.5)= 0.000861

From TableCS-2: B = 8,098.2799 psi

Pa = B / (Ro / t)= 8,098.2799 / (72.625 / 0.5)= 55.7541 psi

Check the Maximum External Pressure, UG-33(a)(1) Appendix 1-4(d)P = 2*S*E*t / ((L*M + 0.2*t)*1.67) - Ps2

=2*17,100*1*0.5 / ((72.125*1.7509 +0.2*0.5)*1.67) - 0

= 81.02 psi

The maximum allowable external pressure (MAEP) is 55.75 psi.% Extreme fiber elongation - UCS-79(d)EFE = (75*t / Rf)*(1 - Rf / Ro)

= (75*0.4375 / 4.5938)*(1 - 4.5938 / )= 7.1429%

84

b. Code Case 2695

Determine the maximum allowable working pressure (MAWP) for the proposed seamless torispherical head.


Fig E4.3.4b CC 2695 Torispherical Head MAWP Comparison

ii. COMPRESS Report

Parameter COMPRESS ASME DifferenceD (in) 72.25 72.25 0.00%

L (in) 72.125 72.125 0.00%

r (in) 4.5 4.5 0.00%

t (in) 0.5 0.5 0.00%

th (rad) 1.0842 1.0842 0.00%

th (rad) 1.3345 1.3345 0.00%

Rth (in) 36.125 36.125 0.00%

C1 0.4939 0.494 0.02%

C2 1.25 1.25 0.00%

C3 26,900 26,900 0.00%

Peth (psi) 5352.44 5353.9445 0.03%

Py (psi) 98.83 98.8274 0.00%

G 54.1595 54.1747 0.03%

Pck (psi) 199.57 199.5671 0.00%

Pak (psi) 133.04 133.0447 0.00%

Pac (psi) 236.27 236.2694 0.00%

Pa (psi) 133.04 133.0447 0.00%

85

F&D Head #1

ASME Section VIII Division 1, 2013 Edition (Code Case 2695)Component F&D Head

Material SA-387 11 1 (II-D p. 38, ln. 27)ImpactTested Normalized









Inner Diameter 72"Crown Radius L 72"

Knuckle Radius r 4.375"Minimum Thickness 0.625"




New 931.2 166.69Corroded 743.49 169.56



Results SummaryGoverning condition Operating Hot & CorrodedDesign thickness due to internal pressure (t) 0.5022"Minimum thickness per 4.1.2 0.1875"Maximum allowable working pressure (MAWP) 133.04 psiRated MDMT -96.7F

86

Material Toughness RequirementsMaterial impact test temperature per 3.11.7 = -50FStress ratio, Rts = 0.2811*1 / (0.625 - 0.125 - 0) = 0.5623Reduction in MDMT from Figure UCS-66.1 = 46.7FMDMT = max[Timpact - TR, -155] = max[ -50 - 46.7 , -155] = -96.7F

Design MDMT of -20F is acceptable.

Division 2 4.3.6.1 Design Thickness for Internal Pressure0.7 L / D 1 (4.3.5)r / D 0.06 (4.3.6)20 L / t 2,000 (4.3.7)th = arccos[(0.5*D - r) / (L - r)] (4.3.8)th = (L * t)1/2 / r (4.3.9)Rth = (0.5*D - r) / cos[th - th] + r for th < th (4.3.10)Rth = 0.5*D for th th (4.3.11)C1 = 9.31*r / D - 0.086 for r / D 0.08 (4.3.12)C1 = 0.692*r / D + 0.605 for r / D > 0.08 (4.3.13)C2 = 1.25 for r / D 0.08 (4.3.14)C2 = 1.46 - 2.6*r / D for r / D > 0.08 (4.3.15)Peth = C1*ET*t2 / (C2*Rth*(Rth / 2 - r)) (4.3.16)C3 = Sy (time-independent properties)C3 = 1.1*S (time-dependent properties 90% yield criterion)C3 = 1.5*S (time-dependent properties 67% yield criterion)Py = C3*t / {C2*Rth*(Rth / (2*r) - 1)} (4.3.17)G = Peth / Py (4.3.20)Pck = 0.6*Peth for G 1 (4.3.18)Pck = {(0.77508*G - 0.20354*G2 + 0.019274*G3) / (1 + 0.19014*G - 0.089534*G2 +0.0093965*G3)} * Py for G > 1 (4.3.19)Pak = Pck / 1.5 (4.3.21)Pac = 2*S*E / (L / t + 0.5) (4.3.22)Pa = min[Pak , Pac] (4.3.23)

Operating Hot & Corroded

0.7 L / D = 72.125 / 72.25 = 0.9983 1 OKr / D = 4.5 / 72.25 = 0.0623 0.06 OK20 L / t = 72.125 / 0.5 = 144.25 2,000 OKth = arccos[(0.5*72.25 - 4.5) / (72.125 - 4.5)] = 1.0842th = (72.125 * 0.3772)1/2 / 4.5 = 1.159Rth = 0.5*72.25 = 36.125"C1 = 9.31*4.5 / 72.25 - 0.086 = 0.4939C2 = 1.25 = 1.25

87

Peth = 0.4939*26.55E+06*0.37722 / (1.25*36.125*(36.125 / 2 - 4.5)) = 3,045.47 psiMaterial is not governed by time dependent properties which start at 900F (Design T = 650F)C3 = Sy = 26,900 psiPy = 26,900*0.3772 / {1.25*36.125*(36.125 / (2*4.5) - 1)} = 74.55 psiG = 3,045.47 / 74.55 = 40.8532Pck = {(0.77508*40.8532 - 0.20354*40.85322 + 0.019274*40.85323) / (1 + 0.19014*40.8532 -0.089534*40.85322 + 0.0093965*40.85323)} * 74.55 = 150 psiPak = 150 / 1.5 = 100 psiPac = 2*17,100*1 / (72.125 / 0.3772 + 0.5) = 178.37 psiPa = min[100 , 178.37] - 0 = 100 psi

td = 0.3772 + 0.125 = 0.5022"Operating Cold & Corroded

tr = (133.04 + 0)*72.125 / (2*17,100*1 - 0.5*(133.04 + 0)) = 0.2811"

Division 2 4.3.6.1 Maximum Pressure Circumferential StressMAWP

0.7 L / D = 72.125 / 72.25 = 0.9983 1 OKr / D = 4.5 / 72.25 = 0.0623 0.06 OK20 L / t = 72.125 / 0.5 = 144.25 2,000 OKth = arccos[(0.5*72.25 - 4.5) / (72.125 - 4.5)] = 1.0842th = (72.125 * 0.5)1/2 / 4.5 = 1.3345Rth = 0.5*72.25 = 36.125"C1 = 9.31*4.5 / 72.25 - 0.086 = 0.4939C2 = 1.25 = 1.25Peth = 0.4939*26.55E+06*0.52 / (1.25*36.125*(36.125 / 2 - 4.5)) = 5,352.44 psiMaterial is not governed by time dependent properties which start at 900F (Design T = 650F)C3 = Sy = 26,900 psiPy = 26,900*0.5 / {1.25*36.125*(36.125 / (2*4.5) - 1)} = 98.83 psiG = 5,352.44 / 98.83 = 54.1595Pck = {(0.77508*54.1595 - 0.20354*54.15952 + 0.019274*54.15953) / (1 + 0.19014*54.1595 -0.089534*54.15952 + 0.0093965*54.15953)} * 98.83 = 199.57 psiPak = 199.57 / 1.5 = 133.04 psiPac = 2*17,100*1 / (72.125 / 0.5 + 0.5) = 236.27 psiPa = min[133.04 , 236.27] - 0 = 133.04 psi

Division 2 6.1.2.3 % Extreme Fiber Elongationf = 100*ln[Db / (Do - 2*t)] (Table 6.1)Forming strain not calculated.

88

E4.3.5 - Ellipsoidal Head

a. Division 1

Determine the maximum allowable working pressure (MAWP) for the proposed seamless 2:1 Ellipsoidal head.


Fig E4.3.5a Division 1 Ellipsoidal Head MAWP Comparison

* COMPRESS solves for K using corroded dimensions:

= 162 + 22 = 162 + 90.252 22.6252 = 0.99632 The example uses uncorroded dimensions D = 90 in and h = 22.5 in, where K = 1.0. This K value is used along with corroded dimensions to solve for MAWP. In COMPRESS, the corroded K value is used with corroded dimensions to solve for MAWP.

ii. COMPRESS Report

Parameter COMPRESS ASME DifferenceK * (corroded) 0.996322 N/A N/A

K (uncorroded) 1 1 0.00%

MAWP * (psi) 443.86 442 0.42%

89

Ellipsoidal Head #1

ASME Section VIII Division 1, 2013 EditionComponent Ellipsoidal Head

Material SA-516 70 (II-D p. 22, ln. 6)Attached To Bottom of vessel




No Yes No No NoDesign



MDMT (F)Internal 100 300

-20External 15 300



Inner Diameter 90"Head Ratio 2





New 3,124.63 468.18Corroded 2,773.38 473.09



Results SummaryGoverning condition external pressureMinimum thickness per UG-16 0.0625" + 0.125" = 0.1875"Design thickness due to internal pressure (t) 0.35"Design thickness due to external pressure (te) 0.3591"Maximum allowable working pressure (MAWP) 443.86 psiMaximum allowable external pressure (MAEP) 171.8 psiStraight Flange governs MDMT -55F

90

Factor KK = (1/6)*[2 + (D / (2*h))2]Corroded K = (1/6)*[2 + (90.25 / (2*22.625))2] 0.9963New K = (1/6)*[2 + (90 / (2*22.5))2] 1

Design thickness for internal pressure, (Corroded at 300 F) Appendix 1-4(c)t = P*D*K / (2*S*E - 0.2*P) + Corrosion

= 100*90.25*0.996322 / (2*20,000*1 - 0.2*100) + 0.125= 0.3499"

Maximum allowable working pressure, (Corroded at 300 F) Appendix 1-4(c)P = 2*S*E*t / (K*D + 0.2*t) - Ps

= 2*20,000*1*1 / (0.996322*90.25 +0.2*1) - 0= 443.86 psi

Design thickness for external pressure, (Corroded at 300 F) UG-33(d)Equivalent outside spherical radius (Ro)Ro = Ko*Do

= 0.8786*92.25= 81.0482 in

A = 0.125 / (Ro / t)= 0.125 / (81.0482 / 0.234088)= 0.000361

From TableCS-2: B =

5,193.4553psi

Pa = B / (Ro / t)= 5,193.4553 / (81.0482 / 0.2341)= 15 psi

t = 0.2341" + Corrosion = 0.2341" + 0.125" = 0.3591"Check the external pressure per UG-33(a)(1) Appendix 1-4(c)t = 1.67*Pe*D*K / (2*S*E - 0.2*1.67*Pe) + Corrosion

= 1.67*15*90.25*0.996322 / (2*20,000*1 - 0.2*1.67*15) + 0.125= 0.1813"

The head external pressure design thickness (te) is 0.3591".Maximum Allowable External Pressure, (Corroded at 300 F) UG-33(d)Equivalent outside spherical radius (Ro)Ro = Ko*Do

= 0.8786*92.25= 81.0482 in

A = 0.125 / (Ro / t)= 0.125 / (81.0482 / 1)= 0.001542

From TableCS-2: B =

13,924.45psi

Pa = B / (Ro / t)= 13,924.45 / (81.0482 / 1)= 171.8045 psi

91

Check the Maximum External Pressure, UG-33(a)(1) Appendix 1-4(c)P = 2*S*E*t / ((K*D + 0.2*t)*1.67) - Ps2

= 2*20,000*1*1 / ((0.996322*90.25 +0.2*1)*1.67) - 0= 265.79 psi

The maximum allowable external pressure (MAEP) is 171.8 psi.% Extreme fiber elongation - UCS-79(d)EFE = (75*t / Rf)*(1 - Rf / Ro)

= (75*0.375 / 15.4875)*(1 - 15.4875 / )= 1.816%


92

b. Code Case 2695

Determine the maximum allowable working pressure (MAWP) for the proposed seamless 2:1 Ellipsoidal head.


Fig E4.3.5b CC 2695 Ellipsoidal Head MAWP Comparison

* The example solves for k, L, and r using uncorroded dimensions. COMPRESS solvesfor k, L, and r using corroded dimensions:

= 2 = 90.252 22.625 = 1.9945 = 0.5

0.08 = 90.25 0.51.9945 0.08 = 15.405

= (0.44 + 0.02) = 90.25(0.44 1.9945 + 0.02) = 81.0056 These calculations account for differences shown above.

ii. COMPRESS Report

Parameter COMPRESS ASME Differencek * 1.9945 2 0.28%

D (in) 90.25 90.25 0.00%

L * (in) 81.0056 81.125 0.15%

r * (in) 15.405 15.425 0.13%

t (in) 1 1 0.00%

th (rad) 1.1006 1.1017 0.10%

th (rad) 0.5842 0.5839 0.05%

Rth (in) 49.581 49.6057 0.05%

C1 0.7231 0.7233 0.03%

C2 1.0162 1.0157 0.05%

Peth (psi) 43,275.72 43,321.6096 0.11%

Py (psi) 1094.58 1096.8927 0.21%

G 39.5362 39.4948 0.10%

Pck (psi) 2201.55 2206.1634 0.21%

Pak (psi) 1467.7 1470.8 0.21%

Pac (psi)

2015 7500 verification manual

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