52379610 pressure vessel design calculations

127
Cairo Oil Refining Co. ول א א Subsidery of Egyotian Gen. Petroleum Corp. ول א א אد P.O. Box : Heliopolis 11757 Cairo A.R.E. دد א ١١٧٥٧ سوو : .. صTel. : (+2) 02 - 2529821 (5 Lines) (طوط ٥) ٢٠٢ - ٢٥٢٩٨٢١ ون: Fax : (+2) 02 - 2529826 ٢٠٢ - ٢٥٢٩٨٢٦ س: E-mail : [email protected] corc2000@excite.com :ودא Pressure Vessel DESIGN CALCULATIONS Code : ASME Section VIII, Division 1, Edition 2001, Addenda 2002 Code Stamp : U Client : Amerya Petroleum Refining Co. (APRC) Project : Design & Fabrication of Debutanizer Reflux Reliever Drum Location : Alexandria, EGYPT Item No. : 1-D-5 Serial No. : 7434-33-U-2006 Title : Horizontal Pressure Vessel Service : Deputanizer Reflux Reliever Drum Job No. : 7434-33 Dwg. No. : 7434-33-3A, Rev. 1 Vessel ID 1556 MM Tangent-to-Tangent Length 4820 MM Vessel Wall Thickness 22 MM MAWP 18 Kg/CM 2 G Design Temperature 65 o C MDMT -12 o C Vessel capacity 10.1518 M 3 Weight of vessel empty (erection weight), W 7428 Kg Weight of test liquid (water), Wc 10152 Kg Total test weight (weight of vessel and test liquid), Wt 17580 Kg Number of saddles 2 Saddles By Eng. Abdel Halim Galala Design Sector Manager (assist.) Design Sector מعאط Page : 1 of 126 Sheet 1 of 2

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Page 1: 52379610 Pressure Vessel Design Calculations

Cairo Oil Refining Co. ���א����ول������ ��א����

Subsidery of Egyotian Gen. Petroleum Corp. ��د���� ��א�����א������א�� ��������ول

P.O. Box : Heliopolis 11757 Cairo A.R.E. ص.�.��:����و�و�س�١١٧٥٧ ����א��دد�

Tel. : (+2) 02 - 2529821 (5 Lines) ��%ون�:�٢٥٢٩٨٢١ - ٢٠٢ (٥ #طوط)

Fax : (+2) 02 - 2529826 س�:��٢٥٢٩٨٢٦ - ٢٠٢ &

E-mail : [email protected] [email protected]��:�'(و����د�א�

Pressure Vessel

DESIGN CALCULATIONS

Code : ASME Section VIII, Division 1, Edition 2001, Addenda 2002

Code Stamp : U

Client : Amerya Petroleum Refining Co. (APRC)

Project : Design & Fabrication of Debutanizer Reflux Reliever Drum

Location : Alexandria, EGYPT

Item No. : 1-D-5

Serial No. : 7434-33-U-2006

Title : Horizontal Pressure Vessel

Service : Deputanizer Reflux Reliever Drum

Job No. : 7434-33

Dwg. No. : 7434-33-3A, Rev. 1

Vessel ID 1556 MM

Tangent-to-Tangent Length 4820 MM

Vessel Wall Thickness 22 MM

MAWP 18 Kg/CM2G

Design Temperature 65oC

MDMT -12oC

Vessel capacity 10.1518 M3

Weight of vessel empty (erection weight), W 7428 Kg

Weight of test liquid (water), Wc 10152 Kg

Total test weight (weight of vessel and test liquid), Wt 17580 Kg

Number of saddles 2 Saddles

By

Eng. Abdel Halim GalalaDesign Sector Manager (assist.)

Design Sector +ط ع�א����מ

Page : 1 of 126 Sheet 1 of 2

Page 2: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 2 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 2

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

A. Title (cont.)

DESIGN CALCULATIONSCode : ASME Section VIII, Division 1, Edition 2001, Addenda 2002

Client : Amerya Petroleum Refining Co. (APRC)

Project : Design & Fabrication of Debutanizer Reflux Receiver Drum

Location : Alexandria, EGYPT

Item No. : 1-D-5

Serial No. : 7434-33-U-2006

Title : Horizontal Pressure Vessel

Service : Debutanizer Reflux Receiver Drum

Job No. : 7434-33Dwg. No. : 7434-33-3A, Rev. 1

3

2

1 Issued for approval 18.2.2004

0 Issued for comments 6.4.2003 6.4.2003 6.4.2003

Designed by Reviewed by Approved by

Rev. Description Date Date Date

Revision Table Dwg. No. : 7434-33-3A Rev. : 1

Page 3: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 3 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 1

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

B. Copyright.

Copyright 2004 by

CORC

A.H.Galala, the Design Manager, on behalf of

Cairo Oil Refining Co. (CORC)

All right reserved.

1st. date of issue - April 6th., 2003

No part of this document may be reproduced in any form,

electronic retrieveal system or any otherwise without the

prior written permission of Designer.

Page 4: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 4 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 1

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

C. Revision Description.

This page is a record of all revisions of the document, and the

following revision(s) has (have) been made to this document.

Sheet

Rev. Date No. Revision Description

0 6.4.2003 all Issued for comments

1 18.2.2004 all Issued for approval

Page 5: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 5 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 1

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

D. Contents. Description Page

A. Title. Page : 1 of 126

B. Copyright. Page : 3 of 126

C. Revision Description. Page : 4 of 126

D. Contents. Page : 5 of 126

E. Applicable Loading Considered in Design. Page : 6 of 126

F. Impact Test Requirements. Page : 7 of 126

G. Standarad ASME B16.5 Flange Rating Class. Page : 7 of 126

H. Cylindrical Shell Thickness. Page : 8 of 126

I. Check of Cylindrical Shell Thickness for External Pressure, FV. Page : 12 of 126

J. Ellipsoidal Head Thickness Under Internal Pressure. Page : 13 of 126

K. Maximum Working Pressure, MWP (New/cold & Operating/corroded). Page : 14 of 126

L. Check of Ellipsoidal Head Thickness for External Pressure (Convex Side), FV. Page : 15 of 126

M. Nozzle Neck thicknesses & Nozzle Openings Compensation : Thk., MM

M1 N11 1-1/2" 300# WNRF Sch. XXS 10.16 Page : 16 of 126

M2 N8 24" 300# WNRF Sch. 30 14.27 Page : 21 of 126

M3 Leg 20" Sch. 30 12.7 Page : 26 of 126

M4 N1 8" 300# WNRF Sch. 60 12.7 Page : 31 of 126

Integral Type Flange (Blind) N1 8" 300# Thickness Calculation Page : 36 of 126

M5 N1 6" 300# WNRF Sch. 80 10.97 Page : 46 of 126

M6 N2 6" 300# WNRF Sch. 80 10.97 Page : 50 of 126

M7 N9 4" 300# WNRF Sch. 120 11.13 Page : 55 of 126

M8 N18 3" 300# WNRF Sch. 160 8.74 Page : 60 of 126

M9 N3,N4&N7 2" 300# WNRF Sch. XXS 10.16 Page : 65 of 126

M10 N6&N17 1-1/2" 300# WNRF Sch. XXS 9.09 Page : 70 of 126

M11 N16 1" 300# WNRF Sch. XXS 10.16 Page : 75 of 126

M12 N5A,N5B&N12 1-1/2" 300# WNRF Sch. XXS 10.16 Page : 79 of 126

M13 N10A& N10B 1/2" 300# WNRF Sch. XXS 7.47 Page : 85 of 126

N. Design of Saddle Supports. Page : 90 of 126

O. Lowest MDMT Without Impact Test. Page : 97 of 126

P. Radiography. Page : 110 of 126

Q. Hydrostatic Test Pressure. Page : 110 of 126

R. Post Weld Heat Treatment (PWHT). Page : 110 of 126

S. Vessel Weight Calculation. Page : 111 of 126

T. Sresses in Vessel on Two Saddle Supports. Page : 114 of 126

U. Check of the Anchor Bolts Due to Seismic and Wind Loading. Page : 122 of 126

V. Lifting Lugs Thickness Calculations. Page : 123 of 126

W. Mesh Pad (Demister) Calculations. Page : 125 of 126X. References. Page : 126 of 126

Page 6: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 6 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 1

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Page : 2 of 126

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

E. Applicable Loading Considered in Design. [UG-22 & UG-98]

I. By considering UG-22 :

1. The loadings to be considered in design of vessel shall include the following :

a. Internal design pressure (see item II below).

b. Weight of the vessel and contents under test conditions.

c. Attachment of vessel supports such as lifting lugs and saddles.

2. No expected effect for superimposed static reactions such as piping.

There is no attached equipment such as motors, machinery, other vessels,

lining and insulation.

3. The effect of the following loadings is considered negligible and/or not applicable :

a. Cyclic and dynamic reactions due to pressure for thermal variations.

b. Wind, snow, and seismic reactions.

c. Impact reactions due to fluid chock.

d. Temperature gradients and differential thermal expansion.

II. By considering UG-21 & UG-98 :

The max. allowable working pressure for a vessel part is the max.internal

pressure at the highest point of vessel.

Since the vessel is intended to be erected horizontaly, the static head

equals almost the ID and the hight of leg :

Max. Operating Pressure 227.3 PSIG 16 Kg/cm2G

Internal design pressure, P (MAWP) (at highest point of vessel) 257 PSIG 18 Kg/cm2G

External design pressure, Pex 0 PSIG 0 Kg/cm2G

Vessel ID 61.2598 INCH 1556 MM

Max. leg height = 12 + 12 + 503 + 2 + 165 27.3228 INCH 694 MM

Max. height of drain N4 = 12 + 12 + 502 + 2 + 165 + 200 35.1969 INCH 894 MM

Water sp. gr. 1

Fluid sp. gr.at 15 oC 0.5

Max. hydrostatic head at internal bottom of vessel 2.21023 PSIG 0.1556 Kg/cm2G

Max. hydrostatic head at bottom of leg 3.19602 PSIG 0.225 Kg/cm2G

Max. hydrostatic head at drain N4 3.48011 PSIG 0.245 Kg/cm2G

Max. pressure for calculation at internal bottom of vessel 257.892 PSIG 18.1556 Kg/cm2G

Max. pressure for calculation at bottom of leg 258.878 PSIG 18.225 Kg/cm2G

Max. pressure for calculation at outlet drain N4 259.162 PSIG 18.245 Kg/cm2G

Page 7: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 7 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

F. Impact Test Requirements. [UG-22 & UG-98]

Impact test is not mandatory for the following pressure vessels materials :

I. Pressure Parts.

a. Main Vessel Components : P-No. Group No. Curve

a. Shell : ASME SA516 Grade 70 1 2 D

b Heads : ASME SA516 Grade 70 1 2 D

c. Flanges : ASME SA 105 1 2 B

d. Nozzle Necks : ASME SA 106 Grade B 1 1 B

e. Fittings, Tees : ASME SA 234 Grade WPB 1 1 B

b. Stud Bolts & Nuts :

f. Stud Boltshell ASME SA 193 Grade B7 UNS No. G41400 [Size < 2-1/2"]

g. Nuts ASME SA 194 Grade 2H

II. Non-Pressure Parts.

a. Saddle plate : ASME SA516 Grade 70 1 2 D

b. Lifting lugs & Pads : ASME SA516 Grade 70 1 2 D

Thickness of vessel components :

- Shell & Heads ASME SA516 Grade 70 0.9 INCH 22 MM

- Max. Nozzle Necks Thk. ASME SA 106 Grade B 0.56181 INCH 14.27 MM

Where the MDMT is 10oF -12

oC

in accordance with UG-20(f), UCS-66 and FIG. UCS-66, no impact test is required.

Please refer pages from Page : 97 of 126

Impct Test is not required as per Code,

but is required as a client request.

G. Standard ASME Flange Rating Class.

1. Standard ASME B16.5 welded neck flanges shall be used.

2. For standard flange, Carbon Steel material in accordance

with ASME SA105, P-No. 1, Group No. 2, and for MAWP 255.682 PSIG 18 Kg/CM2G

and Design temp. 149oF 65

oC

The rating of flanges shall be 150# class, which satisfys the requirements of

Table 2 of ASME B16.5-1996.

3. As a client request, the rating shall be 300#

Page 8: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 8 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3

Type : Horizontal

H. Cylindrical Shell Thickness Under Internal Pressure [UG-27(c)]

Shell material, Killed Carbon Steel, ASME SA516 Grade 70

Normalized & Notch Toughness Tested

Shell material Specifications [Table 1A, Suppart 1, ASME Sec. II, Part D]

P-No. 1

Group No. 2

External Pressure Chart No. CS-2

Vessel Inside Diameter, D 61.2598 INCH 1556 MM

Shell Inside Diameter, D 61.2598 INCH 1556 MM

Shell Inside Radius, Ri 30.6299 INCH 778 MM

Shell length from Tangent-to-Tangent (T/T), L 189.764 INCH 4820 MM

Max. Design Temperature 149oF 65

oC

Min. Design Metal Temperature, MDMT 10oF -12

oC

Max. Operating Temperature 122oF 50

oC

Max. Operating Pressure 227.273 PSIG 16 Kg/CM2G

Max. Internal Design Pressure, P (MAWP) 255.682 PSIG 18 Kg/CM2G

External Design Pressure (Full Vacuum) Not Applicable 0 PSIG 0 Kg/CM2G

Shell Inside Diameter, D 61.26 INCH 1556 MM

Shell Inside Radius, R 30.63 INCH 778 MM

Static Head = Vessel Diameter 1.556 M

Static Head Pressure (water head x sp. gr. 1.0) 2.216 PSIG 0.156 Kg/CM2G

Internal Design Pressure at bottom of vessel, 257.898 PSIG 18.156 Kg/CM2G

Max. Allowable Stress @ Design Temp.(65 oC), S 20000 PSIG 1408 Kg/CM

2G

Max. Allowable Stress @ Test Temp.(40 oC), St 20000 PSIG 1408 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Hydrostatic Test Pressure, Ph = 1.3 x MAWP x (St/S) [UG-99(b)] 332.386 PSIG 23.4 Kg/CM2G

Hydrostatic Test Pressure, Ph = 1.5 x MAWP x (St/S) [Client request] 383.523 PSIG 27 Kg/CM2G

Corrosion Allowance, C [UG-25] 0.236 INCH 6 MM

Joint Efficiency, E [TABLE UW-12] 0.85

[Spot Radiography], [Table UCS-57] 15%

Page 9: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 9 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

H. Cylinderical Shell Thickness Under Internal Pressure (cont.) [UG-27(c)]

Value of 0.385 SE [UG-27(c)(1)] 6545 PSIG 460.768 Kg/CM2G

Since P does not exceed 0.385 SE, Use Thin Wall Equation:

[1] Min. Wall Thickness for Longitudinal Joints,

t1 = PR / (SE - 0.6P) [UG-27(c)(1)] 0.469 INCH 11.913 MM

Value of 1.25 SE [UG-27(c)(1)] 21250 PSIG 1496 Kg/CM2G

Since P does not exceed 1.25 SE, Use Thin Wall Equation:

[2] Min. Wall Thickness for Circumferential Joints,

t2 = PR / (2SE + 0.4P) [UG-27(c)(2)] 0.232 INCH 5.893 MM

The min. wall thickness shall be the greater of t1 or t2 0.469 INCH 11.913 MM

By Adding Corrosion Allowance to Wall Tickness, t 0.705 INCH 17.907 MM

Use Thickness of Construction, t (Adopted thickness) 0.866 INCH 22 MM

Corroded Thickness = Adopted thk. - Corrosion allowance 0.63 INCH 16 MM

In case of using shell fab. from pipe '20" Pipe nominal thickness, t (Sch.40) 0.472440945 INCH 12 MM

20" Pipe nominal thickness under tolerance tn = t - 0.125 t 0.472440945 INCH 12 MM

20" Pipe Corroded Thickness = tn - Corrosion allow ance 0.236440945 INCH 6 MM

Using 20" pipe sch. 40 is OK

By using APPENDIX 1-1 (In terms of the Outside Diameter) :

tm = P Ro / (SE + 0.4 P) 0.458 INCH 11.633 MM

Thickness adjusted for w all thickness tolerance :

t = tm / (100%-12.5%) 0.523 INCH 13.284 MM

By Adding Corrosion Allow ance to Wall Tickness, t 0.759 INCH 19.284 MM

Using 20" pipe w ith commercial w all thickness, sch. 40 is OK

Ladders and Platforms N.A.

Vessel saddle supports Yes Page : 90 of 126

Hot/cold Insulation N.A.

Post Weld Heat Treatment, PWHT Not required per CodePage : 110 of 126

Impact Test Per Code Page : 7 of 126

Note. Impact test is required as a client request.

Page 10: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 10 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

H. Check of Shell Thickness Under Internal Pressure

[ For horizontal pressure vessels, with supplemental loading ] (vessel weight & hydrostatic liquid content)

[APPENDIX L-2.2.2]

Vessel OD 61.2598 INCH 1600 MM

Vessel Wall Thickness in the Corroded Condition, t 0.63 INCH 16 MM

Vessel I.D. in the Corroded Condition, 2R = OD - 2 t 59.9998 INCH 1568 MM

Shell length from Tangent-to-Tangent (T/T), L 189.764 INCH 4820 MM

Shell Length from W.L.- to - W.L, L' 186.614 INCH 4740 MM

Joint Efficiency (Longitudinal Seams), E 0.85

Joint Efficiency (Circumferential Seams), E 0.85

Weight of Vessel, W 16377.3 lb 7428 Kg

Weight of Contents, Wc 22383.2 lb 10152 Kg

Total Weight of Vessel and Contents, Wt 38760.5 lb 17580 Kg

Assume a Total no. of Saddles 2

Reaction at each Saddle, Q 19380.3 lb 8790 Kg

Head (Cap) Depth - to - T.L, [Table 8, ASME B16.9-1993] 15.315 INCH 389 MM

Saddle - to - T.L., A 22.047 INCH 560 MM

Material to Chart for Compressive Stress,

[ FIG.CS-2 CHART, SUBPART 3 , ASME SEC.II , PART D ]

Shell, Ro 31.4961 INCH 800 MM

N.B. See vessel drawing layout, Page : 91 of 126

* Here three cases must be investigated:

Case 1. Circumferential Stress due to Internal Pressure,

t = PR / ( SE-0.6 P) [UG-27C(1)] 0.465 INCH 11.811 MM

Case 2. Longitudinal Tensile Strength due to Bending

( at the midpoint between the saddles) must be

added to the longitudinal Stress due to Internal

Pressure.

[ APPENDIX L-2.2.2]

t 0.238 INCH 6.045 MM

N.B. Circumferential joint at center of vessel is the point of max. positive moment.

Max. negative moment is at supports but there is no joint there.Other circumferential joint

must be investigated using moment at the joint in calculating the compined stresses.

Page 11: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 11 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

H. Check of Shell Thickness Under Internal Pressure (cont.)

[ For horizontal pressure vessels, with supplemental loading ] (vessel weight & hydrostatic liquid content)

[APPENDIX L-2.2.2]

Case 3 . Longitudinal Compressive Stress due to Bending.

First determine the max. allowable compressive stress :

Factor A = 0.125 / (Ro / t ) [UG-23(b)] 0.00344

Therefore, B [SUBPART 3 OF ASME SEC.II, PART D, FIG.CS-2] 16000 PSIG 1126.4 Kg/CM2G

NOTES:

1. No need to calculate the value of B by equation B = AE / 2 ,

since the value of A falls under the applicable Material/Temp. line.

[ Suppart 3 of ASME Sec.II, Part D, Fig. CS-2]

2. The general equatioin for thickness is the same as for

longitudinal tensile stress except the pressure portion drops

out since the most severe condition occurs when there is no

pressure in the vessel .

3. The joint efficiency for butt-welded joints shall be taken as

unity when investigating longitudinal compression. [UG-23(b)]

[ APPENDIX L-2.2.2]

Thickness , t 0.00902 INCH 0.229 MM

Page 12: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 12 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

I. Check of Shell Thickness for External Pressure (Full Vacuum)

Design Temperature 149oF 65

oC

For external pressure on cylinder, use UG-28 and Subpart 3.

Determine the effective length of shell without stiffening rings, L

Shell length from Tangent-to-Tangent (T/T), L1 189.764 INCH 4820 MM

Internal Height of Elliptical Head 2:1, h = ID/4 15.315 INCH 389 MM

Head Wall Thickness, th 0.7874 INCH 20 MM

Internal Height of Ellipsoidal Head 2:1, ho = h + th 16.1024 INCH 409 MM

Effective shell length without stiffening, L = L1 + 2/3 ho 200.499 INCH 5092.667 MM

Assume t for internal pressure (at corroded condition) 0.62992 INCH 16 MM

Do = ID + 2 t 62.7559 INCH 1594 MM

L / Do 3.1949

Do / t 99.625 > 10

Since Do/t > 10, use UG-28(c)(1)

a. Enter Fig. G with L / Do and read across to sloping line of Do/t

Read factor A 0.00038

b. Enter Fig. CS-2 with A (to find factor B), which falls under the curve. 5500 PSI 387.2 Kg/CM2G

Follow step (6) of UG-28(c)(1), and calculate the value of max. allowable

external working pressure, PA = 4B / 3 (Do / t) 73.6094 PSI 5.1821 Kg/CM2G

Change t untill PA > 15 PSI (full vacuum) 15 PSI 1.056 Kg/CM2G

OK

E = Modulus of elasticity at design temp. 2.9E+07 PSI 2024352 Kg/CM2G

at amp. temp. 2.9E+07 PSI 2055680 Kg/CM2G

Notes.

1. For value of A falling to the left of the material-temp. line, the value

of Pa can be calculated as follows : Pa = 2 A E / 3 (Do /t)

2. For L/Do > 50, use L/Do = 50

For L/Do < 0.05, use L/Do = 0.05

3. For Do/t > 10, use UG-28(c)(1)

For Do/t < 10, use UG-28(c)(2)

Page 13: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 13 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 2

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

J. Ellipsoidal Head Thickness Under Internal Pressure [UG-32(f)]

Head material, Carbon Steel ASME SA516 Grade 70

Head type [Seamless] Ellipsoidal 2:1

Head material Specifications [Table 1A, Suppart 1, ASME Sec. II, Part D]

P-No. 1

Group No. 2

External Pressure Chart No. CS-2

Head ID 61.2598 INCH 1556 MM

Head OD [ASME B16.5-1996] 62.9921 INCH 1600 MM

Head Outside Radius 31.4961 INCH 800 MM

Design Temperature 149oF 65

oC

Min. Design Metal Temperature, MDMT 10oF -12

oC

Max. Allowable Working Pressure, MAWP 257.898 PSIG 18.156 Kg/CM2G

Operating Pressure 227.273 PSIG 16 Kg/CM2G

Internal Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Head Skirt Inside Diameter, D 61.26 INCH 1556 MM

Head Inside Radius, L ( ri ) 30.63 INCH 778 MM

Max. Allowable Stress @ Design Temp.(60 oC), S 20000 PSIG 1408 Kg/CM

2G

Max. Allowable Stress @ Test Temp.(40 oC), St 20000 PSIG 1408 Kg/CM

2G

[TABLE 1A , SUBPART 1 , ASME SEC. II , PART D]

Hydrostatic Test Pressure, Ph = 1.3*MAWP(St/S) [UG-99(b)] 335.27 PSIG 23.603 Kg/CM2G

Corrosion Allowance, C [UG-25] 0.23622 INCH 6 MM

Joint Efficiency, E (Seamless & Full Radiography) [TABLE UW-12] 0.85

Outside Diameter of Head, Do 62.9921 INCH 1600 MM

Outside Radius of Head, Ro 31.4961 INCH 800 MM

Value of 0.665 SE 11305 PSIG 795.872 KG/CM2G

Since the value of 0.66SE > P, Use Thin Wall Equation for

Calculating the Min. required Thickness of Head, t:

t1 = PD / (2SE-0.2P) [UG-32(d)] (1) 0.46538 INCH 11.82059 MM

Compare to Thickness of Seamless Spherical Shell :

Ps = 0.665 SE 11305 PSIG 795.872 KG/CM2G

Since P < Ps, Calculate Thickness for thin Wall Spherical Shell:

t2 = PRo/(2SE+0.8P) [APPENDIX 1-1] (2) 0.23746 INCH 6.031587 MM

For thin Wall ellipsoidal 2:1 head :

t = PD/(2SE-0.2P) [UG-32(d)] 0.46538 INCH 11.82059 MM

Page 14: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 14 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 2

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

J. Ellipsoidal Head Thickness Under Internal Pressure (cont.) [UG-32(f)]

Head Thickness due to Internal Pressure, t = MAX ( t1 , t2) 0.46538 INCH 11.82059 MM

By adding Corrosion Allowance to Wall Thickness, 0.7016 INCH 17.82059 MM

Use Thickness of Construction, t (Adopted thickness) 0.787 INCH 20 MM

[ t Represents the Min. Thickness after Forming ]

Corroded Thickness = Adopted thk. - Corrosion allowance 0.55118 INCH 14 MM

In case of using '20" Cap nominal thickness, t (Sch. 40) 0.787401575 INCH 20 MM

20" Cap nominal thickness under tolerance tn = t - 0.125 t 0.787401575 INCH 20 MM

20" Cap Corroded Thickness = tn - Corrosion allow ance 0.551181102 INCH 14 MM

Using 20" Cap sch. 80 is OK

Required Head Thickness :

Head tr = PD / (2SE - 0.2 P) 0.46538 INCH 11.82059 MM

K. Maximum Working Pressure, MWP (New & Operating)

a. For Shell :

MWP, New & cold (20 MM) P = SE t /(R + 0.6 t) [UG-27(c)(1)] 472.622 PSIG 33.273 Kg/CM2G

MWP, Operating & corroded (14 MM) P = SE t /(R + 0.6 t) 345.395 PSIG 24.316 Kg/CM2G

b. For Head :

MWP, New & cold (20 MM) P = 2SE t /(D + 0.2 t) [UG-32(d)(1)] 435.675 PSIG 30.67149 Kg/CM2G

MWP, Operating & corroded (14 MM), P = 2SE t /(D + 0.2 t) [305.362 PSIG 21.49751 Kg/CM2G

Page 15: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 15 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 2

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

L. Check of Ellipsoidal Head Thickness for External Pressure (Convex Side), (Full Vacuum)

[UG-33(d)]

Assumed corroded thickness of head, t 0.55118 INCH 14 MM

Outside diameter of the head skirt, Do 62.3622 INCH 1584 MM

The equivalent outside spherical, Ro = Ko Do [UG-33(b)] 54.342 INCH 1380.288 MM

Outside height of the ellipsoidal head (measured from head-bend line), ho 16.1024 INCH 409 MM

Ratio of the major to the minor axis of ellipsoidal head, Do/2ho 1.93643

Factor depending on the ellipsoidal head proportions Do/2ho, Ko 0.87139

(use interpolation) [See Table UG-33.1]

The required thickness of an ellipsoidal head having pressure on the

convex side, either seamless or of built-up construction with butt joints,

shall not be less than that determined by the following procedure :

Step 1. Assume a value for t and calculate the value of factor A

using the following formula : A = 0.125 / (Ro / t) 0.00127

Step 2. Using the value of A calculate in Step 1, follow the same

procedure as that given for spherical shells in UG-28(d),

Step 2 through 6 :

a. Enter Fig. CS-2 with A (to find factor B), which is under the curve, B 9500 PSI 668.8 Kg/CM2G

Follow step (4) of UG-28(d), and calculate the value of max. allowable

external working pressure, PA = B / (Ro / t) 96.3567 PSI 6.783514 Kg/CM2G

Change t untill PA > 15 PSI (full vacuum) 0 PSI 0 Kg/CM2G

Notes. OK

1. For value of A falling to the left of the material-temp. line, the value

of Pa can be calculated in accordance with Step 5 of UG-28(d), as

follows : Pa = 0.0625 E / (Ro /t)2

E = Modulus of elasticity at design temp. 2.6E+07 PSI

Page 16: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 16 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M1. Nozzle Mark : N11, 1-1/2"NPS, Sch. XXS, 300# WNRF(Located entirely within a centrally located circle of head's leg)

No. of nozzles, n 1

Nozzle Neck Thickness Calculation [UG-27 & Appendix 1-1] (Cap 20" NPS, Sch. 30)

Determine if the opening and its reinforcement in the ellipsoidal head (cap)

are located entirelly within a centrally located circle which has a diameter

equal to 80% of the shell/leg diameter [see UG-37(a) & Appendix L-7.6]

0.8 x Shell/leg ID 15.2 INCH 386.08 MM

2 d 3.34488 INCH 84.96 MM

Therefore, the required head thickness for reinforcement calculations, tr

are to be determined by the hemispherical head formula using a radius of

K1D where K1 = 0.9 for 2:1 ellip[soidal head. 0.9

Nozzle Size, NPS 1.5 INCH 40 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 259.166 PSIG 18.2453 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating [Section G] 300#

[ANSI/ASME B16.5-1996]

Max. Allowable Stress of Nozzle Material @ Design Temp.(75 oC), Sn 17100 PSIG 1203.84 Kg/CM

2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 0.95 INCH 24.13 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.01431 INCH 0.363508 MM

[APPENDIX 1.1]

By adding Corrosion Allowance, t [UG-25] 0.25053 INCH 6.363508 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.28185 INCH 7.158947 MM

Use Nozzle 1-1/2" NPS with Selected Neck Sch. XXS,

with Thickness 0.4" ( 10.15 MM ). [Table 2 of ANSI B 36.10M-1985-(R-1994)] 0.4 INCH 10.16 MM

Page 17: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 17 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M1. Nozzle Mark : N11 1-1/2 300# WNRF (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27 & Appendix 1-1]

Nozzle Pipe Size, NPS 1.5 INCH 40 DN

Nozzle Pipe Sch. XXS

Design Pressure, P 259.166 PSIG 18.24529 Kg/CM2G

Design Temparture 149oF 65

oC

Shell & Head Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA 106 Grade B

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell & Head Thickness 0.5 INCH 12.7 MM

Shell & Head Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell & Head Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.5 INCH 12.7 MM

Shell & Head Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.26378 INCH 6.7 MM

Nozzle Wall Nominal Thickness 0.4 INCH 10.16 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.35 INCH 8.89 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.11378 INCH 2.89 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.11378 INCH 2.89 MM

Reinforced Pad Thickness, te 0.47244 INCH 12 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell & Head Outside Diameter, OD 20 INCH 508 MM

Shell & Head Inside Diameter in Corroded Condition, 2R = OD - 2 t 19.4724 INCH 494.6 MM

Shell & Head Inside Radius in Corroded Condition, R 9.73622 INCH 247.3 MM

Nozzle Outside Diameter, OD 1.9 INCH 48.26 MM

Nozzle Inside Diameter, ID 1.1 INCH 27.94 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 0.65945 INCH 16.75 MM

h2 = 2.5 ti 0.28445 INCH 7.225 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 1.67244 INCH 42.48 MM

Finished Radius of Circular Opening, Rn 0.83622 INCH 21.24 MM

Page 18: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 18 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M1. Nozzle Mark : N11 1-1/2 300# WNRF (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27 & Appendix 1-1]

* Outside Diameter of Reinforced Pad [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 3.34488 INCH 84.96 MM

Dp2 = 2 (Rn + nozzle wall thk., tn + vessel wall thk., t ) 2.42756 INCH 61.66 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 3.34488 INCH 84.96 MM

Calculating Size of Fillet Welds : [UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.4 INCH 10.16 MM

tmin.3 (shell wall thickness) 0.47244 INCH 12 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.4 INCH 10.16 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 tmin. 0.28 INCH 7.112 MM

tc = lesser of t c1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in Dwg. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld [FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.47244 INCH 12 MM

tmin.3 ( shell wall thickness) 0.5 INCH 12.7 MM

tmin. = lesser of t min.1, t min. 2 & t min.3 0.47244 INCH 12 MM

1/2 tmin. 0.23622 INCH 6 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(t min./2) 0.33407 INCH 8.5 MM

Use Leg with Dimension D in Dwg. No. 7434-33-3A 0.35433 INCH 9 MM

* Wall Thickness Required : [UG-27(c)(1)]

Head tr = PK1D / (2SE - 0.2 P) 0.13742 INCH 3.490341 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.01279 INCH 0.324866 MM

* Strength Reduction Factors : Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 19: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 19 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M1. Nozzle Mark : N11 1-1/2 300# WNRF (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.24901 INCH 6.324866 MM

B*. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.32997 INCH 8.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.37364 INCH 9.490341 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.3631 INCH 9.222625 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 1-1/2", Sch. std0.145 INCH 3.683 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.32997 INCH 8.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.32997 INCH 8.38125 MM

The nominal nozzle pipe wall thk. 0.4 INCH 10.16 MM

The min. nozzle thk. provided = t (1-0.125) 0.35 INCH 8.89 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

* Since the opening is access/inspection, UG-45(b) is not applicable [UG-45(b)[

Page 20: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 20 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M1. Nozzle Mark : N11 1-1/2 300# WNRF (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27]

Area of Reinforcement (with Reinforcing Element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 0.23435 INCH2

151.195 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 0.20717 INCH2

133.6563 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.09125 INCH2

58.87124 MM2

A1 = The Greater of A11 or A12 0.20717 INCH2

133.6563 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.11388 INCH2

73.47186 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.13071 INCH2

84.32815 MM2

A2 = The Lesser of A21 or A22 0.11388 INCH2

73.47186 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.1283 INCH2

82.77683 MM2

A32 = 5 ti ti fr2 0.05534 INCH2

35.70523 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.12555 INCH

281 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 :

A5 = (Dp - d - 2tn) te fr4 0.68262 INCH2

440.4 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A43 + A5 1.34391 INCH2

867.0381 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 21: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 21 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Shee t : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M2. Nozzle Mark : N8 24" NPS, Sch. 30, 300# WNRF (Manhole Located at Shell with Reinforcement)

No. of nozzles, n 1

Nozzle Neck Thickness Calculation [UG-27(c) & Appendix 1-1]

Nozzle Size, NPS 24 INCH 600 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Max. Allowable Stress of Nozzle Material @ Design Temp.(75 oC), Sn 17100 PSIG 1203.84 Kg/CM

2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 12 INCH 304.8 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.1799 INCH 4.569353 MM

[APPENDIX 1.1]

By adding Corrosion Allowance, t [UG-25] 0.41612 INCH 10.56935 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.46813 INCH 11.89052 MM

Use Nozzle 24" NPS with Selected Neck Sch. 30, 0.562 INCH 14.2748 MM

with Thickness 0.562" (14.27 MM). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.49175 INCH 12.49045 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.25553 INCH 6.49045 MM

MWP, New & cold (14.275 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 712.422 PSIG 50.15448 Kg/CM2G

MWP, Operating & corroded (9.49 MM) P = Sn E t /(Ron - 0.4 t) 367.258 PSIG 25.85495 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 22: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 22 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Date : 18.2.2004

Project : Design & Procurement of ASME Pressure Vessel Client : APRC

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M2. Nozzle Mark : N8 24" Sch. 30, 300# WNRF Manhole (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27(c) & Appendix 1-1]

Nozzle Pipe Size, NPS 24 INCH 600 DN

Nozzle Pipe Sch. 30

Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.562 INCH 14.2748 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.49175 INCH 12.49045 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.25553 INCH 6.49045 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.25553 INCH 6.49045 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 24 INCH 609.6 MM

Nozzle Inside Diameter, ID 22.876 INCH 581.0504 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.63882 INCH 16.22613 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 23.4889 INCH 596.6191 MM

Finished Radius of Circular Opening, Rn 11.7445 INCH 298.3096 MM

Page 23: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 23 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M2. Nozzle Mark : N8 24" Sch. 30, 300# WNRF Manhole (cont.)

Nozzle Opening Calculation With Reinforcing (cont.)

[UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 46.9779 INCH 1193.238 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 25.2598 INCH 641.6 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 46.9779 INCH 1193.238 MM

Calculating Siz of Fillet Welds : [UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.562 INCH 14.2748 MM

tmin.3 (shell wall thickness) 0.47244 INCH 12 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.47244 INCH 12 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.33071 INCH 8.4 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in Dwg. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld [FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 tmin. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in Dwg. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47256 INCH 12.0029 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.17874 INCH 4.540115 MM

* Strength Reduction Factors : Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 24: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 24 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M2. Nozzle Mark : N8 24" Sch. 30, 300# WNRF Manhole (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.41497 INCH 10.54012 MM

B*. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.29872 INCH 7.5875 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.29872 INCH 7.5875 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70878 INCH 18.0029 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.29872 INCH 7.5875 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.29872 INCH 7.5875 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.56435 INCH 14.33438 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 24", Sch. Std. 0.375 INCH 9.525 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.29872 INCH 7.5875 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.41497 INCH 10.54012 MM

The nominal nozzle pipe wall thk. 0.562 INCH 14.2748 MM

The min. nozzle thk. provided = t (1-0.125) 0.49175 INCH 12.49045 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

* Since the opening is access/inspection, UG-45(b) is not applicable [UG-45(b)[

Page 25: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 25 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M2. Nozzle Mark : N8 24" Sch. 30, 300# WNRF Manhole (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27]

Area of Reinforcement (witht Reinforcing element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 11.1348 INCH2

7183.753 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 3.6847 INCH2

2377.221 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.26702 INCH2

172.2696 MM2

A1 = The Greater of A11 or A12 3.6847 INCH2

2377.221 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.20677 INCH2

133.4029 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.19761 INCH2

127.4869 MM2

A2 = The Lesser of A21 or A22 0.19761 INCH2

127.4869 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.68812 INCH2

443.9468 MM2

A32 = 5 ti ti fr2 0.27914 INCH2

180.0884 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 :

A5 = (Dp - d - 2tn) te fr4 19.9021 INCH2

12840.04 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 + A5 24.3029 INCH2

15679.26 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 26: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 26 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Shee t : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M3. Nozzle Mark : Leg 20"NPS, Sch. 30 (Leg Located at Shell with Reinforcement)

No. of nozzles, n 1

Nozzle Neck Thickness Calculation [UG-27(c) & Appendix 1-1]

Nozzle Size, NPS 20 INCH 500 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 259.166 PSIG 18.24529 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating #VALUE!

[ANSI/ASME B16.5-1996]

Max. Allowable Stress of Nozzle Material @ Design Temp.(75 oC), Sn 17100 PSIG 1203.84 Kg/CM

2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 10 INCH 254 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.15065 INCH 3.826403 MM

[APPENDIX 1.1]

By adding Corrosion Allowance, t [UG-25] 0.38687 INCH 9.826403 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.43522 INCH 11.0547 MM

Use Nozzle 20" NPS with Selected Neck Sch. 30, 0.5 INCH 12.7 MM

with Thickness 0.5" (12.7 MM). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

A cap 20" NPS, Sch. 30, BW in accordance with ASME 16.9 shall be used for leg.

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.4375 INCH 11.1125 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.20128 INCH 5.1125 MM

MWP, New & cold (12.7 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 761.45 PSIG 53.60611 Kg/CM2G

MWP, Operating & corroded (8.11 MM) P = Sn E t /(Ron - 0.4 t) 346.982 PSIG 24.42751 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 27: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 27 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M3. Nozzle Mark : Leg 20" Sch. 30 (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27(c) & Appendix 1-1]

Nozzle Pipe Size, NPS 20 INCH 500 DN

Nozzle Pipe Sch. 30

Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.5 INCH 12.7 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.4375 INCH 11.1125 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.20128 INCH 5.1125 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.20128 INCH 5.1125 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 20 INCH 508 MM

Nozzle Inside Diameter, ID 19 INCH 482.6 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.5032 INCH 12.78125 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 19.5974 INCH 497.775 MM

Finished Radius of Circular Opening, Rn 9.79872 INCH 248.8875 MM

Page 28: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 28 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M3. Nozzle Mark : Leg 20" Sch. 30 (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.)

[UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 39.1949 INCH 995.55 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 21.2598 INCH 540 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 39.1949 INCH 995.55 MM

Calculating Siz of Fillet Welds : [UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.5 INCH 12.7 MM

tmin.3 (shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.5 INCH 12.7 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.35 INCH 8.89 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in Dwg. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld [FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 tmin. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in Dwg. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47256 INCH 12.0029 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.14913 INCH 3.787937 MM

* Strength Reduction Factors : Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 29: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 29 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M3. Nozzle Mark : Leg 20" Sch. 30 (located at shell) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.38535 INCH 9.787937 MM

B*. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.32997 INCH 8.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70878 INCH 18.0029 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.75597 INCH 19.20165 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 20", Sch. 40 0.594 INCH 15.0876 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.32997 INCH 8.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.38535 INCH 9.787937 MM

The nominal nozzle pipe wall thk. 0.5 INCH 12.7 MM

The min. nozzle thk. provided = t (1-0.125) 0.4375 INCH 11.1125 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

* Since the opening is access/inspection, UG-45(b) is not applicable [UG-45(b)[

Page 30: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 30 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M3. Nozzle Mark : Leg 20" Sch. 30 (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27]

Area of Reinforcement (witht Reinforcing element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 9.28846 INCH2

5992.541 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 3.07479 INCH2

1983.729 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.25242 INCH2

162.8512 MM2

A1 = The Greater of A11 or A12 3.07479 INCH2

1983.729 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.14043 INCH2

90.60008 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.12211 INCH2

78.7796 MM2

A2 = The Lesser of A21 or A22 0.12211 INCH2

78.7796 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.54203 INCH2

349.695 MM2

A32 = 5 ti ti fr2 0.17319 INCH2

111.7385 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 :

A5 = (Dp - d - 2tn) te fr4 16.6255 INCH2

10726.1 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 + A5 20.3409 INCH2

13123.12 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 31: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 31 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Shee t : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M4. Nozzle Mark : N1 8"NPS, Sch. 80, 300# WNRF (Located at Shell)

No. of nozzles, n 1

Nozzle Neck Thickness Calculation [UG-45, UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 8 INCH 200 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Max. Allowable Stress of Nozzle Material @ Design Temp.(75 oC), Sn 17100 PSIG 1203.84 Kg/CM

2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 4.3125 INCH 109.5375 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.06465 INCH 1.642111 MM

[APPENDIX 1.1]

By adding Corrosion Allowance, t [UG-25] 0.30087 INCH 7.642111 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.33848 INCH 8.597375 MM

Use Nozzle 8" NPS with Selected Neck Sch. 80, 0.5 INCH 12.7 MM

with Thickness 0.5" ( 12.7 MM ). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.4375 INCH 11.1125 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.20128 INCH 5.1125 MM

MWP, New & cold (9.271 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 1808.16 PSIG 127.2943 Kg/CM2G

MWP, Operating & corroded (4.289 MM) P = Sn E t /(Ron - 0.4 t) 813.301 PSIG 57.25639 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 32: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 32 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Date : 18.2.2004

Project : Design & Procurement of ASME Pressure Vessel Client : APRC

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M4. Nozzle Mark : N1 8" 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS 8 INCH 200 DN

Nozzle Pipe Sch. 80

Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.5 INCH 12.7 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.4375 INCH 11.1125 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.20128 INCH 5.1125 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.20128 INCH 5.1125 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 8.625 INCH 219.075 MM

Nozzle Inside Diameter, ID 7.625 INCH 193.675 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.5032 INCH 12.78125 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 8.22244 INCH 208.85 MM

Finished Radius of Circular Opening, Rn 4.11122 INCH 104.425 MM

Page 33: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 33 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M4. Nozzle Mark : N1 8" 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 16.4449 INCH 417.7 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 9.88484 INCH 251.075 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 16.4449 INCH 417.7 MM

Calculating Size of Fillet Welds : [UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.5 INCH 12.7 MM

tmin.3 (shell wall thickness) 0.47244 INCH 12 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.47244 INCH 12 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.33071 INCH 8.4 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in Dwg. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld [FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 t min. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in Dwg. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47256 INCH 12.0029 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.06257 INCH 1.589294 MM

* Strength Reduction Factors : Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 34: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 34 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M4. Nozzle Mark : N1 8" 300# WNRF (located at shell) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.29879 INCH 7.589294 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.32997 INCH 8.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70878 INCH 18.0029 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.51797 INCH 13.15645 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 8", Sch. Std. 0.322 INCH 8.1788 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.32997 INCH 8.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.32997 INCH 8.38125 MM

The nominal nozzle pipe wall thk. 0.5 INCH 12.7 MM

The min. nozzle thk. provided = t (1-0.125) 0.4375 INCH 11.1125 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 35: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 35 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M4. Nozzle Mark : N1 8" 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27]

Area of Reinforcement (with reinforcing Element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 3.91314 INCH2

2524.602 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 1.28475 INCH2

828.8676 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.25242 INCH2

162.8512 MM2

A1 = The Greater of A11 or A12 1.28475 INCH2

828.8676 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.37353 INCH2

240.9873 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.3248 INCH2

209.546 MM2

A2 = The Lesser of A21 or A22 0.3248 INCH2

209.546 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.54203 INCH2

349.695 MM2

A32 = 5 ti ti fr2 0.17319 INCH2

111.7385 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 :

A5 = (Dp - d - 2tn) te fr4 6.77313 INCH2

4369.75 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 + A5 8.90116 INCH2

5742.674 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 36: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 36 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 1 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3

Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) [Appendix 2] [FIG. 2-4, Sketch (7)]

Flange Material, [Attached by Bolts] ASME SA 105 Subjected to internal press.

Design Temperature (shell side) 149oF 65

oC

Min. Design Metal Temperature, MDMT 10oF -12

oC

Bolt-up and Gasket Seating Temperature 86oF 30

oC

Assume corrosion, C [UG-25] 0.19685 INCH 5 MM

Operating Pressure 227.273 PSIG 16 Kg/CM2G

Internal Design Pressure, P (MAWP) 255.682 PSIG 18 Kg/CM2G

Allowable Stress of Bolt Material, SB :

* at design temp.(operating condition), Sb 25000 PSIG 1760 Kg/CM2G

* or at atmospheric temp./bolt-up temp. (gasket seating), Sa 25000 PSIG 1760 Kg/CM2G

Allowable Stress of Flange Material :

* at design temp.(operating condition), SfH 20000 PSIG 1408 Kg/CM2G

* or at atmospheric temp./bolt-up temp. (gasket seating), SfC 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle neck, Vessel or Pipe wall Material :

* at design temp.(operating condition), SnH 17100 PSIG 1203.84 Kg/CM2G

* or at atmospheric temp./bolt-up temp.(gasket seating), SnC 17100 PSIG 1203.84 Kg/CM2G

[Table 1A , SubPart 1 , ASME Sec. II , Part D]

Figure (1)

No. of bolts 12

Nominal bolt dia., dB 0.875

[Appendix 2]

FIG. 2-4, Sketch (7)

Bolt Hole, d 1 INCH 25.4 MM

Flange outside diameter, A 15 INCH 381 MM

Flange inside diameter, B 6.15591 INCH 156.36 MM

Bolt circut diameter (B.C.D.), C = B + 2(g1 + h1+ R) [Appendix 2-3] 13 INCH 330.2 MM

Hup thickness at small end, go = Shell Thickness t 0.43189 INCH 10.97 MM

Hup thickness at back of flange, g1 (assume g1 = 2 go) 0.86378 INCH 21.94 MM

R must not less than 1.5 the bolt hole (see TEMA Table D-5)1.5 INCH 38 MM

Hup length, h (must greater than 1.5 go) [FIG. 2-4, Sketch 6]1.295669291 INCH 32.91 MM

Use max. slope 1:3, h = 3.5 g02.498031496 INCH 63.45 MM

Slope angle, Y = arc Tan [(g1-go)/h]9.809015445 Degree

Fillet radius, r = 0.25 g1 [but not less than 3/16"(4.7625 MM)] [FIG. 2-4, Sketch 6, Note a]0.215944882 INCH 5.485 MM

Use r 0.215944882 INCH 5.485 MM

h1 = r * Tan (45-Y/2) 0.181813441 INCH 5 MM

E = (A-C)/2 (Check D292 ) 1 INCH 25.4 MM

Page 37: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 37 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 2 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Appendix 2] [FIG. 2-4, Sketch (7)]

[Attached by Bolts] Subjected to internal pressure

Nominal pipe size 8"

Pipe Schedule 60

No. of bolts 12

Nominal bolt dia., dB 0.875 INCH 22.225 MM

Bolt diameter at root of thread 0.75689 INCH 19.225 MM

Actual cross-sectional area of each bolt, [TEMA Table D-5] 0.419 INCH2 270.322 MM

2

Total actual cross-sectional area of bolts, Ab 5.028 INCH2 3243.86 MM

2

Flange outside diameter, A 15 INCH 381 MM

Flange inside diameter, B 6.15591 INCH 156.36 MM

Bolt circut diameter (B.C.D.), C 13 INCH 330.2 MM

Gasket Details: - Spiral-Wound metal, asbestos filled, stainless steel 0.125 INCH 3.175 MM

- Outside diameter = (B.C.D - d) - 2*13 10.2362 INCH 260 MM

- Inside diameter = O.D - 2N 8.8189 INCH 224 MM

- Width, N 0.70866 INCH 18 MM

Gasket Dimensions:

Basic gasket seating width, bO = N/2 [Table 2-5.2] 0.35433 INCH 9 MM

Since bo > 1/4 inch (6.35 MM), [Table 2-5.2]

Effective gasket seating width, b = 0.5*SQRT(bO) [Table 2-5.2] 0.29763 INCH 7.55976 MM

Gasket Factor, m [Table 2-5.1] 3

Min. Seating Stress, y [Table 2-5.1] 10000 PSIG 704 Kg/CM2G

Facing Sketch [Table 2-5.1] (1a); Column II

Diameter at location of gasket load reaction, G

When bo is larger than 1/4", G = O.D.of gasket contact face - 2 b 9.64096 INCH 244.88 MM

[Appendix 2-3]

N.B. When b < 1/4", the effective gasket seating width, b = bo [Table 2-5.2]

N.B. When b > 1/4", the effective gasket seating width, b = 0.5*SQRT(bO) [Table 2-5.2]

Page 38: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 38 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 3 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Appendix 2] [FIG. 2-4, Sketch (7)]

[Attached by Bolts] Subjected to internal pressure

1. Bolt loading and size of bolts: [Appendix 2-5(c)]

(a) Total hydrostatic end force, H = 0.785 G2

P [Appendix 2-3] 18655.6 lb 8462.07 Kg

(b) Total joint-contact surface compression load, Hp =2b*3.14GmP 13822.1 lb 6269.63 Kg

[Appendix 2-3]

(c) Min. required bolt load for operating conditions, Wm1 = H + Hp 32477.8 lb 14731.7 Kg

Min. required bolt load for gasket seating, Wm2 = 3.14 b G y 90099.9 lb 40868.7 Kg

Allowable Bolt Stress at atmospheric temp., Sa 25000 PSIG 1760 Kg/CM2G

Allowable Bolt Stress at design temp., Sb 25000 PSIG 1760 Kg/CM2G

[Table 1A , SubPart 1 , ASME Sec. II , Part D]

(d) Total cross-sectional area of bolts at root of thread required for:

- operating conditions, Am1 = Wm1 / Sb 1.29911 INCH2

838.135 MM2

- Gasket seating, Am2 = Wm2 / Sa 3.604 INCH2

2325.16 MM2

[Appendix 2-3]

Total required cross-sectional of bolts, Am = the greater of Am1 & Am2 3.604 INCH2

2325.16 MM2

Since the actual bolt area Ab = 18.58 inch2, for 20 bolt, 1-1/4 in. dia. 5.028 INCH

23243.86 MM

2

bolts, the bolts are adequately enough.

(e) Flang design bolt load, W:

- For operating conditions, Wo = Wm1 [Appendix 2-5(d)] 32477.8 lb 14731.7 Kg

- For gasket seating, Wa = 0.5(Am + Ab) * Sa [Appendix 2-5(d)] 107900 lb 48942.7 Kg

2. Total flange moment for design condition: [Appendix 2-5(c)]

Flange Loads:

Hydrostatic end force on area inside flange, HD = 0.785 B2 P 7605.95 lb 3450 Kg

Gasket load (flange design bolt load - total hydrostatic end force), HG

Gasket seating force HG = Wm1 - H 13822.1 lb 6269.63 Kg

Difference bet. total hydrostatic end force and the hydrostatic end force on area inside of flange, HT

HT = H - HD 11049.7 lb 5012.07 Kg

Lever arms:

hD = R' + 0.5 g1 [Table 2-6] 2.1137 INCH 53.6881 MM

hG = (C - G) / 2 [Table 2-6] 1.67952 INCH 42.6598 MM

hT = (R' + g1 + hG) / 2 [Table 2-6] 2.11256 INCH 53.6589 MM

Where R' = R + h1 1.68181 INCH 42.7181 MM

Page 39: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 39 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 4 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Appendix 2] [FIG. 2-4, Sketch (7)]

[Attached by Bolts] Subjected to internal presure

Flange Moments:

Component of moment due to HD, MD = HD hD [Appendix 2-3 16076.7 lb-in 185.224 Kg-M

Component of moment due to HG, MG = HG hG [Appendix 2-323214.6 lb-in 267.461 Kg-M

Component of moment due to HT, MT = HT hT [Appendix 2-323343.1 lb-in 268.942 Kg-M

Total moment acting upon the flange, Mo: [Appendix 2-6]

- For operating condition MO1 = MD + MG + MT 62634.4 in.-lb 721.627 Kg-M

5219.53 ft-lb

3. Total flange moment for bolt-up condition (Gasket condition):

[Appendix 2-6]

Flange Load: HG = WA = 0.5 (Am + Ab) * Sa 107900 lb 48942.7 Kg

Lever Arm., hG = (C - G) / 2 1.67952 INCH 42.6598 MM

Flange Moment for gasket condition, MO2 = HG hG = WA (C - G) / 2 (5) 181220 lb-in 2087.88 Kg-M

Mo2 * (SfH / SfC ) 181220 lb-in 2087.88 Kg-M

4. MO = The greater of MO1 or MO2 (SfH/SfC) 181220 lb-in 2087.88 Kg-M

15101.7 ft-lb

5. Shape constants for flange:

2.43668

From Appendix 2, FIG. 2-7.1:

1.3584

1.40507

2.31617

2.54524

g1/go 2

ho = SQRT(B go) 1.63054

h/ho 1.53202

From Appendix 2, FIG. 2-7.2: F 0.69863

From Appendix 2, FIG. 2-7.3: V 0.12928

From Appendix 2, FIG. 2-7.6: f 1

d = (U/V) ho go2 (for integral type flanges) [APPENDIX 2-3] 5.9877 INCH

398120.8 MM

3

e = F / ho (for integral type flanges) [APPENDIX 2-3] 0.42847 INCH-1

0.01687 MM-1

KB

A=

TK Log k

k k=

+ −

+ −

2

10

2

1 8 55246 1

104720 19448 1

( . )

( . . )( )

ZK

K=

+

21

2 1

YK

K Log K

K=

+

12

10

21

0 66845 5 716901

. .

UK Log K

K K=

+ −

− −

2

2

1 8 5524610

1

136136 1 1

( . )

. ( )( )

Page 40: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 40 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 5 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Appendix 2] [FIG. 2-4, Sketch (7)]

[Attached by Bolts] Subjected to internal pressure

6. Calculation of flange actual stresses

Assume t 1.42126 INCH 36.1 MM

[Appendix 2-3] 1.66392

Where t = flange thickness

factor e = F/ ho (for integral type flanges) [Appendix 2-3] 0.42847 INCH-1

0.01687 MM-1

e = FL/ ho (for loose type flanges) [Appendix 2-3] NA

F = factor for integral type flanges [Fig. 2-7.2] 0.69863

T = factor involving K [Fig. 2-7.1] 1.3584

d = (U/V) ho go2 [Appendix 2-3] 5.9877 INCH

398120.8 MM

3

For integral type flange, actual stresses (calculated) : [Fig. 2-4, Sketch (6a)]

1. a. Longitudinal hub stress, operating SH = f Mo / L g12

B (6) [Appendix 2-723712.4 PSIG 1669.35 Kg/CM2G

b. Longitudinal hub stress, seating SH = f Mo2 / L g12

B (6) [Appendix 2-723712.4 PSIG 1669.35 Kg/CM2G

2. a. Radial flange stress, operating SR = (1.33 t e +1) Mo / L t2 B (7) [Appendix 15869.9 PSIG 1117.24 Kg/CM

2G

b. Radial flange stress, seating SR = (1.33 t e +1) Mo2 / L t2 B (7) [Appendix 15869.9 PSIG 1117.24 Kg/CM

2G

3. a. Tangential flange stress, operating ST = (Y Mo / t2 B) - Z SR (8) [Appendix 11456.6 PSIG 806.545 Kg/CM

2G

b. Tangential flange stress, seating ST = (Y Mo2 / t2 B) - Z SR (8) [Appendix 11456.6 PSIG 806.545 Kg/CM

2G

4. a. Flange stress, operating 0.5 (SH + SR) [Appendix 2-8(a)(4)] 19791.1 PSIG 1393.3 Kg/CM2G

b. Flange stress, seating 0.5 (SH + SR) [Appendix 2-8(a)(4)] 19791.1 PSIG 1393.3 Kg/CM2G

5. a. Flange stress, operating 0.5 (SH + ST) [Appendix 2-8(a)(4)] 17584.5 PSIG 1237.95 Kg/CM2G

b. Flange stress, seating 0.5 (SH + ST) [Appendix 2-8(a)(4)] 17584.5 PSIG 1237.95 Kg/CM2G

6. a. Bolt stress, operating = Wm1 / Ab 6459.39 PSIG 454.741 Kg/CM2G

b. Bolt stress, seating = Wm2 / Ab 17919.6 PSIG 1261.54 Kg/CM2G

7. a. Shear stress carried by the fillet weld 0 PSIG 0 Kg/CM2G

7. Actual Stresses (Calculated) Compared with Allowable Stresses [APPENDIX 2-8]

7.a. For Operating Condition :

Allowable design stress of flange at operating condiotion, Sf 20000 PSIG 1408 Kg/CM2G

Allowable design stress of nozzle/vessel at operating condition, Sn 17100 PSIG 1203.84 Kg/CM2G

Assume flange thickness (without C.A), toperating 1.42126 INCH 36.1 MM

Allowable stresses Actual stresses

(Calculated )

PSIG Kg/CM2

PSIG Kg/CM2

Longitudinal Hub Stress SH1 = 1.5 Sf [Appendix 2-8(a)(1)(b)] 30000

Longitudinal Hub Stress SH2 = 2 Sn [Appendix 2-8(a)(1)(b)] 34200

The calculated (actual) hub stress SH < SH (min.) allowable 30000 > 23712.4

Radial Flange Stress SR = Sf [Appendix 2-8(a)(2)] 20000 > 15869.9

The calculated (actual) radial stress SR < SR allowable

Factor Lt

T

t

d

e=

++

1 3^

Page 41: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 41 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 6 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Appendix 2] [FIG. 2-4, Sketch (7)]

Subjected to internal pressure

Tangential Flange Stress ST = Sf [Appendix 2-8(a)(3)] 20000 > 11456.6

The calculated (actual) tangential stress ST < ST allowable

0.5(SH + SR) = Sf 20000 > 19791.1

The calculated (actual) stress < Allowable stress

0.5(SH + ST) = Sf 20000 > 17584.5

The calculated (actual) stress < Allowable stress

Bolt stress = Wm1 / Ab 25000 > 6459.39

The calculated (actual) stress < Allowable stress

7.b. For Gasket Seating :

Allowable design stress of flange at gasket seating, Sf 20000 PSIG 1408 Kg/CM2G

Allowable design stress of nozzle/vessel at gasket seating, Sn 17100 PSIG 1203.84 Kg/CM2G

Assume flange thickness (without C.A), tgasket 1.42126 INCH 36.1 MM

Allowable stresses Actual stresses

(Calculated )

PSIG Kg/CM2

PSIG Kg/CM2

Longitudinal Hub Stress SH1 = 1.5 Sf [Appendix 2-8(a)(1)(b)] 30000

Longitudinal Hub Stress SH2 = 2 Sn [Appendix 2-8(a)(1)(b)] 34200

The calculated (actual) hub stress SH < SH (min.) allowable 30000 > 23712.4

Radial Flange Stress SR = Sf [Appendix 2-8(a)(2)] 20000 > 15869.9

The calculated (actual) radial stress SR < SR allowable

Tangential Flange Stress ST = Sf [Appendix 2-8(a)(3)] 20000 > 11456.6

The calculated (actual) tangential stress ST < ST allowable

0.5(SH + SR) = Sf 20000 > 19791.1

The calculated (actual) stress < Allowable stress

0.5(SH + ST) = Sf 20000 > 17584.5

The calculated (actual) stress < Allowable stress

Bolt stress = Wm2 / Ab 25000 > 17919.6

The calculated (actual) stress < Allowable stress

The min. flange thickness, t = Max. (toperating, tgasket) 1.42126 INCH 36.1 MM

Page 42: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 42 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 7 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Appendix 2] [FIG. 2-4, Sketch (7)]

Subjected to internal pressure

Since all actual stresses are less than the allowable stresses, the selection of t is adequate.

If an optimum min. thicknessof flange is desired, calculations must be operated with a smaller

value of t until one of the actual stresses or stress combination is approximately equal to the

allowable stress even though other actual stresses are less than the allowable stress for that

actual stress.

Flange thickness with C.A & RF = t + 2*corrosion all. + raised face 1.81496 INCH 46.1 MM

Use flange thickness for construction 1.85039 INCH 47 MM

BOLT SUMMARY

Factor K = A/B 2.43668

Gasket width, N 0.70866 INCH 18 MM

Total required cross-sectional area of bolts 3.604 INCH2 2325.16 MM

2

Actual bolt cross-sectional area, Ab 5.028 INCH2 3243.86 MM

2

Nominal bolt dia., dB 0.875 INCH 22.225 MM

1. Actual Edge distance, E from drawing = 1/2 (A - C) 1 INCH 25.4 MM Min. Edge distance, E (for bolt size 0.75")

0.8125 INCH 20.6375 MM

Min. Edge distance, E (for bolt size 7/8") [TEMA Table D-5] 0.9375 INCH 23.8125 MM

Min. Edge distance, E (for bolt size 1") 1.0625 INCH 26.9875 MM

Min. Edge distance, E (for bolt size 1-1/8")1.125 INCH 28.575 MM

Min. Edge distance, E (for bolt size 1-1/4") [TEMA Table D-5]1.25 INCH 31.75 MM

2. Actual Bolt spacing, B from drawing 3.36465 INCH 85.462 MM

Min. Bolt spacing, B (for bolt size 0.75") 1.75 INCH 44.45 MM

Min. Bolt spacing, B (for bolt size 7/8") 2.0625 INCH 52.3875 MM

Min. Bolt spacing, B (for bolt size 1") 2.25 INCH 57.15 MM

Min. Bolt spacing, B (for bolt size 1-1/8") 2.5 INCH 63.5 MM

Min. Bolt spacing, B (for bolt size 1-1/4") [TEMA Table D-5] 2.8125 INCH 71.4375 MM

Max. Recommended bolt spacing, Bmax = 2 dB + 6 t / (m + 0.5) [TEMA RCB-4.18645 INCH 106.336 MM

3. Actual Radial distance, Rh from drawing = (C-B)/2-(g1+h1) 2.36142 INCH 59.98 MM

Min. Radial distance, Rh (for bolt size 0.75") 1.125 INCH 28.575 MM

Min. Radial distance, Rh (for bolt size 7/8")1.25 INCH 31.75 MM

Min. Radial distance, Rh (for bolt size 1") 1.375 INCH 34.925 MM

Min. Radial distance, Rh (for bolt size 1-1/8") 1.5 INCH 38.1 MM

Min. Radial distance, Rh (for bolt size 1-1/4") [TEMA Table D-5] 1.75 INCH 44.45 MM

Use construction flange thickness, including corrosion allowance 1.61811 INCH 41.1 MM

[The same thickness for 8" 300# blind flange in accordance with ASME B16.5]

Page 43: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 43 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 8 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Appendix 2] [FIG. 2-4, Sketch (7)]

FLANGE FACTORS Subjected to internal pressure

(a) For Integral Flanges

Factor F per Fig. 2-7.2 is then solved by 0.69863

Factor V per Fig. 2-7.3 is then solved by 0.12928

Factor f per Fig. 2-7.6 is then solved by f = C36 / (1 + A) 1 h/SQRT(BGo 1.532023693

The values used in the above equations are solved using Eqs. (1) through (45) below based on the values g1, g0, h and ho

as defined by 2-3. When g1 = go, F = 0.908920, V = 0.550103, and f = 1; thus Eqs. (1) through (45) need not be solved.

(b) For Loose Hub Flanges

Factor FL per Fig. 2-7.4 is solved by

0.70076

Factor VL per Fig. 2-7.5 is solved by 0.13057

Factor f per Fig. 2-7.6 is set equal to 1. f = 1 1

The values used in the above equations are solved using Eqs. (1) through (5), (7), (9), (10), (12),

(14), (16), (18), (20), (23), and (26) below based on the values of g1, g0, h, and ho as defined by 2-3.

go 0.43189 INCH 10.97 MM

g1 0.86378 INCH 21.94 MM

h 2.49803 INCH 63.45 MM

ho = SQRT(B go), Effective hub length 1.63054 INCH 41.4158 MM

B 6.15591 INCH 156.36 MM

(1) A = (g1/go) - 1 1

(2) C = 43.68(h/ho)4

240.627

(3) C1 = 1/3 + A/12 0.41667

(4) C2 = 5/42 + 17 A / 336 0.16964

(5) C3 = 1/210 + A/360 0.00754

(6) C4 = 11/360 + 59 A/5040 + (1+3 A)/C 0.05889

(7) C5 = 1/90 + 5 A/1008 - (1+ A)3/C -0.01718

FE

C A

C

=+

6

1 4

3

2 73

1[

.]

( )/

VE

CA

=

+

4

1 4 32 731[

.] ( )/

F

CA

CA

CA A

C A

C

L =

+

+ +

+ +

− −

+

1 8 2 1 2 4

1 4 3

1

2 6

1

4

1 1

8 4

1

7 0 1 0 5

1

4 0 7 2

2 7 3

1

.

( )/

V

C CC

CA

L =

− − −

+

1

4 5

3

2

2 731

24 21

18

1 4

3.( )

/

Page 44: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 44 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 9 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Appendix 2] [FIG. 2-4, Sketch (7)]

FLANGE FACTORS (CONT.) Subjected to internal pressure

(8) C6 = 1/120 + 17 A/5040 +1 /C 0.01586

(9) C7 = 215/2772 + 51 A/1232 + (60/7 + 225 A/14 + 75A2/7 + 5 A

3/2)/C 0.27628

(10) C8 = 31/6930 + 128 A/45045 + (6/7 + 15 A/7 + 12A2/7 + 5 A

3/11)/C 0.0288

(11) C9 = 533/30240 + 653 A/73920 + (1/2 + 33 A/14 + 39 A2/28 + 25 A

3/840.04536

(12) C10 = 29/3780 + 3 A/704 - (1/2 + 33 A/14 + 81 A2/28 + 13 A

3/12)/C -0.01646

(13) C11 = 31/6048 + 1763 A/665280 + (1/2 + 6 A/7 + 15 A2/28 + 5 A

3/42)/ 0.01614

(14) C12 = 1/2925 + 71 A/300300 + (8/35 + 18 A /35 + 156 A2/385 + 6 A

3/550.0058

(15) C13 = 761/831600 + 937 A/1663200 + (1/35 + 6 A /35 + 11 A2/70 + 3 A0.00314

(16) C14 = 197/415800 + 103 A/332640 - (1/35 + 6 A /35 + 17 A2/70 + A

3/ -0.00147

(17) C15 = 233/831600 + 97 A/554400 + (1/35 + 3 A /35 + A2/14 + 2 A

3/1050.00131

(18) C16 = C1C7C12 + C2C8C3 + C3C8C2 - (C32C7 + C8

2C1 + C2

2C12) 0.00021

(19) C17 = [C4C7C12 + C2C8C13 + C3C8C9 - (C13C7C3 + C82C4 + C12C2C9)] / 0.0917

(20) C18 = [C5C7C12 + C2C8C14 + C3C8C10 - (C14C7C3 + C82C5 + C12C2C10)] / -0.02242

(21) C19 = [C6C7C12 + C2C8C15 + C3C8C11 - (C15C7C3 + C82C6 + C12C2C11)] / 0.01666

(22) C20 = [C1C9C12 + C4C8C3 + C3C13C2 - (C32C9 + C13C8 C1 + C12C4C2)] / 0.1323

(23) C21 = [C1C10C12 + C5C8C3 + C3C14C2 - (C32C10 + C14C8 C1 + C12C5C2)] / -0.04642

(24) C22 = [C1C11C12 + C6C8C3 + C3C15C2 - (C32C11 + C15C8 C1 + C12C6C2)] / 0.05587

(25) C23 = [C1C7C13 + C2C9C3 + C4C8C2 - (C3C7C4 + C8C9 C1 + C22C13)] / C -0.23441

(26) C24 = [C1C7C14 + C2C10C3 + C5C8C2 - (C3C7C5 + C8C10 C1 + C22C14)] / 0.00573

(27) C25 = [C1C7C15 + C2C11C3 + C6C8C2 - (C3C7C6 + C8C11 C1 + C22C15)] / -0.07383

(28) C26 = - (C/4)1/4

-2.78497

(29) C27 = C20 - C17 - 5/12 + C17C26 -0.63146

(30) C28 = C22 - C19 - 1/12 + C19C26 -0.0905

(31) C29 = - (C/4)1/2

-7.75608

(32) C30 = - (C/4)3/4

-21.6005

(33) C31 = 3 A/2 - C17 C30 3.4808

(34) C32 = 1/2 - C19 C30 0.85979

(35) C33 = 0.5 C26C32 + C28C31C29 - (0.5 C30C28 + C32C27C29) -3.94227

(36) C34 = 1/12 + C18 - C21 - C18C26 0.04488

(37) C35 = - C18 (C/4)3/4

0.48436

(38) C36 = (C28C35C29 - C32C34C29)/C33 -0.16217

(39) C37 = [0.5 C26C35 + C34C31C29 - (0.5 C30C34 + C35C27C29)] / C33 0.95722

(40) E1 = C17C36 + C18 + C19C37 -0.02135

(41) E2 = C20C36 + C21 + C22C37 -0.01439

(42) E3 = C23C36 + C24 + C25C37 -0.02693

(43) E4 = 1/4 + C37/12 + C36/4 - E3/5 - 3E2/2 - E1 0.33755

(44) E5 = E1 (1/2 + A/6) + E2(1/4 + 11A/84) + E3(1/70 + A/105) -0.02036

(45) E6 = E5 - C36(7/120 +A/36 + 3A/C) - 1/40 - A/72 - C37(1/60 +A/120 + 1/C-0.07117

Page 45: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER Page : 45 of 126

According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 Sheet : 10 of 10

Designed by : Eng. Abdel Halim Galala, Design General Manager (Assistant) Rev. : 1

Project : Design & Procurement of Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Sheet : 5 Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. : 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Integral Type Flange N1 8" 300# Thickness (Bolt Connected) (cont.) [Appendix 2] [FIG. 2-4, Sketch (7)]

Subjected to internal pressure

APPENDIX 2-3

When B < 20 g1, it will be optional for the designer to substitute B1 in the

formula stress SH = f * Mo /( L * g12 * B).

20 * g1 17.2756 INCH 438.8 MM

B 6.15591 INCH 156.36 MM

B1 = B + g1 for loose & integral type flanges have f <1 ( the min. f permitted is 7.01969 INCH 178.3 MM

B1 = B + go for integral type flanges when f = > 1 6.5878 INCH 167.33 MM

Page 46: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 46 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M5. Nozzle Mark : N1 6" NPS, Sch. 80 300# WNRF (Located at Blind Flange of N1)

No. of nozzles, n 1

NOZZLE NECK THICKNESS CALCULATION [UG-45 , UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 6 INCH 150 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 3.3125 INCH 84.1375 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.04966 INCH 1.261332 MM

[APPENDIX 1.1]

By adding Corrosion Allowance, t [UG-25] 0.28588 INCH 7.261332 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.32161 INCH 8.168998 MM

Use Nozzle 6" NPS with Selected Neck Sch. 80, 0.432 INCH 10.9728 MM

with Thickness 0.432 ( 10.97 MM ). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.378 INCH 9.6012 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.14178 INCH 3.6012 MM

MWP, New & cold (9.271 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 2044.67 PSIG 143.9444 Kg/CM2G

MWP, Operating & corroded (4.289 MM) P = Sn E t /(Ron - 0.4 t) 744.652 PSIG 52.42352 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 47: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 47 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Date : 18.2.2004

Project : Design & Procurement of ASME Pressure Vessel Client : APRC

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M5. Nozzle Mark : N1 6" NPS 300# WNRF (located at Blind Flange of N1) (cont.)

Nozzle Opening Calculation Without Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS 6 INCH 150 DN

Nozzle Pipe Sch. 80

Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Blind Flkange Material ASME SA 105

Reinforcing Pad Material N.A.

Allowable Stress of Shell Material, 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 0 PSIG 0 Kg/CM2G

Allowable Stress of Blind Flange Material, Sv (nozzle located at blind) 20000 PSIG 1408 Kg/CM2G

Shell (Blind Flange 8" 300#) Thickness 1.61811 INCH 41.1 MM

Shell (Blind Flange 8" 300#) Corrosion Allowance, Cas 0.19685 INCH 5 MM

Shell (Blind Flange 8" 300#)Thickness less Tolerance 1.55811 INCH 39.576 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 1.36126 INCH 34.576 MM

Nozzle Wall Nominal Thickness 0.432 INCH 10.9728 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.378 INCH 9.6012 MM

Nozzle Corrosion Allowance, Can 0.19685 INCH 5 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.18115 INCH 4.6012 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.18115 INCH 4.6012 MM

Reinforced Pad Thickness, te 0 INCH 0 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 60.2696 INCH 1530.848 MM

Shell Inside Radius in Corroded Condition, R 30.1348 INCH 765.424 MM

Nozzle Outside Diameter, OD 6.625 INCH 168.275 MM

Nozzle Inside Diameter, ID 5.761 INCH 146.3294 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0.45287 INCH 11.503 MM

h1 = 2.5 t 3.40315 INCH 86.44 MM

h2 = 2.5 ti 0.45287 INCH 11.503 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 6.2627 INCH 159.0726 MM

Finished Radius of Circular Opening, Rn 3.13135 INCH 79.5363 MM

Page 48: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 48 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M5. Nozzle Mark : N1 6" NPS 300# WNRF (located at Blind Flange of N1) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 12.5254 INCH 318.1452 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 9.34752 INCH 237.427 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 0 INCH 0 MM

Calculating Size of Fillet Welds : [UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld 41 [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.432 INCH 10.9728 MM

tmin.3 [shell (blind) wall thickness] 1.61811 INCH 41.1 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.432 INCH 10.9728 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.3024 INCH 7.68096 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in Dwg. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld (NA) [FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0 INCH 0 MM

tmin.3 [shell (blind) wall thickness] 1.61811 INCH 41.1 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0 INCH 0 MM

1/2 t min. 0 INCH 0 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0 INCH 0 MM

Use Leg with Dimension D in Dwg. No. 7434-33-3A 0 INCH 0 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell (blind) tr 1.3363 INCH 33.942 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.04766 INCH 1.210501 MM

* Strength Reduction Factors : Sp / Sv 0

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 0

See file T-109, Sheet 15 for design calculation

Page 49: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 49 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M5. Nozzle Mark : N1 6" NPS 300# WNRF (located at Blind Flange of N1) (cont.)

MIN. NOZZLE NECK WALL THICKNESS CHECK PER UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.24451 INCH 6.210501 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.2906 INCH 7.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.2906 INCH 7.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 1.53315 INCH 38.942 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.2906 INCH 7.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.2906 INCH 7.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.44185 INCH 11.223 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 6", Sch.Std. 0.28 INCH 7.112 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + C.A. 0.25935 INCH 6.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + C.A. 0.44685 INCH 11.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + C.A. 0.2906 INCH 7.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.2906 INCH 7.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.2906 INCH 7.38125 MM

The nominal nozzle pipe wall thk. 0.432 INCH 10.9728 MM

The min. nozzle thk. provided = t (1-0.125) 0.378 INCH 9.6012 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 50: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 50 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M6. Nozzle Mark : N2 6" NPS, Sch. 80, 300# WNRF (located at shell) (cont.)

No. of nozzles, n 1

NOZZLE NECK THICKNESS CALCULATION [UG-45 , UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 6 INCH 150 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 3.3125 INCH 84.1375 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.04966 INCH 1.261332 MM

[Appendix 1.1]

By adding Corrosion Allowance, t [UG-25] 0.28588 INCH 7.261332 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.32161 INCH 8.168998 MM

Use Nozzle 6" NPS with Selected Neck Sch. 80, 0.432 INCH 10.9728 MM

with Thickness 0.432" ( 10.97 MM ). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.378 INCH 9.6012 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.14178 INCH 3.6012 MM

MWP, New & cold (9.271 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 2044.67 PSIG 143.9444 Kg/CM2G

MWP, Operating & corroded (4.289 MM) P = Sn E t /(Ron - 0.4 t) 744.652 PSIG 52.42352 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 51: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 51 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Date : 18.2.2004

Project : Design & Procurement of ASME Pressure Vessel Client : APRC

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M6. Nozzle Mark : N2 6" NPS, Sch. 80, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS [UG-45 , UGINCH 0 DN

Nozzle Pipe Sch. 80

Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.432 INCH 10.9728 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.378 INCH 9.6012 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.14178 INCH 3.6012 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.14178 INCH 3.6012 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 6.625 INCH 168.275 MM

Nozzle Inside Diameter, ID 5.761 INCH 146.3294 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.35445 INCH 9.003 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 6.34144 INCH 161.0726 MM

Finished Radius of Circular Opening, Rn 3.17072 INCH 80.5363 MM

Page 52: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 52 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M6. Nozzle Mark : N2 6" NPS, Sch. 80, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 12.6829 INCH 322.1452 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 7.88484 INCH 200.275 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 12.6829 INCH 322.1452 MM

CALCULATING SIZE OF FILLET WELDS :

[UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.432 INCH 10.9728 MM

tmin.3 (shell wall thickness) 2.89259 INCH 73.47186 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.432 INCH 10.9728 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.3024 INCH 7.68096 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in DWG. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld (Not Applicable)

[FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 t min. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in DWG. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47256 INCH 12.0029 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.04826 INCH 1.22572 MM

* Strength Reduction Factors :

Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 53: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 53 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M6. Nozzle Mark : N2 6" NPS, Sch. 80, 300# WNRF (located at shell) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.28448 INCH 7.22572 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.32997 INCH 8.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70878 INCH 18.0029 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.48122 INCH 12.223 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 6", Sch. Std. 0.28 INCH 7.112 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.32997 INCH 8.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.32997 INCH 8.38125 MM

The nominal nozzle pipe wall thk. 0.432 INCH 10.9728 MM

The min. nozzle thk. provided = t (1-0.125) 0.378 INCH 9.6012 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 54: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 54 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M6. Nozzle Mark : N2 6" NPS, Sch. 80, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27]

Area of Reinforcement (with reinforcing Element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 3.01611 INCH2

1945.874 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 0.99146 INCH2

639.6485 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.23641 INCH2

152.5214 MM2

A1 = The Greater of A11 or A12 0.99146 INCH2

639.6485 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.25185 INCH2

162.4828 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.1952 INCH2

125.9364 MM2

A2 = The Lesser of A21 or A22 0.1952 INCH2

125.9364 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.3818 INCH2

246.3221 MM2

A32 = 5 ti ti fr2 0.08593 INCH2

55.44094 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 :

A5 = (Dp - d - 2tn) te fr4 5.24698 INCH2

3385.144 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 + A5 6.64833 INCH2

4289.239 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 55: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 55 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (Located at Shell)

No. of nozzles, n 1

Nozzle Neck Thickness Calculation [UG-45, UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 4 INCH 100 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 2.25 INCH 57.15 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.03373 INCH 0.856754 MM

[Appendix 1.1]

By adding Corrosion Allowance, t [UG-25] 0.26995 INCH 6.856754 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.30369 INCH 7.713848 MM

Use Nozzle 4" NPS with Selected Neck Sch. 120, 0.438 INCH 11.1252 MM

with Thickness 0.438" ( 11.13 MM ). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.38325 INCH 9.73455 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.14703 INCH 3.73455 MM

MWP, New & cold (9.271 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 3125.66 PSIG 220.0466 Kg/CM2G

MWP, Operating & corroded (4.289 MM) P = Sn E t /(Ron - 0.4 t) 1147.42 PSIG 80.77811 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 56: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 56 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Date : 18.2.2004

Project : Design & Procurement of ASME Pressure Vessel Client : APRC

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS 4 INCH 100 DN

Nozzle Pipe Sch. 120

Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.438 INCH 11.1252 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.38325 INCH 9.73455 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.14703 INCH 3.73455 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.14703 INCH 3.73455 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 4.5 INCH 114.3 MM

Nozzle Inside Diameter, ID 3.624 INCH 92.0496 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.36757 INCH 9.336375 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 4.20594 INCH 106.8309 MM

Finished Radius of Circular Opening, Rn 2.10297 INCH 53.41545 MM

Page 57: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 57 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 8.41188 INCH 213.6618 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 5.75984 INCH 146.3 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 8.41188 INCH 213.6618 MM

CALCULATING SIZE OF FILLET WELDS :

[UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.438 INCH 11.1252 MM

tmin.3 (shell wall thickness) 5.25208 INCH 133.4029 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.438 INCH 11.1252 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.3066 INCH 7.78764 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in DWG. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld (Not Applicable)

[FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 t min. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in DWG. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47256 INCH 12.0029 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.03201 INCH 0.812955 MM

* Strength Reduction Factors :

Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 58: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 58 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (located at shell) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.26823 INCH 6.812955 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.32997 INCH 8.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70878 INCH 18.0029 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.4436 INCH 11.26733 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 6", Sch. Std. 0.237 INCH 6.0198 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.32997 INCH 8.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.32997 INCH 8.38125 MM

The nominal nozzle pipe wall thk. 0.438 INCH 11.1252 MM

The min. nozzle thk. provided = t (1-0.125) 0.38325 INCH 9.73455 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 59: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 59 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27]

Area of Reinforcement (with reinforcing Element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 2.00769 INCH2

1295.28 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 0.65516 INCH2

422.6846 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.23782 INCH2

153.4329 MM2

A1 = The Greater of A11 or A12 0.65516 INCH2

422.6846 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.30975 INCH2

199.8371 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.24266 INCH2

156.5542 MM2

A2 = The Lesser of A21 or A22 0.24266 INCH2

156.5542 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.39594 INCH2

255.4432 MM2

A32 = 5 ti ti fr2 0.09242 INCH2

59.62284 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 :

A5 = (Dp - d - 2tn) te fr4 3.38824 INCH2

2185.96 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 + A5 4.50076 INCH2

2903.708 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 60: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 60 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (Located at Shell)

No. of nozzles, n 1

[For vessels not subject to rapid flactuations in pressure, do not require reinforcement other than that inherent in the construction under the following conditions

Nozzle Neck Thickness Calculation [UG-45, UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 3 INCH 80 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 1.75 INCH 44.45 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.02623 INCH 0.666364 MM

[Appendix 1.1]

By adding Corrosion Allowance, t [UG-25] 0.26246 INCH 6.666364 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.29526 INCH 7.49966 MM

Use Nozzle 3" NPS with Selected Neck Sch. 160, 0.438 INCH 11.1252 MM

with Thickness 0.438" (11.125 MM). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.38325 INCH 9.73455 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.14703 INCH 3.73455 MM

MWP, New & cold (11.125 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 4104.45 PSIG 288.9533 Kg/CM2G

MWP, Operating & corroded (6.735 MM) P = Sn E t /(Ron - 0.4 t) 1486.65 PSIG 104.6602 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 3050# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 61: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 61 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS 3 INCH 80 DN

Nozzle Pipe Sch. 160

Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.438 INCH 11.1252 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.38325 INCH 9.73455 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.14703 INCH 3.73455 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.14703 INCH 3.73455 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 3.5 INCH 88.9 MM

Nozzle Inside Diameter, ID 2.624 INCH 66.6496 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.36757 INCH 9.336375 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 3.20594 INCH 81.4309 MM

Finished Radius of Circular Opening, Rn 1.60297 INCH 40.71545 MM

Page 62: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 62 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 6.41188 INCH 162.8618 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 4.75984 INCH 120.9 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 6.41188 INCH 162.8618 MM

CALCULATING SIZE OF FILLET WELDS :

[UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.438 INCH 11.1252 MM

tmin.3 (shell wall thickness) 5.25208 INCH 133.4029 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.438 INCH 11.1252 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.3066 INCH 7.78764 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in DWG. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld (Not Applicable)

[FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 t min. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in DWG. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47256 INCH 12.0029 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.0244 INCH 0.619668 MM

* Strength Reduction Factors :

Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 63: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 63 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (located at shell) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.26062 INCH 6.619668 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.32997 INCH 8.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70878 INCH 18.0029 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.42522 INCH 10.8006 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 3", Sch. Std. 0.216 INCH 5.4864 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.32997 INCH 8.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.32997 INCH 8.38125 MM

The nominal nozzle pipe wall thk. 0.438 INCH 11.1252 MM

The min. nozzle thk. provided = t (1-0.125) 0.38325 INCH 9.73455 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 64: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 64 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27]

Area of Reinforcement (with reinforcing Element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 1.53513 INCH2

990.4066 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 0.4978 INCH2

321.1583 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.23782 INCH2

153.4329 MM2

A1 = The Greater of A11 or A12 0.4978 INCH2

321.1583 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.33024 INCH2

213.0579 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.25871 INCH2

166.9116 MM2

A2 = The Lesser of A21 or A22 0.25871 INCH2

166.9116 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.39594 INCH2

255.4432 MM2

A32 = 5 ti ti fr2 0.09242 INCH2

59.62284 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 : (Not applicable)

A5 = (Dp - d - 2tn) te fr4 2.5221 INCH2

1627.16 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 + A5 3.4933 INCH2

2253.739 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 65: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 65 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M9. Nozzle Mark : N3, N4 & N7 2" NPS, Sch.160, 300# WNRF (Located at Shell)

No. of nozzles, n 3

[For vessels not subject to rapid flactuations in pressure, do not require reinforcement other than that inherent in the construction under the following conditions

Nozzle Neck Thickness Calculation [UG-45, UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 2 INCH 50 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 258.324 PSIG 18.186 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 1.1875 INCH 30.1625 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.01783 INCH 0.452918 MM

[Appendix 1.1]

By adding Corrosion Allowance, t [UG-25] 0.25405 INCH 6.452918 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.28581 INCH 7.259533 MM

Use Nozzle 2" NPS with Selected Neck Sch. 160, 0.344 INCH 8.7376 MM

with Thickness 0.344" (8.74 MM). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.301 INCH 7.6454 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.06478 INCH 1.6454 MM

MWP, New & cold (8.74 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 4823.45 PSIG 339.5707 Kg/CM2G

MWP, Operating & corroded (4.645 MM) P = Sn E t /(Ron - 0.4 t) 953.634 PSIG 67.13583 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 66: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 66 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M9. Nozzle Mark : N3, N4 & N7 2" NPS, Sch. 160, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation Without Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS 2 INCH 50 DN

Nozzle Pipe Sch. 160

Design Pressure, P 258.324 PSIG 18.18601 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.344 INCH 8.7376 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.301 INCH 7.6454 MM

Nozzle Corrosion Allowance, Can 0.19685 INCH 5 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.10415 INCH 2.6454 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.10415 INCH 2.6454 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 2.375 INCH 60.325 MM

Nozzle Inside Diameter, ID 1.687 INCH 42.8498 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.26037 INCH 6.6135 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 2.1667 INCH 55.0342 MM

Finished Radius of Circular Opening, Rn 1.08335 INCH 27.5171 MM

Page 67: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 67 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M9. Nozzle Mark : N3, N4 & N7 2" NPS, Sch. 160, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 4.3334 INCH 110.0684 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 3.63484 INCH 92.325 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 4.3334 INCH 110.0684 MM

CALCULATING SIZE OF FILLET WELDS :

[UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.344 INCH 8.7376 MM

tmin.3 (shell wall thickness) 9.48769 INCH 240.9873 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.344 INCH 8.7376 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.2408 INCH 6.11632 MM

tc = lesser of tc1 & tc2 0.2408 INCH 6.11632 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.34054 INCH 8.649783 MM

Use Leg with Dimension E in DWG. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld (Not Applicable)

[FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 t min. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in DWG. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47334 INCH 12.02291 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.01652 INCH 0.419494 MM

* Strength Reduction Factors :

Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 68: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 68 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M9. Nozzle Mark : N3, N4 & N7 2" NPS, Sch. 160, 300# WNRF (located at shell) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.21337 INCH 5.419494 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.2906 INCH 7.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.2906 INCH 7.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70956 INCH 18.02291 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.2906 INCH 7.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.2906 INCH 7.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.3316 INCH 8.42265 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 2", Sch. Std. 0.154 INCH 3.9116 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.25935 INCH 6.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.44685 INCH 11.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.2906 INCH 7.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.2906 INCH 7.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.2906 INCH 7.38125 MM

The nominal nozzle pipe wall thk. 0.344 INCH 8.7376 MM

The min. nozzle thk. provided = t (1-0.125) 0.301 INCH 7.6454 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 69: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 69 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M9. Nozzle Mark : N3, N4 & N7 2" NPS, Sch. 160, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation Without Reinforcing [UG-27]

Area of Reinforcement (with reinforcing Element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 1.03989 INCH2

670.8949 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 0.33453 INCH2

215.8248 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.22515 INCH2

145.2577 MM2

A1 = The Greater of A11 or A12 0.33453 INCH2

215.8248 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.23599 INCH2

152.252 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.16881 INCH2

108.9115 MM2

A2 = The Lesser of A21 or A22 0.16881 INCH2

108.9115 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.28047 INCH2

180.9454 MM2

A32 = 5 ti ti fr2 0.04637 INCH2

29.91705 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 :

A5 = (Dp - d - 2tn) te fr4 1.69625 INCH2

1094.355 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 + A5 2.41429 INCH2

1557.601 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 70: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 70 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch.XXS, 300# WNRF (Located at Shell)

No. of nozzles, n 2

[For vessels not subject to rapid flactuations in pressure, do not require reinforcement other than that inherent in the construction under the following conditions

Nozzle Neck Thickness Calculation [UG-45, UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 1.5 INCH 40 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 0.95 INCH 24.13 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.01424 INCH 0.36174 MM

[Appendix 1.1]

By adding Corrosion Allowance, t [UG-25] 0.25046 INCH 6.36174 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.28177 INCH 7.156958 MM

Use Nozzle 1-1/2" NPS with Selected Neck Sch. XXS, 0.4 INCH 10.16 MM

with Thickness 0.4" (10.16 MM). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.35 INCH 8.89 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.11378 INCH 2.89 MM

MWP, New & cold (10.16 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 7388.89 PSIG 520.1778 Kg/CM2G

MWP, Operating & corroded (5.89 MM) P = Sn E t /(Ron - 0.4 t) 2151.08 PSIG 151.4363 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 71: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 71 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS 1.5 INCH 40 DN

Nozzle Pipe Sch. XXS

Design Pressure, P 257.898 PSIG 18.15602 KG/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 KG/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 KG/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 KG/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.4 INCH 10.16 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.35 INCH 8.89 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.11378 INCH 2.89 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.11378 INCH 2.89 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 1.9 INCH 48.26 MM

Nozzle Inside Diameter, ID 1.1 INCH 27.94 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.28445 INCH 7.225 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 1.67244 INCH 42.48 MM

Finished Radius of Circular Opening, Rn 0.83622 INCH 21.24 MM

Page 72: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 72 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 3.34488 INCH 84.96 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 3.15984 INCH 80.26 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 3.34488 INCH 84.96 MM

CALCULATING SIZE OF FILLET WELDS :

[UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.4 INCH 10.16 MM

tmin.3 (shell wall thickness) 19.7318 INCH 501.1874 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.4 INCH 10.16 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.28 INCH 7.112 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in DWG. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld (Not Applicable)

[FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 t min. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in DWG. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47256 INCH 12.0029 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.01273 INCH 0.323262 MM

* Strength Reduction Factors :

Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 73: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 73 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.24895 INCH 6.323262 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.32997 INCH 8.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70878 INCH 18.0029 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.3631 INCH 9.222625 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 1-1/2", Sch. Std0.145 INCH 3.683 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.32997 INCH 8.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.32997 INCH 8.38125 MM

The nominal nozzle pipe wall thk. 0.4 INCH 10.16 MM

The min. nozzle thk. provided = t (1-0.125) 0.35 INCH 8.89 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 74: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 74 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27]

Area of Reinforcement (with reinforcing Element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 0.80591 INCH2

519.9429 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 0.25799 INCH2

166.4467 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.22887 INCH2

147.6604 MM2

A1 = The Greater of A11 or A12 0.25799 INCH2

166.4467 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.27213 INCH2

175.5649 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.19882 INCH2

128.2721 MM2

A2 = The Lesser of A21 or A22 0.19882 INCH2

128.2721 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.3064 INCH2

197.676 MM2

A32 = 5 ti ti fr2 0.05534 INCH2

35.70523 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 :

A5 = (Dp - d - 2tn) te fr4 1.25147 INCH2

807.4 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 + A5 1.92298 INCH2

1240.629 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 75: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 75 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M11. Nozzle Mark : N16 1" NPS, Sch.XXS, 300# WNRF (Piping branch from N4)

No. of nozzles, n 1

[For vessels not subject to rapid flactuations in pressure, do not require reinforcement other than that inherent in the construction under the following conditions

Nozzle Neck Thickness Calculation [UG-45, UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 1 INCH 25 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 258.324 PSIG 18.186 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 0.6575 INCH 16.7005 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.00987 INCH 0.250774 MM

[Appendix 1.1]

By adding Corrosion Allowance, t [UG-25] 0.24609 INCH 6.250774 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.27686 INCH 7.03212 MM

Use Nozzle 1" NPS with Selected Neck Sch. XXS, 0.358 INCH 9.0932 MM

with Thickness 0.358" (9.093 MM). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.31325 INCH 7.95655 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.07703 INCH 1.95655 MM

MWP, New & cold (9.093 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 10065 PSIG 708.5736 Kg/CM2G

MWP, Operating & corroded (4.956 MM) P = Sn E t /(Ron - 0.4 t) 2101.85 PSIG 147.9703 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 76: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 76 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M11. Nozzle Mark : N16 1" NPS, Sch. XXS, 300# WNRF (Piping branch from N4) (cont.)

Nozzle Opening Calculation Without Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS 1 INCH 25 DN

Nozzle Pipe Sch. XXS

Design Pressure, P 258.324 PSIG 18.18601 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.358 INCH 9.0932 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.31325 INCH 7.95655 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.07703 INCH 1.95655 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.07703 INCH 1.95655 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 1.315 INCH 33.401 MM

Nozzle Inside Diameter, ID 0.599 INCH 15.2146 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.19257 INCH 4.891375 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 1.16094 INCH 29.4879 MM

Finished Radius of Circular Opening, Rn 0.58047 INCH 14.74395 MM

Page 77: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 77 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M11. Nozzle Mark : N16 1" NPS, Sch. XXS, 300# WNRF (Piping branch from N4) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 2.32188 INCH 58.9758 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 2.57484 INCH 65.401 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 2.57484 INCH 65.401 MM

CALCULATING SIZE OF FILLET WELDS :

[UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.358 INCH 9.0932 MM

tmin.3 (shell wall thickness) 6.39696 INCH 162.4828 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.358 INCH 9.0932 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.2506 INCH 6.36524 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in DWG. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld (Not Applicable)

[FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 t min. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in DWG. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47334 INCH 12.02291 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.00885 INCH 0.224769 MM

* Strength Reduction Factors :

Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 78: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 78 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 4

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M11. Nozzle Mark : N16 1" NPS, Sch. XXS, 300# WNRF (Piping branch from N4) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.24507 INCH 6.224769 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.32997 INCH 8.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70956 INCH 18.02291 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.3526 INCH 8.955925 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 1", Sch. Std. 0.133 INCH 3.3782 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.32997 INCH 8.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.32997 INCH 8.38125 MM

The nominal nozzle pipe wall thk. 0.358 INCH 9.0932 MM

The min. nozzle thk. provided = t (1-0.125) 0.31325 INCH 7.95655 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 79: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 79 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 6

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M12. Nozzle Mark : N5A, N5B & N12 1-1/2" NPS, Sch.XXS, 300# WNRF (Located at Head, F = 0.5)

No. of nozzles, n 3

[For vessels not subject to rapid flactuations in pressure, do not require reinforcement other than that inherent in the construction under the following conditions

Nozzle Neck Thickness Calculation [UG-45, UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 1.5 INCH 40 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 0.95 INCH 24.13 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.01424 INCH 0.36174 MM

[Appendix 1.1]

By adding Corrosion Allowance, t [UG-25] 0.25046 INCH 6.36174 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.28177 INCH 7.156958 MM

Use Nozzle 1-1/2" NPS with Selected Neck Sch. XXS, 0.4 INCH 10.16 MM

with Thickness 0.4" (10.16 MM). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.35 INCH 8.89 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.11378 INCH 2.89 MM

MWP, New & cold (10.16 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 7388.89 PSIG 520.1778 Kg/CM2G

MWP, Operating & corroded (5.89 MM) P = Sn E t /(Ron - 0.4 t) 2151.08 PSIG 151.4363 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 80: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 80 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 6

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M12. Nozzle Mark : N5A, N5B & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS 1.5 INCH 40 DN

Nozzle Pipe Sch. XXS

Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MM

Shell Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MM

Shell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.4 INCH 10.16 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.35 INCH 8.89 MM

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.11378 INCH 2.89 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.11378 INCH 2.89 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1 0.5

E1 [Nozzle in solid plate] 1

Shell Outside Diameter, OD 62.9921 INCH 1600 MM

Shell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MM

Shell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 1.9 INCH 48.26 MM

Nozzle Inside Diameter, ID 1.1 INCH 27.94 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 1.5748 INCH 40 MM

h2 = 2.5 ti 0.28445 INCH 7.225 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d' = OD - 2*tn 1.67244 INCH 42.48 MM

Radius of Circular Opening, Rn 0.83622 INCH 21.24 MM

Page 81: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 81 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 6

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M12. Nozzle Mark : N5A, N5B & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 7.26139 INCH 184.4394 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 3.15984 INCH 80.26 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 7.26139 INCH 184.4394 MM

CALCULATING SIZE OF FILLET WELDS :

[UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.4 INCH 10.16 MM

tmin.3 (shell wall thickness) 6.39696 INCH 162.4828 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.4 INCH 10.16 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.28 INCH 7.112 MM

tc = lesser of tc1 & tc2 0.25 INCH 6.35 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.35355 INCH 8.980256 MM

Use Leg with Dimension E in DWG. No. 7434-33-3A 0.35433 INCH 9 MM

* For Outer Reinforcing Pad Weld (Not Applicable)

[FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.86614 INCH 22 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 t min. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in DWG. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell tr = PR / (SE - 0.6 P) 0.47256 INCH 12.0029 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.01273 INCH 0.323262 MM

* Strength Reduction Factors :

Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 82: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 82 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 6

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M12. Nozzle Mark : N5A, N5B & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

[UG-45 , UG-27(c) & APPENDIX 1-1]

* Calculation of the Opening Finished Cord Length, d at the Midsurface of Shell Thickness :

Shell thickness less corrosion allowance, t 0.62992 INCH 16 MM

Min. required shell thickness, tr 0.47256 INCH 12.0029 MM

Shell inside radius in corroded condition, R 30.8661 INCH 784 MM

Distance between center of nozzle and vessel centerline, L 27.5591 INCH 700 MM

Inside radius of nozzle circular opening, Rn 0.83622 INCH 21.24 MM

Nozzle wall thickness less corrosion allowance & 12.5%, tn 0.11378 INCH 2.89 MM

Shell mean radius, Rm = R + tr/2 31.1024 INCH 790.0015 MM

O1 = ASIN((L-Rn)/Rm) 59.2256 DEG.

O2 = ASIN((L+Rn)/Rm)) 65.9177 DEG.

O = O2 - O1 6.69214 DEG.

Finished cord length, d = 2 Rm *SQRT(1 - COS^2(O/2)) 3.6307 INCH 92.21968 MM

N.B. The opening finished cord length , d , of nozzle N8A is

the same as for nozzle N8B due to similarity of both

nozzles around vessel centerline ( L= 700 MM ).

Page 83: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 83 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 6

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M12. Nozzle Mark : N5A, N5B & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.24895 INCH 6.323262 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.32997 INCH 8.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.70878 INCH 18.0029 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.32997 INCH 8.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.3631 INCH 9.222625 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 1-1/2", Sch. Std0.145 INCH 3.683 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.29872 INCH 7.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.48622 INCH 12.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.32997 INCH 8.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.32997 INCH 8.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.32997 INCH 8.38125 MM

The nominal nozzle pipe wall thk. 0.4 INCH 10.16 MM

The min. nozzle thk. provided = t (1-0.125) 0.35 INCH 8.89 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 84: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 84 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 6 of 6

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M12. Nozzle Mark : N5A, N5B & N17 1-1/2" NPS, Sch. XXS, 300# WNRF (located at shell) (cont.)

Nozzle Opening Calculation With Reinforcing [UG-27]

Area of Reinforcement (with reinforcing Element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 1.7313 INCH2

1116.963 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 0.56616 INCH2

365.2611 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.22887 INCH2

147.6604 MM2

A1 = The Greater of A11 or A12 0.56616 INCH2

365.2611 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.27213 INCH2

175.5649 MM2

A22 = 2 (tn - trn)(2.5tn+te) fr2 0.19882 INCH2

128.2721 MM2

A2 = The Lesser of A21 or A22 0.19882 INCH2

128.2721 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.3064 INCH2

197.676 MM2

A32 = 5 ti ti fr2 0.05534 INCH2

35.70523 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.10735 INCH

269.255 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.10735 INCH

269.255 MM

2

Area Available in Reinforcing Pad, A5 :

A5 = (Dp - d - 2tn) te fr4 2.9476 INCH2

1901.673 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 + A5 3.92727 INCH2

2533.716 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 85: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 85 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M13. Nozzle Mark : N10A & N10B 1/2" NPS, Sch.XXS, 300# WNRF (Located at Leg)

No. of nozzles, n 2

[For vessels not subject to rapid flactuations in pressure, do not require reinforcement other than that inherent in the construction under the following conditions

Nozzle Neck Thickness Calculation [UG-45, UG-27 & APPENDIX 1-1]

Nozzle Size, NPS 0.5 INCH 15 DN

Nozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2G

Design Temperature 149oF 65

oC

For nominated Design Pressure & Temperature, Flange Rating 300#

[ANSI/ASME B16.5-1996]

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Max. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM

2G

[Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 0.42 INCH 10.668 MM

Joint Efficiency of Nozzle, En (Seamless Pipe) 1

Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM

Nozzle Thickness Calculation :

Longitudinal Stress, t = PRon /(Sn*En + 0.4 P) 0.0063 INCH 0.159927 MM

[Appendix 1.1]

By adding Corrosion Allowance, t [UG-25] 0.24252 INCH 6.159927 MM

By adding Pipe Tolerance 12.5% to the Thickness of Nozzle, t 0.27283 INCH 6.929918 MM

Use Nozzle 1/2" NPS with Selected Neck Sch. XXS, 0.294 INCH 7.4676 MM

with Thickness 0.294" (7.47 MM). [Table 2 of ANSI B 36.10M-1985-(R-1994)]

Nozzle Neck Maximum Working Pressure, MWP (New & Operating)

Nozzle wall thickness less tolerance 12.5% 0.25725 INCH 6.53415 MM

Nozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.02103 INCH 0.53415 MM

MWP, New & cold (10.16 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 13872.5 PSIG 976.6252 Kg/CM2G

MWP, Operating & corroded (5.89 MM) P = Sn E t /(Ron - 0.4 t) 873.701 PSIG 61.50854 Kg/CM2G

Nozzle Flange Maximum Working Pressure, MWP (New & Operating)

MWP, New & cold, 300# @ 100 oF [ASME B.165, Table 2] 740 PSIG 52.096 Kg/CM

2G

MWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM

2G

Page 86: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 86 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M13. Nozzle Mark : N10A & N10B, 1/2" NPS, Sch. XXS, 300# WNRF (located at leg) (cont.)

Nozzle Opening Calculation Without Reinforcing [UG-27(c) & APPENDIX 1-1]

Nozzle Pipe Size, NPS 0.5 INCH 15 DN

Nozzle Pipe Sch. XXS

Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2G

Design Temparture 149oF 65

oC

Shell Material ASME SA516 Grade 70

Nozzle Material ASME SA 106 Grade B

Reinforcing Pad Material ASME SA516 Grade 70

Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2G

Allowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2G

Allowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell (leg) Thickness 0.5 INCH 12.7 MM

Shell (leg) Corrosion Allowance, Cas 0.23622 INCH 6 MM

Shell (leg) Thickness less Pipe Tolerance 12.5% 0.4375 INCH 11.1125 MM

Shell (leg) Thickness less Corrosion Allowance & 12.5%, t 0.20128 INCH 5.1125 MM

Nozzle Wall Nominal Thickness 0.294 INCH 7.4676 MM

Nozzle Wall Thickness less Pipe Tolerance 12.5% 0.25725 INCH 6.53415 MM

Nozzle Corrosion Allowance, Can 0.15748 INCH 4 MM

Nozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.09977 INCH 2.53415 MM

Nozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.09977 INCH 2.53415 MM

Reinforced Pad Thickness, te 0.86614 INCH 22 MM

Joint Efficiency of Shell, E 1

Joint Efficiency of Nozzle, En 1

Correction Factor, F [UG-37(a)] 1

E1 [Nozzle in solid plate] 1

Shell (leg) Outside Diameter, OD 20 INCH 508 MM

Shell (leg) Inside Diameter in Corroded Condition, 2R = OD - 2 t 19.5974 INCH 497.775 MM

Shell (leg) Inside Radius in Corroded Condition, R 9.79872 INCH 248.8875 MM

Nozzle Outside Diameter, OD 0.84 INCH 21.336 MM

Nozzle Inside Diameter, ID 0.252 INCH 6.4008 MM

Nozzle Projection beyond Inner Vessel Wall, h = min. (h1,h2) 0 INCH 0 MM

h1 = 2.5 t 0.5032 INCH 12.78125 MM

h2 = 2.5 ti 0.24942 INCH 6.335375 MM

Nozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 0.64046 INCH 16.2677 MM

Finished Radius of Circular Opening, Rn 0.32023 INCH 8.13385 MM

Page 87: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 87 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M13. Nozzle Mark : N10A & N10B, 1/2" NPS, Sch. XXS, 300# WNRF (located at leg) (cont.)

Nozzle Opening Calculation With Reinforcing (cont.) [UG-27(c) & APPENDIX 1-1]

* Outside Diameter of Reinforced Pad (if used) [UG-40(b)&FIG.UG-37.1]

Dp1 = 2 d 1.28092 INCH 32.5354 MM

Dp2 = 2 (Rn + nozzle wall thk. , tn + vessel wall thk. , t ) 1.24256 INCH 31.561 MM

OD of Reinf. Pad, Dp = the greater of Dp1 or Dp2 1.28092 INCH 32.5354 MM

CALCULATING SIZE OF FILLET WELDS :

[UW-16(c)(2)&FIG.UW-16.1]

* For Outward Nozzle Weld [UW-16(c)(2)&FIG.UW-16.1SKETCH (c)]

Calculation of tmin. :

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 (nozzle wall nominal thickness) 0.294 INCH 7.4676 MM

tmin.3 (shell wall thickness) 6.39696 INCH 162.4828 MM

tmin. = lesser of tmin.1, tmin. & tmin.3 0.294 INCH 7.4676 MM

Calculation of tc : tc1 = 0.25 inch 0.25 INCH 6.35 MM

tc2 = 0.7 t min. 0.2058 INCH 5.22732 MM

tc = lesser of tc1 & tc2 0.2058 INCH 5.22732 MM

By Considering Equal Legs Fillet Welds :

Leg of Outward Nozzle Weld = SQRT2 * tc 0.29105 INCH 7.392547 MM

Use Leg with Dimension E in DWG. No. 7434-33-3A 0.31496 INCH 8 MM

* For Outer Reinforcing Pad Weld (Not Applicable)

[FIG.UW-16 SKETCH (c)]

tmin.1 = 0.75 inch 0.75 INCH 19.05 MM

tmin.2 ( te = thk. of reinforcing element) 0.86614 INCH 22 MM

tmin.3 ( shell wall thickness) 0.5 INCH 12.7 MM

tmin. = lesser of tmin.1, tmin. 2 & tmin.3 0.75 INCH 19.05 MM

1/2 t min. 0.375 INCH 9.525 MM

By Considering Equal Legs Fillet Welds :

Leg of Outer Pad Weld = SQRT(2)*(tmin./2) 0.53033 INCH 13.5 MM

Use Leg with Dimension D in DWG. No. 7434-33-3A 0.55118 INCH 14 MM

* Wall Thickness Required : [UG-27(c)(1)]

Shell (leg) tr = PR / (SE - 0.6 P) 0.12734 INCH 3.234404 MM

Nozzle trn = PRn /(SnEn - 0.6 P) 0.00487 INCH 0.123793 MM

* Strength Reduction Factors :

Sp / Sv 1

fr1 = Sn / Sv 0.855

fr2 = Sn / Sv 0.855

fr3 = lesser of Sn/Sv or Sp/Sv 0.855

fr4 = Sp / Sv 1

Page 88: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 88 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M13. Nozzle Mark : N10A & N10B, 1/2" NPS, Sch. XXS, 300# WNRF (located at leg) (cont.)

Min. Nozzle Neck Wall Thickness Check Per UG-45

A. Wall Thickness per UG-45(a) : trna = trn + Can 0.16235 INCH 4.123793 MM

B. Wall Thickness per UG-45(b) : trnb = Min. (trnb1, trnb2, trnb3, trnb4) 0.25123 INCH 6.38125 MM

Wall Thickness per UG-45(b)(1), trnb1 = Min. (trnb11, trnb12) 0.25123 INCH 6.38125 MM

trnb11 = tr + Cas (tr for shell or head at E=1) 0.36356 INCH 9.234404 MM

trnb12 = Min Wall Thickness per UG-16(b), see below 0.25123 INCH 6.38125 MM

Wall Thickness per UG-45(b)(2), trnb2 (apply to external pressure only), NA INCH #VALUE! MM

Wall Thickness per UG-45(b)(3), trnb3 (apply to internal & external pressure)

= Max. (trnb1, trnb2) 0.25123 INCH 6.38125 MM

Wall Thickness per UG-45(b)(4), trnb4

= Min. thickness of std. wall pipe (1-0.125)+ Can 0.25286 INCH 6.422525 MM

(Under tolerance12.5% in accordance with ASME B36.10M)

Nominal thickness of std. pipe wall thickness, NPS 1/2", Sch. Std0.109 INCH 2.7686 MM

Wall Thickness per UG-16(b), trnb12

I - Min. Wall Thickness 1/16" + Cas 0.21998 INCH 5.5875 MM

II - Min. Wall Thickness of Unfired Steam Boilers = 1/4" + Cas 0.40748 INCH 10.35 MM

III - Min. Wall Thickness of Shell/Head in Compressed Air

Service, Steam Service, and Water Service = 3/32" + Cas 0.25123 INCH 6.38125 MM

Selected Vessel Service in our case is : Case III (compressed air)

So, the Min. Wall Thickness per UG-16(b), trnb12 0.25123 INCH 6.38125 MM

The min. nozzle wall thk. = Max. thk. determined by UG-45(a), or by UG-45(b) 0.25123 INCH 6.38125 MM

The nominal nozzle pipe wall thk. 0.294 INCH 7.4676 MM

The min. nozzle thk. provided = t (1-0.125) 0.25725 INCH 6.53415 MM

So, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't require

a calculationon shear stresses caused by UG-22(c).

Page 89: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 89 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 5

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

M13. Nozzle Mark : N10A & N10B, 1/2" NPS, Sch. XXS, 300# WNRF (located at leg) (cont.)

Nozzle Opening Calculation Without Reinforcing [UG-27]

Area of Reinforcement (without reinforcing Element) :

Required Area, A = d tr F + 2 tn tr F(1-fr1) 0.08524 INCH2

54.99329 MM2

Area Available in Shell, A1:

A11 = d (E1 t - F tr) - 2tn (E1 t - F tr)(1-fr1) 0.04522 INCH2

29.17209 MM2

A12 = 2 (t + tn)(E1 t - F tr) - 2tn (E1 t - F tr)(1-f r1) 0.04238 INCH2

27.34207 MM2

A1 = The Greater of A11 or A12 0.04522 INCH2

29.17209 MM2

Area Available in Nozzle Projecting Outward, A2 :

A21 = 5 (tn - trn) fr2 t 0.08166 INCH2

52.68061 MM2

A22 = 5 (tn - trn) fr2 tn 0.04047 INCH2

26.11258 MM2

A2 = The Lesser of A21 or A22 0.04047 INCH2

26.11258 MM2

Area Available in Inward Nozzle, A3 : (Not applicable)

A31 = 5 t ti fr2 0.08585 INCH2

55.38622 MM2

A32 = 5 ti ti fr2 0.04255 INCH2

27.45369 MM2

A33 = 2 h ti fr2 0 INCH2

0 MM2

A3 = The Greater of A31, A32 or A33 0 INCH2

0 MM2

Area Available in Outward Nozzle Weld, A41:

A41 = (LEG)2 fr3 0.08482 INCH

254.72 MM

2

Area Available in Outer Reinforcing Pad Weld, A42:

A42 = (LEG)2 fr4 0.3038 INCH

2196 MM

2

Area Available in Inward Nozzle Weld, A43 :

A43 = (LEG)2 fr2 0.08482 INCH

254.72 MM

2

Area Available in Reinforcing Pad, A5 : (Not applicable)

A5 = (Dp - d - 2tn) te fr4 0.3819 INCH2

246.3868 MM2

Total Area Available, AT :

AT = A1 + A2 + A41 + A42 + A43 0.25532 INCH2

164.7247 MM2

AT is greater than A, therefore opening is adequately reinforced.

NOTE. No need for Strength Path Calculations.

Page 90: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 90 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 7

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

N. Design of Saddle Supports

The design of saddle supports for horizontal cylindrical pressure

vessel shall include the required plate thicknesses calculations

for the following saddle components :

I. Top flange (reinforcement/wear) thickness , tf.

II. Web (saddle plate) thickness , tw.

III. Stiffener (rip plates) thickness , ts.

IV. Base plate thickness , tb.

The Design Data is as Follows :

Vessel type & position Cylindrical & Horizontal

Design pressure , P 257.898 PSI 18.156 Kg/CM2G

Design temperature 149oF 65

oC

Radiography (only for pressure parts, BW) 85%

Vessel inside dia., D 61.2598 INCH 1556 MM

Vessel outside dia., Do 62.9921 INCH 1600 MM

Vessel outside radius, Ro 31.4961 INCH 800 MM

Vessel wall thickness, t 0.86614 INCH 22 MM

Corrosion allowance, C 0.23622 INCH 6 MM

Material : shell ASME SA516 Grade 70

heads ASME SA516 Grade 70

saddles ASME SA283 Grade C

Min. tensile stress : shell 60000 PSIG 4224 Kg/CM2G

heads 60000 PSIG 4224 Kg/CM2G

saddles 55000 PSIG 3872 Kg/CM2G

Min. yield stress, sy : shell & heads 32000 PSIG 2252.8 Kg/CM2G

saddles 30000 PSIG 2112 Kg/CM2G

Allowable tensile stress: shell 20000 PSIG 1408 Kg/CM2G

heads 20000 PSIG 1408 Kg/CM2G

saddles 15700 PSIG 1105.28 Kg/CM2G

Vessel weight , empty , W 16377.3 lb 7428 Kg

liquid (water), Wc 22383.1 lb 10152 Kg

Vessel total weight , Wt 38760.4 lb 17580 Kg

Number of saddles used 2

Load per saddle , Q 19380.2 lb 8790 Kg

Saddle angle of contact , B 120 DEG

Saddle width, b 11.811 INCH 300 MM

Ring stiffeners adjacent to saddle N.A.

Page 91: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 91 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 7

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

N. Design of Saddle Supports (cont.)

Vessel Layout :

Figure (3)

Shell Inside Diameter, D 61.2598 INCH 1556 MM

Shell wall thickness, ts 0.86614 INCH 22 MM

Head wall thickness (min.), th 0.7874 INCH 20 MM

Distance from tangent line - to - saddle support , A 22.0472 INCH 560 MM

Head depth - to - tangent line , Ho = ID / 4 + th 16.1024 INCH 409 MM

Shell length from Tangent - to - tangent (T/T) , L 189.764 INCH 4820 MM

Distance from tangent line - to - welding line (Skirt), l 1.5748 INCH 40 MM

Shell length from Welding - to - welding (W/W) , L' 186.614 INCH 4740 MM

Saddle - to - saddle distance (S/S) , L" = L - 2 A 145.669 INCH 3700 MM

Total Ellipsoidal Head depth (external depth), H = Ho + l 17.6772 INCH 449 MM

Total vessel overall length = L + 2 Ho 221.969 INCH 5638 MM

Vessel weight , empty , W 16377.3 lb 7428 Kg

liquid (water), Wc 22383.1 lb 10152 Kg

Vessel total weight (water), Wt 38760.4 lb 17580 Kg

Figure (4)

Page 92: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 92 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 7

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

N. Design of Saddle Supports (cont.)

(a) Determining the number of stiffeners (rip plates) and its thickness, ts

*An approximate approach for determining the number

of stiffeners, N is :

N = m" / 24 + 1 (empirical formula)

where m" = total length of base plate , in.

= 0.8 x vessel O.D. , in. 50.3937 INCH 1280 MM

N 3.09974

Use 4 stiffeners, n 4

* Total length of base plate m , can also be calculated

in accordance with saddle angle of contact, B :

m' = 2 (Ro + tf) sin B 55.5075 INCH 1409.889 MM

Use m 62.9921 INCH 1600 MM

* The stiffener (rip plate) thickness (ts) is 3/8" (9.5 mm)

min. for vessels up to 6 ft (1830 mm) in diameter ,

Therefore use 4 stiffeners with thickness , ts 0.55118 INCH 14 MM

Baseplate-Stiffeners' fillet weld clearance, cl = Min. (ts , tb) 0.59055 INCH 15 MM

The stiffeners are equaly spaced by, Ss = [m-2(0.5ts+cl)]/(n-1) 20.4199 INCH 518.6667 MM

Use equally spaced stiffeners, Ss 20.4199 INCH 518.6667 MM

Use b 11.811 INCH 300 MM

Use rip plate width, Rw = 1/2[b - (2*cl + tw)] 5.03937 INCH 128 MM

Use distance, c 37.8346 INCH 961 MM

Page 93: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 93 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 7

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

N. Design of Saddle Supports (cont.)

(b) Calculation of top flange (reinforcement) thickness, tf :

Flange thickness , tf = SQRT(6*Mb / Sb)

Where ,

Mb = Bending Moment, lb-in.

Sb = Allowable design bending stress

= 0.66 Sy ( per AISC Spesifications) 19800 PSIG 1393.92 Kg/CM2G

Pll = Linear load per unit lengh , lb/in.

Q = load per one saddle , lb 19380.2 lb 8790 Kg

Ro = Vessel outside radius , in. 31.4961 INCH 800 MM

0 = Angle of contact , deg. 120 Degree

B = 180 - 0 /2 120 Degree

. . PI 500.925 lb/in 8945.495 Kg/M

. . Bending moment , Mb 739.555 lb-in 8.520584 Kg-M

Flange thickness , tf = SQRT(6*Mb / Sb) 0.4734 INCH 12.02436 MM

Use top flange plate thickness , tf 0.55118 INCH 14 MM

Use top flange plate width, B = 2* Rip width + 2*(55) + tw 14.9606 INCH 380 MM

= ---- [ --------------------------] .

Q 1 + cos B

Ro II - B + cos B * sin B

PII

= ---- x ---- x ---- = P ----- b 2 4 8

M P b b b

b II

II

Page 94: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 94 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 7

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

N. Design of Saddle Supports (cont.)

(c) Calculation of web (saddle) plate thickness , tw :

Use 0.5" thick plate min. ( i.e. assume tw = 0.5" ) 0.5 INCH 13 MM

Calculate the max. allowable height h of a 1" wide

strip column 0.5" thick under PII .

Area , a = 1 x 0.5 IN.2

Min. radius of gyration , k = 0.289 tw

From

We get h = tw * SQRT [(1500/PII)(18000 tw - PII )] 79.7655 INCH 2026.044 MM

= 2127 MM > distance c (961 MM)

Where c 37.8346 INCH 961 MM

Use web ( saddle ) with thickness , tw 0.55118 INCH 14 MM

(d) Calculation of base plate thickness , tb :

tb = SQRT [(Q * b) / 26400 * m] 0.371 INCH 9.423482 MM

Use base plate with thickness , tb 0.98425 INCH 25 MM

* Check for the bearing pressure :

Bearing pressure = Q / (b*m) 26.0486 PSIG 1.833821 Kg/CM2G

< 750 PSI allowable OK

= ---------------------------] 18000

1+ -------- [ ---- ]

P-----a

1 h

18000 k

2

Page 95: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 95 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 6 of 7

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

N. Design of Saddle Supports (cont.)

D. Stresses in Shell Due to Temperature Expansion :

Expansion dl = a * l * dT

Where dl =

a = Thermal expansion coefficent 7.1E-06

l = Tangent - to - tangent distance (T/T) , in.

dT = Difference in temp. = 167-70 79oF 26.11111

oC

(consider ampient temp. 70 oF ) 70

oF 21.11111

oC

Expansion , dl 0.10644 INCH 2.703538 MM

Therefore use slots for anchor bolts located in the sliding

saddle with distance c/c 65 MM , and provide lubrite

plates underneath the sliding saddle .

Friction coefficient, fo 0.1

Shear force at the saddle base, fo * Q 1938.02 lb 879 Kg

Centroid of saddle arc, xo = ro * sin 60 / rad. 60 26.047 INCH 661.5947 MM

Use Saddle height under vessel 3.28084 ft. 1000 MM

Distance, c 37.8346 INCH 961 MM

Elevation , Z =Ro + tf + c + tb 70.8661 INCH 1800 MM

Support Saddle Detail :

Figure (5)

m 62.9921 INCH 1600 MM

b 11.811 INCH 300 MM

B 14.9606 INCH 380 MM

Width of outside stiffeners, Sw = 2 Rw + tw 10.6299 INCH 270 MM

Page 96: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 96 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 7 of 7

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

N. Design of Saddle Supports (cont.)

Bending moment = fo * Q ( Z - xo ) 86860.3 lb-in. 1000.738 Kg-M

This bending moment is counteracted by the weight of

the vessel , Q * b/2 .

i.e fo * Q ( Z - xo ) = Q * b/2

Therefore , the min. value for b = 2 * BM /Q 8.96382 INCH 227.6811 MM

( the value used for b = 300 MM > 227.68 MM ) OK < 300 MM

Page 97: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 97 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

Min. Design Metal Temperature, MDMT 10oF -12

oC

THICK. THICK. P No Gr No CURVE

1. Pressure Parts Materials INCH MM

a. Shell Plate : ASME SA516 Grade 70 (normalized) 0.9 22 1 2 D

b. Formed Heads : ASME SA516 Grade 70 (normalized) 0.8 20 1 2 D

c. Flanges : ASME SA105 (normalized/tempered) (Castings) 0.94 24 1 2 B

d. Nozzle Necks : ASME SA106 Grade B (Seamless Pipe Nozzles) 1 1 B

M1. Nozzle Mark : N11, 1-1/2"NPS, Sch. XXS, 300# WNRF(Located entirely within a centrally located circle of head's leg0.4 10.16

M2. Nozzle Mark : N8 24" NPS, Sch. 30, 300# WNRF (Manhole Located at Shell with Reinforcement0.56 14.27

M3. Nozzle Mark : Leg 20"NPS, Sch. 30 (Leg Located at Shell with Reinforcement0.5 12.7

M4. Nozzle Mark : N1 8"NPS, Sch. 80, 300# WNRF (Located at Shell) 0.5 12.7

M5. Nozzle Mark : N1 6" NPS, Sch. 80 300# WNRF (Located at Blind Flange of N0.43 10.97

M6. Nozzle Mark : N2 6" NPS, Sch. 80, 300# WNRF (located at shell) (cont.) 0.43 10.97

M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (Located at Shell) 0.44 11.13

M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (Located at Shell) 0.44 11.13

M9. Nozzle Mark : N3, N4 & N7 2" NPS, Sch.160, 300# WNRF (Located at Shell0.34 8.74

M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch.XXS, 300# WNRF (Located at Shell0.4 10.16

M11. Nozzle Mark : N16 1" NPS, Sch.XXS, 300# WNRF (Piping branch from N 0.36 9.09

M12. Nozzle Mark : N5A, N5B & N12 1-1/2" NPS, Sch.XXS, 300# WNRF (Located at Head, F 0.4 10.16

M12. Nozzle Mark : N16 1-1/2" NPS, Sch.XXS, 300# WNRF (Located at Shell, F = 0.5) 0.4 10.16

M13. Nozzle Mark : N10A & N10B 1/2" NPS, Sch.XXS, 300# WNRF (Located at Leg0.29 7.47

Note : Rest of nozzles are N17, N18 and N19 which represent the instruments for LC & LG.

e. Fittings : Tees : ASME SA234 WPB 1 1 B

Half Coupling : ASME SA 105 N1, 3/4" 3000# 0.4 10.97

f. Stud Bolts : ASME SA193 Grade B7, Galvanized 2.5 63.5

g. Nuts : ASME SA194 Grade 2H, Galvaanized 2.5 63.5 to be checked 0

2. Non-Pressure Parts Materials

a. Saddle Plate : ASME SA516 Grade 70 0.6 14 1 2 D

b. Lifting Lug Reinf. Plate : ASME SA516 Grade 70 (if required) 0.9 22 1 2 D

Page 98: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 98 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

1. Pressure Parts Materials

a. For cylindrical shell

Material ASME SA516 Grade 70

Condition Normalized

Curve D

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.86614 INCH 22 MM

Point of combination of MDMT & thkickness Below, so we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.47256 INCH 12.0029 MM

Corrosion allowance, Cas 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 0.551") -36.2835oF -37.93526

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.2] 0.63765 > 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 35oF 1.666667

oC

Adjusted MDMT w/o impact testing -71.2835oF -57.3797

oC

Impact testing required ? NO

b. For formed heads

Material ASME SA516 Grade 70

Condition Normalized

Curve D

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.787 INCH 20 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.46538 INCH 11.82059 MM

Corrosion allowance, Cah 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.3385827") -39.632oF -39.79556

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.7182 > 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 30oF -1.111111

oC

Adjusted MDMT w/o impact testing -69.632oF -56.46222

oC

Impact testing required ? No

Page 99: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 99 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

c. For B16.5 flanges :

Material ASME SA105 Ferritic Steel

ASME/ANSI B16.5

Condition

Curve B

MDMT 10oF -12

oC

Impact testing exemption temp. [UCS-66(c)(1)] -20oF -29

oC

Note. The same condition apply for flanges B16.47, split loose

flanges of SA216 Grade WCB and LWN flanges.

[UCS-66(c)(2),(3)&(4)]

For blind flanges :

- M2, N8 24" NPS, 300# :

Material ASME SA105 Ferritic Steel

ASME/ANSI B16.5

Condition

Curve B

MDMT 10oF -12

oC

Blind thickness, tA 2.75197 INCH 69.9 MM

Governing thickness, tg1 = tA/4 0.68799 17.475 MM

[Fig. UCS-66.3(c)]

MDMT without impact testing (for thickness 2.9374016") 10.0394oF -12.20035

oC

For blind flanges :

- M4, N1 8" NPS, 300# :

Material ASME SA105 Ferritic Steel

ASME/ANSI B16.5

Condition

Curve B

MDMT 10oF -12

oC

Blind thickness, tA 1.61811 INCH 41.1 MM

Governing thickness, tg1 = tA/4 0.40453 10.275 MM

[Fig. UCS-66.3(c)]

MDMT without impact testing (for thickness 2.9374016") -16.6929oF -27.05162

oC

Page 100: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 100 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

d.

M1. Nozzle Mark : N11, 1-1/2"NPS, Sch. XXS, 300# WNRF(Located entirely within a centrally located circle of head's leg

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.4 INCH 10.16 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.01279 INCH 0.324866 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 2.9374016") -17.2oF -27.33333

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.06638 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -152.2oF -102.3333

oC

Impact testing required ? No

M2. Nozzle Mark : N8 24" NPS, Sch. 30, 300# WNRF (Manhole Located at Shell with Reinforcement)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.56181 INCH 14.27 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.17874 INCH 4.540115 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.8759843") -1.06614oF -18.37008

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.46664 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -136.066oF -93.37008

oC

Impact testing required ? No

Page 101: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 101 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M3. Nozzle Mark : Leg 20"NPS, Sch. 30 (Leg Located at Shell with Reinforcement)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.5 INCH 12.7 MM

Point of combination of MDMT & thkickness Below, we need to check ratio tr.E/(tn-c)

Required thickness, tr 0.06257 INCH 1.589294 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.6259843") -7oF -21.66667

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.20163 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -142oF -96.66667

oC

Impact testing required ? No

M4. Nozzle Mark : N1 8"NPS, Sch. 80, 300# WNRF (Located at Shell)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.5 INCH 12.7 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.06257 INCH 1.589294 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -7oF -21.66667

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.20163 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -142oF -96.66667

oC

Impact testing required ? No

Page 102: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 102 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 6 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M5. Nozzle Mark : N1 6" NPS, Sch. 80 300# WNRF (Located at Blind Flange of N1)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.43189 INCH 10.97 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.F/(tn-c)

Required thickness, tr 0.04766 INCH 1.210501 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -7oF -21.66667

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.20703 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -142oF -97

oC

Impact testing required ? No

#REF!

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.43189 INCH 10.97 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.04826 INCH 1.22572 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -13.6283oF -25.34908

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.20963 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -148.628oF -100.3491

oC

Impact testing required ? No

Page 103: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 103 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 7 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M7. Nozzle Mark : N9 4" NPS, Sch. 120, 300# WNRF (Located at Shell)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.43819 INCH 11.13 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.03201 INCH 0.812955 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -12.9339oF -24.96325

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.1347 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -147.934oF -99.96325

oC

Impact testing required ? No

M8. Nozzle Mark : N18 3" NPS, Sch. 160, 300# WNRF (Located at Shell)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.43819 INCH 11.13 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.0244 INCH 0.619668 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -12.9339oF -24.96325

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.10267 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -147.934oF -100

oC

Impact testing required ? No

Page 104: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 104 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 8 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M9. Nozzle Mark : N3, N4 & N7 2" NPS, Sch.160, 300# WNRF (Located at Shell)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.34409 INCH 8.74 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.01652 INCH 0.419494 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -20oF -28.88889

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.13013 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -155oF -103.8889

oC

Impact testing required ? No

M10. Nozzle Mark : N6 & N17 1-1/2" NPS, Sch.XXS, 300# WNRF (Located at Shell)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.4 INCH 10.16 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.01273 INCH 0.323262 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -17.2oF -27.33333

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.06605 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -152.2oF -102

oC

Impact testing required ? No

Page 105: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 105 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 9 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M11. Nozzle Mark : N16 1" NPS, Sch.XXS, 300# WNRF (Piping branch from N4)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.35787 INCH 9.09 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.00885 INCH 0.224769 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -20oF -28.88889

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.06183 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -155oF -103.8889

oC

Impact testing required ? No

M12. Nozzle Mark : N5A, N5B & N12 1-1/2" NPS, Sch.XXS, 300# WNRF (Located at Head, F = 0.5)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.4 INCH 10.16 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.01273 INCH 0.323262 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -17.2oF -27.33333

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.06605 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -152.2oF -102

oC

Impact testing required ? No

Page 106: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 106 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 10 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

M12. Nozzle Mark : N5A, N5B & N12 1-1/2" NPS, Sch.XXS, 300# WNRF (Located at Head, F = 0.5)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.4 INCH 10.16 MM

Point of combination of MDMT & thkickness Below , w e have to check ratio tr.E/(tn-c)

Required thickness, tr 0.012726838 INCH 0.323261675 MM

Corrosion allow ance, Can 0.236220472 INCH 6 MM

Joint eff iciency, E = E* 0.85

MDMT w ithout impact testing (for thickness 1.1496063") -17.2oF -27.33333333

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.066051063 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222222

oC

Adjusted MDMT w /o impact testing [UCS-66(b)] -152.2oF -102.3333333

oC

Impact testing required ? No

M13. Nozzle Mark : N10A & N10B 1/2" NPS, Sch.XXS, 300# WNRF (Located at Leg)

Material ASME SA 106 Grade B

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.29409 INCH 7.47 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.00487 INCH 0.123793 MM

Corrosion allowance, Can 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.1496063") -20oF -28.88889

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.07158 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -155oF -104

oC

Impact testing required ? No

Page 107: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 107 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 11 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

e. Stud bolts :

Material ASME SA193 Grade B7

Curve 0

Size 1.25 INCH 31.75 MM

MDMT 10oF -12

oC

Impact testing exemption [Fig. UCS-66, Bolting] -55oF -48

oC

[Size 1.25" < 2.5"]

Nuts :

Material ASME SA 194 Grade 2H

Curve 0

Size 1.25 INCH 31.75 MM

MDMT 10oF -12

oC

Impact testing exemption [Fig. UCS-66, Bolting] -55oF -48

oC

[Size 1.25" < 2.5"]

f. Fittings : For equal tee : 1.5" x 1.5"

Size, NPS 1.5 INCH

Sch. XXS

Material ASME SA234 Grade WPB

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.4 INCH 10.16 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.01273 INCH 0.323262 MM

Corrosion allowance, C 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.0669291") -17.2oF -27.33333

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.06605 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -152.2oF -102.3333

oC

Impact testing required ? No

Page 108: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 108 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 12 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

f. Fittings (cont.): For equal tee : 2" x 1"

Size, NPS 2 INCH

Sch. XXS

Material ASME SA234 Grade WPB

Condition Tempered

Curve B

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.34409 INCH 8.74 MM

Point of combination of MDMT & thkickness Below, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.01652 INCH 0.419494 MM

Corrosion allowance, C 0.23622 INCH 6 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing (for thickness 1.0669291") -23.4614oF -30.8119

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.13013 < 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 135oF 57.22222

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -158.461oF -105.8119

oC

Impact testing required ? No

Page 109: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 109 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 13 of 13

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

O. Lowest MDMT Without Impact Test (cont.) [UG-20(f)] , [UCS-66] & [FIG.UCS-66]

2. For Non-Pressure Parts :

a. Saddle Plate (tf) :

Material ASME SA516 Grade 70

Condition Normalized

Curve D

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) (tf) 0.55118 INCH 14 MM

Point of combination of MDMT & thkickness Belo, we have to check ratio tr.E/(tn-c)

Required thickness, tr 0.4734 INCH 12.02436 MM

Corrosion allowance, C 0 INCH 0 MM

Joint efficiency, E = E* 0.85

MDMT without impact testing -51.7244oF -46.51356

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 0.73005 > 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 20oF -6.666667

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -71.7244oF -57.62467

oC

Impact testing required ? No

b. Lifting Lug Reinf. Plate :

Material ASME SA516 Grade 60

Condition Normalized

Curve D

MDMT 10oF -12

oC

Nominal thickness, tn (adopted thickness) 0.86614 INCH 22 MM

Point of combination of MDMT & thkickness Above, no need to check ratio tr.E/(tn-c)

Required thickness, tr 0.86614 INCH 22 MM

Corrosion allowance, C 0 INCH 0 MM

Joint efficiency, E = E* 1

MDMT without impact testing -31.5669oF -35.31496

oC

Ratio = tr . E / (tn -c) [Fig. UCS-66.1] 1 > 0.35 [Fig. UCS-66-1]

Reduction in MDMT [Temp. versus ratio in Fig. UCS-66.1] 0oF -17.77778

oC

Adjusted MDMT w/o impact testing [UCS-66(b)] -31.5669oF -35.31496

oC

Impact testing required ? No

Conclusion :

MDMT without Impact Testing for Whole Vessel 10oF -12

oC

So, the vessel can be operated at the nominated MDMT with impact test exemption in accordance with UG-20(f),

UCS-66 and Fig. UCS-66.

Page 110: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 110 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 2

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

P. Radiography Spot

RT3

Q. Hydrostatic Test Pressure [UG-99(b)]

Design Temperature 149oF 65

oC

Test Temperature 86oF 30

oC

Internal Design Pressure, P (MAWP) 255.682 PSI 18 Kg/CM2G

Max. Allowable Stress @ Design Temperature, S 20000 PSIG 1408 Kg/CM2G

Max. Allowable Stress @ Test Temperature, St 20000 PSIG 1408 Kg/CM2G

[TABLE 1A, SUBPART 1, ASME SEC. II, PART D]

Hydrostatic Test Pressure, Ph = 1.3 * MAWP (St/S) 332.386 PSI 23.4 Kg/CM2G

Client Request for Hydrostatic Test Pressure, Ph = 1.5 * MAWP (St/S) 383.523 PSI 27 Kg/CM2G

Check for hydrostatic test : For shell, S = Ph ( R + 0.6 t ) / E t 16229.6 PSIG 1142.561 KG/CM2G

< 20000 PSIG OKMax. Working Pressure (New & Cold) for Whole of Vessel , MWPn 435.6745808 PSIG 30.67149147 Kg/CM2G

Max. Working Pressure (Operating & corroded) for Whole of Vessel, MWPo 305.3623162 PSIG 21.49750775 Kg/CM2G

Shop Hydrostatic Test Pressure (new & cold), Ph = 1.3 * MWPn (St/S) 566.3769551 PSI 39.87293891 Kg/CM2G

Check for shop hydrostatic test : For shell, S = Ph ( R + 0.6 t ) / E t 23967.41693 PSIG 1687.306187 KG/CM2G

< 20000 PSIG OK

R. Post Weld Heat Treatment (PWHT)

[UW-40 & TABLE UCS-56]

Shell Material ASME SA516 Grade 70

P- No. 1

Gr. No. 2

Max. Welded Nominal Thickness (Shell) 0.866 INCH 22 MM

Max. Welded Nominal Thickness (N1 8" 300# Blind) 0.63 INCH 41.1 MM

a. According to UW-40 & UCS-56(f), the vessel material is exempted from PWHT.

b. According to UW-40, UCS-56 and Table UCS-56, the joint between nozzle 6" NPS N1 & Blind Flange,

the vessel component shall be partially postweld heat treated in accordance to the following procedure :

1. Heating up to temp. 1148oF 620

oC

Starting from 350oC for a time 1 Hour 58 Minute

2. Holding temp. 1148oF 620

oC

for a time 1 Hour 50 Minute

3. Cooling up to 572oF 300

oC

for a time 1 Hour 52 Minute

Up to room temp. 86oF 30

oC

Page 111: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 110a of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 2

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

Heating

C1 C2 Rate, Rh Thickness

Heating from, OC to,

OC

oC /Hr/inch Inch

350 620 222 1.61811

Heating Time = (Thickness, t) (C2-C1) / (Heating Rate, Rh) 1.96797 Hour

1 Hr 58 Minutes

Holding, Min. Holding Time per Thickness 1 hr/Inch

Holding Time = (Thickness, t) (Min. Holding Time per Thickness, Th) 1.61811 Hr

1 Hr 50 Minutes

Cooling

C3 C4 Rate, Rc Thickness

Cooling from, OC to,

OC

oC /Hr/inch Inch

620 300 278 1.61811

Cooling Time = (Thickness, t) (C3-C4) / (Cooling Rate, Rc) 1.86257 Hour

1 Hr 52 Minutes

Note : 593 oC can be assumed to be 620

oC + /- 25

oC

Page 112: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 111 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 3

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

S. Calculation of Vessel Weight

1.Volume of vessel :

Shell volume = 3.14 * R2 * L' 9.013374 M

3

Head volume = 3.14 * R2 * (2*KD/3 + l ) 0.569199 M

3

( where KD = Depth of head ), K = 0.00984 INCH 0.25 MM

Head skirt, l 1.5748 INCH 40 MM

Total volume of vessel 10.15177 M3

Tangent - to - Tangent distance (T/T) , L 189.764 INCH 4820 MM

Welding - to - Welding distance (W/W) , L' 186.614 INCH 4740 MM

2.Weight of liquid water , Wc 22381.1 lb. 10151.77 Kg

Total Oveall Length = L + 2 H0 221.969 INCH 5638 MM

3.Weight of vessel empty , W :

a. weight of shell = II *(Ro2 - R

2 ) * L' * $ 8946.77 lb. 4058.145 Kg

( where $ = steel density ) 7850 Kg/M3

b.weight of two ellipsoidal heads

=(3.14/4) * D2 * (4/3) * KD *$ = (3.14/3)*K*(Do

3 -D

3)*$ 1789.08 lb. 811.5047 Kg

= 8*(3.14/3)*K*(Ro3 - R

3)*$ + weight of 2 skirts

Weight of skirt of two ellipsoidal heads = II *(Ro2 - R

2 ) * 2 Skirt* $ 137.099 lb. 62.18644 KG

c. weight of saddles :

- Base plate, 1600x400x25 207.678 lb. 94.2 Kg

Saddle plate length 70.4724 INCH 1790 MM

- Saddle plate, 1790x480x14 164.806 lb. 74.75398 Kg

Web plate ( saddle plate ) height, h = Z - (Ro+tf) cos(B/2) 54.8425 INCH 1393 MM

Web plate ( saddle plate ) width, Lw = m - 2*(ts + cl) 60.7087 INCH 1542 MM

angle b = B/2 60 Deg.

where h1 = height of segment 17.0079 INCH 432 MM

y = m - m' = (m-2cl) - 2 (Ro+tf) sin(B/2) 6.30357 INCH 160.1106 MM

Area of segment, As = (Ro+tf)2 [(3.14 * b)/180 - Sin b* Cos b] 0.406956 M

2

Area of web plate excluding segment, A = (m -2cl) * h - As - 2y2/SQRT(3) 1.750452 M

2

- Weight of web plate (1542x1393x14) = A * tw * $ 424.118 lb. 192.3747 Kg

Rip plates weights (per saddle) :

Rip plates, thickness, ts 0.55118 INCH 14 MM

Rip plates # 1 width, Rw 5.03937 INCH 128 MM

Rip plates # 1 , height 39.5046 INCH 1003.416 MM

Weight of rip plates # 1 (no. off 4 ) , 1006x178x14 124.476 lb. 56.461 Kg

Rip plates # 2 width, Sw 10.6299 INCH 270 MM

Rip plates # 2 , height 54.8425 INCH 1393 MM

Weight of rip plates # 2 (no. off 2 ) , 1393x370x14 182.256 lb. 82.66898 Kg

- Weight of rip plates ( per one saddle ) 306.732 lb. 139.13 Kg

- Weight of one saddle 1103.33 lb. 500.4587 Kg

- Weight of two ( 2 ) saddles 2206.67 lb. 1000.917 Kg

Page 113: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 112 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 3

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

S. Calculation of Vessel Weight (cont.)

Weight of leg : weight of pipe 20" Sch. 30, L = 600 MM 205.191 lb. 93.072 Kg

weight of cap 20" Sch.30 99.209 lb. 45 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 219.209 lb. 99.43042 Kg

e. Weight of nozzles 3434.11 lb. 1557.671 Kg

i. Weight of Nozzle, N12 24" Sch. 30, WNRF 300#

- weight of WN flange 544.547 lb. 247 Kg

- weight of nozzle pipe (184 MM) 85.0415 lb. 38.57376 Kg

- weight of Blind Flange 753.989 lb. 342 Kg

- weight of Stud Bolts & Nuts 74.0761 lb. 33.6 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 314.645 lb. 142.7193 Kg

ii. Weight of Nozzle, N1 10" Sch. 60, WNRF 300# :

- weight of SO flange 90.3905 lb. 41 Kg

- weight of nozzle pipe (180 MM) 32.362 lb. 14.679 Kg

- weight of Blind Flange 127.869 lb. 58 Kg

- weight of Stud Bolts & Nuts 15.6618 lb. 7.104 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 37.8217 lb. 17.15545 Kg

iii. Weight of Nozzle, N1 8" Sch. 80, WNRF 300# :

- weight of WN flange 66.1394 lb. 30 Kg

- weight of nozzle pipe (180+2000 MM) 310.668 lb. 140.9152 Kg

iv. Weight of Nozzle, N6 & N9 2" Sch. 160, WNRF 300# :

- weight of WN flange 26.4557 lb. 12 Kg

- weight of nozzle pipe (1490 MM) 218.973 lb. 99.3234 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 7.6038 lb. 3.448988 Kg

v. Weight of Nozzle, N3 & N7 3" Sch. 160, WNRF 300# :

- weight of WN flange 15.4325 lb. 7 Kg

- weight of nozzle pipe (160 MM) 7.53107 lb. 3.416 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 5.56824 lb. 2.525687 Kg

vi. Weight of Nozzle, N10 & N14 6" Sch. 120, WNRF 300# :

- weight of WN flange 0 lb. 0 Kg

- weight of nozzle pipe (160 MM) 0 lb. 0 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 0 lb. 0 Kg

vii. Weight of Nozzle, N9 4" Sch. 120, WNRF 300# :

- weight of WN flange 24.2511 lb. 11 Kg

- weight of nozzle pipe (160 MM) 9.98969 lb. 4.5312 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 9.74459 lb. 4.420027 Kg

viii. Weight of Nozzle, N2, N3, N4, N8A, N8B, N11, N13 & N16 1-1/2" Sch. 160, WNRF 300# :

- weight of WN flange 46.2976 lb. 21 Kg

- weight of nozzle pipe (160 MM) 45.1864 lb. 20.496 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 4.78483 lb. 2.170339 Kg

Page 114: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 113 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 3

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

S. Calculation of Vessel Weight (cont.)

ix. Weight of Nozzle, N15 1" Sch. XXS, WNRF 300# :

- weight of WN flange 4.40929 lb. 2 Kg

- weight of nozzle pipe (160 MM) 7.53107 lb. 3.416 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 0.94545 lb. 0.428843 Kg

x. Weight of Nozzle, N5A & N5B 1/2" Sch. 160, WNRF 300# :

- weight of WN flange 6.61394 lb. 3 Kg

- weight of nozzle pipe (160 MM) 15.0621 lb. 6.832 Kg

- weight of Pad =3.14/4 (Dp2-OD

2) te p 0.36083 lb. 0.163669 Kg

xi. Weight of Nozzle, N4 3/4", half coupling 3000# : 0.55116 lb. 0.25 Kg

Weight of vessel empty (erection weight), W 16376.1 lb. 7428 Kg

Weight of test liquid (water), Wc 22381.6 lb. 10152 Kg

Total test weight (weight of vessel and test liquid), Wt 38757.7 lb. 17580 Kg

Page 115: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 114 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 8

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Project : Design & Procurement of ASME Pressure Vessel Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method

Shell material ASME SA516 Grade 70

Heads material ASME SA516 Grade 70

Saddles material ASME SA283 Grade C

Heads type Ellipsoidal 2:1

Design temperature 149oF 65

oC

Vessel internal pressure, P 255.682 PSIG 18 Kg/CM2G

Allowable stress in shell, Sts 20000 PSIG 1408 Kg/CM2G

Allowable stress in heads, Sth 20000 PSIG 1408 Kg/CM2G

Allowable stress in web, Sw 15700 PSIG 1105.28 Kg/CM2G

Shell compression yield point, Y 32000 PSIG 2252.8 Kg/CM2G

Saddle & anchor bolt compression yield point, Re 30000 PSIG 2112 Kg/CM2G

Outer shell diameter, Do 62.9918 INCH 1600 MM

Wall nominal thickness of shell, ts 0.866 INCH 22 MM

Wall nominal thickness of heads (min.), th 0.7874 INCH 20 MM

Corrosion allowance for shell & heads, Cas 0.236 INCH 6 MM

Shell joint efficiency, Es 0.85

Head joint efficiency, Eh 0.85

Head internal depth, h 15.315 INCH 389 MM

Head depth -to- tangent line (external depth), Ho 16.102 INCH 409 MM

Insulation thickness, tis 0 INCH 0 MM

Wear (reinf./top flange) plate width, B 14.961 INCH 380 MM

Wear (reinf./top flange) plate thickness, tf 0.551 INCH 14 MM

Wall corroded thickness of shell 0.236 INCH 6 MM

Wall corroded thickness of heads 0.551 INCH 14 MM

Wall corroded thickness of shell + reinf. plate 0.787 INCH 20 MM

Outer shell radius, Ro = Do / 2 31.496 INCH 800 MM

Shell length from Tangent - to - tangent (T/T), L 189.764 INCH 4820 MM

Saddle - to - saddle distance (S/S), L" 145.669 INCH 3700 MM

Transverse distance between anchor bolts, Y 39.3701 INCH 1000 MM

Distance from tangent line -to- center of saddle support, A 22.047 INCH 560 MM

Saddle contact angle, B 120 Degree

Longitudinal width of saddle at shell, b 14.961 INCH 380 MM

Transverse width of saddle at shell (baseplate length), m 62.992 INCH 1600 MM

Height of saddle to vessel center line, Z 70.866 INCH 1800 MM

Web width of saddle, hs 62.992 INCH 1600 MM

Web thickness of saddle, tw 0.551 INCH 14 MM

Equivalent diameter of vessel, Deq = 1.5 (Do + 2 * tis) 94.488 INCH 2400 MM

Equivalent length of vessel, Leq = L + 2Ho + 2 tis 221.969 INCH 5638 MM

Page 116: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 115 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 8

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.)

1. Seismic & wind forces on vessel

a. Seismic force UBC-1997

Total design force or shear at the base, F = z . I . C . Wt / Rw 5329.18 lb 2417.25 Kg

Seismic Zone 2A :

For zone 2A : z = Seismic zone factor [Table No. 23-I] 0.15

I = Importance factor [Table No. 23-L] 1

C = Numerical coefficient [Table No. 23-P] 2.75 Max.

Rw = Numerical coefficient [TableS NoS. 23-O & 23-Q] 3

= 3 ( horizontal vessel on pier)

Total vessel dead weight, Wt 38757.7 lb 17580 Kg

b. Wind force ANSI A58.1

F = Cf . Gh . qz . Af

qz = 0.00256 . kz . (I V)2

27.0848 PSF 13.49792 N/M2

For exposure C :

h = Height 0-15 Ft

kz = Velocity pressure exposure coefficient 0.8

Wind Velocity, V = Basic wind speed 115 MPH 51.399 M/Sec.

Gh = Gust response factor 1.32

Cf = Force coefficient 0.8

c. Forces in longitudinal direction

Figure ( 6 )

Seismic longitudinal force, Fls = z . I . C . Wt / Rw 5329.18 lb 2417.25 Kg

Wind longitudinal exposed area, Afl = (pi/8*Deq + Z) * Deq 70.8472 Ft2

6.58192 M2

Wind longitudinal force, Flw = Cf . Gh . qz . Afl 2026.34 lb 919.1228 Kg

Fl = Greater value of Fls & Flw 5329.18 lb 2417.25 Kg

Page 117: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 116 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 3 of 8

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.)

d. Forces in transverse direction

Figure ( 7 )

Seismic transverse force, Fts = 0.5 Fls = 0.5 x z x I x C x Wt / Rw 2664.59 lb 1208.625 Kg

Wind transvere exposed area, Aft = Deq * Leq 145.649 Ft2

13.5312 M2

Wind transverse force, Ftw = 0.5 x Cf x Gh x x qz x Aft 2082.89 lb 944.7727 Kg

Ft = Greater value of Fts & Ftw 2664.59 lb 1208.625 Kg

2. Reaction force per saddle support

a. Reaction due to full vessel weight, Qo = Wt/2 19378.8 lb 8790 Kg

b. Reaction in longitudinal direction due to earthquake & wind :

By taking moments about saddle support : Fl . Z = Ql . L"

Ql = Fl . Z / L" 2592.57 lb 1175.959 Kg

c. Reaction in transverse direction due to earthquake & wind :

By taking moments about saddle support : Ft . Z = Qt . (m/2)

Qt = 3 ( 2 . Ft . Z / m) 17986 lb 8158.219 Kg

d. Max. reaction due to earthquake & wind, Qmax. = Max. (Ql , Qt) 17986 lb 8158.219 Kg

e. Total reaction due to full vessel weight, earthquake and wind, Q

Total longitudinal reaction, Qlt = Qo + Ql 21971.4 lb 9965.959 Kg

Total transverse reaction, Qtt = Qo + Qt 37364.8 lb 16948.22 Kg

Q = Greater value of Qlt & Qtt 37364.8 lb 16948.22 Kg

3. Modified stresses at saddles :

Ratio (Qo + Qmax.) / Qo 1.92813

a. Modif ied circumferential stresses, SIG 5' = Ratio . < OK

SIG 5' = Ratio . < OK

SIG 4' = Ratio . < OK

b. Modif ied tangential stresses, SIG 2' = Ratio . < OK

Page 118: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 117 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 4 of 8

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.)

a. Stresses in longitudinal direction

Longitudinal force, Fl 5329.18 lb 2417.278 Kg

Max. moment, Mmax. = Fl . Z 377658 lb-in. 4351.091 Kg-M

Figure ( 8 )

Cross-sectional Area, A = Lw * tw + 2 Sw * ts+ 2(n-2) Rw * ts 56.2899 INCH2

36316 MM2

Moment of inertia, Ix-x = Lw*tw3/12+(n-2) ts*Sw

3/12+2ts(Sw

3-tw

3)/12 221.512 INCH

492200201 MM

4

Section modulus, Wx-x =Lw*tw2/6+2ts*Sw

2/6+2ts(Sw

3-tw

3)/(6 Sw) 44.5915 INCH

3730724.6 MM

3

Dimension X1 = Ix-x / Wx-x 4.96758 INCH 126.1764 MM

Bending stress, Sb = Mmax. / Wx-x 8469.26 PSIG 596.2362 Kg/CM2G

Allowable bending stress, S' = 1.2 . S 18840 PSIG 1326.336 Kg/CM2G

Shear stress, T = Fl / A 94.6738 PSIG 6.665034 Kg/CM2G

Allowable shear stress, S' = 0.5 . S 7850 PSIG 552.64 Kg/CM2G

OK

b. Stresses in transverse direction

Transverse force, Ft 2664.59 lb 1208.639 Kg

Max. moment, Mmax. = Ft . Z 188829 lb-in. 2175.546 Kg-M

Figure ( 9 )

Cross-sectional Area, A 56.2899 INCH2

36316 MM2

Moment of inertia, Iy-y = tw*Lw3/12+Sw[(Lw+2ts)

3-Lw

3]/12+2Rw((Ss(n-1-2)+ts)322429.5 INCH

49.34E+09 MM

4

Section modulus, Wy-y =tw*Lw2/6+Sw*[(Lw+2ts)

3-Lw

3]/6(Lw+2ts)]+2Rw[(Ss+ts 804.78 INCH

313187989 MM

3

Dimension Y1 = Iy-y / Wy-y 27.8703 INCH 707.9063 MM

Bending stress, Sb = Mmax. / Wy-y 234.634 PSI 16.51823 Kg/CM2G

Allowable bending stress, S' = 1.2 . S 18840 PSI 1326.336 Kg/CM2G

OK

Shear stress, T = Ft / A 47.3369 PSI 3.332517 Kg/CM2G

Allowable shear stress, S' = 0.5 . S 7850 PSI 552.64 Kg/CM2G

OK

Page 119: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 118 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 5 of 8

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.)

1. Bending moment & bending stress at saddles

Bending moment at saddle in tension & compression, M1

823586 lb-in 9488.744 Kg-M

Longitudinal bending stress in tension, S1 = M1 / K1 R2 ts 2861.77 PSIG 201.4689 Kg/CM

2G

Longitudinal bending stress in compression, S1 = - M1 / K8 R2 ts -1589.87 PSIG -111.9271 Kg/CM

2G

2. Bending moment & bending stress at midspan

Bending moment at midspan, M2

3333925 lb-in 38411.02 Kg-M

Longitudinal bending stress at midspan, S1' = - M1' / 3.14 R

2 ts -1235.31 PSIG -86.9661 Kg/CM

2G

3. Stress in the shell due to internal pressure,

S = P R / (2 Es ts) 5470.01 PSIG 385.089 Kg/CM2

4. Sum of tensile stress

Value of S1 + S 8331.79 PSIG 586.5578 Kg/CM2G

Value of S1' + S -2825.19 PSIG -198.8932 Kg/CM

2G

Greater value of (S1 + S) & (S1' + S) 8331.79 PSIG 586.5578 Kg/CM

2G

Shell allowable tensile stress 20000 PSIG 1408 Kg/CM2G

Stress ratio = Greater stress/Allowable stress 0.41659 < 1 Passed

5.Tangential shear stress, S2

5.a. Tangential shear stress on shell, S2

In case of A > R/2 and ring not used or rings are adjacent to the saddle.

1106.25 PSIG 77.88014 Kg/CM2G

Shell allowable tangential stress = 0.8 S 16000 PSIG 1126.4 Kg/CM2G

Stress ratio = S2 / 0.8 S 0.06914 < 1 Passed

+

−+−

−=

L3

H41

LA2

HR

L

A1

1AQM

22

1

M Q L

R H

LH

L

A

L1

2 2

21 2

14

3

4'=

+−

+

SK Q

R t

L A

LH

s

22 2

4

3

=−

+

Page 120: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 119 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 6 of 8

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.)

5.b. Tangential shear stress on shell, S2

In case of A > R/2 and ring used in plane of saddle.

301.362 PSIG 21.21585 Kg/CM2G

Shell allowable tangential stress = 0.8 S 16000 PSIG 1126.4 Kg/CM2G

Stress ratio = S2 / 0.8 S 0.01884 < 1 Passed

5.c. Tangential shear stress on head, S2h

In case of A > R/2 and ring not used or rings are adjacent to th saddle.

1216.68 PSIG 85.65414 Kg/CM2G

Head allowable tangential stress = 0.8 S 16000 PSIG 1126.4 Kg/CM2G

Stress ratio = S2 / 0.8 S 0.07604 < 1 Passed

5.d. Tangential shear stress on shell

In case of A <= R/2

S2 = K4 Q / R ts 1205.51 PSIG 84.86817 Kg/CM2G

Shell allowable tangential stress = 0.8 S 16000 PSIG 1126.4 Kg/CM2G

Stress ratio = S2 / 0.8 S 0.07534 < 1 Passed

5.e. Tangential shear stress on head

In case of A <= R/2 S2 = K4 Q / R th 1325.85 PSIG 93.33971 Kg/CM2G

Shell allowable tangential stress = 0.8 S 16000 PSIG 1126.4 Kg/CM2G

Stress ratio = S2 / 0.8 S 0.08287 < 1 Passed

5.f. Additional tangential shear stress in head

In case of A <= R/2 S3 = K5 Q / R th 604.165 PSI 42.53321 Kg/CM2G

S3 + stress due to int. pres. (PR/(2Es ts) 5470.01 PSI 385.089 Kg/CM2G

Head allowable tensile stress = 1.25 S 25000 PSI 1760 Kg/CM2G

Stress ratio = S3 / 1.25 S 0.2188 < 1 Passed

+

−=

3

H4L

A2L

tR

QKS

h

2

h2

+

−=

3

H4L

A2L

tR

QKS

s

3

2

Page 121: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 120 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 7 of 8

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.)

6. Circumferential stress

6.a. Circumferential stress at saddle horn

In case of L >= 8 R (unstiffened)

-1806.46 PSIG -127.1747 Kg/CM2G

Shell allowable circumferential stress = 1.5 S 30000 PSIG 2112 Kg/CM2G

Stress ratio = S4 / 1.5 S 0.06022 < 1 Passed

6.b. Circumferential stress at saddle horn

In case of L < 8 R (unstiffened)

-2828.5 PSIG -199.1262 Kg/CM2G

Shell allowable circumferential stress = 1.5 S 30000 PSIG 2112 Kg/CM2G

Stress ratio = S4 / 1.5 S 0.09428 < 1 Passed

6.c. Circumferential stress at bottom of shell

(stiffened or unstiffened)

-1419.03 PSIG -99.89967 Kg/CM2G

0.5 compression yield point of shell material 16000 PSIG 1126.4 Kg/CM2G

Stress ratio = S5 / 0.5 S 0.08869 < 1 Passed

7. Check tension in web saddle

Horizontal force in web, Fw = K8 Q 22531 lb 10219.78 Kg

Effective web area, Aw = hs tw 34.7086 INCH2

22392.6 MM2

Stress in web, Sw = Fw / Aw 649.147 PSIG 45.69996 Kg/CM2G

Allowable stress in web, Saw = 0.6 Y 18000 PSIG 1267.2 Kg/CM2G

Stress ratio = Sw / 0.6 Y 0.03606 < 1 Passed

Vertical force in web, Fv = Q 37364.8 lb 16948.22 Kg

Stress in web, Sv = Fv / Aw 1076.53 lb 488.3004 Kg

Allowable stress in web (compressiuon), Saw = 0.33 Y 9900 PSIG 696.96 Kg/CM2G

Stress ratio = Sv / 0.33 Y 0.10874 < 1 Passed

2s

6

ss

4

t2

QK3

tR561bt4

QS −

+

−=

).(

2s

6

ss

4

tL

RQK12

tR561bt4

QS −

+

−=

).(

).(ss

7

5

tR561bt

QKS

+

−=

Page 122: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 121 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 8 of 8

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

T. Stresses in Vessel on Two Saddle Supports Using ZICK's Method (cont.)

8. Check of the saddle at the lowest section (web plate thickness) :

The saddle at the lowest section must resist the horizontal force (F).

The effective cross section of the saddle to resist this load is R/3.

Figure (10)

F = K11 . Q 7622.42 lb 3457.437 Kg

To resist this force, the effective area of web plate, A = (R/3) . tw 5.78668 INCH2

3733.333 MM2

The calculated stress, Scal. = F / A 1317.24 PSIG 92.73342 Kg/CM2G

The allowable stress, Sall. = (2/3) Sw 10466.7 PSIG 736.8534 Kg/CM2G

Stress ratio = Scal. / Sall. 0.12585 < 1 Passed

So, the thickness of the web plate is satisfactory for horizontal force (F).

Values of Constant K

For contact angle B = 120o : 120

o

K1 (K1 = 3.14 if the shell is stiffened by ring or head, A > R/2) 0.335

K2 1.171

K3 (K3 is constant for any contact angle) 0.319

K4 0.88

K5 0.401

K6 (K6 depends on the ratio A/R, see chart in vessel handbook)

K6 for A/R > 1.00 0.053

K6 for A/R < 0.5 0.013

A 22.047 INCH 560 MM

R 31.496 INCH 800 MM

A/R 0.69999

K6 for A/R = 0.69 0.0238 [From table]

K7 0.76

K8 0.603

K11 0.204

Page 123: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 122 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 1

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

U. Check for the Anchor Bolts Due to Seismic and Wind Loading

1. For longitudinal forces, Fl

Figure (11)

Fl 5329.18 lb. 2417.25 Kg

Max. moment, Mmax. = Fl . Z 377658 lb-in. 4351.091 Kg-M

Cross-sectional area per anchor bolt, Ab (7/8" M26) 0.419 INCH2

270.322 MM2

No. of anchor bolts per saddle, nb 4 each

Total cross-sectional area of anchor bolts, A = nb . Ab 1.676 INCH2

1081.288 MM2

Shear stress, T = Fl / A 3179.7 PSIG 223.851 Kg/CM2G

Bending stress, Sb = Mmax. / (A . L") 1546.88 PSIG 108.9005 Kg/CM2G

Resultant stress, Si = SQRT (Sb2 + 3 T

2 ) 5720.52 PSIG 402.7246 Kg/CM

2G

Allowable stress, S' = 0.5 . Re 15000 PSIG 1056 Kg/CM2G

OK

2. For transverse forces, Ft

Figure (12)

Ft 2664.59 lb. 1208.639 Kg

Max. moment, Mmax. = Ft . Z 188829 lb-in. 2175.546 Kg-M

Cross-sectional area per anchor bolt, Ab (7/8" M26) 0.419 INCH2

270.322 MM2

No. of anchor bolts per saddle, nb 4 each

Total cross-sectional area of anchor bolts, A = nb . Ab 1.676 INCH2

1081.288 MM2

Shear stress, T = Ft / A 1589.85 PSIG 111.9255 Kg/CM2G

Bending stress, Sb = 2 Mmax. / (A . Y) 5723.45 PSIG 402.9309 Kg/CM2G

Resultant stress, Si = SQRT (T2 + 3 Sb

2 ) 10040 PSIG 706.8149 Kg/CM

2G

Allowable stress, S' = 0.5 . Re 15000 PSIG 1056 Kg/CM2G

OK

Page 124: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 123 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 2

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

V. Lifting Lugs Thickness Calculations

(Reference : Pressure Vessel Handbook)

Check of the thickness of lifting lugs :

Material ASME SA 516 Grade 70

Allowable tensile strength 20000 PSIG 1408 Kg/CM2G

Allowable shear strength = 0.49 St 9800 PSIG 689.92 Kg/CM2G

By neglecting the effect of both wind loads and pipe thrust,

assume 2 (two) lifting lugs with dimensions shown in Figure (13).

Leg of fillet weld, h = the thinner of thicknesses joined

= 10 MM (0.394 INCH)

Figure (13)

Height of lifting lug, L 6.49606 INCH 165 MM

Thickness of lifting lug, b 0.86614 INCH 22 MM

Fillet weld, h 0.64961 INCH 16.5 MM

Length of lifting lug, l 7.08661 INCH 180 MM

F = Wt / (SQRT2) 27405.8 lb. 12430.94 Kg

Vertical component of F, F1 = F/ SQRT2 19378.8 lb. 8790 Kg

Horizontal component of F, F2 = F1 19378.8 lb. 8790 Kg

Average unit stress = 0.707 * F1 / h * I 3241.38 PSIG 2.281928 Kg/CM2G

Max. expected normal stress :

= F2 / (h*I *(b+h))*SQRT(2L2+(b+h)

2)) 298.273 PSIG 0.209984 Kg/CM

2G

< Allowable shear strength 9800 PSIG 6.8992 Kg/CM2G

OK

Page 125: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 124 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 2

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

V. Lifting Lugs Thickness Calculations (cont.)

(Reference : Pressure Vessel Handbook)

Figure (14)

L 6.49606 INCH 165 MM

b 0.86614 INCH 22 MM

l 7.08661 INCH 180 MM

R 2.95276 INCH 75 MM

r 1.1811 INCH 30 MM

Page 126: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 125 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 1

Designed by : Eng. Abdel Monem Mohamed, Process Design Dept.Manager Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

W. Mesh Pad/Blanket (Demister) Calculation.

Mesh Pad (Demister) Material, Stainless Steel TP 316

Denisty of liquid, p l 31.786 lb/ft3

509.48 Kg/M3

Denisty of vapour, p v 1.3162 lb/ft3

21.0966 Kg/M3

Allowable superficial vapour velocity across inlet face of mesh,Va = K [pl - pv]/pv]0.5

1.684 ft/Sec. 0.513283 M/Sec.

Factor, K 0.35

Design velocity, VD = 0.75 Va 1.263 ft/Sec. 0.384963 M/Sec.

Mesh pad thickness 6 INCH 152.4 MM

Pressure drop through wire mesh, Delta P = 0.12 VD2 pv 0.25195 INCH Water

Page 127: 52379610 Pressure Vessel Design Calculations

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 126 of 126

According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 1

Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004

Job Name : Demineralization Plant Job No. : 7434-33

Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRC

Vessel : Deputanizer Reflux Receiver Drum Item No. : 1-D-5 Capacity : 10.152 M3 Type : Horizontal

X. References

The following references are used in the design calculations of

saddles and lifting lugs of pressure vessel under considerations.

1. ASME Boiler and Pressure Vessel Code, Section VIII,

Division 1, 2001 Edition, without Addendum.

2. "Pressure Vessel Design Handbook", Edition 1981,

by Henry H. Bednar, P.E. published by Van Nostrand Reinhold

Co. 135 west 50th. street, New York, N.Y. 10020, USA.

3. "Modern Welding Technology", Edition 1989, by Howard B.

Carry, Prentice Hall, Englewood Cliffs, New Jersey 07632, USA..

4. "Pressure Vessel Handbook", Fifth Edition January 1981,

by Eugene F. Megyese, Publishing Inc., P.O. Box 35365,

Tulsa, OK 74135, USA.

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