26. Pressure_vessel_design_calcula by Abdel Halim Galala

Cairo Oil Refining Co. Subsidery of Egyotian Gen. Petroleum Corp.

P.O. Box : Heliopolis 11757 Cairo A.R.E. :..

Tel. : (+2) 02 - 2529821 (5 Lines) (# ) - :%

Fax : (+2) 02 - 2529826 - :

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E-mail : [email protected] [email protected]:'(

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 MMTangent-to-Tangent Length 4820 MMVessel Wall Thickness 22 MMMAWP 18 Kg/CM2GDesign Temperature 65 oCMDMT -12 oC

Vessel capacity 10.1518 M3Weight of vessel empty (erection weight), W 7428 KgWeight of test liquid (water), Wc 10152 KgTotal test weight (weight of vessel and test liquid), Wt 17580 KgNumber of saddles 2 Saddles

By Eng. Abdel Halim GalalaDesign Sector Manager (assist.)

Design Sector +Page : 1 of 126 Sheet 1 of 2

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 2 of 126According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 2Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1

Project : Design & Procurement of ASME Pressure Vessel Date : 18.2.2004Job Name : Demineralization Plant Job No. : 7434-33 Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRCVessel : 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 2002Client : Amerya Petroleum Refining Co. (APRC) Project : Design & Fabrication of Debutanizer Reflux Receiver DrumLocation : Alexandria, EGYPT Item No. : 1-D-5Serial No. : 7434-33-U-2006Title : Horizontal Pressure VesselService : Debutanizer Reflux Receiver DrumJob 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



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 theprior written permission of Designer.



C. Revision Description.

This page is a record of all revisions of the document, and thefollowing revision(s) has (have) been made to this document.

SheetRev. Date No. Revision Description

0 6.4.2003 all Issued for comments1 18.2.2004 all Issued for approval



D. Contents. Description PageA. Title. Page : 1 of 126 B. Copyright. Page : 3 of 126C. Revision Description. Page : 4 of 126D. Contents. Page : 5 of 126E. Applicable Loading Considered in Design. Page : 6 of 126F. Impact Test Requirements. Page : 7 of 126G. Standarad ASME B16.5 Flange Rating Class. Page : 7 of 126H. Cylindrical Shell Thickness. Page : 8 of 126I. Check of Cylindrical Shell Thickness for External Pressure, FV. Page : 12 of 126J. Ellipsoidal Head Thickness Under Internal Pressure. Page : 13 of 126K. Maximum Working Pressure, MWP (New/cold & Operating/corroded). Page : 14 of 126L. 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 126O. Lowest MDMT Without Impact Test. Page : 97 of 126P. Radiography. Page : 110 of 126Q. Hydrostatic Test Pressure. Page : 110 of 126R. Post Weld Heat Treatment (PWHT). Page : 110 of 126S. Vessel Weight Calculation. Page : 111 of 126T. Sresses in Vessel on Two Saddle Supports. Page : 114 of 126U. Check of the Anchor Bolts Due to Seismic and Wind Loading. Page : 122 of 126V. Lifting Lugs Thickness Calculations. Page : 123 of 126W. Mesh Pad (Demister) Calculations. Page : 125 of 126X. References. Page : 126 of 126

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 6 of 126According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 1 of 1Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Page : 2 of 126


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



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 Db Heads : ASME SA516 Grade 70 1 2 Dc. Flanges : ASME SA 105 1 2 Bd. Nozzle Necks : ASME SA 106 Grade B 1 1 Be. 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 Db. 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 10 oF -12 oCin 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. 149 oF 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#



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

Shell material, Killed Carbon Steel, ASME SA516 Grade 70Normalized & 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 MMShell Inside Diameter, D 61.2598 INCH 1556 MMShell Inside Radius, Ri 30.6299 INCH 778 MMShell length from Tangent-to-Tangent (T/T), L 189.764 INCH 4820 MM

Max. Design Temperature 149 oF 65 oCMin. Design Metal Temperature, MDMT 10 oF -12 oCMax. Operating Temperature 122 oF 50 oC

Max. Operating Pressure 227.273 PSIG 16 Kg/CM2GMax. Internal Design Pressure, P (MAWP) 255.682 PSIG 18 Kg/CM2GExternal Design Pressure (Full Vacuum) Not Applicable 0 PSIG 0 Kg/CM2G

Shell Inside Diameter, D 61.26 INCH 1556 MMShell Inside Radius, R 30.63 INCH 778 MMStatic Head = Vessel Diameter 1.556 MStatic Head Pressure (water head x sp. gr. 1.0) 2.216 PSIG 0.156 Kg/CM2GInternal 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/CM2GMax. Allowable Stress @ Test Temp.(40 oC), St 20000 PSIG 1408 Kg/CM2G [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 MMJoint Efficiency, E [TABLE UW-12] 0.85 [Spot Radiography], [Table UCS-57] 15%



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/CM2GSince 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/CM2GSince 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 MMBy Adding Corrosion Allowance to Wall Tickness, t 0.705 INCH 17.907 MMUse Thickness of Construction, t (Adopted thickness) 0.866 INCH 22 MMCorroded 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 126Hot/cold Insulation N.A.Post Weld Heat Treatment, PWHT Not required per CodePage : 110 of 126Impact Test Per Code Page : 7 of 126 Note. Impact test is required as a client request.



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 MMVessel Wall Thickness in the Corroded Condition, t 0.63 INCH 16 MMVessel I.D. in the Corroded Condition, 2R = OD - 2 t 59.9998 INCH 1568 MMShell length from Tangent-to-Tangent (T/T), L 189.764 INCH 4820 MMShell Length from W.L.- to - W.L, L' 186.614 INCH 4740 MMJoint Efficiency (Longitudinal Seams), E 0.85Joint Efficiency (Circumferential Seams), E 0.85Weight of Vessel, W 16377.3 lb 7428 KgWeight of Contents, Wc 22383.2 lb 10152 KgTotal Weight of Vessel and Contents, Wt 38760.5 lb 17580 KgAssume a Total no. of Saddles 2Reaction at each Saddle, Q 19380.3 lb 8790 KgHead (Cap) Depth - to - T.L, [Table 8, ASME B16.9-1993] 15.315 INCH 389 MMSaddle - to - T.L., A 22.047 INCH 560 MMMaterial to Chart for Compressive Stress, [ FIG.CS-2 CHART, SUBPART 3 , ASME SEC.II , PART D ] Shell, Ro 31.4961 INCH 800 MMN.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 MMCase 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.



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 forlongitudinal tensile stress except the pressure portion dropsout since the most severe condition occurs when there is nopressure in the vessel .

3. The joint efficiency for butt-welded joints shall be taken asunity when investigating longitudinal compression. [UG-23(b)]

[ APPENDIX L-2.2.2]

Thickness , t 0.00902 INCH 0.229 MM



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

Design Temperature 149 oF 65 oCFor 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 MMInternal Height of Elliptical Head 2:1, h = ID/4 15.315 INCH 389 MMHead Wall Thickness, th 0.7874 INCH 20 MMInternal Height of Ellipsoidal Head 2:1, ho = h + th 16.1024 INCH 409 MMEffective 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/CM2GNotes.1. For value of A falling to the left of the material-temp. line, the valueof 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)



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

Head material, Carbon Steel ASME SA516 Grade 70Head type [Seamless] Ellipsoidal 2:1Head 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 MMHead OD [ASME B16.5-1996] 62.9921 INCH 1600 MMHead Outside Radius 31.4961 INCH 800 MM

Design Temperature 149 oF 65 oCMin. Design Metal Temperature, MDMT 10 oF -12 oCMax. Allowable Working Pressure, MAWP 257.898 PSIG 18.156 Kg/CM2GOperating Pressure 227.273 PSIG 16 Kg/CM2GInternal Design Pressure, P 257.898 PSIG 18.156 Kg/CM2GHead Skirt Inside Diameter, D 61.26 INCH 1556 MMHead Inside Radius, L ( ri ) 30.63 INCH 778 MMMax. Allowable Stress @ Design Temp.(60 oC), S 20000 PSIG 1408 Kg/CM2GMax. Allowable Stress @ Test Temp.(40 oC), St 20000 PSIG 1408 Kg/CM2G [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 MMJoint Efficiency, E (Seamless & Full Radiography) [TABLE UW-12] 0.85

Outside Diameter of Head, Do 62.9921 INCH 1600 MMOutside Radius of Head, Ro 31.4961 INCH 800 MM

Value of 0.665 SE 11305 PSIG 795.872 KG/CM2GSince the value of 0.66SE > P, Use Thin Wall Equation forCalculating the Min. required Thickness of Head, t: t1 = PD / (2SE-0.2P) [UG-32(d)] (1) 0.46538 INCH 11.82059 MMCompare to Thickness of Seamless Spherical Shell : Ps = 0.665 SE 11305 PSIG 795.872 KG/CM2GSince P < Ps, Calculate Thickness for thin Wall Spherical Shell: t2 = PRo/(2SE+0.8P) [APPENDIX 1-1] (2) 0.23746 INCH 6.031587 MMFor thin Wall ellipsoidal 2:1 head : t = PD/(2SE-0.2P) [UG-32(d)] 0.46538 INCH 11.82059 MM



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 MMBy adding Corrosion Allowance to Wall Thickness, 0.7016 INCH 17.82059 MMUse 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/CM2GMWP, 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/CM2GMWP, Operating & corroded (14 MM), P = 2SE t /(D + 0.2 t) [305.362 PSIG 21.49751 Kg/CM2G



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 MMOutside diameter of the head skirt, Do 62.3622 INCH 1584 MMThe equivalent outside spherical, Ro = Ko Do [UG-33(b)] 54.342 INCH 1380.288 MMOutside height of the ellipsoidal head (measured from head-bend line), ho 16.1024 INCH 409 MMRatio 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 theconvex 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/CM2GNotes. OK1. For value of A falling to the left of the material-temp. line, the valueof Pa can be calculated in accordance with Step 5 of UG-28(d), asfollows : Pa = 0.0625 E / (Ro /t)2

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



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, trare 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 DNNozzle Material ASME SA 106 Grade B

Design Pressure, P 259.166 PSIG 18.2453 Kg/CM2GDesign Temperature 149 oF 65 oCFor 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/CM2GMax. Allowable Stress of Nozzle Materiall @ Test Temp.(40 oC), Snt 17100 PSIG 1203.84 Kg/CM2G [Table 1A, SubPart 1, ASME Sec. II, Part D]

Outside Radius of Nozzle, Ron 0.95 INCH 24.13 MMJoint Efficiency of Nozzle, En (Seamless Pipe) 1Nozzle 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



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 DNNozzle Pipe Sch. XXSDesign Pressure, P 259.166 PSIG 18.24529 Kg/CM2GDesign Temparture 149 oF 65 oC

Shell & Head Material ASME SA516 Grade 70Nozzle Material ASME SA 106 Grade BReinforcing Pad Material ASME SA 106 Grade BAllowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2GAllowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2GAllowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell & Head Thickness 0.5 INCH 12.7 MMShell & Head Corrosion Allowance, Cas 0.23622 INCH 6 MMShell & Head Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.5 INCH 12.7 MMShell & 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 MMNozzle Wall Thickness less Pipe Tolerance 12.5% 0.35 INCH 8.89 MMNozzle Corrosion Allowance, Can 0.23622 INCH 6 MMNozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.11378 INCH 2.89 MMNozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.11378 INCH 2.89 MMReinforced Pad Thickness, te 0.47244 INCH 12 MMJoint Efficiency of Shell, E 1Joint Efficiency of Nozzle, En 1Correction Factor, F [UG-37(a)] 1E1 [Nozzle in solid plate] 1Shell & Head Outside Diameter, OD 20 INCH 508 MMShell & Head Inside Diameter in Corroded Condition, 2R = OD - 2 t 19.4724 INCH 494.6 MMShell & Head Inside Radius in Corroded Condition, R 9.73622 INCH 247.3 MM

Nozzle Outside Diameter, OD 1.9 INCH 48.26 MMNozzle Inside Diameter, ID 1.1 INCH 27.94 MMNozzle 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 MMNozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 1.67244 INCH 42.48 MMFinished Radius of Circular Opening, Rn 0.83622 INCH 21.24 MM



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 MMBy 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



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 MMThe nominal nozzle pipe wall thk. 0.4 INCH 10.16 MMThe min. nozzle thk. provided = t (1-0.125) 0.35 INCH 8.89 MMSo, the thickness provided meets the rules of UG-45. OK

Since there is no superimposed loads, the vessel doesn't requirea calculationon shear stresses caused by UG-22(c).

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



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 INCH2 69.255 MM2

Area Available in Outer Reinforcing Pad Weld, A42: A42 = (LEG)2 fr4 0.12555 INCH2 81 MM2

Area Available in Inward Nozzle Weld, A43 : A43 = (LEG)2 fr2 0.10735 INCH2 69.255 MM2

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.

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 21 of 126According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Shee t : 1 of 5Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Rev. : 1


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 DNNozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2GDesign Temperature 149 oF 65 oCFor nominated Design Pressure & Temperature, Flange Rating 300# [ANSI/ASME B16.5-1996]


Outside Radius of Nozzle, Ron 12 INCH 304.8 MMJoint Efficiency of Nozzle, En (Seamless Pipe) 1Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM




Use Nozzle 24" NPS with Selected Neck Sch. 30, 0.562 INCH 14.2748 MMwith 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 MMNozzle wall thickness less tolerance 12.5% - Corrosion allowance 0.25553 INCH 6.49045 MMMWP, New & cold (14.275 MM) P = Snt E t /(Ron - 0.4 t) [App. 1.1] 712.422 PSIG 50.15448 Kg/CM2GMWP, 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/CM2GMWP, Operating & corroded, 300# @ 149 oF [ANSI B16.5, Table 2] 708.15 PSIG 49.85376 Kg/CM2G

DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 22 of 126According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Date : 18.2.2004

Project : Design & Procurement of ASME Pressure Vessel Client : APRCJob Name : Demineralization Plant Job No. : 7434-33 Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRCVessel : 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 DNNozzle Pipe Sch. 30Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2GDesign Temparture 149 oF 65 oC

Shell Material ASME SA516 Grade 70Nozzle Material ASME SA 106 Grade BReinforcing Pad Material ASME SA516 Grade 70Allowable Stress of Shell Material, Sv 20000 PSIG 1408 Kg/CM2GAllowable Stress of Nozzle Material, Sn 17100 PSIG 1203.84 Kg/CM2GAllowable Stress of Pad Material, Sp 20000 PSIG 1408 Kg/CM2G

Shell Thickness 0.86614 INCH 22 MMShell Corrosion Allowance, Cas 0.23622 INCH 6 MMShell Thickness less Pipe Tolerance 12.5% (12.5% NA) 0.86614 INCH 22 MMShell Thickness less Corrosion Allowance & 12.5%, t (12.5% NA) 0.62992 INCH 16 MM

Nozzle Wall Nominal Thickness 0.562 INCH 14.2748 MMNozzle Wall Thickness less Pipe Tolerance 12.5% 0.49175 INCH 12.49045 MMNozzle Corrosion Allowance, Can 0.23622 INCH 6 MMNozzle Wall Thick. less Corr. Allowance & 12.5% , tn 0.25553 INCH 6.49045 MMNozzle Wall Thick.of Internal Projection (less Corr. Allowance & 12.5%), ti 0.25553 INCH 6.49045 MMReinforced Pad Thickness, te 0.86614 INCH 22 MMJoint Efficiency of Shell, E 1Joint Efficiency of Nozzle, En 1Correction Factor, F [UG-37(a)] 1E1 [Nozzle in solid plate] 1Shell Outside Diameter, OD 62.9921 INCH 1600 MMShell Inside Diameter in Corroded Condition, 2R = OD - 2 t 61.7323 INCH 1568 MMShell Inside Radius in Corroded Condition, R 30.8661 INCH 784 MM

Nozzle Outside Diameter, OD 24 INCH 609.6 MMNozzle Inside Diameter, ID 22.876 INCH 581.0504 MMNozzle 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 MMNozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 23.4889 INCH 596.6191 MMFinished Radius of Circular Opening, Rn 11.7445 INCH 298.3096 MM



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


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 MMBy 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




M2. Nozzle Mark : N8 24" Sch. 30, 300# WNRF Manhole (cont.)Min. Nozzle Neck Wall Thickness Check Per UG-45




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







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








Total Area Available, AT : AT = A1 + A2 + A41 + A42 + A43 + A5 24.3029 INCH2 15679.26 MM2





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 DNNozzle Material ASME SA 106 Grade B

Design Pressure, P 259.166 PSIG 18.24529 Kg/CM2GDesign Temperature 149 oF 65 oCFor nominated Design Pressure & Temperature, Flange Rating #VALUE! [ANSI/ASME B16.5-1996]


Outside Radius of Nozzle, Ron 10 INCH 254 MMJoint Efficiency of Nozzle, En (Seamless Pipe) 1Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM




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





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 DNNozzle Pipe Sch. 30Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2GDesign Temparture 149 oF 65 oC




Nozzle Outside Diameter, OD 20 INCH 508 MMNozzle Inside Diameter, ID 19 INCH 482.6 MMNozzle 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 MMNozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 19.5974 INCH 497.775 MMFinished Radius of Circular Opening, Rn 9.79872 INCH 248.8875 MM



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


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 MMBy 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





M3. Nozzle Mark : Leg 20" Sch. 30 (located at shell) (cont.)Min. Nozzle Neck Wall Thickness Check Per UG-45




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







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








Total Area Available, AT : AT = A1 + A2 + A41 + A42 + A43 + A5 20.3409 INCH2 13123.12 MM2





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 DNNozzle Material ASME SA 106 Grade B

Design Pressure, P 257.898 PSIG 18.156 Kg/CM2GDesign Temperature 149 oF 65 oCFor nominated Design Pressure & Temperature, Flange Rating 300# [ANSI/ASME B16.5-1996]


Outside Radius of Nozzle, Ron 4.3125 INCH 109.5375 MMJoint Efficiency of Nozzle, En (Seamless Pipe) 1Nozzle Corrosion Allowance, Can 0.23622 INCH 6 MM




Use Nozzle 8" NPS with Selected Neck Sch. 80, 0.5 INCH 12.7 MMwith Thickness 0.5" ( 12.7 MM ). [Table 2 of ANSI B 36.10M-1985-(R-1994)]



DESIGN CALCULATIONS OF PRESSURE VESSEL Page : 32 of 126According to ASME Code, Section VIII, Division 1, Edition 2001, Addenda 2002 Sheet : 2 of 5Designed by : Eng. Abdel Halim Galala, Design General Manager (assist.) Date : 18.2.2004

Project : Design & Procurement of ASME Pressure Vessel Client : APRCJob Name : Demineralization Plant Job No. : 7434-33 Serial No. : 7434-33-U-2006 Dwg. No. : 7434-33-3A, Rev. 1 Client : APRCVessel : 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 DNNozzle Pipe Sch. 80Design Pressure, P 257.898 PSIG 18.15602 Kg/CM2GDesign Temparture 149 oF 65 oC




Nozzle Outside Diameter, OD 8.625 INCH 219.075 MMNozzle Inside Diameter, ID 7.625 INCH 193.675 MMNozzle 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 MMNozzle ID Without Corrosion Allowance & 12.5% , d = OD - 2*tn 8.22244 INCH 208.85 MMFinished Radius of Circular Opening, Rn 4.11122 INCH 104.425 MM



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


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 MMBy 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





M4. Nozzle Mark : N1 8" 300# WNRF (located at shell) (cont.)Min. Nozzle Neck Wall Thickness Check Per UG-45


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)(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






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

26. Pressure_vessel_design_calcula by Abdel Halim Galala

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Transcript of 26. Pressure_vessel_design_calcula by Abdel Halim Galala