Mechanical Design Calculations of Pressure Vessel - Sample

8/17/2019 Mechanical Design Calculations of Pressure Vessel - Sample

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EQP. TAG No. : ------- DESIGN REF No - -------- SHEET No. : 1 of 35

MSN : -

VENVEL THERMAL & MECHANICAL

DESIGNERSNAMAKKAL, TAMILNADU, INDIA.

Mai l : sakth ive l@venve ldes igners .com

Website : www.venve ldes igners .com

Mob :+91 9965764325

MECHANICAL DESIGN

CALCULATION REPORT – 500 Lit PROJECT -

EQUIPMENT NAME CATCH POT

CLIENT ------------

PO NO -

REFERENCE DATA SHEET NO Mail

CODE OF CONSTRUCTION ASME SECTION VIII DIV 1, EDITION 2013

EQUIPMENT TAG NO. --------------

MFR’S SERIAL NUMBER -

Job No -

0 21/11/15 First Issue

REV

NO

DATE DESCRIPTION OF REVISION PREPARED

AND APPROVED BY

DESIGN ENGINEER

REVIEWED

BY

CUSTOMER

COVER PAGEREV No. : 0

DATED : 21/11/15


2/27


MSN : -

SR.

No.DESCRIPTION

SHEET

NO.

REVISION No.

0 1 2 31.

COVER PAGE 1 21/11/15

2.

INDEX 2 21/11/15

3.

DRAWING DETAILS AND VESSEL SUMMARY 3 21/11/15

4.

APPLICABLE CODES / STANDARDS & UOM 4 21/11/15

5.

DESIGN DATA 5 21/11/15

6.

CALCULATION FOR INTERNAL VOLUME 6 21/11/15

7.

LOADING AS PER UG – 22 7 21/11/15

8.

EVALUTION OF MATERIALS 8 21/11/15

9.

EVALUTION OF DESIGN PRESSURE 9 21/11/15

10.

HYDROSTATIC TEST PRESSURE UG -99 10 21/11/15

11.

REQUIREMENT OF INSPECTION OPENING UG -46 11 21/11/15

12.

REQUIREMENT OF DRAIN – UG – 25 11 21/11/15

13.

OVERPRESSURE PROTECTION – UG – 125 12 21/11/15

14.

RADIOGRAPHY & JOINT EFFICIENCY 12-13 21/11/15

15.

PERMISSABLE OUT OF ROUNDNESS OF SHELL – UG 80(a) 14 21/11/15

16.

SHELL – UG – 27 15–16 21/11/15

17. DISHED END UG – 32 17-18 21/11/15

18.

REQUIREMENT OF UG-79 & UCS – 79 19 21/11/15

19. NOZZLE NECK - (N1, N2 ) AS PER UG – 45, UG – 36 20 21/11/15

20.

NOZZLE NECK - (N3,N6) AS PER UG – 45, UG – 36 21 21/11/15

21.

NOZZLE NECK - (N4,N5) AS PER UG – 45, UG – 36 22 21/11/15

22.

EVALUTION OF LARGE OPENINGS – UG – 36 23 21/11/15

23. CHECK FOR MULTIPLE OPENINGS – UG – 42 24 21/11/15

24. IMPACT TEST REQUIREMENTS – UG – 20(f),UHA-51 (d) (1)) 25 21/11/15

25.

FLANGE RATING CALCULATIONS AS PER UG-44 & B16.5 26 21/11/15

26.

PWHT REQUIREMENTS - UHA-32 27 21/11/15 27.

WIND AND SEISMIC LOAD CALCULATIONS 28-29 21/11/15

28.

SKIRT SUPPORT AND BASE PLATE DESIGN 30-33 21/11/15

29.

LIFTING LUG DESIGN 34-35 21/11/15

INDEXREV No. : 0

DATED : 21/11/15


3/27


MSN : -

DRAWINGS

SR.

NO.

DESCRIPTION DRAWING No.REVISION No.

0 1 2 3

1GENERAL ARRANGEMENT AND

DETAILED DRAWING FOR CATCH POT

VFE/UAR /003

Sheet 1 of 221/11/15

2 DISH END DRAWING FOR CATCH POTVFE/UAR /003

Sheet 2 of 221/11/15

VESSEL SUMMARY

NOZZLE SCHDULE

DRAWINGS

AND VESSEL SUMMARY REV No. : 0

DATED : 21/11/15

S.No Part Name Inside Diameter Min.Thickness Cal. / Nominal

1 Shell 700 mm 4.601 mm / 6 mm

2 Dish Ends 700 mm4.571 mm / 6 mm

( 4.75 mm After forming)

Sr.NoNozzle

No.Size

Schedule (WT

in mm)

RF Pad

Dimensio

n

Nozzle Rating

/ Flange Type

SERVICE

Orientation of

Nozzle

(Deg)

1 N1 DN 80 SCH 80 / 7.62 N.A150# / B16.5

SORFINLET

LHS of TOP

DISH END

2 N2 DN 80 SCH 80 / 7.62 N.A150# / B16.5

SORFOUTLET

RHS of TOP

DISH END

3 N3 DN 25 SCH 160 / 6.35 N.A150# / B16.5

SORFDRAIN

Centre of

Bottom dish

end

4 N4 DN 50 SCH 80 / 7.14 N.A150# / B16.5

SORF

SIDE ENTRY

TOP /

INSPECTION

OPENING

Shell - Top

5 N5 DN 50 SCH 80 / 7.14 N.A 150# / B16.5SORF

SIDE ENTRY

BOTTOM /INSPECTION

OPENING

Shell -

Bottom

6 N6 DN 25 SCH 160 / 6.35 N.A150# / B16.5

SORF

PRV/PRESSURE

GAUGE

Centre of Top

dish end


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MSN : -

SR.

No.

CODES / STANDARDS/ REFERENCES YEAR / EDITION

1.

ASME BOILER & PRESSURE VESSEL CODE ,SECTION VIII DIV.1 EDITION 2013

2.

ASME BOILER & PRESSURE VESSEL CODE ,SECTION II PART A EDITION 2013 3.

ASME BOILER & PRESSURE VESSEL CODE ,SECTION II PART C EDITION 2013 4.

ASME BOILER & PRESSURE VESSEL CODE ,SECTION II PART D (Metric) EDITION 2013 5. STANDARD FOR WELDED AND SEAMLESS WROUGHT STEEL PIPE B36.10M 2004

6.

STANDARD FOR PIPE FLANGES AND STANDARD FITTINGS B16.5 2013

7.

CODE OF PRACTICE FOR DESIGN LOAD (WIND LOAD) IS 875 (Part 3) 1987

8.

CRITERIA FOR EARTHQUAKE RESISTANT (SEISMIC LOAD) IS 1893 (Part 1) 2002

9.

PRESSURE VESSEL DESIGN HANDBOOK BY H.H.BEDNER 2nd Edition 1991

10.

PRESSURE VESSEL DESIGN MANUAL BY DENNIS MOSS 2nd Edition 2004

Units of Measurement:

Parameter Unit used

Pressure MPa and Kg/cm2

Temperature Deg C

Length mm

Conversion calculations :

FROM APPENDIX GG TABLE OF ASME SEC.VIII Div.1 EDITION 2013.

1 lb= 0.4535924 kg

1lb / inch2 (Psi) = 0.4535924 / (2.54)ˆ2 = 0.4535924 / 6.452 = 0.07030260 kg / cm2

1 Psi= 0.0068948 MPa

0.0068948 MPa = 0.07030260 Kg/cm2

1MPa =0.070306963/0.0068948 = 10.196 kg / cm² (g)

APPLICABLE CODES / STANDARDS REV No. : 0

DATED : 21/11/15


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MSN : -

EQUIPMENT DESIGN DATA :

CONFIGURATION (TYPE) : VERTICAL

SERVICE ( LETHAL OR NON LETHEL) : NON – LETHAL

DESIGN AND MANUFACTURING CODE : ASME SECTION VIII DIV 1, EDITION 2013 INTERNAL DESIGN PRESSURE : 1.50 MPa (g) (Refer Sheet No : 9)

EXTERNAL DESIGN PRESSURE : N.A

MAXIMUM ALLOWABLE WORKING PRESSURE (MAWP) : 1.50 MPa (g) @ 65 Deg C

DESIGN TEMPERATURE (MAX) : 65 Deg C

DESIGN TEMPERATURE (MIN) : 10 Deg C

MINIMUM DESIGN METAL TEMPERATUE (MDMT) : 10 Deg C @ 1.50 MPa (g)

CORROSION ALLOWANCE : 0 mm (Shell / Dish / Nozzles)

RADIOGRAPHY : RT2 - AS PER UG 116 (e) (2),UW-11(a) & UW-11(a) 5 (b)

: LONG SEAM – FULL,UW-11(a)

TOP D’END CIRC SEAM – SPOT, UW-11(a) 5 (b)

BOTTOM D’END CIRC SEAM – SPOT, UW-11(a) 5 (b)

JOINT EFFICIENCY FOR SHELL (CIRC STRESS / LONG STRESS) : 1.00/ 0.70

FOR TOP HEAD

FOR BOTTOM HEAD

: 1.0

: 1.0

OPERATING PRESSURE (Min / Max) : 0.45 / 0.8 MPa(g)

OPERATING TEMPERATURE (Min / Max) : 10 / 45 Deg C

PROCESS FLUID : CONDENSATE

PROCESS FLUID DENSITY (MAX) : 1.1195 kg / m3

HIGHEST LIQUID LEVEL FROM BOTTOM : 1835 mm

CAPACITY : 0.5 m3 (Refer Sheet No : 6) ( ~ 500 Lit)

INSULATION/ FIRE PROOFING THK : N.A.mm

HYDROSTATIC TEST PRESSURE (AT TOP) VERTICAL POSITION: 1.95 (20) MPa (g) (kg/cm2 (g))

Do not exceed 25 Kg/cm2 (g) (Refer Sheet No : 10)

HYDROTEST TEMPERATURE (MIN/MAX) : 27 / 48 Deg C (Recommended)

PNEUMATIC TEST PRESSURE : N.A

POST WELD HEAT TREATMENT (PWHT) (Refer Sheet No : 28) : EXEMPTED (As per UHA-32)

IMPACT TEST(Refer Sheet No : 27) : EXEMPTED(AS PER UG – 20(f), UHA-51 (d) (1))

POST FORMING HEAT TREATMENT (SHELL /DISH ENDS): : NOT REQUIRED (Refer Sheet No : 19)

RATINGS OF FLANGES : ASME B16.5, 2013 Edition

ASME CERTIFICATION MARK : YES – WITH “U” DESIGNATION

NATIONAL BOARD REGISTRATION : NO

OVER PRESSURE PROTECTION : IN THE SCOPE OF CLIENT (PROVISION PROVIDED) – N6

(DN 25)

WIND AND SEISMIC LOADINGS Refer Sheet No: 7

WEIGHT DETAILS :

EMPTY WEIGHT(We ) : 284 kg

OPERATING WEIGHT(Wo ) : 284.6 kg

HYDRO TEST WEIGHT (Wh) : 784 kg

MATERIAL OF CONSTRUCTION :

SHELL / DISH END : SA 240 TP 316LNOZZLE PIPES : SA 312 TP 316L

NOZZLE FLANGES : SA 182 F 316L

SKIRT SUPPORT, LUG PLATE : SA 240 TP 304

BASE PLATE, NAME PLATE : SA 240 TP 304

NAME PLATE BRACKET : SA 240 TP 316L

DESIGN DATAREV No. : 0

DATED : 21/11/15


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MSN : -

Shell I.D. (Di)

Length T.L-T.L(l)

Type of Dished End

Dish Depth (h)

Dish End ID (Di)

= 700 mm

= 1070 mm

=Ellipsoidal(2:1)

= 175 mm

= 700 mm

= 0.700 m

= 1.070 m

= 0.175 m

= 0.700 m

Volume of shell

Vs = (π / 4)x(Di)²x l

= (3.14/4) x(0.700)²x 1.070

= 0.785 x 0.72 x 1.070

= 0.412 m³

Volume of Dished End

Vd = (π /24) x(Di3)

= ( 3.14 / 24)x(0.7)3

= 0.131 x 0.343= 0.045 m³

Total Internal Volume of Vessel

V = Vs + (2 x (Vd))

= 0.412 + (2 x 0.045)

= 0.412 + 0.09

= 0.502 m³ = 502 Lit ~ 500 Liter

CALCULATION FOR INTERNAL VOLUME REV No. : 0

DATED : 21/11/15


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MSN : -

SR NO APPLICABLE

CLAUSE

DESCRIPTION APPLICABLE

YES/NO

REMARKS

1 UG – 22(a) INTERNAL DESIGN PRESSURE YES -

EXTERNAL DESIGN PRESSURE NO -

2 UG – 22(b)

WEIGHT OF THE VESSEL AND NORMAL CONTENTS

UNDER OPERATING OR TEST CONDITIONS (THIS

INCLUDES ADDITIONAL PRESSURE DUE TO STATIC

HEAD OF LIQUIDS).

NO -

3 UG – 22(c)

SUPERMIPOSED STATIC REACTIONS FROM WEIGHT

OF ATTACHED EQUIPMENT, SUCH AS MOTORS,

MACHINERY, OTHER VESSELS, PIPING, LININGS,

AND INSULATION.

NO

-

4 UG – 22(d)

THE ATTACHMENT OF: -

INTERNALS NO -

VESSEL SUPPORTS, SUCH AS LUGS, RINGS, SKIRTS,

SADDLES, AND LEGS

YES SKIRT

5

UG – 22(e)

CYCLIC AND DYNAMIC REACTIONS DUE TO

PRESSURE OR THERMAL VARIATIONS, OR FROM

EQUIPMENT MOUNTED ON A VESSEL, AND

MECHANICAL LOADINGS

NO -

6

UG – 22(f)

WIND REACTIONS. YES -

SEISMIC REACTIONS. YES -

SNOW REACTIONS. NO -

7 UG – 22(g) IMPACT REACTIONS SUCH AS THOSE DUE TO

FLUID SHOCK.

NO -

8 UG – 22(h) TEMPERATURE GRADIENTS AND DIFFERENTIAL

THERMAL EXPANSION. NO -

9 UG – 22(i) ABNORMAL PRESSURES, SUCH AS THOSE CAUSED

BY DEFLAGRATION. NO -10 UG – 22(j) TEST PRESSURE AND COINCIDENT STATIC HEAD

ACTING DURING THE TEST

YES -

LOADINGS AS PER UG -22 REV No. : 0

DATED : 21/11/15


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MSN : -

Sr.

No ComponentType

Material SpecNo

Table

No

P.No /

GroupNo

Page No/

Line No inASME

Sec II – D

Design

Temp

° C

Allow

Stress atDesign

temp

(MPa)

Allow

Stress @Test

(27° C)

temp

(MPa)

Allow

Stress@ (10°)

(MPa)

Max.

Temp.Limits

° C

Specified

Cautionary Notes

Applicability

of Notes

1. SHELL SA 240 TP 316L 1A 8 / 1 74/10 65 115 115 115 454 G5,G21 None

2. DISH ENDS SA 240 TP 316L 1A 8 / 1 74/10 65 115 115 115 454 G5,G21 None3. NOZZLE

PIPESSA 312 TP 316L 1A 8 / 1 74/15 65 115 115 115 454 G5,G21,W12,W14 None

3. NOZZLEFLANGES

SA 182 F 316L 1A 8 / 1 74/01 65 115 115 115 454 G5,G21 None

4 WEAR PLATES SA 240 TP 316L 1A 8 / 1 74/10 65 115 115 115 454 G5,G21 None5. SKIRT

SUPPORT,

LIFTING LUG,

BASE PLATE

SA 240 TP 304 1A 1 / 1 94/07 65 126 138 138 816 G12,T8 None

EVALUATION OF MATERIALS REV No. : 0

DATED : 21/11/15


9/27


MSN : -

P’ : MAXIMUM ALLOWABLE WORKING PRESSURE (GIVEN BY CLIENT)

P : INTERNAL DESIGN PRESSURE

Di : INTERNAL DIAMETER OF SHELL

Ls : T.L. TO T.L. LENGTH

HLL : HEIGHEST LIQUID LEVEL FROM BOTTOM

(INCLUDING TOLERANCE) ( 2170 + 5 )

TYPE OF DISHED END

Di : INSIDE DIAMETER OF DISHED END

hi : INSIDE DEPTH OF HEAD = Di / 4 = 700 / 4

ρ : DENSITY OF FLUID

: 1.50 MPa (g)

: MAWP + Pressure due to static head

: 700 mm

: 1070 mm

: 1835 mm

: 2:1 Ellipsoidal

: 700 mm

: 175 mm

: 1.1195 kg/m3

DESIGN PRESSURE TABLE FOR DIFFERENT PARTS OF AIR RECEIVER

SR.No. PART P’

(MPa g)

H

(mm)

Ph

= H X ρ X9.8067x 10^-6

1000

(MPa g)

P= P’+Ph

(MPa g)

1 NOZZLE N4

(AT TOP) 1.50 1835 19.76

x 10^-6 *

(Negligible )

1.50

PRESSURE INCLUDING THE HEAD IS NEGLIGIABLE. HENCE, IT IS NOT CONSIDERED.

*Ph = (1835 x 1.1195 x 9.8067 x 10^-6) / 1000

P = P’ + Ph = 1.50 + 0.00001976 = 1.50001976 MPa (g)

Rounded to = 1.5 MPa (g)

WHERE,

H : HEIGHT OF FLUID TO BE CONSIDERED FOR STATIC HEAD.

Ph : PRESSURE DUE TO STATIC HEAD OF FLUID.

P : INTERNAL DESIGN PRESSURE WITH STATIC HEAD TO BE CONSIERED IN PART DESIGN

CONCLUSION :- DESIGN PRESSURE SHALL BE THE HEIGHEST PRESSURE “P” CALCULATED FOR THE ABOVE PART,

LOCATED ON TOP OF THE VESSEL. AS THERE IS NO CHANGE IN THE INTERNAL DESIGN PRESSURE DURING THE

OPERATING CONDITION, INCLUDING STSTIC HEAD. THE “MAWP” IS CONSIDERED SAME AS INTERNAL DESIGN

PRESSURE.-

AS PER UG-99 END NOTE.36 , “THE MAXIMUM ALLOWABLE WORKING PRESSURE MAY BE ASSUMED TO BE

THE SAME AS THE DESIGN PRESSURE WHEN CALCULATIONS ARE NOT MADE TO DETERMINE THE

MAXIMUM ALLOWABLE WORKING PRESSURE”.

EVALAUATION OF DESIGN PRSSURE REV No. : 0

DATED : 21/11/15


10/27


MSN : -

Shop test pressure determination for vessel based on Design Pressure at top of vessel (P) and design Temperature (T) as per Clause No. UG-99(b).

P : Design Pressure (Top of vessel) =1.50 MPa (g)

Tc : Design Temperature = 65 Deg C

Sr. No. Description Design Pressure

P

(MPa (g))

Stress @ Test

Temp.

Sa (MPa)

Stress @ Design

Temp.

S (MPa)

Stress Ratio

Sa / S

1 SHELL 1.0 115 115 1.0

2 DISH END 1.0 115 115 1.0

3 PIPES 1.0 115 115 1.0

4 FLANGES 1.0 115 115 1.0

Stress Ratio =Sa / S = 138/138 = 1.00 (Taken Least Stress Ratio of Sr.No. 1 to 4)As per UG – 99 (b)

Loading in Bolting part : NOT APPLICABLE

-------------------------------------------------------------------------------------------------------------------------------------------------------------------------------

Hydrostatic Test Pressure = 1.3 x P x(Sa / S) = 1.3 x 1.50x (115 / 115) = 1.3 x 1.50 x 1.00 = 1.95 MPa (g)

------------------------------------------------------------------------------------------------------------------------------------------------------------------------------

FROM, Page No 4 of Units of Measurement and Conversion :

1.95 MPa g = 1.95 x 10.196 = 19.88 kg / cm² (g) ~ 20 kg/cm2(g)

AS PER UG-99 (h) BODY METAL TEMPERATURE DURING HYDRO TEST (RECOMMENTED) MAY BE

(17 + 10 (MDMT) ) = 27 DEG C MINIMUM, AND 48 DEG C MAXIMUM, AND ANY CASE NOT LESS THEN 10 Deg C.

AS PER UG-99 END NOTE.36 , “THE MAXIMUM ALLOWABLE WORKING PRESSURE MAY BE ASSUMED TO BE THE SAME

AS THE DESIGN PRESSURE WHEN CALCULATIONS ARE NOT MADE TO DETERMINE THE MAXIMUM ALLOWABLE

WORKING PRESSURE”.HENCE, HERE IN THIS CASE DESIGN PRESSURE AND MAWP ARE TAKEN SAME.

HYDROSTATIC TEST PRESSURE –UG-99(b) REV No. : 0

DATED : 21/11/15


11/27


MSN : -

Sr.No

Clause No EVALUTION OF CONDITIONS APPLICABILITY

1 UG-46(a) ALL PRESSURE VESSELS FOR USE WITH COMPRESSED AIR AND THOSE

SUBJECT TO INTERNAL CORROSION OR HAVING PARTS SUBJECTED TO

EROSION OR MECHANICAL ABRASION (SEE UG-25) EXCEPT AS PERMITTED

OTHERWISE IN THIS PARAGRAPH, SHALL BE PROVIDED WITH SUITABLE

MANHOLE, HANDHOLE, OR OTHER INSPECTION OPENINGS FOR

EXAMINATION AND CLEANING.

COMPRESSED AIR AS USED IN THIS PARAGRAPH IS NOT INTENDED TO

INCLUDE AIR WHICH HAS HAD MOISTURE REMOVED TO PROVIDE AN

ATMOSPHEIC DEW POINT OF – 46 Deg C OR LESS.

YES

2 UG-46(f)(2) AS PER ALL VESSELS 450 mm TO 900 mm, INCLUSIVE,I.D.SHALL HAVE A

MANHOLE OR AT LEAST TWO HANDHOLES OR TWO PLUGGED, THREADED

INSPECTION OPENINGS OF NOT LESS THAN DN 50.

YES

N4,N5 PROVIDED

WITH DN 50, DN 80SIZE

3 UG-46(f)(7) FLANGED AND/ OR THREADED CONNECTIONS FROM WHICH PIPING,

INSTRUMENTS, OR SIMILAR ATTACHMENTS CAN BE REMOVED MAY BE

USED IN PLACE OF THE REQUIRED INSPECTION OPENINGS PROVIDED THAT

(-a) THE CONNECTIONS ARE AT LEAST EQUAL TO THE SIZE OF THE

REQUIRED OPENINGS

(-b) THE CONNECTIONS ARE SIZED AND LOCATED TO AFFORD AT LEAST

AN EQUAL VIEW OF THE

INTEROR AS THE REQUIRED INSPECTION OPENING.

YES

LOCATION

IDENTIFIED AS

1.

TOP DISH

END –N5

2.

BOTTOM

SHELL – N4

CONCLUSION: AS PER UG-46(f)(2) , WE HAVE PROVIDED TWO NOZZLES OF SIZE DN 50 NOZZLE N4 AND DN 80 SIZE N5 AS

AN INSPECTION OPENING AS PER ABOVE CONDITIONS AND MEETS THE CODE REQUIREMENTS.

AS PER UG-25(f), VESSELS SUBJECT TO CORROSION SHALL BE SUPPLIED WITH A SUITABLE DRAIN OPENING AT THE

LOWEST POINT PRACTICABLE IN THE VESSEL.

NOZZLE “N3”(DN 25) IS PROVIDED AT THE BOTTOM MOST POINT OF THE VESSEL, FOR THIS PURPOSE.

REQUIREMENT OF INSPECTION OPENING –UG-46 REV No. : 0

DATED : 21/11/15

EQP. TAG No. : -- DESIGN REF No - - SHEET No. : 11 of 35

MSN : -REQUIREMENT OF DRAIN –UG-25

REV No. : 0

DATED : 21/11/15


12/27


MSN : -

AS PER UG-125(a) (4),

THE OVERPRESSURE PROTECTION SYSTEM NEED NOT BE SUPPLIED BY THE VESSEL MANUFACTURER.

ALSO, AS PER CLIENT REQUIREMENT –THE PROVISION FOR PRESSURE RELIEF DEVICE IS PROVIDED AS N6 (DN 25)

NOZZLE.

EVALUTION OF RADIOGRAPHY APPLICABILITY

(A) FULL RADIOGRAPHY. THE FOLLOWING WELDED JOINTS SHALL BE EXAMINED RADIO GRAPHY FOR

THEIR FULL LENGTH IN THE MANNER PRESCRIBED IN UW-51:

(1) ALL BUTT WELDS IN THE SHELL AND HEADS OF VESSELS USED TO CONTAIN LETHAL SUBSTANCES[SEE UW-2(A)]; NA

(2) ALL BUTT WELDS IN THE SHELL AND HEADS OF VESSELS IN WHICH THE NOMINAL THICKNESS

[SEE (G) BELOW]

AT THE WELDED JOINT EXCEEDS 11/2 IN. (38 MM), OR EXCEEDS THE LESSER THICK- NESSES PRESCRIBED IN

UCS-57, UNF-57, UHA-33, UCL-35, OR UCL-36 FOR THE MATERIALS COVERED THEREIN, OR AS OTHER-

WISE PRESCRIBED IN UHT-57, ULW-51, ULW-52(D), ULW-54,OR ULT-57;

NA

(3) ALL BUTT WELDS IN THE SHELL AND HEADS OF UNFIRED STEAM BOILERS HAVING DESIGN PRESSURES (-A)

EXCEEDING 50 PSI (350 KPA) [SEE UW-2(C)]; (-B) NOT EXCEEDING 50 PSI (350 KPA) [SEE UW-2(C)] BUT WITH

NOMINAL THICKNESS AT THE WELDED JOINT EXCEEDING THE THICKNESS SPECIFIED IN (2) ABOVE;

NA

(4) ALL BUTT WELDS IN NOZZLES, COMMUNICATING CHAMBERS, ETC., WITH THE NOMINAL THICKNESS AT

THE WELDED JOINT THAT EXCEEDS THE THICKNESS IN (2) ABOVE OR ATTACHED TO THE SHELL OR HEADS OF

VESSELS UNDER (1), (2),OR(3) ABOVE THAT ARE REQUIRED TO BE FULLY RADIO GRAPHED; HOWEVER, EXCEPT

AS REQUIRED BY UHT-57(A),CATEGORIES BAND C BUTT WELDS IN NOZZLES AND COMMUNICATING

CHAMBERS THAT NEITHER EXCEED NPS 10 (DN 250) NOR 11/8 IN. (29 MM) WALL THICKNESS DO NOT REQUIREANY RADIOGRAPHIC EXAMINATION;

NA

(5) ALL CATEGORY A AND D BUTT WELDS IN THE SHELL AND HEADS OF VESSELS WHERE THE DESIGN OF THE

JOINT OR PART IS BASED ON A JOINT EFFICIENCY PERMITTED BY UW-12(a),IN WHICH CASE:

(-a) CATEGORY A AND B WELDS CONNECTING THE SHELL OR HEADS OF VESSELS SHALL BE OF TYPE NO. (1)

OR TYPE NO. (2) OF TABLE UW-12;

(-b) CATEGORY B OR C BUTT WELDS [BUT NOT INCLUDING THOSE IN NOZZLES AND COMMUNICATING

CHAMBERS EXCEPT AS REQUIRED IN (4) ABOVE] WHICH INTERSECT THE CATEGORY A BUTT WELDS IN

THE SHELL OR HEADS OF VESSELS OR CONNECT SEAMLESS VESSEL SHELL OR HEADS SHALL, AS A

MINIMUM, MEET THE REQUIREMENTS FOR SPOT RADIOGRAPHY IN ACCORDANCE WITH

UW-52.SPOT RADIOGRAPHY REQUIRED BY THIS PARAGRAPH SHALL NOT BE USED TO SATISFY THE SPOT

RADIOGRAPHY RULES AS APPLIED TO ANY OTHER WELD INCREMENT.

APPLICABLE

APPLICABLE

(6) ALL BUTT WELDS JOINED BY ELECTRO GAS WELDING WITH ANY SINGLE PASS GREATER THAN 11/2 IN.

(38 MM) AND ALL BUTT WELDS JOINED BY ELECTRO SLAG WELDING;

NA

(7) ULTRASONIC EXAMINATION IN ACCORDANCE WITH UW-53 MAY BE SUBSTITUTED FOR RADIOGRAPHY

FOR THE FINAL CLOSURE SEAM OF A PRESSURE VESSEL IF THE CONSTRUCTION OF THE VESSEL DOES NOT

PERMIT INTERPRETABLE RADIOGRAPHS IN ACCORDANCE WITH CODE REQUIREMENTS. THE ABSENCE OF

SUITABLE RADIO- GRAPHIC EQUIPMENT SHALL NOT BE JUSTIFICATION FOR SUCH SUBSTITUTION.

NA

OVER PRESSURE PROTECTION –UG – 125 REV No. : 0

DATED : 21/11/15

EQP. TAG No. : --- DESIGN REF No - ---- SHEET No. : 12 of 35

MSN : -EVALUTION OF RADIOGRAPHY REQUIREMENTS

REV No. : 0

DATED : 21/11/15


13/27


MSN : -

AS PER CLIENT REQUIREMENT JOINT EFFICIENCY IS 1.0, HENCE FOR CATEGORY- A OF SHELL LONG SEAM WELD

CONSIDERED FULL RADIOGRAPHY AND FOR HEAD TO SHELL CATEGORY- B WELD JOINT THE SPOT RADIOGRAPHY

AS PER REQUIREMENT OF UW-11 (a) (5) (b) IS CONSIDERED.

BASED ON ABOVE CONDITION VESSEL SHALL BE MARKED WITH RT-2 AS PER UG-116 (e) (2).

AS PER UW-12 (b): JOINT EFFICIENCY

SR. NO. JOINT

CATEGORY

JOINT

TYPE

DESCRIPTION RT REQ. JOINT EFFICIENCY

1 A 1 SHELL LONG SEAMS

(Circumferential Stress / Longitudinal Stress)

FULL 1/0.70

2 B 1 SHELL TO DISHED END C / S JOINT - TOP SPOT* 1 (U -12(d))

3 B 1 SHELL TO DISHED END C / S JOINT -

BOTTOM

SPOT* 1 (U -12(d))

5 D 1 NOZZLE NECK TO

SHELL/ DISH JOINT

NIL N.A.

* AS PER UW- 11 (a) (5) (b) CATEGORY B OR C BUTT WELDS [BUT NOT INCLUDING THOSE IN NOZZLES AND

COMMUNICATING CHAMBERS EXCEPT AS REQUIRED IN (4) ABOVE] WHICH INTERSECT THE CATEGORY A BUTT

WELDS IN THE SHELL OR HEADS OF VESSELS OR CONNECT SEAMLESS VESSEL SHELL OR HEADS SHALL, AS A

MINIMUM, MEET THE REQUIREMENTS FOR SPOT RADIOGRAPHY IN ACCORDANCE WITH

UW- 52.SPOTRADIOGRAPHSREQUIREDBYTHISPARAGRAPHSHALL NOT BE USED TO SATISFY THE SPOT RADIOGRAPHY

RULES AS APPLIED TO ANY OTHER WELD INCREMENT.

RADIOGRAPHY & JOINT EFFICIENCY REV No. : 0

DATED : 21/11/15


14/27


MSN : -

UG-80(a)(1)

THE DIFFERENCE BETWEEN THE MAXIMUM AND MINIMUM INSIDE DIAMETERS OF THE SHELL AT ANY

CROSS SECTION SHALL NOT EXCEED 1% OF THE NOMINAL DIAMETERS OF THE SHELL AT THE CROSS

SECTION UNDER CONSIDERATION.

D : NOMINAL INSIDE DIAMETER OF THE SHELL = 700 mm

Diff 1 : 0.01 X D = (0.01 X 700) = 7.00 mm

UG-80(a)(2)

THE DIFFERENCE BETWEEN THE MAXIMUM AND MINIMUM INSIDE DIAMETERS OF THE SHELL AT THE

CENTER OF THE OPENING. SHALL BE INCREASED BY 2 % OF THE INSIDE DIAMETER OF THE OPENING.

PERMISSIBLE DIFFERENCE IN THE INSIDE DIAMETER FOR, (From Sheet No : 20 to 24)

NOZZLE N1 : Diff 1+ 0.02 x d = 7.0 + (0.02 x75.56) = 7.0 + 1.51 = 8.51 mmNOZZLE N2 : Diff 1+ 0.02 x d = 7.0 + (0.02 x75.56) = 7.0 + 1.51 = 8.51 mm

NOZZLE N3 : Diff 1+ 0.02 x d = 7.0 + (0.02 x22.29) = 7.0 + 0.446 = 7.446 mm

NOZZLE N4 : Diff 1+ 0.02 x d = 7.0 + (0.02 x 47.804) = 7.0 + 0.96 = 7.96 mm



WHERE ,”d” IS INSIDE DIAMETER OF NOZZLE.

UG-81 (a):

THE INNER SURFACE OF A TORISPHERICAL, TORICONICAL, HEMISPHERICAL, OR ELLIPSOIDAL HEAD SHALL NOT

DEVIATE OUTSIDE OF THE SPECIFIED SHAPE BY MORE THAN 1 ¼ % OF D, NOR INSIDE THE SPECIFIED SHAPE BY MORE

THAN 5/8 % OF D, WHERE D IS THE NOMINAL INSIDE DIAMETER OF THE VESSEL SHELL AT POINT OF ATTACHMENT.

SUCH DEVIATIONS SHALL BE MEASURED PERPENDICULAR TO THE SPECIFIED SHAPE AND SHALL NOT BE ABRUPT.

THE KNUCKLE RADIUS SHALL NOT BE LESS THAN THAT SPECIFIED.

IN OUR CASE, OVER CROWNING IS 8.75 mm, HOWEVER LIMITED TO 8 mm.

UNDER CROWING IS 4.38 mm, HOWEVER LIMITED TO 4 mm

UG-81 (d):

THE SKIRTS OF HEADS SHALL BE SUFFICIENTLY TRUE TO ROUND SO THAT THE DIFFERENCE BETWEEN THEMAXIMUM AND MINIMUM INSIDE DIAMETERS SHALL NOT EXCEED 1% OF THE NOMINAL DIAMETER.

NOMINAL INSIDE DIAMETER OF THE VESSEL (D) = 700 mm.

Diff 1 : 0.01 X D = (0.01 X 700) = 7.00 mm

ALLOWABLE OUT OF ROUNDNESS FOR SKIRT PORTION OF DISH END = 7.00 mm.

PERMISSIBLE OUT-OF-ROUNDNESS OF SHELL

AS PER UG-80(a) REV No. : 0

DATED : 21/11/15

EQP. TAG No. :---- DESIGN REF No - ---- SHEET No. : 14 of 35

MSN : - TOLERANCE FOR FORMED HEADS – UG-81 (a) & (d) REV No. : 0

DATED : 21/11/15


15/27


MSN : -

MATERIAL : SA 240 TP 316L

P :INTERNAL DESIGN PRESSURE : 1.50 MPa (g)

Tc :DESIGN TEMPERATURE : 65 Deg C

C :CORROSION ALLOWANCE : 0 mm

Di :INSIDE DIAMETER OF SHELL : 700 mm

Tol :PERMISSABLE TOLERANCE FOR INSIDE DIAMETER OF SHELL : + / - 5 mm

Ri :INSIDE RADIUS OF SHELL IN CORRODED CONDITION

((Di/2)+C) = ((700/2) +0) = 350 : 350 mm

ts : ASSUMED THICKNESS OF SHELL : 6 mm

S : MAXIMUM ALLOWABLE STRESS VALUE AT DESIGN TEMP. : 115 MPa (g)

(AS PER ASME SEC.II PART.D)

El :JOINT EFFICIENCY FACTOR FOR CIRCUMFERENTIAL STRESS : 1.00

Ec :JOINT EFFICIENCY FACTOR FOR LONGITUDINAL STRESS : 0.70

NOMINAL CASE

UG-27(c) (1)

t cal 1 : MINIMUM REQUIRED THICKNESS OF CYLINDRICAL SHELL CIRCUMFERENTIAL STRESS

(Ri / 2) > ( ts- C)

(350 / 2 ) > (6 –0) 175 mm > 6 mm OK

(0.385 x S x El ) > P

(0.385 x 115 x 1) > 1.50 43.7 MPa g > 1.50 MPa g OK

AS ABOVE TWO CONDITIONS ARE SATISFY FOLLOWING FORMULA SHALL APPLY.

t cal 1 = [(P x Ri) / ((S x El) – (0.6 x P))]+ C

= [(1.50 x 350 )/((115 x 1.00)-(0.6 x 1.50))] + 0

= [525 / (115-0.9)] + 0 = [525 /114.1] + 0 = 4.601 + 0 : 4.601 mm

UG-27(c) (2)

t cal 1 : MINIMUM REQUIRED THICKNESS OF CYLINDRICAL SHELL LONGITUDINAL STRESS

(Ri / 2) > ( ts- C)

(350 / 2 ) > (6-0) 175 mm > 6 mm OK

(1.25 x S x Ec )> P

(1.25 x 115 x 0.70) > 1.50 100.625 MPa g > 1.50 MPa g OK

AS ABOVE TWO CONDITIONS ARE STATISFY FOLLOWING FORMULA SHALL APPLY.

t cal 1 = [(P x Ri) / ((2 x S x Ec) +(0.4x P))]+ C

= [(1.50 x 350 )/((2 x 115 x 0.70)+(0.4 x 1.50))] + 0

= [525 / (161 + 0.6)] + 0 = [525 / 161.6] + 0 = 3.249 + 0 : 3.249 mm

GOVERNING THICKNESS GREATER OF UG-27 (c) 1 & UG-27 (c) 2

= GREATER OF (4.601, 3.249) : 4.601 mm ------------------ (1)

SHELL – UG -27 REV No. : 0

DATED : 21/11/15


16/27


MSN : -

UG-16 (b) (4)

t min : MINIMUM REQUIRED THICKNESS OF CYLINDRICAL SHELL : 2.50 mm ----------------- (2)

FOR COMPRESSED AIR SERVICE + C = 2.5 + 0

tr : MINIMUM REQUIRED THICKNESS OF CYLINDRICAL SHELL : 4.601 mm

GREATER OF (1) & (2) = Greater of ( 4.601, 2.50) = 4.601

td : DESIGN THICKNESS OF SHELL WITH CORROSION ALLOWANCE : 4.601 mm

ts : PROVIDED SHELL THICKNESS* : 6.00 mm

* Mill under tolerance as per UG-16 (c) ( smaller of 0.25 mm or 6 % of the order thickness )

= Smaller (0.25, 0.36) : 0.25 mm

PROVIDED THICKNESS = 6 mm - 0.25 mm = 5.75 mm , 5.75 (Provided) > 4.601 mm (Required) (Inclusive of corrosion allowance )

AS REQUIRED THICKNESS IS LESS THEN NOMINAL THICKNESS, PLATE SUPPLIED WITH ABOVE UNDER TOLERANCE MAY BE

ACCEPTED AND CAN BE USED AT RATED MAWP.

SHELL – UG -27 REV No. : 0

DATED : 21/11/15


17/27


MSN : -

MATERIAL : SA 240 TP 316L

TYPE OF DISHED END : 2:1 Ellipsoidal

P : INTERNAL DESIGN PRESSURE : 1.50 MPa (g)

Tc : DESIGN TEMPERATURE : 65 Deg C

C : CORROSION ALLOWANCE : 0 mm

D’ : INSIDE DIAMETER OF DISHED END SKIRT : 700 mm

h : DEPTH OF THE DISH END : 250 mm

L' : INSIDE CROWN RADIUS,D / 2h = 700 / (2 x 175) = 700/ 350 = 2,

(FROM TABLE UG -37)K1 = 0.9 =: 0.9 x 700 : 630 mm

L : INSIDE CROWN RADIUS CORRODED CONDITION=(L'+C) : 630 mm (For t/L calculations)

S.F : STRAIGHT FACE OF DISHED END : 40 mm

D : INSIDE DIAMETER OF DISHED END SKIRT (CORRODED CONDITION)

[700 + (0 x2)] = [700 + 0] : 700 mm

tnom : ASSUMED NOMINAL DISH THICKNESS BEFORE FORMING (BLANK) : 6 mm

x : FORMING THICKNESS TOLERANCE (THINING ) : 1 mm

ts : ASSUMED DISH THICKNESS AFTER FORMING = ( tnom – x ) = (6 - 1) : 5 mm

S : MAXIMUM ALLOWABLE STRESS VALUE AT DESIGN TEMP : 115 MPa (g)

(AS PER ASME SEC.II PART –D)

E : JOINT EFFIRNCY FACTOR FOR CIRCUMFERENTIAL STRESS : 1

(SHELL TO DISH END JOINT)

As per UG – 32 (d)

(ts-C)/L=(6 )/630: 0.009 > 0.002

AS(ts-C)/L>=0.002,THE RULES OF 1-4(f) SHALL NOT REQUIRED OK

t req1 : MINIMUM REQUIRED THICKNESS OF HEAD AFTER FORMING

[(P x D ) / ((2 x S x El)–(0.2 x P))] +C

= [(1.50 x 700)/((2 x 115 x 1) – (0.2 x 1.50))]+ 0

= [ 1050 / (230 – 0.3)] +0 = [1050 / 229.7] + 0 = 4.571 + 0 : 4.571 mm

UG-16(b)(4)

t req2 : MINIMUM REQUIRED THICKNESS OF DISHED END : 2.50 mm

FOR COMPRESSED AIR SERVICE + C = 2.50 + 0

treq , : MINIMUM REQUIRED THICKNESS OF DISHED END AFTER FORMING : 4.571 mm

MAXIMUM OF(t req1,treq2) = MAXIMUM (4.571,2.50)

DISHED END –UG -32 REV No. : 0

DATED : 21/11/15


18/27


MSN : -

td : MINIMUM DESIGN THICKNESS OF DISHED END AFTER FORMING

Max (4.571 , 2.5) : 4.571 mm

th : PROVIDED DISHED END NOMINAL THICKNESS* : 6.0 mm

* Mill Under tolerance as per UG-16( c ) : 0.25 mm

(Smaller of 0.25mm or 6% of the order thickness = Smaller ( 0.25, 0.36) )

NOMINAL THICKNESS OF PLATE IN UNDER TOLARANCE COND ITION = 6 – 0.25 : 5.75 mm (4.75 mm After forming)

Ts: MINIMUM SPECIFIED THICKNESS OF DISHED END AFTER FORMING : 4.571 mm

4.75 > 4.571 (Inclusive of corrosion allowance) ACCEPTABLE *

* Note : After forming actual thickness shall be inspected before use.

CHECK FOR SKIRT LENGTH OF DISHED END AS PER UG-32(l) & UW-13.

AS PER UG-32(l), WHEN THE THICKNESS OF THE HEAD IS EQUAL TO OR LESS THAN THE THICKNESS OF THE SHELL,NEED NOT

HAVE AN INTEGRAL SKIRT. BUT WE HAVE PROVIDED 40 MM SKIRT WHEN SKIRT IS PROVIDED,ITS THICKNESS SHALL BE AT

LEAST THAT REQUIRED FOR A SEAMLESS SHELL OF THE SAME INSIDE DIAMETER

D : SKIRT INSIDE DIAMETER CORRODED CONDITION : 700 mm

R : SKIRT INSIDE RADIUS CORODDED CONDITION =D/2 = 700/2 : 350 mm

E : SEAMLESS SHELL : 1 -

REQUIRED SKIRT THICKNESS AS PER UG-27( c)(1)

Trsk : [(P xR)/((S x E) –(0.6 x P))] +C

= [(1.50 x 350 )/((115 x 1.00)-(0.6 x 1.50))] + 0

= [525 / (115-0.9)] + 0 = [525 /114.1] + 0 = 4.601 + 0 : 4.601 mm

PROVIDED MINIMUM SKIRT THICKNESS FOR DISHED END : 6.00 mm

OK

DISHED END –UG -32 REV No. : 0

DATED : 21/11/15


19/27


MSN : -

FORMING PRESSURE PARTS : .

UCS- 79 (d): VESSEL SHELL SECTIONS, HEADS, AND OTHER PRESSURE BOUNDARY PARTS OF CARBON AND

LOW ALLOY STEEL PLATES FABRICATED BY COLD FORMING SHALL BE HEAT TREATED

SUBSEQUENTLY WHEN THE RESULTING EXTREME FIBER ELONGATION IS MORE THAN 5%

FROM THE AS-ROLLED CONDITION.

CYLINDRICAL SHELL AND PIPE:

-

% EXTREME FIBER ELONGATION FOR SHELL = [((50 x t)/Rf) x (1-(Rf/Ro))] = [((50x6)/353) x (1-(353/INFINITY))]

- PLATE THICKNESS TO BE VERIFIED WITH ACTUAL PLATE THICKNESS.

PART MATERIAL THICKNESS

NOMINAL

t(mm)

OD AFTER

FORMING

mm

FINAL C/L

RADIUS

(Rf) mm

ORIGINAL

C/L RADIUS

(Ro) mm

EXTREME

FIBRE

ELONGATION

%

S.R. REQD

(YES /No)

SHELL SA 240

TP316L

6 712 = 350 + (6/2)

=350+3= 353

INFINITY 0.85% No

SINCE EXTREME FIBRE ELONGATION IS LESS THEN 5%. STRESS RELEIVING MAY NOT REQUIRED.

DISHED END: (TOP and BOTTOM)

Rf :INSIDE KNUCKLE RADIUS (Approximately- For Fibre Elongation)= 0.17 x 700: 119 mm

UCS-79 (d) VESSEL SHELL SECTIONS, HEADS, AND OTHER PRESSURE BOUNDARY PARTS OF CARBON) AND LOW ALLOY

STEEL PLATES FABRICATED BY COLD FORMING SHALL BE HEAT TREATED SUBSEQUENTLY (UCS – 56), WHEN THE

RESULTING EXTREME FIBER ELONGATION IS MORE THEN 5% FROM THE AS – ROLLED CONDITION.

% EXTREME FIBER ELONGATION FOR DISHED END =[((75xt)/Rf)x(1-(Rf/Ro))]=[((75x 6)/122) x(1-(122/INFINITY)

= 4.88%

-

PLATE THICKNESS TO BE VERIFIED WITH ACTUAL PLATE THICKNESS.

PART MATERIAL THICKNESS

NOMINAL

t(mm)

OD AFTER

FORMING

mm

FINAL C/L

RADIUS (Rf)

(Kr) mm

ORIGINAL

C/L RADIUS

(Ro) (Cr) mm

EXT.FIB

ELONG %

S.R. REQD

(YES /No)

DISHED

END

SA 240

TP316L

6 712 = (119 + 6/2)

= (119 + 3)

= 122

INFINITY 4.018% No

SINCE EXTREME FIBRE ELONGATION IS LESS THEN 5%. STRESS RELEIVING MAY NOT REQUIRED.

REQUIREMENT OF – UG-79 REV No. : 0

DATED : 21/11/15


20/27


MSN : -

SUB CLAUSE NOZZLE MARK :N1,N2

NOZZLE

LOCATION: ON DISH

UG-45 IS NOZZLE TYPE = ACCESS OPENING OR USED ONLY FOR INSPECTION NO

INTERNAL DESIGN PRESSURE P MPa (g) 1.5

EXTERNAL DESIGN PRESSURE Pe MPa NOT APPLICABLE

N O Z Z L E P A R A M E T E R S

MATERIAL DESIGNATION SA 312 TP316L

MAXIMUM ALLOWABLE STRESS S MPa 115.00

OUTSIDE DIAMETER OF PIPE Do mm 88.9

OUTSIDE RADIUS OF PIPE = Do / 2 = 88.9 / 2 Ro mm 44.45

NOMINAL PIPE SIZE 3 “ NPS (DN 80)

CORROSION ALLOWANCE CA mm 0

LONGITUDINAL JOINT TYPE SEAMLESS

JOINT EFFICIENCY FOR NECK PIPE E 1.00

UG-27 (a) AS PER APPENDIX 1 – 1 (a)

t = P * Ro / ( S*E +0.4 * P) + CAa = 1.5 x 44.45 / ( 115.00 x 1.00 + 0.4 x 1.00 ) + 0 0.578

tb1

(a)

REQUIRED THICKNESS OF DISH (USING E =1) AT NOZZLE

LOCATION

(From Sheet No 17) = 4.571 + 0 = 4.571 mm

(b) MINIMUM REQUIRED THICKNESS FOR COMPRESSED AIR

APPLICATION AS PER UG (16)(b)(4) . = 2.5 + 0 = 2.5 mm

Max of (a,b) = Max (4.571, 2.5) = 4.571 mm

tb1 mm 4.571

tb2 THICKNESS REQUIRED FOR EXTERNAL PRESSURE tb2 mm 0.00

b3 THICKNESS REQUIRED AS PER TABLE UG-45 + CA = (4.80 + 0) b3 mm 4.80

UG -45b = Min (tb3, max (tb1,tb2) = Min ( 4.80, max (4.571, 0.00)

= Min (4.80, 4.571 )tb mm 4.80

GOVERNING THICKNESS GREATER OF (ta, tb)

= GREATER OF (0.578,4.80) tn mm 4.80

GOVERNING THICKNESS FOR ABOVE tn mm 4.80PROVIDED NOMINAL THICKNESS t mm 7.62

PIPE THICKNESS DURING UNDER TOLARENCE CASE = 7.62 x 0.875 = 6.668

AS REQUIRED THK. (4.80 mm)


21/27


MSN : -


NOZZLE

LOCATION: ON DISH









NOMINAL PIPE SIZE 3 “ NPS (DN 80)





t = P * Ro / ( S*E +0.4 * P) + CAa = 1.5 x 16.7 / ( 115.00 x 1.00 + 0.4 x 1.00 ) + 0 0.217

tb1

(a)


LOCATION

(From Sheet No 17) = 4.571 + 0 = 4.571 mm



Max of (a,b) = Max (4.571, 2.5) = 4.571 mm

tb1 mm 4.571




= Min ( 2.96, 4.571 )tb mm 2.96


= GREATER OF (0.217, 2.96) tn mm 2.96





22/27


MSN : -


NOZZLE

LOCATION: ON SHELL









NOMINAL PIPE SIZE 2“ NPS (DN 50)





t = P * Ro / ( S*E +0.4 * P) + CAa = 1.5 x 30.15 / ( 115.00 x 1.00 + 0.4 x 1.00 ) + 0 0.392

tb1

(a)


LOCATION

(From Sheet No 15) = 4.601 + 0 = 4.601 mm



Max of (a,b) = Max (4.601, 2.5) = 4.601 mm

tb1 mm 4.601




= Min (3.42, 4.601 )tb mm 3.42


= GREATER OF (0.392,3.42) tn mm 3.42





23/27


MSN : -

1. ALL OPENINGS ARE CIRCULAR IN SHAPE. HENCE REQUIREMENTS OF UG-36(a)(1)& (2) DO NOT APPLY

2.

CHECK FOR APPLCABLITY OF APPENDIX1-7 (LARGE OPENINGS),

AS PER UG-36(b)(1), FOR OPENINGS EXCEEDING BELOW LIMITS , SUPPLEMENTAL RULES OF 1-7 SHALL BE

SATISFIED IN ADDITION TO THE RULES OF UG-36 THROUGH UG-43

a.

ONE HALF OF THE VESSEL INSIDE DIAMETER FOR VESSEL NOT EXCEEDING 1500 mm INSIDE DIAMETER.

b.

OPENING SIZE NOT TO EXCEED 500 mm.

D = VESSEL INSIDE DIAMETER IN CORRODED CONDITION (mm)

d = FINISHED OPENING SIZE IN CORRODED CONDITION (mm)

NOZZLE N1 N2 N3 N4 N5 N6

D 700 700 700 700 700 700

D/2 350 350 350 350 350 350

d 75.56 75.56 22.29 47.804 47.804 22.29

d=


24/27


MSN : -

NOZZLE OPENINGS ON SHELL:

SR.No. NOZZLE

MARK SIZE

OPENING DIA

.(CORRODED)

SYMBOL VALUE (mm)

1.

N1 DN 25 d 1 75.56

2.

N2 DN 25 d 2 75.56 3.

N3 DN 25 d 3 22.29 4. N4 DN 50 d 4 47.804

5.

N5 DN 80 d 5 47.804

6.

N6 DN 25 d 5 6 22.29

THERE ARE NO PAIR OF MULTIPLE OPENINGS. HENCE, REQUIREMENTS OF UG-42 DO NOT APPLY.

EVALUATION OF MULTIPLE OPENING –UG-42 REV No. : 0

DATED : 21/11/15


25/27


MSN : -

UG-20(f):IMPACT TESTING AS PER UG-84 IS NOT MANDATORY FOR PRESSURE VESSEL

MATERIALS THAT SATISFY ALL OF THE FOLLOWING:

SR.NO CONDITION CONDITION SATISFIED

1 THE MATERIAL SHALL BE LIMITED TO P-No.1 OR 2.AND THE THICKNESS,.AS

DEFINED IN UCS-66(a),SHALL NOT EXCEED THAT GIVEN IN (a) OR (b) BELOW :

(a)

13mm FOR MATERIALS LISTED IN CURVE"A”OF FIG.UCS-66 NOT APPLICABLE

(b)

25mmFOR MATERIALS LISTED IN CURVE "B”, "C”,OR" D” OF FIG.UCS-66 YES

2 THE COMPLETED VESSEL SHALL BE HYDROSTATICALLY TESTED AS PER UG-

99(b) OR (c ) OR 27–4

YES

3 DESIGN TEMPERATURE IS NO WARMER THAN 345Deg C NOR COLDER THAN -29

Deg C. OCCASIONAL OPERATING TEMPERATURE COLDER THAN -29 Deg C ARE

ACCEPTABLE WHEN DUE TO LOWER SEASONAL ATMOSPHERIC TEMPERATURE.

YES

4 THE THERMAL OR MECHANICAL SHOCK LOADINGS ARE NOT A CONTROLLING

DESIGN REQUIREMENT.(UG-22)

YES

5 CYCLICAL LOADING IS NOT A CONTROLLING DESIGN REQUIREMENT.(UG-22). YES

CONSIDERING ALL ABOVE,IT CAN BE CONCLUDED THAT MATERIAL AND WPS(WELDING PROCEDURE

SPECIFICATION)NEED NOT INCLUDE IMPACT TEST OF WELD AND HEAT AFFECTED ZONE (HAZ)MADE IN

ACCORDANCE WITHUG-84.ACCORDINGLY,PRODUCTION TEST COUPONS(PTC)FOR IMPACT TESTING ARE NOT

REQUIRED.

HENCE, IMPACT TEST IS EXEMPTED FOR FLANGES MADE OF ALLOY STEEL MATERIAL AS PER UG-20(f).

UHA-51 (d) EXEMPTIONS FROM IMPACT TESTING FOR BASE METALS AND HEAT AFFECTED ZONES. IMPACT TESTING IS

NOT REQUIRED FOR TABLE UHA-23 BASE METALS FOR THE FOLLOWING COMBINATIONS OF BASE METALS AND HEAT

AFFECTED ZONES (IF WELDED) AND MDMTs, EXCEPT AS MODIFIED IN UHA-51 (c):

UHA-51 (d) (1) FOR THE AUSTENITIC CHROMIUM- NICKEL STAINLESS STEELS AS FOLLOWS:

(a)

TYPES 304, 304L, 316, 316 L, 321 AND 347 AT MDMTs of -320 DEG F (-196 DEG C) AND WARMER

AS PER THE TABLE UHA-23 ALL MATERIAL ARE EXEMPTED FROM THE IMPACT TESTING

HENCE, IMPACT TEST IS EXEMPTED FOR SHELL, PIPES, AND FLANGES OF MATERIAL SA 182 F316L.

IMPACT TEST REQUIREMENTS REV No. : 0

DATED : 21/11/15


26/27


MSN : -

AS PER UG-44, FLANGES AS PER ASME B16.5 ARE ACCEPTABLE.

NOZZLE MARK N1,N2 N3,N6 N4,N5 -NOZZLE SIZE DN 80 DN 25 DN 50 -

ASME RATING CLASS OF

FLANGE

300 300 300 -

TYPE SORF

B 16.5

SORF

B 16.5

SORF

B 16.5 -

MATERIAL SA 182 F 316L SA 182 F 304L SA 182 F 304L -MATERIAL GROUP No. AS

PER TABLE 1A OF ASME

B16.47 AND B16.5

2.3 2.3 2.3 -

APPLICABLE PRESSURE

TEMPERATURE RATING

TABLE

2 – 2.3 2 – 23 2 – 2.3 -

DESIGN TEMPERATURE 65 65 65 Deg C

MAX.ALLOWABLEWORKING PRESSURE FOR

SELECTED RATING

38.38 38.38 38.38 ar (g)

546 546 546 PSI (g)

3.838 3.838 3.838 MPa (g)

DESIGN PRESSURE 1.5 1.5 1.5 MPa (g)

FROM TABLE GG OF ASME SEC.VIII Div.1EDITION 2013

1PSI = 0.06894757 Bar

From Sheet No : 10 1 PSI = 0.0068948 MPa

BOLTING:

1)

AS PER CLAUSE 5.3 OF ASME B16.47,BOLTING MATERIALS LISTED IN TABLE 1B CAN BE USED IN FLANGED

JOINTS.THE SELECTED BOLTING SPECIFICATION IS SA 193 GR B8 WHICH FALLS IN HIGH STRENGTH

CATEGORY.

2)LENGTH OF BOLTING IS IN LINE WITH TABLE-8

3)AS PER UG-13(a) OF ASME SEC.VIII Div.1,NUT SHALL ENGAGE THE THREADS FOR THE FULL DEPTH OF THE

UNIT.

4)AS PER UCS-11(c) OF ASME SEC.VIII Div.1,HEAVY SERIES NUTS SHALL BE USED.THREADING SHALL BE AS PER

ASME B18.2.2.

5)AS PER UG-13(b) OF ASME SEC.VIII Div.1,WASHERS ARE PTIONAL AND ARE NOT CONSIDERED.

GASKET:

AS PER NOTE 2 OF TABLE-1B OF ASME B16.47, ALL LISTED GASKET MATERIALS CAN BE USED IN FLANGED

JOINTS. SPWD (SELF ENERGIZING TYPE)GASKETS ARE SELECTED.

FLANGE RATING CALCULATION –

AS PER UG-44, & B 16.5

REV No. : 0

DATED : 21/11/15


27/27


MSN : -

POST WELD HEAT TREATMENT IS REQUIRED WHEN ANY OF FOLLOWING CONDITION EXIT:

SR.No. APPLICABLE

CLAUSE

DESCRIPTION APPLICABLE

YES / NO

REMARKS

1. UW-2(a) LETHAL SERVICE NO -

2. UW-2(c) UNFIRED STEAM BOILER WITH DESIGN

PRESSURE EXCEEDING 345 Kpa

NO -

3. UCS-68 (b) IF MDMT IS COLDER THAN -48 Deg C

AND THE COINCIDENT RATIO DEFINED

IN FIG. UCS-66.1 IS 0.35 OR GREATER

NO OUR VESSEL MDMT is

10 Deg C – MAXIMUM

DESIGN TEMPERATURE

is 75 Deg C

4. UHA-32 MATERIAL OVER ANY NOMINAL

THICKNESS AS DEFINED IN UW-40 (f)

NO Note

NOTE : (P NO. 8 GR. NOS. 1, 2, 3, 4) POSTWELD HEAT TREATMENT IS NEITHER REQUIRED NOR PROHIBITED FOR

JOINTS BETWEEN AUSTENITIC STAINLESS STEELS OF THE P NO. 8 GROUP. 1

PWHT REQUIREMENTS –UW-2, UHA-32 REV No. : 0

DATED : 21/11/15

Mechanical Design Calculations of Pressure Vessel - Sample

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