CademPVD by CADEM Softwares
Most value for money software for the mechanical design of process equipment
Trial version ava...
EXAMPLE NO. PV-01
DESIGN
OF
PRESSURE VESSEL (GAS FILTER)
NOTE:
1) Link to youtube video of this design: http://www.youtube...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
Index
Licensee :
Sunay Wagle, CADEM Services,
Pu...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
EQUIPMENT INFORMATION :
DESIGN & REVIEWAL :
INSP...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
(1) PROCESS DETAILS :
(3) TEST PR. : kgf/mm² g
(...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
VESSEL DESIGN DATA
1. MATERIAL OF CONSTRUCTION :...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
SUMMARY OF EFFECTIVE DESIGN PRESSURES IN kgf/mm²...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
ITEM WISE WEIGHT SUMMARY
Licensee :
Sunay Wagle,...
27 Lifting Lugs 2 Nos. 1.596 0 1.596
28 Pad (Lifting Lugs)
70 Long x 170 Wide x 8 Thk, 2
Nos.
1.507 0 1.507
29 Insulation
...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
TEST PRESSURES CALCULATION AS PER UG-99 / UG-100...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
Vessel Inside
Legend :
Licensee :
Sunay Wagle, C...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
EXTREME FIBRE ELONGATION CALCULATION
Legend :
Li...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Corroded ...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Corroded ...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Corroded ...
= 27973 + 157907.4
= 185880.4 kgf
7. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b2) :
Minimum required bolt load for gask...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Corroded ...
= 2458.4 + 13877.8
= 16336.3 kgf
7. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b2) :
Minimum required bolt load for gaske...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Corroded ...
6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1)
Total joint - contact surface compression load [Hp]
= 2 x ( p x b x G x...
= 36.5 mm
Radial distance from the bolt circle to the circle on which HD acts [hD]
= R + 0.5 x g1
= 36.5 + 0.5 x 17
= 45 m...
= 108.7 3
/ 306079.1
= 4.195
Factor [l]
= g + d
= 1.073 + 4.195
= 5.268
18. FLANGE STRESSES AS PER APPENDIX 2-7 & 2-8
Equi...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Corroded ...
6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1)
Total joint - contact surface compression load [Hp]
= 2 x ( p x b x G x...
= 45 mm
Radial distance from gasket load reaction to the bolt circle [hG]
= 0.5 x ( C - G )
= 0.5 x ( 1363 - 1294.4 )
= 34...
= MAX [ MO , MO' x Sfo / Sfa ]
= MAX [ 147545.1 , 10560086 x 14.06 / 14.06 ]
= 10560086 kgf-mm
Corrected equivalent moment...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Corroded ...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Corroded ...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. LUG DATA :
2. BOLT DATA :
3. GUSSET DATA :
4....
= [ 4 x 940925.4 / ( 1570 x 4 ) ] + 2388.5 / 4
= 1196.4 kgf
Maximum axial force in gusset [P1]
= Q / n
= 1196.4 / 2
= 598....
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. LUG DATA :
2. BOLT DATA :
3. GUSSET DATA :
4....
= [ 4 x 288590.5 / ( 1570 x 4 ) ] + 1841.2 / 4
= 644.1 kgf
Maximum axial force in gusset [P1]
= Q / n
= 644.1 / 2
= 322.1 ...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
DESIGN CONDITIONS
NOZZLE DATA
SHELL DATA ( Main ...
= 0.01055 x 628 / ( 14.06 x 1.0 - 0.6 x 0.01055 )
= 0.471 mm
Standard wall thickness as per UG 45(b)(4) , [t3]
= 7.112 mm
...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITION :
2. ATTACHMENT DATA :
3. EX...
7. COMBINING STRESSES :
** Only absolute values of quantities in bracket shall be used while combining stresses
( 1 ) : Fr...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITION :
2. ATTACHMENT DATA :
3. EX...
7. COMBINING STRESSES :
** Only absolute values of quantities in bracket shall be used while combining stresses
( 1 ) : Fr...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
DESIGN CONDITIONS
NOZZLE DATA
SHELL DATA ( Main ...
= 0.01055 x 628 / ( 14.06 x 1.0 - 0.6 x 0.01055 )
= 0.471 mm
Standard wall thickness as per UG 45(b)(4) , [t3]
= 7.112 mm
...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITION :
2. ATTACHMENT DATA :
3. EX...
7. COMBINING STRESSES :
** Only absolute values of quantities in bracket shall be used while combining stresses
( 1 ) : Fr...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITION :
2. ATTACHMENT DATA :
3. EX...
7. COMBINING STRESSES :
** Only absolute values of quantities in bracket shall be used while combining stresses
( 1 ) : Fr...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
DESIGN CONDITIONS
NOZZLE DATA
HEAD DATA ( Dished...
= 0.01087 kgf/mm² g
Thickness of head as per UG 45(b)(1)
Min. head thickness reqd. as per UG 27(d) , [trn2 = tr1]
= 4.828 ...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITION :
2. ATTACHMENT DATA :
3. EX...
7. COMBINING STRESSES :
** Only absolute values of quantities in bracket shall be used while combining stresses
( 1 ) : Fr...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. LIFTING LUG DATA :
2. DESIGN LOADS :
3. CALCU...
= 5.028 mm
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
FOUNDATION LOAD DATA
Licensee :
Sunay Wagle, CAD...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
CENTER OF GRAVITY DATA
Licensee :
Sunay Wagle, C...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
Index
Licensee :
Sunay Wagle, CADEM Services,
Pu...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
EQUIPMENT INFORMATION :
DESIGN & REVIEWAL :
INSP...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
(1) PROCESS DETAILS :
(3) TEST PR. : kgf/mm² g
(...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
VESSEL DESIGN DATA
1. MATERIAL OF CONSTRUCTION :...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
SUMMARY OF EFFECTIVE DESIGN PRESSURES IN kgf/mm²...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
ITEM WISE WEIGHT SUMMARY
Licensee :
Sunay Wagle,...
27 Lifting Lugs 2 Nos. 1.596 0 1.596
28 Pad (Lifting Lugs)
70 Long x 170 Wide x 8 Thk, 2
Nos.
1.507 0 1.507
29
30
31
32
33...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
TEST PRESSURES CALCULATION AS PER UG-99 / UG-100...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
Vessel Inside
Legend :
Licensee :
Sunay Wagle, C...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Hydrotest Mode , Corroded...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Hydrotest Mode , Corroded...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Hydrotest Mode , Corroded...
= 28027.1 + 158212.8
= 186239.9 kgf
7. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b2) :
Minimum required bolt load for ga...
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Hydrotest Mode , Corroded...
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
Pressure Vessel Design
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Pressure Vessel Design
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Pressure Vessel Design

Download this document here: http://www.cadem.in/software/cadempvd/reports/pressure-vessels/design-of-pressure-vessel-1.pdf This example covers design of a simple pressure vessel. This pressure vessel has a top flat cover and a bottom dished end. The top cover is of bolted type and is connected to the shell through top body flange. The pressure vessel is provided with lugs support and lifting lug.
Published on: Mar 6, 2016
Published in: Engineering      Technology      Business      
Source: www.slideshare.net


Transcripts - Pressure Vessel Design

  • 1. CademPVD by CADEM Softwares Most value for money software for the mechanical design of process equipment Trial version available on our website www.cadem.in • 28 years of equipment design experience captured, polished, compacted and is now ready for transfer to designers, fabricators and plant engineers • Intelligent, works with minimum inputs For instance, in case of say a body flange, the software automatically evaluates optimum configuration of all undefined parameters: Flange OD, Flange ID, PCD, Number and Size of bolts, Gasket OD & ID, etc. meeting the requirements of the specified equipment design code. • Generates final design at estimation stage, saves more than 80% of your design & estimation time • Earn more as you save on costing and quotation making time • High quality documentation with all formulae and relevant code clauses • Most importantly, the user need not be a hard core designer CADEM Softwares Enhancing your business strengths and design capabilities. Website: www.cadem.in Email: cadem@vsnl.com Phone: +91 9370211312 Address: Office No. 19, SC-1 Building, Kohinoor Estate, Wakdewadi, Pune-Mumbai Road, Pune 411003, Maharashtra, India Follow Us: @facebook: www.facebook.com/cademindia OR www.cadem.in/facebook @youtube: www.youtube.com/cademchannel OR www.cadem.in/youtube @linkedin: www.linkedin.com/company/cadem OR www.cadem.in/linkedin @google+: http://plus.google.com/116314947079178385899 OR www.cadem.in/googleplus @twitter: www.twitter.com/cademindia OR www.cadem.in/twitter YOU CAN DOWNLOAD THIS DOCUMENT, OTHERS AND HELP GUIDE AT www.cadem.in/links Pressure Vessels Reaction Vessels Agitator Shafts Heat Exchangers Process Columns Storage Tank Floating Roof Chimney ASME Sec. VIII Div. 1 TEMA EEUA IS 2825 EN 13445 API 650 API 620 IS 6533
  • 2. EXAMPLE NO. PV-01 DESIGN OF PRESSURE VESSEL (GAS FILTER) NOTE: 1) Link to youtube video of this design: http://www.youtube.com/watch?v=3Y0yrt1Z6fI&list=PLPL8SPZUxm- mFqQZceyhr13QYDEruelJx 2) As you can see in the video, the inbuilt intelligence in the software generates all information by itself. Eg: For a body flange, the software evaluates all the undefined parameters Flange OD, Flange ID, PCD, Number and Size of bolts, Gasket OD & ID, etc. meeting the requirements of specified equipment design code. 3) In case of any changes to the interconnected shell geometry and / or design conditions (pressure / temperature) including material of constructions, these dimensions automatically regenerated by the software to meet the new requirements. 4) The software can generate cost estimation and BOM in Excel. This example covers design of a simple pressure vessel. This pressure vessel has a top flat cover and a bottom dished end. The top cover is of bolted type and is connected to the shell through top body flange. The pressure vessel is provided with lugs support and lifting lug.
  • 3. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in Index Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Sr. No. Description Page No 1 Title page & equipment info 2 Design data 3 Material of constructions 4 Effective Pressures 5 Weight summary report 6 Test pressure calculations (shell side) 7 Wind load calculations 8 Seismic load calculations 9 Design of Cover (Front) 10 Design of Cover (Front) 11 Design of Shell Flng (Front) 12 Design of Shell Flng (Front) 13 Design of Main Shell 14 Design of Dished End (Rear) 15 Design of Lug Support 16 Design of Lug Support 17 Design of N 01 18 Design of N 01 19 Design of N 01 20 Design of N 02 21 Design of N 02 22 Design of N 02 23 Design of N 03 24 Design of N 03 25 Design of Lifting Lugs 26 Foundation load data 27 C.G. Data
  • 4. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in EQUIPMENT INFORMATION : DESIGN & REVIEWAL : INSPECTION & APPROVAL : EQUIPMENT DATA : OTHER DATA : Customer ABC Company Ltd. Project Soap Plant Location Vapi Site Plant Refrigeration Plant Design Code ASME VIII Div.1, 10 A11 Equipment Name Gas Filter Equipment Type Pressure Vessel Equipment Class N.A. Equipment Category N.A. Reference Drawing No --- Service Compressed Gas Services Support Type Lug Supports Designed By Design Date 31-03-2015 00:25:14 Checked By Approved By Revision R00 Inspection Agency --- Reviewed By --- Front end Flat End Front end flanged True Rear end Dished End Rear end flanged False Shell ID 1250 mm Shell OD 1270 mm Length, Shell (W.L. to W.L) / Overall 1650 / 2254.6 mm Fabricated weight 1898.3 kgf Empty weight + external weights 1898.3 kgf Estimated operating weight 1926.8 kgf Estimated hydrotest weight 4439.8 kgf
  • 5. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in (1) PROCESS DETAILS : (3) TEST PR. : kgf/mm² g (4) TEMPERATURE : °C (5) ALLOWANCES : mm (6) RADIOGRAPHY & JOINT EFFICIENCY : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 VESSEL DESIGN DATA MEDIA DENSITY kg/m³ Operating Process Gas 10 Design1 Process Gas 12 Design2 Startup Shutdown Upset Hydrotest Water 1000 Pneumatic Process Gas 1.2 (2) PR. : kgf/mm² g INT. EXT. Operating 0.1 0.12 0.01055 Design1 0.12 0.12 0.01055 Design2 Startup Shutdown Upset Based on Input Pr MAWP MAP Hydrotest 0.156 0.156 0.169 Pneumatic 0.132 0.132 0.143 MIN. MAX. Input MDMT Operating 20 -14.28 100 Design1 20 -11.75 150 Design2 Startup Shutdown Upset Hydrotest 21.67 -11.57 50 Pneumatic 21.67 -11.75 50 INT. EXT. Corrosion 3 0 Polishing 0 0 RADIOGRAPHY JOINT EFFICIENCY Shell Spot + T Joints 0.85 Head Full 1.00
  • 6. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in VESSEL DESIGN DATA 1. MATERIAL OF CONSTRUCTION : 2. NOZZLE CONNECTIONS : 3. INSULATION & CLADDING: Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Shell side Shell SA-516 GR. 70 Plt. [UNS:K02700] Head SA-516 GR. 70 Plt. [UNS:K02700] Body flange SA-105 Frg. [UNS:K03504] Body flange cover SA-516 GR. 70 Plt. [UNS:K02700] Liner Shell side Nozzle neck <= NPS 40 SA-106 GR. B Smls. Pipe [UNS:K03006] Flange SA-105 Frg. [UNS:K03504] Cover flange SA-105 Frg. [UNS:K03504] Nozzle NPS > 40 & < 200 SA-106 GR. B Smls. Pipe [UNS:K03006] Flange SA-105 Frg. [UNS:K03504] Cover flange SA-105 Frg. [UNS:K03504] Nozzle neck >= NPS 200 SA-516 GR. 70 Plt. [UNS:K02700] Flange SA-516 GR. 70 Plt. [UNS:K02700] Cover flange SA-516 GR. 70 Plt. [UNS:K02700] Pad flange SA-516 GR. 70 Plt. [UNS:K02700] Pad flange cover SA-516 GR. 70 Plt. [UNS:K02700] Manhole flange SA-516 GR. 70 Plt. [UNS:K02700] Manhole cover SA-516 GR. 70 Plt. [UNS:K02700] Reinforcement pad SA-516 GR. 70 Plt. [UNS:K02700] External bolt SA-193 GR. B7 Bolt [UNS:G41400] External gasket Spiral metal wound CAF filled (S.S.) Stiffener SA-516 GR. 70 Plt. [UNS:K02700] Lifting lug IS-2062 GR. A Plt. Support IS-2062 GR. A Plt. Anchor bolt Commercial CS Bolt Mat. / Density / Thk. Rockwool (Mineral Fibre) / 136.2 kg/m³ / 25 mm Mat. / Thk. Al. sheet / 1.191 mm
  • 7. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in SUMMARY OF EFFECTIVE DESIGN PRESSURES IN kgf/mm² g VS TEMPERATURE IN °C Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Sr. Item name Temp. Inside pr. Liquid pr. Effective pr. No. +ve -ve +ve -ve 1 Cover (Front) 150 0.12 0.01055 0 0.12 0.01055 2 Shell Flng (Front) 150 0.12 0.01055 0 0.12 0.01055 3 Main Shell 150 0.12 0.01055 0 0.12 0.01055 4 Dished End (Rear) 150 0.12 0.01055 0 0.12 0.01055 5
  • 8. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in ITEM WISE WEIGHT SUMMARY Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Sr.No. Item name Item size Empty wt Volume Filled wt kgf m³ kgf 1 Cover (Front) Blind Flange - 1420 OD x 73.411 Thk, RF, 1363 PCD, Tgrv = 1.588 900.5 0 900.5 2 Shell Flng (Front) Fabricated WN - 1420 OD x 1250 ID x 1363 PCD, RF, 128.692 Thk, Trgv = 1.588, G1 = 20, G0 = 10, hf = 30 312.3 0 312.3 3 Gasket Flng (Front) 1313.5 OD x 1250 ID, 4.763 Thk 0.1 0 0.1 4 Bolt Flng (Front) Hex Head Bolt M24 x 243.128 Lg, 56 Nos. 48.76 0 48.76 5 Main Shell 1270 OD x 10 Thk, 1650 Lg 517.1 2.025 541.4 6 Dished End (Rear) Elliptical D/2H = 2.0, 1270 OD x 10 Nom / 9 Min Thk, SF = 50 181.7 0.317 185.5 7 Gusset Plate 200 Long x 190 Wide x 16 Thk, 8 Nos. 38.51 0 38.51 8 Anchor Bolt Anchor M20 x 200 Lg, 4 Nos. 1.99 0 1.99 9 Support Pad 270 Long x 292 Wide x 10 Thk, 4 Nos. 24.97 0 24.97 10 N 01 ANSIB36.10, 150 NPS Sch.80, 156 Lg 6.697 0.00262 6.728 11 Flange [N 01] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08 12 Gasket [N 01] 166.329 OD x 146.329 ID, 4.763 Thk 0.1 0 0.1 13 Bolt [N 01] Hex Head Bolt M20 x 86.125 Lg, 8 Nos. 1.714 0 1.714 14 Counter Flng [N 01] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08 15 Reinf [N 01] 292.659 OD x 171.275 ID x 10 Thk 3.501 0 3.501 16 N 02 ANSIB36.10, 150 NPS Sch.80, 156 Lg 6.697 0.00262 6.728 17 Flange [N 02] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08 18 Gasket [N 02] 166.329 OD x 146.329 ID, 4.763 Thk 0.1 0 0.1 19 Bolt [N 02] Hex Head Bolt M20 x 86.125 Lg, 8 Nos. 1.714 0 1.714 20 Counter Flng [N 02] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08 21 Reinf [N 02] 292.659 OD x 171.275 ID x 10 Thk 3.501 0 3.501 22 N 03 ANSIB36.10, 50 NPS Sch.160, 150 Lg 1.682 0.00022 1.684 23 Flange [N 03] Weld Neck, ANSI B16.5, RF, 150# for 50 NPS Sch 160 Pipe 2.428 0 2.428 24 Gasket [N 03] 62.85 OD x 42.85 ID, 4.763 Thk 0.1 0 0.1 25 Bolt [N 03] Hex Head Bolt M16 x 67.725 Lg, 4 Nos. 0.431 0 0.431 26 Bolted Cover [N 03] Weld Neck, ANSI B16.5, RF, 150# for 50 160 NPS Pipe 2.522 0 2.522 120 Long x 70 Wide x 12 Thk,
  • 9. 27 Lifting Lugs 2 Nos. 1.596 0 1.596 28 Pad (Lifting Lugs) 70 Long x 170 Wide x 8 Thk, 2 Nos. 1.507 0 1.507 29 Insulation 4084.07 W x 3754.584 L, 25 Thk 52.2 0 52.2 30 Cladding 4087.811 W x 3754.584 L, 1.191 Thk 5.058 0 5.058 31 32 33 34 35 ∑ 2149.7 ∑ 4439.8
  • 10. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in TEST PRESSURES CALCULATION AS PER UG-99 / UG-100 : Vessel Inside Legend : Test Pressure Calculations Pressure due to hydro liquid column, [ Plh ] = Lh x rh x 1E-09 = 0.00225 kgf/mm² g Hydrotest pressure, [ Ph ] = 1.3 x Pt - Plh = 1.3 x 0.12 - 0.00225 = 0.154 kgf/mm² g Pneumatic test pressure, [ Pn ] = 1.1 x Pt = 1.1 x 0.12 = 0.132 kgf/mm² g Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Design Temperature T 150 °C Operating Liquid Density r 12 kg/m³ Hydrotest Liquid Density rh 1000 kg/m³ Hydrotest Liquid Column Lh 2254.6 mm Sr. No. Item Name Pressure ( kgf/mm² g ) Stress Correction ( kgf/mm² ) Pt Pi Pl Pc Pe Peff Sfo Sfa Sfa Sfo 1 Cover (Front) 0.12 0 0 0.01055 0.12 14.06 14.06 1 0.12 2 Shell Flng (Front) 0.12 0 0 0.01055 0.12 14.06 14.06 1 0.12 3 Main Shell 0.12 0 0 0.01055 0.12 14.06 14.06 1 0.12 4 Dished End (Rear) 0.12 0 0 0.01055 0.12 14.06 14.06 1 0.12 5 Min. Pr., Pt 0.12 Pi = Internal positive pressure Pl = Pressure due to design liquid column Pe = Internal vacuum pressure Pc = External negative pressure Peff = Pi + Pl + Pc Sfo = Allowabe stress at design temperature Sfa = Allowable stress at ambient temperature Pt = MAX [ Peff + Pc, Pe ] x ( Sfa / Sfo )
  • 11. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in Vessel Inside Legend : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 CALC. OF MIN. DESIGN METAL TEMPERATURE Design Mode 1 , Corroded Condition CODE ASME VIII Div.1, 10 A11 Design Pressure Pi 0.12 kgf/mm² g Design Temperature T 150 °C Sr. No. Item Name / Material / Group Stress (kgf/mm²) Thickness (mm) MDMT (°C) Smt Sdt tn tg tr Tm Tc MDMT 1 Cover (Front) SA-516 GR. 70 Plt. [UNS:K02700] Curve : B 14.06 14.06 70.41 17.6 17.6 -11.98 40.56 -52.53 2 Shell Flng (Front) SA-105 Frg. [UNS:K03504] Curve : B 14.06 14.06 125.7 7 6.343 -28.89 -17.14 -11.75 3 Main Shell SA-516 GR. 70 Plt. [UNS:K02700] Curve : B 14.06 14.06 7 7 6.343 -28.89 -14.73 -14.16 4 Dished End (Rear) SA-516 GR. 70 Plt. [UNS:K02700] Curve : B 14.06 14.06 7 7 5.364 -28.89 -14.61 -14.28 5 Max, MDMT -11.75 Smt = Stress at minimum design metal temperature. Sdt = Pressure due to design liquid column tn = Stress at design metal temperature. tg = Nominal item thickness excluding corrosion and thinning. tr = Governing metal thickness for the item. Tg = Required minimum thickness of the item. Tm = Minimum metal temperature for the the item. Tc = MDMT Correction MDMT = Final MDMT for the item = Tm - Tc.
  • 12. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in EXTREME FIBRE ELONGATION CALCULATION Legend : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Sr. No. Item Name MOC Rf t Eqn. No. e HT mm mm % 1 Main Shell SA-516 GR. 70 Plt. [UNS:K02700] 625 10 1 0.8 False 2 Dished End (Rear) SA-516 GR. 70 Plt. [UNS:K02700] 1130 10 2 0.664 False 3 4 5 Rf = Mean radius after forming Ro = Infinity t = Nominal thickness of the plate before forming Eqn. 1 = 50 x t / Rf x [ 1 - Rf / Ro ] Eqn. 2 = 75 x t / Rf x [ 1 - Rf / Ro ]
  • 13. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition ) : 3. CALCULATION OF FORCES AND MOMENTS: Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 WIND LOAD CALCULATION CODE Wind [IS:875, 87] Basic wind speed ( Section 5.2 ) Vb 50 m/s Expected life of equipment ( Section 5.3.1 ) 25 Years Probability factor (Risk coeff) ( Section 5.3.1 ) K1 0.902 Terrain category ( Section 5.3.2 ) Category 2 Structure class ( Section 5.3.2.2 ) Class B Topography factor ( Section 5.3.3 ) K3 1.3 Force coefficient (Shape factor) Cf 0.8 Equivalent diameter De 1820 mm Overall length of equipment L 2254.6 mm Height of C.G. of equipment Hcg 1807.5 mm Size and height factor ( Section 5.3.2 ) K2 0.98 Effective transverse cross sectional area = De x L A 4103343.3 mm² Effective wind speed = K1 x K2 x K3 x Vb Vz 57.44 m/s Wind pressure = 6E-08 x Vz 2 Pz 0.0002 kgf/mm² Longitudinal force = Cf x A x Pz F 649.9 kgf Support elevation H 372.5 mm Turning moment = F x ( Hcg - H ) M 932661.5 kgf-mm
  • 14. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition ) : 2. CALCULATION OF FORCES AND MOMENTS: Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 SEISMIC LOAD CALCULATION CODE Seismic [IS:1893, 02] Weight of equipment Wo 1926.8 kgf Importance factor ( Table-6 , 2002 ) I 1.5 Soil profile type Stiff Soil Profile (SD) Foundation type RCC footings + Tie Beams Damping factor 5 Seismic zone Zone III Seismic zone factor ( Table-2 , 2002 ) Z 0.16 Response reduction factor ( Table-7 , 2002 ) R 2.9 Spectral accelerations coeff. ( Fig. 2 , 2002 ) Sa / g 2.5, Use max value Damping correction factor ( Table-3 , 2002 ) Cf 1 Seismic coefficient ( Clause-6.4.2 , 2002 ) = 0.5 x Z x I x Cf x ( Sa / g ) x ( 1 / R ) = 0.5 x 0.16 x 1.5 x 1 x 2.5 x ( 1 / 2.9 ) Ah 0.103 Elevation of support H 372.5 mm Height of C.G. of equipment Hcg 1807.5 mm Seismic base shear force = Ah x Wo = 0.103 x 1926.8 Vb 199.3 kgf Seismic moment of support = Vb x ( Hcg - H ) = 199.3 x ( 1807.5 - 372.5 ) M 286034.2 kgf-mm
  • 15. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition ) : 2. COVER DATA : 3. BOLTING DATA : 4. LINER DATA : 5. GASKET DATA : 6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1) : Total joint - contact surface compression load [Hp] = 2 x (  x b x G + b' x Lp ) x m x P = 2 x (  x 9.554 x 1294.4 + 0 x 0 ) x 3 x 0.12 = 27973 kgf Total hydrostatic end force [H] = 0.25 x  x G 2 x P = 0.25 x  x 1294.4 2 x 0.12 = 157907.4 kgf Minimum required bolt load for operating condition [Wm1] = Hp + H Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 DESIGN OF FLAT BOLTED HEAD ( INTERNAL ) Cover (Front) CODE ASME VIII Div.1, 10 A11 Design pressure P 0.12 kgf/mm² g Design temperature T 150 °C Allowance CA 3 mm Groove allowance Tg 0 mm Radiography Spot + T Joints Joint efficiency E 1 M.O.C. SA-516 GR. 70 Plt. [UNS:K02700] Code allw. stress @ design temp. Sfo 14.06 kgf/mm² Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm² Young’s modulus Ey 19888.4 kgf/mm² Self reinforced False Flange OD A 1420 mm Thickness provided 73.41 mm Thickness available 70.41 mm M.O.C. SA-193 GR. B7 Bolt [UNS:G41400] Code allw. stress @ design temp. Sb 17.58 kgf/mm² Code allw. stress @ atm. temp. Sa 17.58 kgf/mm² Bolt PCD PCD 1363 mm Bolt dia. db 24 mm No. of bolts nb 56 M.O.C. Liner ID mm Liner OD mm Liner thk. mm M.O.C. Spiral metal wound CAF filled (S.S.) Gasket seating stress y 7.031 kgf/mm² Gasket factor m 3 Inside diameter Gi 1256 mm Outside diameter Go 1313.5 mm Width of gasket N 28.75 mm Width of gasket ( as per Table 2-5.2 ) 31.75 mm Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm Effective gasket width ( as per Table 2-5.2 ) b 9.554 mm Dia. at load reaction ( see Table 2-5.2 ) G 1294.4 mm Pass partition gasket width Wp 0 mm Pass partition gasket length Lp 0 mm Effective pass partition gasket width b' 0 mm
  • 16. = 27973 + 157907.4 = 185880.4 kgf 7. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b2) : Minimum required bolt load for gasket seating [Wm2] = (  x b x G + b' x Lp ) x y = (  x 9.554 x 1294.4 + 0 x 0 ) x 7.031 = 273152.4 kgf 8. BOLT AREAS AS PER APPENDIX 2-5 (d) : Total required cross-sectional area of bolts [Am] = MAX [ Wm2 / Sa , Wm1 / Sb ] ........ For Internal '+' Pr Design = Wm2 / Sa ..................................... For External Pr & Self Sealing Design = 15540.6 mm² Actual bolt area using root diameter [Ab] = 17513.9 mm² Flange design bolt load for the gasket seating [W] = 0.5 x ( Am + Ab ) x Sa x 1 .................... average bolt area = Ab x Sa x 1 ..........................................full bolt area = 307837.2 kgf ( Full bolt area and margin factor of 1 ) 9. CHECK FOR GASKET CRUSHING : Minimum gasket width required [Nmin] = Ab x Sb / ( 2 x  x y x G ) = 17513.9 x 17.58 / ( 2 x  x 7.031 x 1294.4 ) = 5.384 mm 10. DESIGN CALCULATION AS PER UG 34, BOLTING CONDITION : Required thickness for bolting condition [t] = G x SQRT [ 1.9 x W x 0.5 x ( PCD - G ) / ( Sfa x E x G 3 ) ] = 1294.4 x SQRT [ 1.9 x 307837.2 x 0.5 x ( 1363 - 1294.4 ) / ( 14.06 x 1 x 1294.4 3 ) ] = 33.2 mm 11. DESIGN CALCULATION AS PER UG 34, OPERATING CONDITION : Required thickness for operating condition [t] = G x SQRT { [ C x P / ( Sfo x E ) ] + 1.9 x Wm1 x 0.5 x ( PCD - G ) / ( Sfo x E x G 3 ) } = 1294.4 x SQRT { [ 0.3 x 0.12 / ( 14.06 x 1 ) ] + 1.9 x 185880.4 x 0.5 x ( 1363 - 1294.4 ) / ( 14.06 x 1 x 1294.4 3 ) } = 70.65 mm Self reinforced False Factor C is user input False Factor C taken from fig. UG 34 or user input 0.3 Maximum factor C value C 0.75 Factor C (effective) 0.3 C = Min ( 2 x 0.3, 0.75 ) for self reinf. C = 0.3 in other cases
  • 17. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition ) : 2. COVER DATA : 3. BOLTING DATA : 4. LINER DATA : 5. GASKET DATA : 6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1) : Total joint - contact surface compression load [Hp] = 2 x (  x b x G + b' x Lp ) x m x P = 2 x (  x 9.554 x 1294.4 + 0 x 0 ) x 3 x 0.01055 = 2458.4 kgf Total hydrostatic end force [H] = 0.25 x  x G 2 x P = 0.25 x  x 1294.4 2 x 0.01055 = 13877.8 kgf Minimum required bolt load for operating condition [Wm1] = Hp + H Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 DESIGN OF FLAT BOLTED HEAD ( EXTERNAL ) Cover (Front) CODE ASME VIII Div.1, 10 A11 Design pressure P 0.01055 kgf/mm² g Design temperature T 150 °C Allowance CA 3 mm Groove allowance Tg 0 mm Radiography Spot + T Joints Joint efficiency E 1 M.O.C. SA-516 GR. 70 Plt. [UNS:K02700] Code allw. stress @ design temp. Sfo 14.06 kgf/mm² Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm² Young’s modulus Ey 19888.4 kgf/mm² Self reinforced False Flange OD A 1420 mm Thickness provided 73.41 mm Thickness available 70.41 mm M.O.C. SA-193 GR. B7 Bolt [UNS:G41400] Code allw. stress @ design temp. Sb 17.58 kgf/mm² Code allw. stress @ atm. temp. Sa 17.58 kgf/mm² Bolt PCD PCD 1363 mm Bolt dia. db 24 mm No. of bolts nb 56 M.O.C. Liner ID mm Liner OD mm Liner thk. mm M.O.C. Spiral metal wound CAF filled (S.S.) Gasket seating stress y 7.031 kgf/mm² Gasket factor m 3 Inside diameter Gi 1256 mm Outside diameter Go 1313.5 mm Width of gasket N 28.75 mm Width of gasket ( as per Table 2-5.2 ) 31.75 mm Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm Effective gasket width ( as per Table 2-5.2 ) b 9.554 mm Dia. at load reaction ( see Table 2-5.2 ) G 1294.4 mm Pass partition gasket width Wp 0 mm Pass partition gasket length Lp 0 mm Effective pass partition gasket width b' 0 mm
  • 18. = 2458.4 + 13877.8 = 16336.3 kgf 7. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b2) : Minimum required bolt load for gasket seating [Wm2] = ( p x b x G + b' x Lp ) x y = ( p x 9.554 x 1294.4 + 0 x 0 ) x 7.031 = 273152.4 kgf 8. BOLT AREAS AS PER APPENDIX 2-5 (d) : Total required cross-sectional area of bolts [Am] = MAX [ Wm2 / Sa , Wm1 / Sb ] ........ For Internal '+' Pr Design = Wm2 / Sa ..................................... For External Pr & Self Sealing Design = 15540.6 mm² Actual bolt area using root diameter [Ab] = 17513.9 mm² Flange design bolt load for the gasket seating [W] = 0.5 x ( Am + Ab ) x Sa x 1 .................... average bolt area = Ab x Sa x 1 ..........................................full bolt area = 307837.2 kgf ( Full bolt area and margin factor of 1 ) 9. CHECK FOR GASKET CRUSHING : Minimum gasket width required [Nmin] = Ab x Sb / ( 2 x p x y x G ) = 17513.9 x 17.58 / ( 2 x p x 7.031 x 1294.4 ) = 5.384 mm 10. DESIGN CALCULATION AS PER UG 34, BOLTING CONDITION : Required thickness for bolting condition [t] = G x SQRT [ 1.9 x W x 0.5 x ( PCD - G ) / ( Sfa x E x G 3 ) ] = 1294.4 x SQRT [ 1.9 x 307837.2 x 0.5 x ( 1363 - 1294.4 ) / ( 14.06 x 1 x 1294.4 3 ) ] = 33.2 mm 11. DESIGN CALCULATION AS PER UG 34, OPERATING CONDITION : Required thickness for operating condition [t] = G x SQRT { [ C x P / ( Sfo x E ) ] + 1.9 x Wm1 x 0.5 x ( PCD - G ) / ( Sfo x E x G 3 ) } = 1294.4 x SQRT { [ 0.3 x 0.01055 / ( 14.06 x 1 ) ] + 1.9 x 16336.3 x 0.5 x ( 1363 - 1294.4 ) / ( 14.06 x 1 x 1294.4 3 ) } = 32.29 mm Self reinforced False Factor C is user input False Factor C taken from fig. UG 34 or user input 0.3 Maximum factor C value C 0.75 Factor C (effective) 0.3 C = Min ( 2 x 0.3, 0.75 ) for self reinf. C = 0.3 in other cases
  • 19. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition ) : 2. FLANGE DATA : 3. BOLTING DATA : 4. LINER DATA : 5. GASKET DATA : 5a. Flange gasket data : 5b. Partition groove gasket data (For H.E. body flange) : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 FLANGE DESIGN ( INTERNAL ) Shell Flng (Front) CODE ASME VIII Div.1, 10 A11 Design pressure P 0.12 kgf/mm² g Design temperature T 150 °C Allowance CA 3 mm Groove allowance Tg 0 mm M.O.C. SA-105 Frg. [UNS:K03504] Code allw. stress @ design temp. Sfo 14.06 kgf/mm² Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm² Inside diameter B 1256 mm Outside diameter A 1420 mm Hub length h 30 mm Thickness ( hub end ) g1 17 mm Thickness ( pipe end ) g0 7 mm Thickness provided 128.7 mm Thickness available 125.7 mm M.O.C. SA-193 GR. B7 Bolt [UNS:G41400] Code allw. stress @ design temp. Sb 17.58 kgf/mm² Code allw. stress @ atm. temp. Sa 17.58 kgf/mm² Bolt PCD C 1363 mm Bolt dia. db 24 mm No. of bolts nb 56 M.O.C. Liner ID mm Liner OD mm Liner thk. mm M.O.C. Spiral metal wound CAF filled (S.S.) Gasket type Ring Gasket Gasket confinement type Unconfined Flange face type Raised Face Flange gakset surface finish Serrated (Normal) Counter flange face type Raised Face Counter gakset surface finish Serrated (Normal) Applicalbe gasket sketch in Table 2-5.2 Type 1B Applicable gasket column in Table 2-5.2 1 Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y 7.031 kgf/mm² Gasket factor ( from Table 2-5.1 ) m 3 Inside diameter Gi 1256 mm Outside diameter Go 1313.5 mm Width of gasket ( as per Table 2-5.2 ) N 28.75 mm Width of gasket ( as per Table 2-5.2 ) w 28.75 mm Width of raised face or gasket contact width 31.75 mm ( as per Table 2-5.2 ) Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm Effective gasket width ( as per Table 2-5.2 ) b 9.554 mm Dia. at load reaction ( see Table 2-5.2 ) G 1294.4 mm M.O.C. --
  • 20. 6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1) Total joint - contact surface compression load [Hp] = 2 x ( p x b x G x m + b' x Lp x m' ) x P = 2 x ( p x 9.554 x 1294.4 x 3 + 0 x 0 x 0 ) x 0.12 = 27973 kgf Total hydrostatic end force [H] = 0.25 x p x G ² x P = 0.25 x p x 1294.4 ² x 0.12 = 157907.4 kgf Minimum required bolt load for operating condition [Wm1a] = Hp + H = 27973 + 157907.4 = 185880.4 kgf Minimum required bolt load for operating condition [Wm1b] ( from mating flange ) = 185880.4 kgf Governing bolt load for operating condition [Wm1] = MAX [ Wm1a , Wm1b ] = MAX [ 185880.4 , 185880.4 ] = 185880.4 kgf 7. BOLT LOAD CALCULATION AS PER APPENDIX 2-5 (b2) Minimum required bolt load for gasket seating [Wm2] = ( p x b x G x y + b' x Lp x y' ) = ( p x 9.554 x 1294.4 x 7.031 + 0 x 0 x 0 ) = 273152.4 kgf 8. BOLT AREAS AS PER APPENDIX 2-5 (d) Total required cross-sectional area of bolts [Am] = MAX [ Wm2 / Sa , Wm1 / Sb ] ........ For Internal '+' Pr Design = Wm2 / Sa ..................................... For External Pr & Self Sealing Design = 15540.6 mm² Actual bolt area using root diameter [Ab] = 17513.9 mm² Flange design bolt load for the gasket seating [W] = 0.5 x ( Am + Ab ) x Sa x 1 .................... average bolt area = Ab x Sa x 1 ..........................................full bolt area = 307837.2 kgf ( Full bolt area and margin factor of 1 ) 9. CHECK FOR GASKET CRUSHING Minimum gasket width required [Nmin] = Ab x Sb / ( 2 x p x y x G ) = 17513.9 x 17.58 / ( 2 x p x 7.031 x 1294.4 ) = 5.384 mm 10. BOLT SPACING CORRECTION FACTOR As per Brownell & Young or IS 2825, = SQRT [ Bolt spacing / ( 2 x db + t ) ] As per TEMA or BS 5500, = SQRT [ Bolt spacing / Bmax ] ................... where, Bmax = maximum recommended bolt spacing = 2 x db + 6 x t / ( m + 0.5 ) Brownell & Young, Cf = 1 ( min. equal to 1 ) 11. LOADS AND FORCES DURING OPERATING CONDITION AS PER APPENDIX 2-3 Hydrostatic end force on area inside of flange [HD] = 0.25 x p x B 2 x P = 0.25 x p x 1256 2 x 0.12 = 148679.3 kgf Gasket load (difference between flange design bolt load and total hydrostatic end force) [HG] = Wm1 - H = 185880.4 - 157907.4 = 27973 kgf Difference between total hydrostatic end force and hydrostatic end force on area inside of flange [HT] = H - HD = 157907.4 - 148679.3 = 9228.2 kgf 12. MOMENT ARMS FOR FLANGE LOADS AS PER TABLE 2-6 Radial distance from the bolt circle to intersection of hub and back of flange, as per Appendix 2-3 [R] = 0.5 x ( C - B ) - g1 = 0.5 x ( 1363 - 1256 ) - 17 Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y' 0 kgf/mm² Gasket factor ( from Table 2-5.1 ) m' 0 Pass partition gasket width Wp 0 mm Pass partition gasket length Lp 0 mm Effective pass partition gasket width b' 0 mm INTEGRAL FLANGE DESIGN Shell Flng (Front)
  • 21. = 36.5 mm Radial distance from the bolt circle to the circle on which HD acts [hD] = R + 0.5 x g1 = 36.5 + 0.5 x 17 = 45 mm Radial distance from gasket load reaction to the bolt circle [hG] = 0.5 x ( C - G ) = 0.5 x ( 1363 - 1294.4 ) = 34.3 mm Radial distance from the bolt circle to the circle on which HT acts [hT] = 0.5 x ( R + g1 + hG ) = 0.5 x ( 36.5 + 17 + 34.3 ) = 43.9 mm 13. FLANGE MOMENTS UNDER OPERATING CONDITION AS PER APPENDIX 2-6 Component of moment due to HD [MD] = HD x hD = 148679.3 x 45 = 6690566.9 kgf-mm Component of moment due to HG [MG] = HG x hG = 27973 x 34.3 = 959588.9 kgf-mm Component of moment due to HT [MT] = HT x hT = 9228.2 x 43.9 = 405136.1 kgf-mm Total moment acting on the flange for operating condition [MO] = MD + MG + MT = 6690566.9 + 959588.9 + 405136.1 = 8055291.9 kgf-mm 14. LOADS AND FORCES DURING GASKET SEATING AS PER APPENDIX 2-3 Gasket load for seating condition [HG] = W = 307837.2 kgf 15. MOMENT UNDER GASKET SEATING AS PER APPENDIX 2-6 Total moment acting on the flange for gasket seating [MO'] = W x hG = 307837.2 x 34.3 = 10560086 kgf-mm 16. SHAPE CONSTANTS 17. STRESS FORMULA FACTORS Assumed thickness [t] = 108.7 mm Factor [a] = t x e + 1 = 108.7 x 0.00922 + 1 = 2.002 Factor [b] = 1.333 x t x e + 1 = 1.333 x 108.7 x 0.00922 + 1 = 2.336 Factor [g] = a / T = 2.002 / 1.866 = 1.073 Factor [d] = t 3 / d A / B K 1.131 Flange factors from Fig. 2-7.1 T 1.866 Z 8.189 Y 15.84 U 17.41 h0 93.77 F / h0 e 0.00922 Factor from Fig. 2-7.2 F 0.864 Factor from Fig. 2-7.3 V 0.261 g1 / g0 2.429 h / h0 0.32 ( U / V ) x h0 x g0 2 d 306079.1 Factor from Fig. 2-7.6 f 2.935
  • 22. = 108.7 3 / 306079.1 = 4.195 Factor [l] = g + d = 1.073 + 4.195 = 5.268 18. FLANGE STRESSES AS PER APPENDIX 2-7 & 2-8 Equivalent moment [Mmax] = MAX [ MO , MO' x Sfo / Sfa ] = MAX [ 8055291.9 , 10560086 x 14.06 / 14.06 ] = 10560086 kgf-mm Corrected equivalent moment per unit length [M] = Mmax x ( Cf / B ) = 10560086 x ( 1 / 1256 ) = 8407.7 kgf Longitudinal hub stress [SH] = f x M / ( l x g1 2 ) = 2.935 x 8407.7 / ( 5.268 x 17 2 ) Radial flange stress [SR] = b x M / ( l x t 2 ) = 2.336 x 8407.7 / ( 5.268 x 108.7 2 ) Tangential flange stress [ST] = ( M x Y / t 2 ) - Z x SR = ( 8407.7 x 15.84 / 108.7 2 ) - 8.189 x 0.316 Average stress = MAX [ 0.5 x ( SH + SR ) , 0.5 x ( SH + ST ) ] = MAX [ 0.5 x ( 16.21 + 0.316 ) , 0.5 x ( 16.21 + 8.69 ) ] 19. FLANGE RIGIDITY CHECKING AS PER APPENDIX 2-14 Rigidity index [J] = 52.14 x V x Mmax / ( l x Efo x g0 2 x KI x h0 ) = 52.14 x 0.261 x 10560086 / ( 5.268 x 19888.4 x 7 2 x 0.3 x 93.77 ) = 0.996 Since J < 1.0, design is safe = 16.21 kgf/mm² .................................... < 1.5 x Sfo = 0.316 kgf/mm² .................................... < Sfo = 8.69 kgf/mm² .................................... < Sfo = 12.45 kgf/mm² .................................... < Sfo Modulus of elasticity for flange Efo 19888.4 kgf/mm² Rigidity factor KI 0.3
  • 23. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition ) : 2. FLANGE DATA : 3. BOLTING DATA : 4. LINER DATA : 5. GASKET DATA : 5a. Flange gasket data : 5b. Partition groove gasket data (For H.E. body flange) : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 FLANGE DESIGN ( EXTERNAL ) Shell Flng (Front) CODE ASME VIII Div.1, 10 A11 Design pressure P 0.01055 kgf/mm² g Design temperature T 150 °C Allowance CA 3 mm Groove allowance Tg 0 mm M.O.C. SA-105 Frg. [UNS:K03504] Code allw. stress @ design temp. Sfo 14.06 kgf/mm² Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm² Inside diameter B 1256 mm Outside diameter A 1420 mm Hub length h 30 mm Thickness ( hub end ) g1 17 mm Thickness ( pipe end ) g0 7 mm Thickness provided 128.7 mm Thickness available 125.7 mm M.O.C. SA-193 GR. B7 Bolt [UNS:G41400] Code allw. stress @ design temp. Sb 17.58 kgf/mm² Code allw. stress @ atm. temp. Sa 17.58 kgf/mm² Bolt PCD C 1363 mm Bolt dia. db 24 mm No. of bolts nb 56 M.O.C. Liner ID mm Liner OD mm Liner thk. mm M.O.C. Spiral metal wound CAF filled (S.S.) Gasket type Ring Gasket Gasket confinement type Unconfined Flange face type Raised Face Flange gakset surface finish Serrated (Normal) Counter flange face type Raised Face Counter gakset surface finish Serrated (Normal) Applicalbe gasket sketch in Table 2-5.2 Type 1B Applicable gasket column in Table 2-5.2 1 Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y 7.031 kgf/mm² Gasket factor ( from Table 2-5.1 ) m 3 Inside diameter Gi 1256 mm Outside diameter Go 1313.5 mm Width of gasket ( as per Table 2-5.2 ) N 28.75 mm Width of gasket ( as per Table 2-5.2 ) w 28.75 mm Width of raised face or gasket contact width 31.75 mm ( as per Table 2-5.2 ) Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm Effective gasket width ( as per Table 2-5.2 ) b 9.554 mm Dia. at load reaction ( see Table 2-5.2 ) G 1294.4 mm M.O.C. --
  • 24. 6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1) Total joint - contact surface compression load [Hp] = 2 x ( p x b x G x m + b' x Lp x m' ) x P = 2 x ( p x 9.554 x 1294.4 x 3 + 0 x 0 x 0 ) x 0.01055 = 2458.4 kgf Total hydrostatic end force [H] = 0.25 x p x G ² x P = 0.25 x p x 1294.4 ² x 0.01055 = 13877.8 kgf Minimum required bolt load for operating condition [Wm1a] = Hp + H = 2458.4 + 13877.8 = 16336.3 kgf Minimum required bolt load for operating condition [Wm1b] ( from mating flange ) = 16336.3 kgf Governing bolt load for operating condition [Wm1] = MAX [ Wm1a , Wm1b ] = MAX [ 16336.3 , 16336.3 ] = 16336.3 kgf 7. BOLT LOAD CALCULATION AS PER APPENDIX 2-5 (b2) Minimum required bolt load for gasket seating [Wm2] = ( p x b x G x y + b' x Lp x y' ) = ( p x 9.554 x 1294.4 x 7.031 + 0 x 0 x 0 ) = 273152.4 kgf 8. BOLT AREAS AS PER APPENDIX 2-5 (d) Total required cross-sectional area of bolts [Am] = MAX [ Wm2 / Sa , Wm1 / Sb ] ........ For Internal '+' Pr Design = Wm2 / Sa ..................................... For External Pr & Self Sealing Design = 15540.6 mm² Actual bolt area using root diameter [Ab] = 17513.9 mm² Flange design bolt load for the gasket seating [W] = 0.5 x ( Am + Ab ) x Sa x 1 .................... average bolt area = Ab x Sa x 1 ..........................................full bolt area = 307837.2 kgf ( Full bolt area and margin factor of 1 ) 9. CHECK FOR GASKET CRUSHING Minimum gasket width required [Nmin] = Ab x Sb / ( 2 x p x y x G ) = 17513.9 x 17.58 / ( 2 x p x 7.031 x 1294.4 ) = 5.384 mm 10. BOLT SPACING CORRECTION FACTOR As per Brownell & Young or IS 2825, = SQRT [ Bolt spacing / ( 2 x db + t ) ] As per TEMA or BS 5500, = SQRT [ Bolt spacing / Bmax ] ................... where, Bmax = maximum recommended bolt spacing = 2 x db + 6 x t / ( m + 0.5 ) Brownell & Young, Cf = 1 ( min. equal to 1 ) 11. LOADS AND FORCES DURING OPERATING CONDITION AS PER APPENDIX 2-3 Hydrostatic end force on area inside of flange [HD] = 0.25 x p x B 2 x P = 0.25 x p x 1256 2 x 0.01055 = 13066.8 kgf Difference between total hydrostatic end force and hydrostatic end force on area inside of flange [HT] = H - HD = 13877.8 - 13066.8 = 811 kgf 12. MOMENT ARMS FOR FLANGE LOADS AS PER APPENDIX TABLE 2-6 Radial distance from the bolt circle to intersection of hub and back of flange, as per Appendix 2-3 [R] = 0.5 x ( C - B ) - g1 = 0.5 x ( 1363 - 1256 ) - 17 = 36.5 mm Radial distance from the bolt circle to the circle on which HD acts [hD] = R + 0.5 x g1 = 36.5 + 0.5 x 17 Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y' 0 kgf/mm² Gasket factor ( from Table 2-5.1 ) m' 0 Pass partition gasket width Wp 0 mm Pass partition gasket length Lp 0 mm Effective pass partition gasket width b' 0 mm INTEGRAL FLANGE DESIGN Shell Flng (Front)
  • 25. = 45 mm Radial distance from gasket load reaction to the bolt circle [hG] = 0.5 x ( C - G ) = 0.5 x ( 1363 - 1294.4 ) = 34.3 mm Radial distance from the bolt circle to the circle on which HT acts [hT] = 0.5 x ( R + g1 + hG ) = 0.5 x ( 36.5 + 17 + 34.3 ) = 43.9 mm 13. FLANGE MOMENTS UNDER OPERATING CONDITION AS PER APPENDIX 2-6 Component of moment due to HD [MD] = HD x ( hD - hG ) = 13066.8 x ( 45 - 34.3 ) = 139760.9 kgf-mm Component of moment due to HT [MT] = HT x ( hT - hG ) = 811 x ( 43.9 - 34.3 ) = 7784.2 kgf-mm Total moment acting on the flange for operating condition [MO] = MD + MT = 139760.9 + 7784.2 = 147545.1 kgf-mm 14. LOADS AND FORCES DURING GASKET SEATING AS PER APPENDIX 2-3 Gasket load for seating condition [HG] = W = 307837.2 kgf 15. MOMENT UNDER GASKET SEATING AS PER APPENDIX 2-6 Total moment acting on the flange for gasket seating [MO'] = W x hG = 307837.2 x 34.3 = 10560086 kgf-mm 16. SHAPE CONSTANTS 17. STRESS FORMULA FACTORS Assumed thickness [t] = 108.9 mm Factor [a] = t x e + 1 = 108.9 x 0.00922 + 1 = 2.004 Factor [b] = 1.333 x t x e + 1 = 1.333 x 108.9 x 0.00922 + 1 = 2.338 Factor [g] = a / T = 2.004 / 1.866 = 1.074 Factor [d] = t 3 / d = 108.9 3 / 306079.1 = 4.217 Factor [l] = g + d = 1.074 + 4.217 = 5.29 18. FLANGE STRESSES AS PER APPENDIX 2-7 & 2-8 Equivalent moment [Mmax] A / B K 1.131 Flange factors from Fig. 2-7.1 T 1.866 Z 8.189 Y 15.84 U 17.41 h0 93.77 F / h0 e 0.00922 Factor from Fig. 2-7.2 F 0.864 Factor from Fig. 2-7.3 V 0.261 g1 / g0 2.429 h / h0 0.32 ( U / V ) x h0 x g0 2 d 306079.1 Factor from Fig. 2-7.6 f 2.935
  • 26. = MAX [ MO , MO' x Sfo / Sfa ] = MAX [ 147545.1 , 10560086 x 14.06 / 14.06 ] = 10560086 kgf-mm Corrected equivalent moment per unit length [M] = Mmax x ( Cf / B ) = 10560086 x ( 1 / 1256 ) = 8407.7 kgf Longitudinal hub stress [SH] = f x M / ( l x g1 2 ) = 2.935 x 8407.7 / ( 5.29 x 17 2 ) Radial flange stress [SR] = b x M / ( l x t 2 ) = 2.004 x 8407.7 / ( 5.29 x 108.9 2 ) Tangential flange stress [ST] = ( M x Y / t 2 ) - Z x SR = ( 8407.7 x 15.84 / 108.9 2 ) - 8.189 x 0.313 Average stress = MAX [ 0.5 x ( SH + SR ) , 0.5 x ( SH + ST ) ] = MAX [ 0.5 x ( 16.14 + 0.313 ) , 0.5 x ( 16.14 + 8.669 ) ] 19. FLANGE RIGIDITY CHECKING AS PER APPENDIX AS PER 2-14 Rigidity index [J] = 52.14 x V x Mmax / ( l x Efo x g0 2 x KI x h0 ) = 52.14 x 0.261 x 10560086 / ( 5.29 x 19888.4 x 7 2 x 0.3 x 93.77 ) = 0.992 Since J < 1.0, design is safe = 16.14 kgf/mm² .................................... < 1.5 x Sfo = 0.313 kgf/mm² .................................... < Sfo = 8.669 kgf/mm² .................................... < Sfo = 12.4 kgf/mm² .................................... < Sfo Modulus of elasticity for flange Efo 19888.4 kgf/mm² Rigidity factor KI 0.3
  • 27. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition ) 2. DESIGN CALCULATION AS PER UG-27 Thickness of shell under internal pressure [ti] = Pi x R / ( S x E - 0.6 x Pi ) = 0.12 x 628 / ( 14.06 x 0.85 - 0.6 x 0.12 ) = 6.343 mm 3. DESIGN CALCULATION OF SHELL THICKNESS UNDER EXTERNAL PRESSURE AS PER UG-28 Allowable external pressure [Pa] = 4 x B / ( 3 x ( OD / te ) ) = 4 x 2.272 / ( 3 x 284.4 ) = 0.01065 kgf/mm² g Since Pa > Pe, design is safe Since available thickness is more than design thickness, design is safe. Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 DESIGN OF SHELL ( INTERNAL AND EXTERNAL PRESSURE ) Main Shell CODE ASME VIII Div.1, 10 A11 Design pressure ( internal ) Pi 0.12 kgf/mm² g Design pressure ( external ) Pe 0.01055 kgf/mm² g Design temperature T 150 °C Material of construction SA-516 GR. 70 Plt. [UNS:K02700] Max. allowable stress at design temp. S 14.06 kgf/mm² Radiography Spot + T Joints Joint efficiency long. seam Ec 0.85 Outside diameter OD 1270 mm Inside radius ( corroded ) R 628 mm Shell length L 1650 mm Design length L1 1650 mm Nominal thickness 10 mm Nominal thickness required as per TEMA N.A. mm Internal allowance, corrosion + polishing 3 mm External allowance, corrosion + polishing 0 mm Thickness undertolerance 0 mm Available thickness 7 mm Assumed te 4.466 mm L1 / OD 1.299 OD / te 284.4 Factor A ( Refer to Fig. G in Subpart 3 of Sec. II, Part D ) 0.00021 Factor B ( CS-2 ) 2.272 kgf/mm²
  • 28. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition ) : 2. DESIGN CALCULATION AS PER UG 32 d / APPENDIX 1-4 ( c ) : Factor [K] = 1 Thickness for internal pressure [t] = K x Pi x ID / ( 2 x S x E - 0.2 x Pi ) = 1 x 0.12 x 1256 / ( 2 x 14.06 x 1 - 0.2 x 0.12 ) = 5.364 mm 3. DESIGN CALCULATION AS PER UG 33 d : Thickness for equivalent external pressure [t] = K x 1.67 x Pe x ID / ( 2 x S x 1.0 - 0.2 x 1.67 x Pe ) = 1 x 1.67 x 0.01055 x 1256 / ( 2 x 14.06 x 1.0 - 0.2 x 1.67 x 0.01055 ) = 0.787 mm Factor [Ko] = 0.77 Assumed head thickness, [te] = 2.779 mm Factor [A] = 0.125 x te / ( Ko x OD ) = 0.125 x 2.779 / ( 0.77 x 1270 ) = 0.00036 Factor with reference to chart (CS-2) [B] = 3.743 kgf/mm² Allowable external pressure [Pa] = B / ( Ko x OD / te ) = 3.743 x 2.779 / ( 0.77 x 1270 ) = 0.01064 kgf/mm² Since Pa > Pe, design is safe Since available thickness is more than design thickness, design is safe. Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 DESIGN OF ELLIPSOIDAL HEAD ( INT. & EXT. PRESSURE ) Dished End (Rear) CODE ASME VIII Div.1, 10 A11 Design pressure ( internal ) Pi 0.12 kgf/mm² g Design pressure ( external ) Pe 0.01055 kgf/mm² g Design temperature T 150 °C Material of construction SA-516 GR. 70 Plt. [UNS:K02700] Max. allowable stress @ design temp. S 14.06 kgf/mm² Radiography Full Joint efficiency E 1 Outside diameter of head OD 1270 mm Inside diameter of shell ID 1256 mm Head shape Elliptical D/2H = 2.0 Nominal thickness 10 mm Nominal thickness required as per TEMA N.A mm Internal allowance, corrosion + polishing 3 mm External allowance, corrosion + polishing 0 mm Thinning allowance / Under tolerance 1 mm Available thickness 6 mm 109
  • 29. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. LUG DATA : 2. BOLT DATA : 3. GUSSET DATA : 4. SHELL DATA : 5. PAD DATA : 6. LOAD AND MOMENT ( Wind ) : 7. DESIGN OF ANCHOR BOLTS : Total uplift force on bolts [T] = [ 4 x M / ( D x N ) ] - Wt / N = [ 4 x 940925.4 / ( 1570 x 4 ) ] - 2388.5 / 4 = 2.203 kgf Required area of bolts [Am] = MAX [ ( T / Fs ) , 0 ] = MAX [ ( 2.203 / 20.88 ) , 0 ] = 0.106 mm² Available area of bolts [Ab] = Ar x Nb ........................................................................................ where, Ar = 217.1 mm², is root area of bolt = 217.1 x 1 = 217.1 mm² Since Ab > Am, bolts provided are sufficient 8. GUSSET DESIGN : Reaction force at each support [Q] = [ 4 x M / ( D x N ) ] + Wt / N Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 LUG SUPPORT DESIGN Lug Support CODE P V Design Manual, D.R. Moss Design Mode 1 , Corroded Condition M.O.C IS-2062 GR. A Plt. No. of support N 4 Base plate width b1 242 mm Base plate depth Lb 200 mm Thickness of base plate tb 16 mm Allowable bending stress Sb 22.15 kgf/mm² M.O.C Commercial CS Bolt No. of bolt / lug Nb 1 Bolt diameter db 20 mm PCD D 1570 mm Diameter of bolt hole 24 mm Allowable tensile stress Fs 20.88 kgf/mm² Thickness tg 16 mm Height h 190 mm Gusset angle θ 51.71 Gusset depth at top Lc 50 mm Number of gussets n 2 Distance between gussets b 200 mm Material SA-516 GR. 70 Plt. [UNS:K02700] OD diameter OD 1270 mm Inside diameter ID 1256 mm Thickness available ts 7 mm Material SA-516 GR. 70 Plt. [UNS:K02700] Thickness tp 10 mm Width W 270 mm Length L 292 mm Max. overturning moment M 940925.4 kgf-mm Design weight of vessel Wt 2388.5 kgf
  • 30. = [ 4 x 940925.4 / ( 1570 x 4 ) ] + 2388.5 / 4 = 1196.4 kgf Maximum axial force in gusset [P1] = Q / n = 1196.4 / 2 = 598.2 kgf Allowable compr. stress in gusset [Sg] = 1800 / [ ( 1 + 12 / 18000 ) x ( h’ / tg ) 2 ] ....................................... where, h’ = 242.1 mm = 1800 / [ ( 1 + 12 / 18000 ) x ( 242.1 / 16 ) 2 ] = 15616.8 psi = 10.98 kgf/mm² Required thickness of gusset [tg’] = 2 x P1 x ( 3 x a - Lb ) / [ Sg x Lb 2 x ( sin θ ) 2 ] = 2 x 598.2 x ( 3 x 150 - 200 ) / [ 10.98 x ( 200 ) 2 x ( sin 51.71 ) 2 ] = 1.106 mm 9. BASE PLATE DESIGN : Bending moment [Mb] = Q x b1 / 6 = 1196.4 x 242 / 6 = 48255.9 kgf-mm Bearing pressure [bp] = Q / ( w x b1 ) ............................................................................... where, w = 120 mm = 1196.4 / ( 120 x 242 ) = 0.0412 kgf/mm² Bending moment due to bearing pressure [Mb’] = bp x b 2 / 10 = 0.0412 x 200 2 / 10 = 164.8 kgf-mm Required thickness of base plate between chairs [tb’] = SQRT { 6 x MAX [ Mb , Mb' ] / [ ( Lb - db ) x Sb ] } = SQRT { 6 x MAX [ 48255.9 , 164.8 ] / [ ( 200 - 20 ) x 22.15 ] } = 8.619 mm 10. CHECK FOR COMPRESSION PLATE : Equivalent radial load [f] = Q x a / h = 1196.4 x 150 / 190 = 472.3 kgf Angle between supports [b] = 2 x p / N = 2 x p / 4 = 1.571 rad Internal bending moment coefficient [Kr] = 0.5 x [ 1 / a - cot ( a ) ] = 0.5 x [ 1 / 1.571 - cot ( 1.571 ) ] = 0.318 Internal bending moment [Mc] = 0.5 x Kr x f x OD = 0.5 x 0.318 x 472.3 x 1270 = 95459.3 kgf-mm Bending stress induced [fb] = Mo / Zc = 95459.3 / 7785.1 = 12.26 kgf/mm² ......................................................................... < Sb = 22.15 kgf/mm² Since, induced stress fb < allow. stress Sb in shell material, design is safe.
  • 31. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. LUG DATA : 2. BOLT DATA : 3. GUSSET DATA : 4. SHELL DATA : 5. PAD DATA : 6. LOAD AND MOMENT ( Seismic ) : 7. DESIGN OF ANCHOR BOLTS : Total uplift force on bolts [T] = [ 4 x M / ( D x N ) ] - Wt / N = [ 4 x 288590.5 / ( 1570 x 4 ) ] - 1841.2 / 4 = -276.5 kgf Required area of bolts [Am] = MAX [ ( T / Fs ) , 0 ] = MAX [ ( -276.5 / 20.88 ) , 0 ] = 0 mm² Available area of bolts [Ab] = Ar x Nb ........................................................................................ where, Ar = 217.1 mm², is root area of bolt = 217.1 x 1 = 217.1 mm² Since Ab > Am, bolts provided are sufficient 8. GUSSET DESIGN : Reaction force at each support [Q] = [ 4 x M / ( D x N ) ] + Wt / N Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 LUG SUPPORT DESIGN Lug Support CODE P V Design Manual, D.R. Moss Design Mode 1 , Corroded Condition M.O.C IS-2062 GR. A Plt. No. of support N 4 Base plate width b1 242 mm Base plate depth Lb 200 mm Thickness of base plate tb 16 mm Allowable bending stress Sb 22.15 kgf/mm² M.O.C Commercial CS Bolt No. of bolt / lug Nb 1 Bolt diameter db 20 mm PCD D 1570 mm Diameter of bolt hole 24 mm Allowable tensile stress Fs 20.88 kgf/mm² Thickness tg 16 mm Height h 190 mm Gusset angle θ 51.71 Gusset depth at top Lc 50 mm Number of gussets n 2 Distance between gussets b 200 mm Material SA-516 GR. 70 Plt. [UNS:K02700] OD diameter OD 1270 mm Inside diameter ID 1256 mm Thickness available ts 7 mm Material SA-516 GR. 70 Plt. [UNS:K02700] Thickness tp 10 mm Width W 270 mm Length L 292 mm Max. overturning moment M 288590.5 kgf-mm Design weight of vessel Wt 1841.2 kgf
  • 32. = [ 4 x 288590.5 / ( 1570 x 4 ) ] + 1841.2 / 4 = 644.1 kgf Maximum axial force in gusset [P1] = Q / n = 644.1 / 2 = 322.1 kgf Allowable compr. stress in gusset [Sg] = 1800 / [ ( 1 + 12 / 18000 ) x ( h’ / tg ) 2 ] ....................................... where, h’ = 242.1 mm = 1800 / [ ( 1 + 12 / 18000 ) x ( 242.1 / 16 ) 2 ] = 15616.8 psi = 10.98 kgf/mm² Required thickness of gusset [tg’] = 2 x P1 x ( 3 x a - Lb ) / [ Sg x Lb 2 x ( sin θ ) 2 ] = 2 x 322.1 x ( 3 x 150 - 200 ) / [ 10.98 x ( 200 ) 2 x ( sin 51.71 ) 2 ] = 0.595 mm 9. BASE PLATE DESIGN : Bending moment [Mb] = Q x b1 / 6 = 644.1 x 242 / 6 = 25979.7 kgf-mm Bearing pressure [bp] = Q / ( w x b1 ) ............................................................................... where, w = 120 mm = 644.1 / ( 120 x 242 ) = 0.02218 kgf/mm² Bending moment due to bearing pressure [Mb’] = bp x b 2 / 10 = 0.02218 x 200 2 / 10 = 88.72 kgf-mm Required thickness of base plate between chairs [tb’] = SQRT { 6 x MAX [ Mb , Mb' ] / [ ( Lb - db ) x Sb ] } = SQRT { 6 x MAX [ 25979.7 , 88.72 ] / [ ( 200 - 20 ) x 22.15 ] } = 6.324 mm 10. CHECK FOR COMPRESSION PLATE : Equivalent radial load [f] = Q x a / h = 644.1 x 150 / 190 = 254.3 kgf Angle between supports [b] = 2 x p / N = 2 x p / 4 = 1.571 rad Internal bending moment coefficient [Kr] = 0.5 x [ 1 / a - cot ( a ) ] = 0.5 x [ 1 / 1.571 - cot ( 1.571 ) ] = 0.318 Internal bending moment [Mc] = 0.5 x Kr x f x OD = 0.5 x 0.318 x 254.3 x 1270 = 51392.7 kgf-mm Bending stress induced [fb] = Mo / Zc = 51392.7 / 7785.1 = 6.601 kgf/mm² ......................................................................... < Sb = 22.15 kgf/mm² Since, induced stress fb < allow. stress Sb in shell material, design is safe.
  • 33. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in DESIGN CONDITIONS NOZZLE DATA SHELL DATA ( Main Shell ) WELD DATA CALCULATION OF NOZZLE NECK THICKNESS AS PER UG 45 Neck thickness for internal pressure as per UG 45(a) Formula in Appendix 1-1 , [trn1] = ( 0.5 x Pi x OD ) / ( Sn x E + 0.4 x Pi ) = ( 0.5 x 0.12 x 168.3 ) / ( 12.02 x 1.0 + 0.4 x 0.12 ) = 0.983 mm Neck thickness for external pressure as per UG 45(a) Neck thickness for external pressure as per UG 28 Assumed neck thickness , [trn3] = 0.512 mm L / OD = 0.891 OD / trn3 = 328.5 Factor A = 0.00025 Factor B = 2.679 kgf/mm² Allowable external pressure , [Pa] = 4 x B / ( 3 x OD / trn3 ) = 4 x 2.679 / ( 3 x 328.5 ) = 0.01088 kgf/mm² g Thickness of shell as per UG 45(b)(1) Min. shell thickness reqd. as per UG 27 , [tr1 = trn2] = Pi x R / ( Sv x E - 0.6 x Pi ) = 0.12 x 628 / ( 14.06 x 1.0 - 0.6 x 0.12 ) = 5.387 mm Thickness for equivalent pressure as per UG 45(b)(2) , [trn4] = Pe x R / ( Sv x E - 0.6 x Pe ) Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 NOZZLE NECK THICKNESS AND REINFORCEMENT DESIGN N 01 CODE ASME VIII Div.1, 10 A11 Design Mode 1 , Corroded Condition Design pressure ( internal ) Pi 0.12 kgf/mm² g Design pressure ( external ) Pe 0.01055 kgf/mm² g Design temperature T 150 °C M.O.C. SA-106 GR. B Smls. Pipe [UNS:K03006] Allowable stress @ design temperature Sn 12.02 kgf/mm² Outside diameter OD 168.3 mm Inside diameter ID 152.3 mm Maximum chord length D 152.3 mm Neck thickness ( provided ) tnp 10.97 mm Internal allowance , corrosion + polishing CAI 3 mm External allowance , corrosion + polishing CAE 0 Neck thickness (tnp - CAI - CAE) tn 7.973 mm Max. under tolerance on thickness Alw 1.372 mm Available neck thickness ( tn - Alw ) ta 6.601 mm Nozzle projection outward ( from vessel outer face ) Lo 150 mm Total length of nozzle ( Lo + Addn for curvature) L 156 mm Connection type Pipe Nozzle Application type Process Opening Reinforcement calculation method Isolated Opening Design as large opening False M.O.C. SA-516 GR. 70 Plt. [UNS:K02700] Allowable stress @ design temperature Sv 14.06 kgf/mm² Inside radius R 628 mm Thickness t 7 mm Min. thickness for external pressure tr2 4.466 mm Nozzle outside weld W1 7 mm
  • 34. = 0.01055 x 628 / ( 14.06 x 1.0 - 0.6 x 0.01055 ) = 0.471 mm Standard wall thickness as per UG 45(b)(4) , [t3] = 7.112 mm Neck thk as per UG 45 , [trn] = MAX { MAX [ trn1, trn3 ] , MIN [ MAX ( trn2 , trn4 ) , 0.875 x t3 ] } ..... for Process Nozzle = MAX [ trn1, trn3 ] ............................................................................ for Access Opening = 5.387 mm .................................................................................... Process Opening Since available neck thickness, ta >= trn, selected neck thickness is adequate.
  • 35. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITION : 2. ATTACHMENT DATA : 3. EXTERNAL LOADS : 4. SHELL DATA : 5. STRESS CONCENTRATION FACTORS : 6. COMPUTING STRESSES : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 LOCAL STRESS ANALYSIS (EDGE OF ATTACHMENT) N 01 CODE D.R. MOSS (EXTRACT OF WRC 107) Design Mode 1, Corroded Condition Design pressure ( internal ) Pi 0.12 kgf/mm² g Design temperature T 150 °C M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006] Outside diameter OD 168.3 mm Weld size w 7 mm Pad diameter Dp 292.7 mm Pad thickness tp 10 mm 0.5 x OD C 84.14 mm Radial force Fr 344.6 kgf Long. moment ML 254724.1 kgf-mm Circ. moment Mc 254724.1 kgf-mm Torsional moment Mt 254724.1 kgf-mm Total eff. shear load Q 487.4 kgf M.O.C SA-516 GR. 70 Plt. [UNS:K02700] Allowable stress Sv 14.06 kgf/mm² Inside radius R 628 mm Thickness of shell tv 7 mm Mean radius of shell , [ Rm ] = R + 0.5 x ( tv + tp ) = 628 + 0.5 x ( 7 + 10 ) = 636.5 mm Thickness , [t] = SQRT [ tv 2 + tp 2 ] = SQRT [ 7 2 + 10 2 ] = 12.21 mm Calculate ratio , [ g ] = Rm / te = 636.5 / 12.21 = 52.14 Calculate ratio , [ b ] = 0.875 x C / Rm = 0.875 x 84.14 / 636.5 = 0.116 Factor , [ Kn ] = 1 Factor , [ Kb ] = 1 Shear stress due to Q , [ t1 ] = Q / ( p x Ro x t ) = 487.4 / ( p x 84.14 x 12.21 ) = 0.151 kgf/mm² Shear stress due to Mt , [ t2 ] = Mt / ( 2 x p x Ro 2 x t ) = 254724.1 / ( 2 x p x 84.14 2 x 12.21 ) = 0.469 kgf/mm² Total shear stress , [ t ] = t1 + t2 = 0.151 + 0.469 = 0.62 kgf/mm² STRESSES FACT FIG. FORCES( kgf ) & MOMENTS( kgf-mm ) STRESS ( kgf/mm² ) Radial load Membrane 5-17A 7.023 x Fr Rm Nf 3.803 Kn x Nf t σf 0.312 5-17B 8.616 x Fr Rm Nx 4.665 Kn x Nx t σx 0.382 Bending 5-18A 0.117 x Fr Mf 40.25 6 x Kb x Mf t 2 σf 1.621 6 x Kb x Mx
  • 36. 7. COMBINING STRESSES : ** Only absolute values of quantities in bracket shall be used while combining stresses ( 1 ) : Fr sign is (+) for outward load, & (-) for inward load. Allowabe Stresses for various catergories: 1. Membrane only, Sm = 1.5 x Sv 2. Membrane + Bending, Sa = 3 x Sv 3. Shear only, Sh = 0.5 x Sv DESIGN IS ACCEPTABLE ? : YES 5-18B 0.0707 x Fr Mx 24.37 t 2 σx 0.981 Long. moment Membrane CL=1 5-19A 3.516 x CL x ML Rm 2 x b Nf 19.11 Kn x Nf t σf 1.566 CL=1 5-19B 1.697 x CL x ML Rm 2 x b Nx 9.222 Kn x Nx t σx 0.756 Bending 5-20A 0.03827 x ML Rm x b Mf 132.4 6 x Kb x Mf t 2 σf 5.331 5-20B 0.06937 x ML Rm x B Mx 240 6 x Kb x Mx t 2 σx 9.665 Circ. moment Membrane Cc=1 5-21A 1.893 x Cc x Mc Rm 2 x b Nf 10.29 Kn x Nf t σf 0.843 Cc=1 5-21B 2.973 x Cc x Mc Rm 2 x b Nx 16.16 Kn x Nx t σx 1.324 Bending 5-22A 0.09066 x Mc Rm x b Mf 313.7 6 x Kb x Mf t 2 σf 12.63 5-22B 0.04678 x Mc Rm x b Mx 161.9 6 x Kb x Mx t 2 σx 6.518 Stress due to σx σf 0° 90° 180° 270° 0° 90° 180° 270° Radial load, Fr.(1) Membrane Nf 0.312 0.312 0.312 0.312 Nx 0.382 0.382 0.382 0.382 Bending Mf 1.621 1.621 1.621 1.621 Mx 0.981 0.981 0.981 0.981 Long. moment, ML. Membrane Nf + ( 1.566 ) -( 1.566 ) Nx + ( 0.756 ) -( 0.756 ) Bending Mf + ( 5.331 ) -( 5.331 ) Mx + ( 9.665 ) -( 9.665 ) Circ moment, Mc. Membrane Nf + ( 0.843 ) -( 0.843 ) Nx + ( 1.324 ) -( 1.324 ) Bending Mf + ( 12.63 ) - ( 12.63 ) Mx + ( 6.518 ) -( 6.518 ) Int. pr., P. Pi x Rm t σf + ( 10.91 ) + ( 10.91) + ( 10.91 ) + ( 10.91 ) Pi x Rm 2 x t σx + ( 5.456 ) + ( 5.456 ) + ( 5.456 ) + ( 5.456 ) Total, ∑ Membrane 6.593 7.162 5.082 4.514 12.86 12.14 9.728 10.45 Mem+Bend 17.24 14.66 -3.601 -1.023 19.74 26.32 5.946 -0.631
  • 37. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITION : 2. ATTACHMENT DATA : 3. EXTERNAL LOADS : 4. SHELL DATA : 5. STRESS CONCENTRATION FACTORS : 6. COMPUTING STRESSES : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 LOCAL STRESS ANALYSIS (EDGE OF PAD) N 01 CODE D.R. MOSS (EXTRACT OF WRC 107) Design Mode 1, Corroded Condition Design pressure ( internal ) Pi 0.12 kgf/mm² g Design temperature T 150 °C M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006] Outside diameter OD 168.3 mm Weld size w 7 mm Pad diameter Dp 292.7 mm Pad thickness tp 0 mm 0.5 x OD C 146.3 mm Radial force Fr 344.6 kgf Long. moment ML 254724.1 kgf-mm Circ. moment Mc 254724.1 kgf-mm Torsional moment Mt 254724.1 kgf-mm Total eff. shear load Q 487.4 kgf M.O.C SA-516 GR. 70 Plt. [UNS:K02700] Allowable stress Sv 14.06 kgf/mm² Inside radius R 628 mm Thickness of shell t 7 mm Mean radius of shell , [ Rm ] = R + 0.5 x t = 628 + 0.5 x 7 = 631.5 mm Calculate ratio , [ g ] = Rm / t = 631.5 / 7 = 90.21 Calculate ratio , [ b ] = 0.875 x C / Rm = 0.875 x 146.3 / 631.5 = 0.203 Factor , [ Kn ] = 1 Factor , [ Kb ] = 1 Shear stress due to Q , [ t1 ] = Q / ( p x Ro x t ) = 487.4 / ( p x 146.3 x 7 ) = 0.151 kgf/mm² Shear stress due to Mt , [ t2 ] = Mt / ( 2 x p x Ro 2 x t ) = 254724.1 / ( 2 x p x 146.3 2 x 7 ) = 0.27 kgf/mm² Total shear stress , [ t ] = t1 + t2 = 0.151 + 0.27 = 0.422 kgf/mm² STRESSES FACT FIG. FORCES( kgf ) & MOMENTS( kgf-mm ) STRESS ( kgf/mm² ) Radial load Membrane 5-17A 4.941 x Fr Rm Nf 2.696 Kn x Nf t σf 0.385 5-17B 11.06 x Fr Rm Nx 6.037 Kn x Nx t σx 0.862 Bending 5-18A 0.04175 x Fr Mf 14.39 6 x Kb x Mf t 2 σf 1.762 6 x Kb x Mx
  • 38. 7. COMBINING STRESSES : ** Only absolute values of quantities in bracket shall be used while combining stresses ( 1 ) : Fr sign is (+) for outward load, & (-) for inward load. Allowabe Stresses for various catergories: 1. Membrane only, Sm = 1.5 x Sv 2. Membrane + Bending, Sa = 3 x Sv 3. Shear only, Sh = 0.5 x Sv DESIGN IS ACCEPTABLE ? : YES 5-18B 0.01857 x Fr Mx 6.398 t 2 σx 0.783 Long. moment Membrane CL=1 5-19A 6.231 x CL x ML Rm 2 x b Nf 19.63 Kn x Nf t σf 2.804 CL=1 5-19B 3.293 x CL x ML Rm 2 x b Nx 10.38 Kn x Nx t σx 1.482 Bending 5-20A 0.0128 x ML Rm x b Mf 25.46 6 x Kb x Mf t 2 σf 3.117 5-20B 0.01693 x ML Rm x B Mx 33.68 6 x Kb x Mx t 2 σx 4.124 Circ. moment Membrane Cc=1 5-21A 3.869 x Cc x Mc Rm 2 x b Nf 12.19 Kn x Nf t σf 1.741 Cc=1 5-21B 7.986 x Cc x Mc Rm 2 x b Nx 25.16 Kn x Nx t σx 3.594 Bending 5-22A 0.06043 x Mc Rm x b Mf 120.2 6 x Kb x Mf t 2 σf 14.72 5-22B 0.026 x Mc Rm x b Mx 51.73 6 x Kb x Mx t 2 σx 6.334 Stress due to σx σf 0° 90° 180° 270° 0° 90° 180° 270° Radial load, Fr.(1) Membrane Nf ( 0.385 ) ( 0.385) ( 0.385 ) ( 0.385 ) Nx ( 0.862 ) ( 0.862 ) ( 0.862 ) ( 0.862 ) Bending Mf ( 1.762 ) ( 1.762 ) ( 1.762 ) ( 1.762 ) Mx ( 0.783 ) ( 0.783 ) ( 0.783 ) ( 0.783 ) Long. moment, ML. Membrane Nf + ( 2.804 ) -( 2.804 ) Nx + ( 1.482 ) -( 1.482 ) Bending Mf + ( 3.117 ) -( 3.117 ) Mx + ( 4.124 ) -( 4.124 ) Circ moment, Mc. Membrane Nf + ( 1.741 ) -( 1.741 ) Nx + ( 3.594 ) -( 3.594 ) Bending Mf + ( 14.72 ) - ( 14.72 ) Mx + ( 6.334 ) -( 6.334 ) Int. pr., P. Pi x Rm t σf + ( 10.83 ) + ( 10.83) + ( 10.83 ) + ( 10.83 ) Pi x Rm 2 x t σx + ( 5.413 ) + ( 5.413 ) + ( 5.413 ) + ( 5.413 ) Total, ∑ Membrane 7.757 9.869 4.793 2.681 14.49 13.43 8.884 9.947 Mem+Bend 12.67 16.99 1.452 -2.87 18.89 29.44 7.051 -3.49
  • 39. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in DESIGN CONDITIONS NOZZLE DATA SHELL DATA ( Main Shell ) WELD DATA CALCULATION OF NOZZLE NECK THICKNESS AS PER UG 45 Neck thickness for internal pressure as per UG 45(a) Formula in Appendix 1-1 , [trn1] = ( 0.5 x Pi x OD ) / ( Sn x E + 0.4 x Pi ) = ( 0.5 x 0.12 x 168.3 ) / ( 12.02 x 1.0 + 0.4 x 0.12 ) = 0.983 mm Neck thickness for external pressure as per UG 45(a) Neck thickness for external pressure as per UG 28 Assumed neck thickness , [trn3] = 0.512 mm L / OD = 0.891 OD / trn3 = 328.5 Factor A = 0.00025 Factor B = 2.679 kgf/mm² Allowable external pressure , [Pa] = 4 x B / ( 3 x OD / trn3 ) = 4 x 2.679 / ( 3 x 328.5 ) = 0.01088 kgf/mm² g Thickness of shell as per UG 45(b)(1) Min. shell thickness reqd. as per UG 27 , [tr1 = trn2] = Pi x R / ( Sv x E - 0.6 x Pi ) = 0.12 x 628 / ( 14.06 x 1.0 - 0.6 x 0.12 ) = 5.387 mm Thickness for equivalent pressure as per UG 45(b)(2) , [trn4] = Pe x R / ( Sv x E - 0.6 x Pe ) Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 NOZZLE NECK THICKNESS AND REINFORCEMENT DESIGN N 02 CODE ASME VIII Div.1, 10 A11 Design Mode 1 , Corroded Condition Design pressure ( internal ) Pi 0.12 kgf/mm² g Design pressure ( external ) Pe 0.01055 kgf/mm² g Design temperature T 150 °C M.O.C. SA-106 GR. B Smls. Pipe [UNS:K03006] Allowable stress @ design temperature Sn 12.02 kgf/mm² Outside diameter OD 168.3 mm Inside diameter ID 152.3 mm Maximum chord length D 152.3 mm Neck thickness ( provided ) tnp 10.97 mm Internal allowance , corrosion + polishing CAI 3 mm External allowance , corrosion + polishing CAE 0 Neck thickness (tnp - CAI - CAE) tn 7.973 mm Max. under tolerance on thickness Alw 1.372 mm Available neck thickness ( tn - Alw ) ta 6.601 mm Nozzle projection outward ( from vessel outer face ) Lo 150 mm Total length of nozzle ( Lo + Addn for curvature) L 156 mm Connection type Pipe Nozzle Application type Process Opening Reinforcement calculation method Isolated Opening Design as large opening False M.O.C. SA-516 GR. 70 Plt. [UNS:K02700] Allowable stress @ design temperature Sv 14.06 kgf/mm² Inside radius R 628 mm Thickness t 7 mm Min. thickness for external pressure tr2 4.466 mm Nozzle outside weld W1 7 mm
  • 40. = 0.01055 x 628 / ( 14.06 x 1.0 - 0.6 x 0.01055 ) = 0.471 mm Standard wall thickness as per UG 45(b)(4) , [t3] = 7.112 mm Neck thk as per UG 45 , [trn] = MAX { MAX [ trn1, trn3 ] , MIN [ MAX ( trn2 , trn4 ) , 0.875 x t3 ] } ..... for Process Nozzle = MAX [ trn1, trn3 ] ............................................................................ for Access Opening = 5.387 mm .................................................................................... Process Opening Since available neck thickness, ta >= trn, selected neck thickness is adequate.
  • 41. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITION : 2. ATTACHMENT DATA : 3. EXTERNAL LOADS : 4. SHELL DATA : 5. STRESS CONCENTRATION FACTORS : 6. COMPUTING STRESSES : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 LOCAL STRESS ANALYSIS (EDGE OF ATTACHMENT) N 02 CODE D.R. MOSS (EXTRACT OF WRC 107) Design Mode 1, Corroded Condition Design pressure ( internal ) Pi 0.12 kgf/mm² g Design temperature T 150 °C M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006] Outside diameter OD 168.3 mm Weld size w 7 mm Pad diameter Dp 292.7 mm Pad thickness tp 10 mm 0.5 x OD C 84.14 mm Radial force Fr 344.6 kgf Long. moment ML 254724.1 kgf-mm Circ. moment Mc 254724.1 kgf-mm Torsional moment Mt 254724.1 kgf-mm Total eff. shear load Q 487.4 kgf M.O.C SA-516 GR. 70 Plt. [UNS:K02700] Allowable stress Sv 14.06 kgf/mm² Inside radius R 628 mm Thickness of shell tv 7 mm Mean radius of shell , [ Rm ] = R + 0.5 x ( tv + tp ) = 628 + 0.5 x ( 7 + 10 ) = 636.5 mm Thickness , [t] = SQRT [ tv 2 + tp 2 ] = SQRT [ 7 2 + 10 2 ] = 12.21 mm Calculate ratio , [ g ] = Rm / te = 636.5 / 12.21 = 52.14 Calculate ratio , [ b ] = 0.875 x C / Rm = 0.875 x 84.14 / 636.5 = 0.116 Factor , [ Kn ] = 1 Factor , [ Kb ] = 1 Shear stress due to Q , [ t1 ] = Q / ( p x Ro x t ) = 487.4 / ( p x 84.14 x 12.21 ) = 0.151 kgf/mm² Shear stress due to Mt , [ t2 ] = Mt / ( 2 x p x Ro 2 x t ) = 254724.1 / ( 2 x p x 84.14 2 x 12.21 ) = 0.469 kgf/mm² Total shear stress , [ t ] = t1 + t2 = 0.151 + 0.469 = 0.62 kgf/mm² STRESSES FACT FIG. FORCES( kgf ) & MOMENTS( kgf-mm ) STRESS ( kgf/mm² ) Radial load Membrane 5-17A 7.023 x Fr Rm Nf 3.803 Kn x Nf t σf 0.312 5-17B 8.616 x Fr Rm Nx 4.665 Kn x Nx t σx 0.382 Bending 5-18A 0.117 x Fr Mf 40.25 6 x Kb x Mf t 2 σf 1.621 6 x Kb x Mx
  • 42. 7. COMBINING STRESSES : ** Only absolute values of quantities in bracket shall be used while combining stresses ( 1 ) : Fr sign is (+) for outward load, & (-) for inward load. Allowabe Stresses for various catergories: 1. Membrane only, Sm = 1.5 x Sv 2. Membrane + Bending, Sa = 3 x Sv 3. Shear only, Sh = 0.5 x Sv DESIGN IS ACCEPTABLE ? : YES 5-18B 0.0707 x Fr Mx 24.37 t 2 σx 0.981 Long. moment Membrane CL=1 5-19A 3.516 x CL x ML Rm 2 x b Nf 19.11 Kn x Nf t σf 1.566 CL=1 5-19B 1.697 x CL x ML Rm 2 x b Nx 9.222 Kn x Nx t σx 0.756 Bending 5-20A 0.03827 x ML Rm x b Mf 132.4 6 x Kb x Mf t 2 σf 5.331 5-20B 0.06937 x ML Rm x B Mx 240 6 x Kb x Mx t 2 σx 9.665 Circ. moment Membrane Cc=1 5-21A 1.893 x Cc x Mc Rm 2 x b Nf 10.29 Kn x Nf t σf 0.843 Cc=1 5-21B 2.973 x Cc x Mc Rm 2 x b Nx 16.16 Kn x Nx t σx 1.324 Bending 5-22A 0.09066 x Mc Rm x b Mf 313.7 6 x Kb x Mf t 2 σf 12.63 5-22B 0.04678 x Mc Rm x b Mx 161.9 6 x Kb x Mx t 2 σx 6.518 Stress due to σx σf 0° 90° 180° 270° 0° 90° 180° 270° Radial load, Fr.(1) Membrane Nf 0.312 0.312 0.312 0.312 Nx 0.382 0.382 0.382 0.382 Bending Mf 1.621 1.621 1.621 1.621 Mx 0.981 0.981 0.981 0.981 Long. moment, ML. Membrane Nf + ( 1.566 ) -( 1.566 ) Nx + ( 0.756 ) -( 0.756 ) Bending Mf + ( 5.331 ) -( 5.331 ) Mx + ( 9.665 ) -( 9.665 ) Circ moment, Mc. Membrane Nf + ( 0.843 ) -( 0.843 ) Nx + ( 1.324 ) -( 1.324 ) Bending Mf + ( 12.63 ) - ( 12.63 ) Mx + ( 6.518 ) -( 6.518 ) Int. pr., P. Pi x Rm t σf + ( 10.91 ) + ( 10.91) + ( 10.91 ) + ( 10.91 ) Pi x Rm 2 x t σx + ( 5.456 ) + ( 5.456 ) + ( 5.456 ) + ( 5.456 ) Total, ∑ Membrane 6.593 7.162 5.082 4.514 12.86 12.14 9.728 10.45 Mem+Bend 17.24 14.66 -3.601 -1.023 19.74 26.32 5.946 -0.631
  • 43. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITION : 2. ATTACHMENT DATA : 3. EXTERNAL LOADS : 4. SHELL DATA : 5. STRESS CONCENTRATION FACTORS : 6. COMPUTING STRESSES : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 LOCAL STRESS ANALYSIS (EDGE OF PAD) N 02 CODE D.R. MOSS (EXTRACT OF WRC 107) Design Mode 1, Corroded Condition Design pressure ( internal ) Pi 0.12 kgf/mm² g Design temperature T 150 °C M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006] Outside diameter OD 168.3 mm Weld size w 7 mm Pad diameter Dp 292.7 mm Pad thickness tp 0 mm 0.5 x OD C 146.3 mm Radial force Fr 344.6 kgf Long. moment ML 254724.1 kgf-mm Circ. moment Mc 254724.1 kgf-mm Torsional moment Mt 254724.1 kgf-mm Total eff. shear load Q 487.4 kgf M.O.C SA-516 GR. 70 Plt. [UNS:K02700] Allowable stress Sv 14.06 kgf/mm² Inside radius R 628 mm Thickness of shell t 7 mm Mean radius of shell , [ Rm ] = R + 0.5 x t = 628 + 0.5 x 7 = 631.5 mm Calculate ratio , [ g ] = Rm / t = 631.5 / 7 = 90.21 Calculate ratio , [ b ] = 0.875 x C / Rm = 0.875 x 146.3 / 631.5 = 0.203 Factor , [ Kn ] = 1 Factor , [ Kb ] = 1 Shear stress due to Q , [ t1 ] = Q / ( p x Ro x t ) = 487.4 / ( p x 146.3 x 7 ) = 0.151 kgf/mm² Shear stress due to Mt , [ t2 ] = Mt / ( 2 x p x Ro 2 x t ) = 254724.1 / ( 2 x p x 146.3 2 x 7 ) = 0.27 kgf/mm² Total shear stress , [ t ] = t1 + t2 = 0.151 + 0.27 = 0.422 kgf/mm² STRESSES FACT FIG. FORCES( kgf ) & MOMENTS( kgf-mm ) STRESS ( kgf/mm² ) Radial load Membrane 5-17A 4.941 x Fr Rm Nf 2.696 Kn x Nf t σf 0.385 5-17B 11.06 x Fr Rm Nx 6.037 Kn x Nx t σx 0.862 Bending 5-18A 0.04175 x Fr Mf 14.39 6 x Kb x Mf t 2 σf 1.762 6 x Kb x Mx
  • 44. 7. COMBINING STRESSES : ** Only absolute values of quantities in bracket shall be used while combining stresses ( 1 ) : Fr sign is (+) for outward load, & (-) for inward load. Allowabe Stresses for various catergories: 1. Membrane only, Sm = 1.5 x Sv 2. Membrane + Bending, Sa = 3 x Sv 3. Shear only, Sh = 0.5 x Sv DESIGN IS ACCEPTABLE ? : YES 5-18B 0.01857 x Fr Mx 6.398 t 2 σx 0.783 Long. moment Membrane CL=1 5-19A 6.231 x CL x ML Rm 2 x b Nf 19.63 Kn x Nf t σf 2.804 CL=1 5-19B 3.293 x CL x ML Rm 2 x b Nx 10.38 Kn x Nx t σx 1.482 Bending 5-20A 0.0128 x ML Rm x b Mf 25.46 6 x Kb x Mf t 2 σf 3.117 5-20B 0.01693 x ML Rm x B Mx 33.68 6 x Kb x Mx t 2 σx 4.124 Circ. moment Membrane Cc=1 5-21A 3.869 x Cc x Mc Rm 2 x b Nf 12.19 Kn x Nf t σf 1.741 Cc=1 5-21B 7.986 x Cc x Mc Rm 2 x b Nx 25.16 Kn x Nx t σx 3.594 Bending 5-22A 0.06043 x Mc Rm x b Mf 120.2 6 x Kb x Mf t 2 σf 14.72 5-22B 0.026 x Mc Rm x b Mx 51.73 6 x Kb x Mx t 2 σx 6.334 Stress due to σx σf 0° 90° 180° 270° 0° 90° 180° 270° Radial load, Fr.(1) Membrane Nf ( 0.385 ) ( 0.385) ( 0.385 ) ( 0.385 ) Nx ( 0.862 ) ( 0.862 ) ( 0.862 ) ( 0.862 ) Bending Mf ( 1.762 ) ( 1.762 ) ( 1.762 ) ( 1.762 ) Mx ( 0.783 ) ( 0.783 ) ( 0.783 ) ( 0.783 ) Long. moment, ML. Membrane Nf + ( 2.804 ) -( 2.804 ) Nx + ( 1.482 ) -( 1.482 ) Bending Mf + ( 3.117 ) -( 3.117 ) Mx + ( 4.124 ) -( 4.124 ) Circ moment, Mc. Membrane Nf + ( 1.741 ) -( 1.741 ) Nx + ( 3.594 ) -( 3.594 ) Bending Mf + ( 14.72 ) - ( 14.72 ) Mx + ( 6.334 ) -( 6.334 ) Int. pr., P. Pi x Rm t σf + ( 10.83 ) + ( 10.83) + ( 10.83 ) + ( 10.83 ) Pi x Rm 2 x t σx + ( 5.413 ) + ( 5.413 ) + ( 5.413 ) + ( 5.413 ) Total, ∑ Membrane 7.757 9.869 4.793 2.681 14.49 13.43 8.884 9.947 Mem+Bend 12.67 16.99 1.452 -2.87 18.89 29.44 7.051 -3.49
  • 45. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in DESIGN CONDITIONS NOZZLE DATA HEAD DATA ( Dished End (Rear) ) WELD DATA CALCULATION OF NOZZLE NECK THICKNESS AS PER UG 45 Thickness of head as per UG 37 Min. head thickness reqd. as per UG 27(d) , [tr1] = 0.5 x Pi x ID1 / ( 2 x Sv x E - 0.2 x Pi ) = 0.5 x 0.12 x 2260.8 / ( 2 x 14.06 x 1.0 - 0.2 x 0.12 ) = 4.828 mm Neck thickness for internal pressure as per UG 45(a) Formula in Appendix 1-1 , [trn1] = ( 0.5 x Pi x OD ) / ( Sn x E + 0.4 x Pi ) = ( 0.5 x 0.12 x 60.33 ) / ( 12.02 x 1.0 + 0.4 x 0.12 ) = 0.353 mm Neck thickness for external pressure as per UG 45(a) Neck thickness for external pressure as per UG 28 Assumed neck thickness , [trn3] = 0.279 mm L / OD = 2.487 OD / trn3 = 216.3 Factor A = 0.00016 Factor B = 1.763 kgf/mm² Allowable external pressure , [Pa] = 4 x B / ( 3 x OD / trn3 ) = 4 x 1.763 / ( 3 x 216.3 ) Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 NOZZLE NECK THICKNESS AND REINFORCEMENT DESIGN N 03 CODE ASME VIII Div.1, 10 A11 Design Mode 1 , Corroded Condition Design pressure ( internal ) Pi 0.12 kgf/mm² g Design pressure ( external ) Pe 0.01055 kgf/mm² g Design temperature T 150 °C M.O.C. SA-106 GR. B Smls. Pipe [UNS:K03006] Allowable stress @ design temperature Sn 12.02 kgf/mm² Outside diameter OD 60.33 mm Inside diameter ID 48.85 mm Maximum chord length D 48.85 mm Neck thickness ( provided ) tnp 8.738 mm Internal allowance , corrosion + polishing CAI 3 mm External allowance , corrosion + polishing CAE 0 Neck thickness (tnp - CAI - CAE) tn 5.738 mm Max. under tolerance on thickness Alw 1.092 mm Available neck thickness ( tn - Alw ) ta 4.645 mm Nozzle projection outward ( from vessel outer face ) Lo 150 mm Total length of nozzle ( Lo + Addn for curvature) L 150 mm Connection type Pipe Nozzle Application type Process Opening Reinforcement calculation method Isolated Opening Design as large opening False Allowable stress @ design temperature Sv 14.06 kgf/mm² Inside diameter of head @ head skirt Dsf 1256 mm D / 2 H for Ellispoidal head 2 Factor from Table UG-37 K1 0.9 Inside diameter of equivalent sphere, K1 x Dsk x 2 ID1 2260.8 mm Thickness t 7 mm Min. thickness for external pressure tr2 2.779 mm Nozzle outside weld W1 6.35 mm
  • 46. = 0.01087 kgf/mm² g Thickness of head as per UG 45(b)(1) Min. head thickness reqd. as per UG 27(d) , [trn2 = tr1] = 4.828 mm Thickness for equivalent pressure as per UG 45(b)(2) , [trn4] = 0.5 x Pe x ID1 / ( 2 x Sv x E - 0.2 x Pe ) = 0.5 x 0.01055 x 2260.8 / ( 2 x 14.06 x 1.0 - 0.2 x 0.01055 ) = 0.424 mm Standard wall thickness as per UG 45(b)(4) , [t3] = 3.912 mm Neck thk as per UG 45 , [trn] = MAX { MAX [ trn1, trn3 ] , MIN [ MAX ( trn2 , trn4 ) , 0.875 x t3 ] } ..... for Process Nozzle = MAX [ trn1, trn3 ] ............................................................................ for Access Opening = 3.423 mm .................................................................................... Process Opening Since available neck thickness, ta >= trn, selected neck thickness is adequate.
  • 47. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITION : 2. ATTACHMENT DATA : 3. EXTERNAL LOADS : 4. HEAD DATA : 5. STRESS CONCENTRATION FACTORS : 6. COMPUTING STRESSES : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 LOCAL STRESS ANALYSIS ( ROUND ATTACHMENT ) N 03 CODE D.R. MOSS (EXTRACT OF WRC 107) Design Mode 1, Corroded Condition Design pressure ( internal ) Pi 0.12 kgf/mm² g Design temperature T 150 °C M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006] Outside diameter OD 60.33 mm Weld size w 7 mm 0.5 x OD Ro = C 30.16 mm Radial force Fr 74.92 kgf Latitudinal moment ML 29967.5 kgf-mm Meridional moment Mc 29967.5 kgf-mm Total eff. moment, [ ML 2 + Mc 2 ] 0.5 M 42380.5 kgf-mm Shear load Q 106 kgf Torsional moment Mt 29967.5 kgf-mm M.O.C SA-516 GR. 70 Plt. [UNS:K02700] Allowable stress Sv 14.06 kgf/mm² Inside radius R 1130.4 mm Thickness ( corroded ) t 7 mm Mean radius of shell , [ Rm ] = R + 0.5 x t = 1130.4 + 0.5 x 7 = 1133.9 mm Calculate factor , [ U ] = 1.82 x 30.16 / SQRT [ 1133.9 x 7 ]] = 0.616 Calculate factor , [ S ] = 1.82 x 0.5 x Dp / SQRT [ Rm x t ] = 1.82 x 0.5 x / SQRT [ 1133.9 x 7 ] = 0.616 Factor , [ Kn ] = 1 Factor , [ Kb ] = 1 Shear stress due to Q , [ t1 ] = Q / ( p x Ro x t ) = 106 / ( p x 30.16 x 7 ) = 0.16 kgf/mm² Shear stress due to Mt , [ t2 ] = Mt / ( 2 x p x Ro 2 x t ) = 29967.5 / ( 2 x p x 30.16 2 x 7 ) = 0.749 kgf/mm² Total shear stress , [ t ] = t1 + t2 = 0.16 + 0.749 = 0.909 kgf/mm² STRESS FIGURE VALUE FROM FIGURE STRESS ( kgf/mm² ) Radial load Membrane 5-25A Nx x t Fr - 0.06044 Kn x Fr t 2 σx - 0.09241 5-25B Nf x t Fr -0.179 Kn x Fr t 2 σf -0.274 Bending 5-26A Mx Fr 0.0621 6 x Kb x Fr t 2 σx 0.57
  • 48. 7. COMBINING STRESSES : ** Only absolute values of quantities in bracket shall be used while combining stresses ( 1 ) : Fr sign is (+) for outward load, & (-) for inward load. Allowabe Stresses for various catergories: 1. Membrane only, Sm = 1.5 x Sv 2. Membrane + Bending, Sa = 3 x Sv 3. Shear only, Sh = 0.5 x Sv DESIGN IS ACCEPTABLE ? : YES 5-26B Mf Fr 0.131 6 x Kb x Fr t 2 σf 1.203 Moment , M Membrane 5-27A Nx x t x SQRT [ Rm x t ] M - 0.05621 Kn x M t 2 x SQRT [ Rm x t ] σx -0.546 5-27B Nf x t x SQRT [ Rm x t ] M -0.159 Kn x M t 2 x SQRT [ Rm x t ] σf -1.541 Bending 5-28A Mx x SQRT [ Rm x t ] M 0.117 6 x Kb x M t 2 x SQRT [ Rm x t ] σx 6.794 5-28B Mf x SQRT [ Rm x t ] M 0.43 6 x Kb x M t 2 x SQRT [ Rm x t ] σf 25.07 Stress due to σx σf 0° 90° 180° 270° 0° 90° 180° 270° Radial load, Fr.(1) Memberane Nx +( - 0.274 ) +( - 0.274 ) +( - 0.274 ) +( - 0.274 ) Nf +( - 0.09241 ) +( - 0.09241 ) +( - 0.09241 ) +( - 0.09241 ) Bending Mx + ( 1.203 ) + ( 1.203 ) + ( 1.203 ) + ( 1.203 ) Mf +( 0.57 ) +( 0.57 ) +( 0.57 ) +( 0.57 ) Moment, M. Memberane Nx +( - 1.541 ) -( - 1.541 ) Nf +( - 0.546 ) -( - 0.546 ) Bending Mx + ( 25.07 ) - ( 25.07 ) Mf + ( 6.794 ) -( 6.794 ) Int. pr., P. Pi x Rm t σf + ( 9.719 ) + ( 9.719) + ( 9.719 ) + ( 9.719 ) + ( 9.719 ) +( 9.719) + ( 9.719 ) + ( 9.719 ) Total, ∑ Membrane 1.815 0.274 -1.267 0.274 0.82 0.274 -0.272 0.274 Mem+Bend 28.09 1.477 -25.14 1.477 8.002 0.662 -6.678 0.662
  • 49. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. LIFTING LUG DATA : 2. DESIGN LOADS : 3. CALCULATION OF REFERENCE DIMENSIONS : 4. DESIGN OF LUG PLATE : 5. CALCULATION OF STRESSES IN LUG PLATE WELDS : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 DESIGN OF LIFTING LUG Lifting Lugs CODE P V Design Manual, D.R. Moss Design Mode 1 , Uncorroded Condition Material IS-2062 GR. A Plt. Length of lug LL 70 mm Width of lug A 120 mm Thickness of lug plate TL 12 mm Straight length B1 10 mm Radius at tip R3 35 mm Pin Hole diameter D1 40 mm Lug to vessel weld size W1 8 mm Min yield stress Sy 24.61 kgf/mm² Allowable tensile stress ( 2 / 3 x Sy ) St 16.4 kgf/mm² Allowable bending stress ( 1.5 x St ) Sb 22.15 kgf/mm² Allowable shear stress (0.6 x St ) Ss 9.843 kgf/mm² Empty weight of equipment Wt 2149.7 kgf Number of lifting lugs N 2 Jirk load factor j 1.5 Dimension [ L1 ] = LL - B1 - R3 = 70 - 10 - 35 = 25 mm Dimension [ L2 ] = L1 / SIN ( q1 ) = 25 / SIN ( 0.395 ) = 65 mm Dimension [ LT ] = LL - R3 = 70 - 35 = 35 mm Angle [ q2 ] = ASIN ( R3 / L2 ) = ASIN ( 35 / 65 ) = 0.569 radians Angle [ q1 ] = ATAN ( 2 x L1 / A ) = ATAN ( 2 x 25 / 120 ) = 0.395 radians Angle [ q3 ] = q1 + q2 = 0.395 + 0.569 = 0.963 radians Dimension [ L3 ] = R3 / SIN ( q3 ) = 35 / SIN ( 0.963 ) = 42.62 mm Effective design load on each lug [ P ] = j x Wt / N = 1.5 x 2149.7 / 2 = 1633 kgf Required min. thickness of lug plate for shear [ t2 ] = P / [ ( R3 - 0.5 x D1) x ss ] = 1633 / [ ( 35 - 0.5 x 40 ) x 9.843 ] = 11.06 mm Required min. thickness of lug plate for bending [ t1 ] = 6 x P x LT / ( A 2 x Sb ) = 6 x 1633 x 35 / ( 120 2 x 22.15 ) = 1.075 mm Required min. thickness of lug plate for shear [ t3 ] = P / [ ( 2 x L3 - D1 ) x ss ] = 1633 / [ ( 2 x 42.62 - 40 ) x 9.843 ] = 2.2 mm Bending stress in weld [ f1 ] = 6 x P x LT / [ 2 x LL2 ] = 6 x 1633 x 35 / ( 2 x 70 2 ) = 34.99 kgf/mm Max. shear stress in weld [ f2 ] = P / [ 2 x A ] = 1633 / ( 2 x 120 ) = 6.804 kgf/mm Min. Size of lug plate weld [ w1 ] = MAX ( f1 , 2 x f2 ) / ( 0.707 x Ss ) = MAX ( 34.99 , 2 x 6.804 ) / ( 0.707 x 9.843 )
  • 50. = 5.028 mm
  • 51. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in FOUNDATION LOAD DATA Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Sr. No. Mode Condition Weight ( kgf ) Wind Seismic Empty Filled Shear ( kgf ) Moment ( kgf-m ) Shear Moment Tran. Long. Tran. Long. ( kgf ) ( kgf- m ) 1 Operating Corroded 1898.3 1922.1 649.9 649.9 940.9 940.9 198.8 285.7 2 Design1 Corroded 1898.3 1926.8 649.9 649.9 940.9 940.9 199.3 286 3 Hydro Corroded 1841.1 4212.7 649.9 649.9 940.9 940.9 435.8 436.7 4 Pneumatic Corroded 1841.1 1843.9 649.9 649.9 940.9 940.9 190.8 275.9 5 Operating Uncorroded 2149.7 2173.2 649.9 649.9 882.1 882.1 224.8 303.3 6 Design1 Uncorroded 2149.7 2177.9 649.9 649.9 882.1 882.1 225.3 303.6 7 Hydro Uncorroded 2092.5 4439.8 649.9 649.9 882.1 882.1 459.3 454.2 8 Pneumatic Uncorroded 2092.5 2095.3 649.9 649.9 882.1 882.1 216.8 294
  • 52. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in CENTER OF GRAVITY DATA Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Sr. No. Mode Condition Empty Operating / Filled Wt ( kgf ) C.G. ( mm ) Wt ( kgf ) C.G. ( mm ) 1 Operating Corroded 1898.3 1820.2 1922.1 1809.6 2 Design1 Corroded 1898.3 1820.2 1926.8 1807.5 3 Hydro Corroded 1841.1 1820.2 4212.7 1374.5 4 Pneumatic Corroded 1841.1 1820.2 1843.9 1818.9 5 Operating Uncorroded 2149.7 1729.8 2173.2 1721.7 6 Design1 Uncorroded 2149.7 1729.8 2177.9 1720.1 7 Hydro Uncorroded 2092.5 1729.8 4439.8 1361.3 8 Pneumatic Uncorroded 2092.5 1729.8 2095.3 1728.8
  • 53. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in Index Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Sr. No. Description Page No 1 Title page & equipment info 2 Design data 3 Material of constructions 4 Effective Pressures 5 Weight summary report 6 Test pressure calculations (shell side) 7 Wind load calculations 8 Seismic load calculations 9 Design of Cover (Front) 10 Design of Shell Flng (Front) 11 Design of Main Shell 12 Design of Dished End (Rear) 13 Design of Lug Support 14 Design of Lug Support 15 Design of N 01 16 Design of N 01 17 Design of N 01 18 Design of N 02 19 Design of N 02 20 Design of N 02 21 Design of N 03 22 Design of N 03 23 Design of Lifting Lugs 24 Foundation load data 25 C.G. Data
  • 54. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in EQUIPMENT INFORMATION : DESIGN & REVIEWAL : INSPECTION & APPROVAL : EQUIPMENT DATA : OTHER DATA : Customer ABC Company Ltd. Project Soap Plant Location Vapi Site Plant Refrigeration Plant Design Code ASME VIII Div.1, 10 A11 Equipment Name Gas Filter Equipment Type Pressure Vessel Equipment Class N.A. Equipment Category N.A. Reference Drawing No --- Service Compressed Gas Services Support Type Lug Supports Designed By Design Date 31-03-2015 00:25:14 Checked By Approved By Revision R00 Inspection Agency --- Reviewed By --- Front end Flat End Front end flanged True Rear end Dished End Rear end flanged False Shell ID 1250 mm Shell OD 1270 mm Length, Shell (W.L. to W.L) / Overall 1650 / 2254.6 mm Fabricated weight 1841.1 kgf Empty weight + external weights 1841.1 kgf Estimated operating weight 4212.7 kgf Estimated hydrotest weight 4439.8 kgf
  • 55. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in (1) PROCESS DETAILS : (3) TEST PR. : kgf/mm² g (4) TEMPERATURE : °C (5) ALLOWANCES : mm (6) RADIOGRAPHY & JOINT EFFICIENCY : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 VESSEL DESIGN DATA MEDIA DENSITY kg/m³ Operating Process Gas 10 Design1 Process Gas 12 Design2 Startup Shutdown Upset Hydrotest Water 1000 Pneumatic Process Gas 1.2 (2) PR. : kgf/mm² g INT. EXT. Operating 0.1 0.12 0.01055 Design1 0.12 0.12 0.01055 Design2 Startup Shutdown Upset Based on Input Pr MAWP MAP Hydrotest 0.156 0.156 0.169 Pneumatic 0.132 0.132 0.143 MIN. MAX. Input MDMT Operating 20 -14.28 100 Design1 20 -11.75 150 Design2 Startup Shutdown Upset Hydrotest 21.67 -11.57 50 Pneumatic 21.67 -11.75 50 INT. EXT. Corrosion 3 0 Polishing 0 0 RADIOGRAPHY JOINT EFFICIENCY Shell Spot + T Joints 0.85 Head Full 1.00
  • 56. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in VESSEL DESIGN DATA 1. MATERIAL OF CONSTRUCTION : 2. NOZZLE CONNECTIONS : 3. INSULATION & CLADDING: Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Shell side Shell SA-516 GR. 70 Plt. [UNS:K02700] Head SA-516 GR. 70 Plt. [UNS:K02700] Body flange SA-105 Frg. [UNS:K03504] Body flange cover SA-516 GR. 70 Plt. [UNS:K02700] Liner Shell side Nozzle neck <= NPS 40 SA-106 GR. B Smls. Pipe [UNS:K03006] Flange SA-105 Frg. [UNS:K03504] Cover flange SA-105 Frg. [UNS:K03504] Nozzle NPS > 40 & < 200 SA-106 GR. B Smls. Pipe [UNS:K03006] Flange SA-105 Frg. [UNS:K03504] Cover flange SA-105 Frg. [UNS:K03504] Nozzle neck >= NPS 200 SA-516 GR. 70 Plt. [UNS:K02700] Flange SA-516 GR. 70 Plt. [UNS:K02700] Cover flange SA-516 GR. 70 Plt. [UNS:K02700] Pad flange SA-516 GR. 70 Plt. [UNS:K02700] Pad flange cover SA-516 GR. 70 Plt. [UNS:K02700] Manhole flange SA-516 GR. 70 Plt. [UNS:K02700] Manhole cover SA-516 GR. 70 Plt. [UNS:K02700] Reinforcement pad SA-516 GR. 70 Plt. [UNS:K02700] External bolt SA-193 GR. B7 Bolt [UNS:G41400] External gasket Spiral metal wound CAF filled (S.S.) Stiffener SA-516 GR. 70 Plt. [UNS:K02700] Lifting lug IS-2062 GR. A Plt. Support IS-2062 GR. A Plt. Anchor bolt Commercial CS Bolt Mat. / Density / Thk. Rockwool (Mineral Fibre) / 136.2 kg/m³ / 25 mm Mat. / Thk. Al. sheet / 1.191 mm
  • 57. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in SUMMARY OF EFFECTIVE DESIGN PRESSURES IN kgf/mm² g VS TEMPERATURE IN °C Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Sr. Item name Temp. Inside pr. Liquid pr. Effective pr. No. +ve -ve +ve -ve 1 Cover (Front) 50 0.12 0 0.00007 0.12 0 2 Shell Flng (Front) 50 0.12 0 0.00023 0.12 0 3 Main Shell 50 0.12 0 0.00188 0.122 0 4 Dished End (Rear) 50 0.12 0 0.00225 0.122 0 5
  • 58. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in ITEM WISE WEIGHT SUMMARY Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Sr.No. Item name Item size Empty wt Volume Filled wt kgf m³ kgf 1 Cover (Front) Blind Flange - 1420 OD x 73.411 Thk, RF, 1363 PCD, Tgrv = 1.588 900.5 0 900.5 2 Shell Flng (Front) Fabricated WN - 1420 OD x 1250 ID x 1363 PCD, RF, 128.692 Thk, Trgv = 1.588, G1 = 20, G0 = 10, hf = 30 312.3 0 312.3 3 Gasket Flng (Front) 1313.5 OD x 1250 ID, 4.763 Thk 0.1 0 0.1 4 Bolt Flng (Front) Hex Head Bolt M24 x 243.128 Lg, 56 Nos. 48.76 0 48.76 5 Main Shell 1270 OD x 10 Thk, 1650 Lg 517.1 2.025 2541.9 6 Dished End (Rear) Elliptical D/2H = 2.0, 1270 OD x 10 Nom / 9 Min Thk, SF = 50 181.7 0.317 498.7 7 Gusset Plate 200 Long x 190 Wide x 16 Thk, 8 Nos. 38.51 0 38.51 8 Anchor Bolt Anchor M20 x 200 Lg, 4 Nos. 1.99 0 1.99 9 Support Pad 270 Long x 292 Wide x 10 Thk, 4 Nos. 24.97 0 24.97 10 N 01 ANSIB36.10, 150 NPS Sch.80, 156 Lg 6.697 0.00262 9.32 11 Flange [N 01] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08 12 Gasket [N 01] 166.329 OD x 146.329 ID, 4.763 Thk 0.1 0 0.1 13 Bolt [N 01] Hex Head Bolt M20 x 86.125 Lg, 8 Nos. 1.714 0 1.714 14 Counter Flng [N 01] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08 15 Reinf [N 01] 292.659 OD x 171.275 ID x 10 Thk 3.501 0 3.501 16 N 02 ANSIB36.10, 150 NPS Sch.80, 156 Lg 6.697 0.00262 9.32 17 Flange [N 02] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08 18 Gasket [N 02] 166.329 OD x 146.329 ID, 4.763 Thk 0.1 0 0.1 19 Bolt [N 02] Hex Head Bolt M20 x 86.125 Lg, 8 Nos. 1.714 0 1.714 20 Counter Flng [N 02] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08 21 Reinf [N 02] 292.659 OD x 171.275 ID x 10 Thk 3.501 0 3.501 22 N 03 ANSIB36.10, 50 NPS Sch.160, 150 Lg 1.682 0.00022 1.898 23 Flange [N 03] Weld Neck, ANSI B16.5, RF, 150# for 50 NPS Sch 160 Pipe 2.428 0 2.428 24 Gasket [N 03] 62.85 OD x 42.85 ID, 4.763 Thk 0.1 0 0.1 25 Bolt [N 03] Hex Head Bolt M16 x 67.725 Lg, 4 Nos. 0.431 0 0.431 26 Bolted Cover [N 03] Weld Neck, ANSI B16.5, RF, 150# for 50 160 NPS Pipe 2.522 0 2.522 120 Long x 70 Wide x 12 Thk,
  • 59. 27 Lifting Lugs 2 Nos. 1.596 0 1.596 28 Pad (Lifting Lugs) 70 Long x 170 Wide x 8 Thk, 2 Nos. 1.507 0 1.507 29 30 31 32 33 34 35 ∑ 2092.5 ∑ 4439.8
  • 60. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in TEST PRESSURES CALCULATION AS PER UG-99 / UG-100 : Vessel Inside Legend : Test Pressure Calculations Pressure due to hydro liquid column, [ Plh ] = Lh x h x 1E-09 = 0.00225 kgf/mm² g Hydrotest pressure, [ Ph ] = 1.3 x Pt - Plh = 1.3 x 0.122 - 0.00225 = 0.157 kgf/mm² g Pneumatic test pressure, [ Pn ] = 1.1 x Pt = 1.1 x 0.122 = 0.134 kgf/mm² g Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 Design Temperature T 50 °C Operating Liquid Density  1000 kg/m³ Hydrotest Liquid Density h 1000 kg/m³ Hydrotest Liquid Column Lh 2254.6 mm Sr. No. Item Name Pressure ( kgf/mm² g ) Stress Correction ( kgf/mm² ) Pt Pi Pl Pc Pe Peff Sfo Sfa Sfa Sfo 1 Cover (Front) 0.12 0.00007 0 0 0.12 14.06 14.06 1 0.12 2 Shell Flng (Front) 0.12 0.00023 0 0 0.12 14.06 14.06 1 0.12 3 Main Shell 0.12 0.00188 0 0 0.122 14.06 14.06 1 0.122 4 Dished End (Rear) 0.12 0.00225 0 0 0.122 14.06 14.06 1 0.122 5 Min. Pr., Pt 0.122 Pi = Internal positive pressure Pl = Pressure due to design liquid column Pe = Internal vacuum pressure Pc = External negative pressure Peff = Pi + Pl + Pc Sfo = Allowabe stress at design temperature Sfa = Allowable stress at ambient temperature Pt = MAX [ Peff + Pc, Pe ] x ( Sfa / Sfo )
  • 61. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in Vessel Inside Legend : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 CALC. OF MIN. DESIGN METAL TEMPERATURE Hydrotest Mode , Corroded Condition CODE ASME VIII Div.1, 10 A11 Design Pressure Pi 0.12 kgf/mm² g Design Temperature T 50 °C Sr. No. Item Name / Material / Group Stress (kgf/mm²) Thickness (mm) MDMT (°C) Smt Sdt tn tg tr Tm Tc MDMT 1 Cover (Front) SA-516 GR. 70 Plt. [UNS:K02700] Curve : B 14.06 14.06 70.41 17.6 17.6 -11.98 40.56 -52.53 2 Shell Flng (Front) SA-105 Frg. [UNS:K03504] Curve : B 14.06 14.06 125.7 7 6.443 -28.89 -17.32 -11.57 3 Main Shell SA-516 GR. 70 Plt. [UNS:K02700] Curve : B 14.06 14.06 7 7 6.443 -28.89 -15.08 -13.81 4 Dished End (Rear) SA-516 GR. 70 Plt. [UNS:K02700] Curve : B 14.06 14.06 7 7 5.465 -28.89 -15.04 -13.85 5 Max, MDMT -11.57 Smt = Stress at minimum design metal temperature. Sdt = Pressure due to design liquid column tn = Stress at design metal temperature. tg = Nominal item thickness excluding corrosion and thinning. tr = Governing metal thickness for the item. Tg = Required minimum thickness of the item. Tm = Minimum metal temperature for the the item. Tc = MDMT Correction MDMT = Final MDMT for the item = Tm - Tc.
  • 62. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Hydrotest Mode , Corroded Condition ) : 3. CALCULATION OF FORCES AND MOMENTS: Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 WIND LOAD CALCULATION CODE Wind [IS:875, 87] Basic wind speed ( Section 5.2 ) Vb 50 m/s Expected life of equipment ( Section 5.3.1 ) 25 Years Probability factor (Risk coeff) ( Section 5.3.1 ) K1 0.902 Terrain category ( Section 5.3.2 ) Category 2 Structure class ( Section 5.3.2.2 ) Class B Topography factor ( Section 5.3.3 ) K3 1.3 Force coefficient (Shape factor) Cf 0.8 Equivalent diameter De 1820 mm Overall length of equipment L 2254.6 mm Height of C.G. of equipment Hcg 1374.5 mm Size and height factor ( Section 5.3.2 ) K2 0.98 Effective transverse cross sectional area = De x L A 4103343.3 mm² Effective wind speed = K1 x K2 x K3 x Vb Vz 57.44 m/s Wind pressure = 6E-08 x Vz 2 Pz 0.0002 kgf/mm² Longitudinal force = Cf x A x Pz F 649.9 kgf Support elevation H 372.5 mm Turning moment = F x ( Hcg - H ) M 651245.2 kgf-mm
  • 63. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Hydrotest Mode , Corroded Condition ) : 2. CALCULATION OF FORCES AND MOMENTS: Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 SEISMIC LOAD CALCULATION CODE Seismic [IS:1893, 02] Weight of equipment Wo 4212.7 kgf Importance factor ( Table-6 , 2002 ) I 1.5 Soil profile type Stiff Soil Profile (SD) Foundation type RCC footings + Tie Beams Damping factor 5 Seismic zone Zone III Seismic zone factor ( Table-2 , 2002 ) Z 0.16 Response reduction factor ( Table-7 , 2002 ) R 2.9 Spectral accelerations coeff. ( Fig. 2 , 2002 ) Sa / g 2.5, Use max value Damping correction factor ( Table-3 , 2002 ) Cf 1 Seismic coefficient ( Clause-6.4.2 , 2002 ) = 0.5 x Z x I x Cf x ( Sa / g ) x ( 1 / R ) = 0.5 x 0.16 x 1.5 x 1 x 2.5 x ( 1 / 2.9 ) Ah 0.103 Elevation of support H 372.5 mm Height of C.G. of equipment Hcg 1374.5 mm Seismic base shear force = Ah x Wo = 0.103 x 4212.7 Vb 435.8 kgf Seismic moment of support = Vb x ( Hcg - H ) = 435.8 x ( 1374.5 - 372.5 ) M 436679.3 kgf-mm
  • 64. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Hydrotest Mode , Corroded Condition ) : 2. COVER DATA : 3. BOLTING DATA : 4. LINER DATA : 5. GASKET DATA : 6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1) : Total joint - contact surface compression load [Hp] = 2 x (  x b x G + b' x Lp ) x m x P = 2 x (  x 9.554 x 1294.4 + 0 x 0 ) x 3 x 0.12 = 28027.1 kgf Total hydrostatic end force [H] = 0.25 x  x G 2 x P = 0.25 x  x 1294.4 2 x 0.12 = 158212.8 kgf Minimum required bolt load for operating condition [Wm1] = Hp + H Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 DESIGN OF FLAT BOLTED HEAD ( INTERNAL ) Cover (Front) CODE ASME VIII Div.1, 10 A11 Design pressure P 0.12 kgf/mm² g Design temperature T 50 °C Allowance CA 3 mm Groove allowance Tg 0 mm Radiography Spot + T Joints Joint efficiency E 1 M.O.C. SA-516 GR. 70 Plt. [UNS:K02700] Code allw. stress @ design temp. Sfo 14.06 kgf/mm² Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm² Young’s modulus Ey 20543.7 kgf/mm² Self reinforced False Flange OD A 1420 mm Thickness provided 73.41 mm Thickness available 70.41 mm M.O.C. SA-193 GR. B7 Bolt [UNS:G41400] Code allw. stress @ design temp. Sb 26.37 kgf/mm² Code allw. stress @ atm. temp. Sa 26.37 kgf/mm² Bolt PCD PCD 1363 mm Bolt dia. db 24 mm No. of bolts nb 56 M.O.C. Liner ID mm Liner OD mm Liner thk. mm M.O.C. Spiral metal wound CAF filled (S.S.) Gasket seating stress y 7.031 kgf/mm² Gasket factor m 3 Inside diameter Gi 1256 mm Outside diameter Go 1313.5 mm Width of gasket N 28.75 mm Width of gasket ( as per Table 2-5.2 ) 31.75 mm Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm Effective gasket width ( as per Table 2-5.2 ) b 9.554 mm Dia. at load reaction ( see Table 2-5.2 ) G 1294.4 mm Pass partition gasket width Wp 0 mm Pass partition gasket length Lp 0 mm Effective pass partition gasket width b' 0 mm
  • 65. = 28027.1 + 158212.8 = 186239.9 kgf 7. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b2) : Minimum required bolt load for gasket seating [Wm2] = (  x b x G + b' x Lp ) x y = (  x 9.554 x 1294.4 + 0 x 0 ) x 7.031 = 273152.4 kgf 8. BOLT AREAS AS PER APPENDIX 2-5 (d) : Total required cross-sectional area of bolts [Am] = MAX [ Wm2 / Sa , Wm1 / Sb ] ........ For Internal '+' Pr Design = Wm2 / Sa ..................................... For External Pr & Self Sealing Design = 10360.4 mm² Actual bolt area using root diameter [Ab] = 17513.9 mm² Flange design bolt load for the gasket seating [W] = 0.5 x ( Am + Ab ) x Sa x 1 .................... average bolt area = Ab x Sa x 1 ..........................................full bolt area = 461755.8 kgf ( Full bolt area and margin factor of 1 ) 9. CHECK FOR GASKET CRUSHING : Minimum gasket width required [Nmin] = Ab x Sb / ( 2 x  x y x G ) = 17513.9 x 26.37 / ( 2 x  x 7.031 x 1294.4 ) = 8.075 mm 10. DESIGN CALCULATION AS PER UG 34, BOLTING CONDITION : Required thickness for bolting condition [t] = G x SQRT [ 1.9 x W x 0.5 x ( PCD - G ) / ( Sfa x E x G 3 ) ] = 1294.4 x SQRT [ 1.9 x 461755.8 x 0.5 x ( 1363 - 1294.4 ) / ( 14.06 x 1 x 1294.4 3 ) ] = 40.66 mm 11. DESIGN CALCULATION AS PER UG 34, OPERATING CONDITION : Required thickness for operating condition [t] = G x SQRT { [ C x P / ( Sfo x E ) ] + 1.9 x Wm1 x 0.5 x ( PCD - G ) / ( Sfo x E x G 3 ) } = 1294.4 x SQRT { [ 0.3 x 0.12 / ( 14.06 x 1 ) ] + 1.9 x 186239.9 x 0.5 x ( 1363 - 1294.4 ) / ( 14.06 x 1 x 1294.4 3 ) } = 70.67 mm Self reinforced False Factor C is user input False Factor C taken from fig. UG 34 or user input 0.3 Maximum factor C value C 0.75 Factor C (effective) 0.3 C = Min ( 2 x 0.3, 0.75 ) for self reinf. C = 0.3 in other cases
  • 66. 'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in 1. DESIGN CONDITIONS ( Hydrotest Mode , Corroded Condition ) : 2. FLANGE DATA : 3. BOLTING DATA : 4. LINER DATA : 5. GASKET DATA : 5a. Flange gasket data : 5b. Partition groove gasket data (For H.E. body flange) : Licensee : Sunay Wagle, CADEM Services, Pune, India Customer ABC Company Ltd. Project / Equipment Soap Plant / Gas Filter Designed By / Revision and Date / R00 , 31-03-2015 00:25:14 FLANGE DESIGN ( INTERNAL ) Shell Flng (Front) CODE ASME VIII Div.1, 10 A11 Design pressure P 0.12 kgf/mm² g Design temperature T 50 °C Allowance CA 3 mm Groove allowance Tg 0 mm M.O.C. SA-105 Frg. [UNS:K03504] Code allw. stress @ design temp. Sfo 14.06 kgf/mm² Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm² Inside diameter B 1256 mm Outside diameter A 1420 mm Hub length h 30 mm Thickness ( hub end ) g1 17 mm Thickness ( pipe end ) g0 7 mm Thickness provided 128.7 mm Thickness available 125.7 mm M.O.C. SA-193 GR. B7 Bolt [UNS:G41400] Code allw. stress @ design temp. Sb 26.37 kgf/mm² Code allw. stress @ atm. temp. Sa 26.37 kgf/mm² Bolt PCD C 1363 mm Bolt dia. db 24 mm No. of bolts nb 56 M.O.C. Liner ID mm Liner OD mm Liner thk. mm M.O.C. Spiral metal wound CAF filled (S.S.) Gasket type Ring Gasket Gasket confinement type Unconfined Flange face type Raised Face Flange gakset surface finish Serrated (Normal) Counter flange face type Raised Face Counter gakset surface finish Serrated (Normal) Applicalbe gasket sketch in Table 2-5.2 Type 1B Applicable gasket column in Table 2-5.2 1 Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y 7.031 kgf/mm² Gasket factor ( from Table 2-5.1 ) m 3 Inside diameter Gi 1256 mm Outside diameter Go 1313.5 mm Width of gasket ( as per Table 2-5.2 ) N 28.75 mm Width of gasket ( as per Table 2-5.2 ) w 28.75 mm Width of raised face or gasket contact width 31.75 mm ( as per Table 2-5.2 ) Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm Effective gasket width ( as per Table 2-5.2 ) b 9.554 mm Dia. at load reaction ( see Table 2-5.2 ) G 1294.4 mm M.O.C. --

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