Design of Reactor With Agitator Shaft 1
Transcript of Design of Reactor With Agitator Shaft 1
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Pressure Vessels
Reaction VesselsAgitator ShaftsHeat ExchangersProcess ColumnsStorage TankFloating RoofChimney
ASME Sec. VIII Div. 1
TEMAEEUAIS 2825EN 13445
API 650API 620IS 6533
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EXAMPLE NO. PC-01
DESIGN OFREACTION VESSEL WITH AGITATOR SHAFT
NOTE:
1) Link to youtube video of this design:https://www.youtube.com/watch?v=Szl9AE_d4pQ&list=PLPL8SPZUxm-mFqQZceyhr13QYDEruelJx&index=6
2) As you can see in the video, the inbuilt intelligence in the software generates maximum information byitself.
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 designcode.
3) In case of any changes to the interconnected shell geometry and / or design conditions (pressure /temperature) including material of constructions, these dimensions are 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 Reaction Vessel with Agitator Shaft.
This reaction vessel has dishes at the top and bottom ends. The jacketing is of plain
shell type, partially covering the main shell and extending on to the bottom dished end.It has an agitator, with say 20 HP power and the agitator shaft RPM is 100. All thecomponents in contact with the internal process liquid are of SS 316 and the jacketing isof SS 304.
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Index
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
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 Wind load calculations
7 Seismic load calculations
8 Design of Dished End (Front)
9 Design of Closure Flng (Front)
10 Design of Closure Flng (Front)
11 Design of Shel l Flng (Front)
12 Design of Shel l Flng (Front)
13 Design of Main Shell
14 Design of Dished End (Rear)
15 Design of Jacket Closure (Top)
16 Design of Jacket Shell
17 Design of Jacket Dish (Bottom)
18 Design of Lug Support
19 Design of Lug Support
20 Design of Shaft
21 Design of Impeller (1)
22 Design of Lifting Lugs
23 Foundation load data
24 C.G. Data
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EQUIPMENT INFORMATION :
DESIGN & REVIEWAL :
INSPECTION & APPROVAL :
EQUIPMENT DATA :
JACKETING DATA :
AGITATOR 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 Reactor R101
Equipment Type Reaction Vessel
Equipment Class N.A.
Equipment Category N.A.
Reference Drawing No ---
Service Chemical Services
Support Type Lug Supports
Designed By
Design Date 06-04-2015 19:23:54
Checked By
Approved By
Revision R00
Inspection Agency ---
Reviewed By ---
Front end Dished End
Front end flanged True
Rear end Dished End
Rear end flanged False
Shell ID 1600 mm
Shell OD 1628 mm
Length, Shell (W.L. to W.L) / Overall 2400 / 3338.3 mm
Jacketing system Shell & Bottom End
Jacket type Plain Jacket
Power 20 hp (MKS)
RPM 100
Duty Factor 2
Diameter of shaft 101 mm
Free Length of shaft 3738.3 mm
No of impellers 1
Propped True
Fabricated weight 5065.2 kgf Empty weight + external weights 5065.2 kgf
Estimated operating weight 11231.4 kgf
Estimated hydrotest weight 10964.4 kgf
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(1) PROCESS DETAILS :
(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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
REACTION VESSEL DESIGN DATA
SHELL SIDE JACKET SIDE
MEDIA DENSITY MEDIA DENSITY
kg/m kg/m
Operating Process 980 Steam 1.5
Design1 1000 1000
Design2
Startup
Shutdown
Upset
Hydrotest Water 1000 Water 1000
Pneumatic Process 1.2 Steam 1.2
(2) PR. : kgf/mm g INT. EXT. INT. EXT.
Input Pr MAWP Input Pr Input Pr MAWP Input Pr
Operating 0.06 0.06 0.01055 0.04 0.04 0.01055
Design1 0.08 0.08 0.01055 0.05 0.05 0.01055
Design2
Startup
Shutdown
Upset
(3) TEST PR. : kgf/mm g Based on Based on
Input Pr MAWP MAP Input Pr MAWP MAP
Hydrotest 0.106 0.106 0.106 0.07085 0.07085 0.07085
Pneumatic 0.08976 0.08976 0.08976 0.05995 0.05995 0.05995
MIN. MDMT. MAX. MIN. MDMT. MAX
Operating 20 120 20 150
Design1 10 180 10 200
Design2
Startup
Shutdown
Upset
Hydrotest 21.67 50 21.67 50
Pneumatic 21.67 50 21.67
INT. EXT. INT. EXT.
Corrosion 0 0 0 0
Polishing 0 0 0
RADIOGRAPHY JOINTEFFICIENCY
RADIOGRAPHY JOINTEFFICIENCY
Shell Spot + T Joints 0.85 Spot + T Joints 0.85
Head Full 1.00 Full 1.00
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REACTION VESSEL DESIGN DATA
1. MATERIAL OF CONSTRUCTION :
2. NOZZLE CONNECTIONS :
3. AGITATOR:
4. INSULATION & CLADDING:
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
Shell side Jacket side
Shell / Channel SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Head SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Body flange SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Body flange cover SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Liner
Shell side Jacket side
Nozzle neck 40 & < 200SA-312 GR. TP316 Smls. Pipe[UNS:S31600]
SA-312 GR. TP304 Smls. Pipe[UNS:S30400]
Flange SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Cover flange SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Nozzle neck >= NPS 200 SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Flange SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Cover flange SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Pad flange SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Pad flange cover SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Manhole flange SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Manhole cover SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]Reinforcement pad SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
External bolt SA-193 GR. B7 Bolt [UNS:G41400] SA-193 GR. B7 Bolt [UNS:G41400]
External gasket Spiral metal wound CAF filled (S.S.) CAF with suitable binder (3 mm.)
Stiffener SA-240 GR. 316 Plt. [UNS:S31600] SA-240 GR. 304 Plt. [UNS:S30400]
Lifting lug IS-2062 GR. A Plt. IS-2062 GR. A Plt.
Support IS-2062 GR. A Plt. IS-2062 GR. A Plt.
Anchor bolt SA-36 / IS-1363,67 Bolt [UNS:K02600] SA-36 / IS-1363,67 Bolt [UNS:K02600]
Shaft SA-479 GR. 316 Bar [UNS:S31600]
Impeller SA-240 GR. 316 Plt. [UNS:S31600]
Internal coupling SA-479 GR. 316 Bar [UNS:S31600]
Housing SA-479 GR. 316 Bar [UNS:S31600]
Housing cover SA-240 GR. 316 Plt. [UNS:S31600]
Mat. / Density / Thk. Rockwool (Mineral Fibre) / 136.2 kg/m / 60 mm
Mat. / Thk. Al. sheet / 1.191 mm
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SUMMARY OF EFFECTIVE DESIGN PRESSURES IN kgf/mm g VS TEMPERATURE IN C
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
Sr. Item name Temp. Inside pr. Liquid pr. Effective pr.
No. +ve -ve +ve -ve
1 Dished End (Front) 180 0.08 0.01055 0 0.08 0.010552 Closure Flng (Front) 180 0.08 0.01055 0 0.08 0.01055
3 Shell Flng (Front) 180 0.08 0.01055 0 0.08 0.01055
4 Main Shell 180 0.08 0.01055 0 0.09055 0.06055
5 Dished End (Rear) 180 0.08 0.01055 0 0.08 0.01055
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ITEM WISE WEIGHT SUMMARY
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
Sr.No. Item name Item sizeEmptywt
Volume Filled wt
kgf m kgf
1 Dished End (Front)Torispherical End CR = 1440,KR = 272, 8 Nom / 7.2 MinThk, SF = 50
216.5 0.607 823.5
2 Closure Flng (Front)Plate Ring - 1786 OD x 1619ID x 1729 PCD, RF, 154.681Thk, Trgv = 1.588
546.9 0 546.9
3 Shell Flng (Front)Plate Ring - 1786 OD x 1631ID x 1729 PCD, RF, 158.474Thk, Trgv = 1.588
522.1 0 522.1
4 Gasket Flng (Front)1695.2 OD x 1631 ID, 4.763Thk
0.1 0 0.1
5 Bolt Flng (Front)
Hex Head Bolt M24 x 354.18
Lg, 68 Nos. 86.25 0 86.25
6 Main Shell 1628 OD x 14 Thk, 2400 Lg 1362.9 4.825 6188.4
7 Dished End (Rear)Torispherical End CR = 1440,KR = 272, 8 Nom / 7.2 MinThk, SF = 50
216.5 0.607 823.5
8 Jacket Closure (Top)5296 Long x 111 Wide x 18Thk
84.65 0 84.65
9 Jacket Shell 1744 OD x 8 Thk, 1850 Lg 645.7 0.122 767.6
10 Jacket Dish (Bottom)Torispherical End CR = 1728,KR = 175, 8 Nom / 7.2 MinThk, SF = 50
222.2 0 222.2
11 Gusset Plate
220 Long x 240 Wide x 16
Thk, 4 Nos. 26.75 0 26.75
12 Anchor Bolt Anchor M20 x 200 Lg, 8 Nos. 3.979 0 3.979
13 Support Pad330 Long x 300 Wide x 14Thk, 4 Nos.
44.35 0 44.35
14 Motor 20 HP x 1450 RPM 200 0 200
15 Gear Box 20 HP x 14.5 Red. Ratio 200 0 200
16 Coupling Flexible Coupled B5 28.38 0 28.38
17 Bearing Housing 222 OD x 43 Thk, 325 Lg 62.87 0.00472 67.59
18 Top Bearing SKF Taper Roller 30216 0.163 0 0.163
19 Bottom Bearing SKF Taper Roller 30217 0.209 0 0.209
20 Shaft Seal Gland Packing 10 0 10
21 Shaft 101 OD x 4438.311 Lg 284.5 0 284.5
22 Impeller (1)Propeller, Sweep Dia Propellerx 4 Blades
27 0 27
23 Lifting Lugs135 Long x 77 Wide x 28 Thk,2 Nos.
4.608 0 4.608
24 Pad (Lifting Lugs)70 Long x 180 Wide x 8 Thk, 2Nos.
1.613 0 1.613
25 Insulation5805.663 W x 5411.911 L, 60Thk
256.7 0 256.7
26 Cladding 5809.404 W x 5411.911 L,1.191 Thk
10.36 0 10.36
27
28
29
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30
5065.2 10964.4
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1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded Condition ) :
3. CALCULATION OF FORCES AND MOMENTS:
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
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 2408 mm
Overall length of equipment L 3338.3 mm
Height of C.G. of equipment Hcg 1804.4 mm
Size and height factor ( Section 5.3.2 ) K2 0.98Effective transverse cross sectional area
= De x L A 8038652.8 mm
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/mm
Longitudinal force
= Cf x A x Pz F 1273.2 kgf
Support elevation H 456.2 mm
Turning moment
= F x ( Hcg - H ) M 1716622.5 kgf-mm
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1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded Condition ) :
2. CALCULATION OF FORCES AND MOMENTS:
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
SEISMIC LOAD CALCULATION
CODE Seismic [IS:1893, 02]
Weight of equipment Wo 11231.4 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 456.2 mm
Height of C.G. of equipment Hcg 1804.4 mm
Seismic base shear force
= Ah x Wo
= 0.103 x 11231.4 Vb 1161.9 kgf
Seismic moment of support
= Vb x ( Hcg - H )
= 1161.9 x ( 1804.4 - 456.2 ) M 1566464.3 kgf-mm
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1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded Condition ) :
2. DESIGN CALCULATION AS PER UG 32 e / APPENDIX 1-4 ( d ) :
Factor [M]
= ( 1 / 4 ) x [ 3 + SQRT [ CR / KR ] ]
= ( 1 / 4 ) x [ 3 + SQRT [ 1440 / 272 ] ]
= 1.325
Thickness for internal pressure [t]
= M x Pi x CR / ( 2 x S x E - 0.2 x Pi )
= 1.325 x 0.08 x 1440 / ( 2 x 13.79 x 1 - 0.2 x 0.08 )= 5.54 mm
3. DESIGN CALCULATION AS PER UG 33 e :
Thickness for equivalent external pressure [t]
= M x 1.67 x Pe x CR / ( 2 x S x 1.0 - 0.2 x 1.67 x Pe )
= 1.325 x 1.67 x 0.01055 x 1440 / ( 2 x 13.79 x 1.0 - 0.2 x 1.67 x 0.01055 )
= 1.219 mm
Assumed head thickness, [te]
= 4.454 mm
Assumed outside crown radius, [CRo]
= 1448 mm
Factor [A]
= 0.125 x te / CRo
= 0.125 x 4.454 / 1448
= 0.00038
Factor with reference to chart (HA-2) [B]
= 3.455 kgf/mm
Allowable external pressure [Pa]
= B x te / CRo
= 3.455 x 4.454 / 1448
= 0.01063 kgf/mm
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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
DESIGN OF TORISPHERICAL HEAD ( INT. & EXT. PRESSURE ) Dished End (Front)
CODE ASME VIII Div.1, 10 A11
Design pressure ( internal ) Pi 0.08 kgf/mm g
Design pressure ( external ) Pe 0.01055 kgf/mm g
Design temperature T 180 C
Material of construction SA-240 GR. 316 Plt. [UNS:S31600]
Max. allowable stress @ design temp. S 13.79 kgf/mm
Radiography Full
Joint efficiency E 1
Outside diameter of head OD 1616 mm
Crown radius CR 1440 mm
Knuckle radius KR 272 mm
Nominal thickness 8 mm
Nominal thickness required as per TEMA N.A mmInternal allowance, corrosion + polishing 0 mm
External allowance, corrosion + polishing 0 mm
Thinning allowance / Under tolerance 0.8 mm
Available thickness 7.2 mm
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1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded 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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
FLANGE DESIGN ( INTERNAL ) Closure Flng (Front)
CODE ASME VIII Div.1, 10 A11
Design pressure P 0.08 kgf/mm g
Design temperature T 180 C
Allowance CA 0 mm
Groove allowance Tg 1.588 mm
M.O.C. SA-240 GR. 316 Plt. [UNS:S31600]
Code allw. stress @ design temp. Sfo 10.46 kgf/mm
Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm
Inside diameter B 1619 mm
Outside diameter A 1786 mm
Hub length h 0 mm
Thickness ( hub end ) g1 0 mmThickness ( pipe end ) g0 0 mm
Thickness provided 154.7 mm
Thickness available 153.1 mm
M.O.C. SA-193 GR. B7 Bolt [UNS:G41400]
Code allw. stress @ design temp. Sb 17.58 kgf/mm
Code allw. stress @ atm. temp. Sa 17.58 kgf/mm
Bolt PCD C 1729 mm
Bolt dia. db 24 mm
No. of bolts nb 68
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 FaceCounter 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/mm
Gasket factor ( from Table 2-5.1 ) m 3
Inside diameter Gi 1631 mm
Outside diameter Go 1695.2 mm
Width of gasket ( as per Table 2-5.2 ) N 32.1 mm
Width of gasket ( as per Table 2-5.2 ) w 32.1 mm
Width of raised face or gasket contact width 38.1 mm
( as per Table 2-5.2 )
Basic gasket seating width ( as per Table 2-5.2 ) b0 16.05 mm
Effective gasket width ( as per Table 2-5.2 ) b 10.1 mm
Dia. at load reaction ( see Table 2-5.2 ) G 1675 mm
M.O.C. --
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6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1)
Total joint - contact surface compression load [Hp]
= 2 x ( x b x G x m + b' x Lp x m' ) x P
= 2 x ( x 10.1 x 1675 x 3 + 0 x 0 x 0 ) x 0.08
= 25499.6 kgfTotal hydrostatic end force [H]
= 0.25 x x G x P
= 0.25 x x 1675 x 0.08
= 176284.5 kgf
Minimum required bolt load for operating condition [Wm1a]
= Hp + H
= 25499.6 + 176284.5
= 201784.1 kgf
Minimum required bolt load for operating condition [Wm1b]
( from mating flange )
= 201784.1 kgf
Governing bolt load for operating condition [Wm1]
= MAX [ Wm1a , Wm1b ]
= MAX [ 201784.1 , 201784.1 ]= 201784.1 kgf
7. BOLT LOAD CALCULATION AS PER APPENDIX 2-5 (b2)
Minimum required bolt load for gasket seating [Wm2]
= ( x b x G x y + b' x Lp x y' )
= ( x 10.1 x 1675 x 7.031 + 0 x 0 x 0 )
= 373499.5 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
= 21249.6 mm
Actual bolt area using root diameter [Ab]
= 21266.9 mm
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
= 373650.9 kgf ( Avg. 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 )
= 21266.9 x 17.58 / ( 2 x x 7.031 x 1675 )
= 5.052 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 x B 2x P
= 0.25 x x 1619 2x 0.08
= 164692.4 kgf
Gasket load (difference between flange design bolt load and total hydrostatic end force) [HG]
= Wm1 - H
= 201784.1 - 176284.5
= 25499.6 kgf
Difference between total hydrostatic end force and hydrostatic end force on area inside of flange [HT]
= H - HD
= 176284.5 - 164692.4
= 11592.1 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 ( 1729 - 1619 ) - 0
Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y' 0 kgf/mm
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
RING FLANGE DESIGN Closure Flng (Front)
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= 55
Radial distance from the bolt circle to the circle on which HD acts [hD]
= R + 0.5 x g1
= 55 + 0.5 x 0
= 55 mm
Radial distance from gasket load reaction to the bolt circle [hG]
= 0.5 x ( C - G )
= 0.5 x ( 1729 - 1675 )
= 27 mm
Radial distance from the bolt circle to the circle on which HT acts [hT]
= 0.5 x ( R + g1 + hG )
= 0.5 x ( 55 + 0 + 27 )= 41 mm
13. FLANGE MOMENTS UNDER OPERATING CONDITION AS PER APPENDIX 2-6
Component of moment due to HD [MD]
= HD x hD
= 164692.4 x 55
= 9058082.2 kgf-mm
Component of moment due to HG [MG]
= HG x hG
= 25499.6 x 27
= 688371.3 kgf-mm
Component of moment due to HT [MT]
= HT x hT
= 11592.1 x 41
= 475251.3 kgf-mmTotal moment acting on the flange for operating condition [MO]
= MD + MG + MT
= 9058082.2 + 688371.3 + 475251.3
= 10221704.8 kgf-mm
14. LOADS AND FORCES DURING GASKET SEATING AS PER APPENDIX 2-3
Gasket load for seating condition [HG]
= W
= 373650.9 kgf
15. MOMENT UNDER GASKET SEATING AS PER APPENDIX 2-6
Total moment acting on the flange for gasket seating [MO']
= W x hG
= 373650.9 x 27
= 10086863.4 kgf-mm
16. SHAPE CONSTANTSFactor [K]
= A / B
= 1786 / 1619
= 1.103
Flange factor from Fig. 2-7.1 [Y]
= 19.74
17. FLANGE THICKNESS REQUIRED AS PER APPENDIX 2-7
Equivalent moment [Mmax]
= MAX [ MO , MO' x Sfo / Sfa ]
= MAX [ 10221704.8 , 10086863.4 x 10.46 / 14.06 ]
= 10221704.8 kgf-mm
Corrected equivalent moment per unit length [M]
= Mmax x Cf / B
= 10221704.8 x 1 / 1619= 6313.6 kgf
Required thickness of flange [t]
= SQRT [ M x Y / Sfo ]
= SQRT [ 6313.6 x 19.74 / 10.46 ]
= 109.2 mm
18. FLANGE RIGIDITY CHECKING AS PER APPENDIX 2-14
Rigidity index [J]
= 109.4 x Mmax / ( Efo x tr 3x KL x ln ( K ) )
= 109.4 x 10221704.8 / ( 18786 x 144.8 3 x 0.2 x ln ( 1.103 ) )
= 0.999Since J < 1.0, design is safe
Assumed flange thickness tr 144.8 mm
Modulus of elasticity for flange Efo 18786 kgf/mm
Rigidity factor KL 0.2
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded 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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
FLANGE DESIGN ( EXTERNAL ) Closure Flng (Front)
CODE ASME VIII Div.1, 10 A11
Design pressure P 0.01055 kgf/mm g
Design temperature T 180 C
Allowance CA 0 mm
Groove allowance Tg 1.588 mm
M.O.C. SA-240 GR. 316 Plt. [UNS:S31600]
Code allw. stress @ design temp. Sfo 10.46 kgf/mm
Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm
Inside diameter B 1619 mm
Outside diameter A 1786 mm
Hub length h 0 mm
Thickness ( hub end ) g1 0 mmThickness ( pipe end ) g0 0 mm
Thickness provided 154.7 mm
Thickness available 153.1 mm
M.O.C. SA-193 GR. B7 Bolt [UNS:G41400]
Code allw. stress @ design temp. Sb 17.58 kgf/mm
Code allw. stress @ atm. temp. Sa 17.58 kgf/mm
Bolt PCD C 1729 mm
Bolt dia. db 24 mm
No. of bolts nb 68
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 FaceCounter 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/mm
Gasket factor ( from Table 2-5.1 ) m 3
Inside diameter Gi 1631 mm
Outside diameter Go 1695.2 mm
Width of gasket ( as per Table 2-5.2 ) N 32.1 mm
Width of gasket ( as per Table 2-5.2 ) w 32.1 mm
Width of raised face or gasket contact width 38.1 mm
( as per Table 2-5.2 )
Basic gasket seating width ( as per Table 2-5.2 ) b0 16.05 mm
Effective gasket width ( as per Table 2-5.2 ) b 10.1 mm
Dia. at load reaction ( see Table 2-5.2 ) G 1675 mm
M.O.C. --
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6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1)
Total joint - contact surface compression load [Hp]
= 2 x ( x b x G x m + b' x Lp x m' ) x P
= 2 x ( x 10.1 x 1675 x 3 + 0 x 0 x 0 ) x 0.01055
= 3361.6 kgfTotal hydrostatic end force [H]
= 0.25 x x G x P
= 0.25 x x 1675 x 0.01055
= 23239.4 kgf
Minimum required bolt load for operating condition [Wm1a]
= Hp + H
= 3361.6 + 23239.4
= 26600.9 kgf
Minimum required bolt load for operating condition [Wm1b]
( from mating flange )
= 26600.9 kgf
Governing bolt load for operating condition [Wm1]
= MAX [ Wm1a , Wm1b ]
= MAX [ 26600.9 , 26600.9 ]= 26600.9 kgf
7. BOLT LOAD CALCULATION AS PER APPENDIX 2-5 (b2)
Minimum required bolt load for gasket seating [Wm2]
= ( x b x G x y + b' x Lp x y' )
= ( x 10.1 x 1675 x 7.031 + 0 x 0 x 0 )
= 373499.5 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
= 21249.6 mm
Actual bolt area using root diameter [Ab]
= 21266.9 mm
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
= 373650.9 kgf ( Avg. 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 )
= 21266.9 x 17.58 / ( 2 x x 7.031 x 1675 )
= 5.052 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 x B 2x P
= 0.25 x x 1619 2x 0.01055
= 21711.2 kgf
Difference between total hydrostatic end force and hydrostatic end force on area inside of flange [HT]
= H - HD
= 23239.4 - 21711.2
= 1528.2 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 ( 1729 - 1619 ) - 0
= 55
Radial distance from the bolt circle to the circle on which HD acts [hD]
= R + 0.5 x g1
= 55 + 0.5 x 0
Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y' 0 kgf/mm
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
RING FLANGE DESIGN Closure Flng (Front)
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= 55 mm
Radial distance from gasket load reaction to the bolt circle [hG]
= 0.5 x ( C - G )
= 0.5 x ( 1729 - 1675 )
= 27 mm
Radial distance from the bolt circle to the circle on which HT acts [hT]
= 0.5 x ( R + g1 + hG )
= 0.5 x ( 55 + 0 + 27 )
= 41 mm
13. FLANGE MOMENTS UNDER OPERATING CONDITION AS PER APPENDIX 2-6
Component of moment due to HD [MD]
= HD x ( hD - hG )= 21711.2 x ( 55 - 27 )
= 608012.7 kgf-mm
Component of moment due to HT [MT]
= HT x ( hT - hG )
= 1528.2 x ( 41 - 27 )
= 21398 kgf-mm
Total moment acting on the flange for operating condition [MO]
= MD + MT
= 608012.7 + 21398
= 629410.7 kgf-mm
14. LOADS AND FORCES DURING GASKET SEATING AS PER APPENDIX 2-3
Gasket load for seating condition [HG]
= W
= 373650.9 kgf15. MOMENT UNDER GASKET SEATING AS PER APPENDIX 2-6
Total moment acting on the flange for gasket seating [MO']
= W x hG
= 373650.9 x 27
= 10086863.4 kgf-mm
16. SHAPE CONSTANTS
Factor [K]
= A / B
= 1786 / 1619
= 1.103
Flange factor from Fig. 2-7.1 [Y]
= 19.74
17. FLANGE THICKNESS REQUIRED AS PER APPENDIX 2-7
Equivalent moment [Mmax]= MAX [ MO , MO' x Sfo / Sfa ]
= MAX [ 629410.7 , 10086863.4 x 10.46 / 14.06 ]
= 7500591.6 kgf-mm
Corrected equivalent moment per unit length [M]
= Mmax x Cf / B
= 7500591.6 x 1 / 1619
= 4632.9 kgf
Required thickness of flange [t]
= SQRT [ M x Y / Sfo ]
= SQRT [ 4632.9 x 19.74 / 10.46 ]
= 93.51 mm
18. FLANGE RIGIDITY CHECKING AS PER APPENDIX 2-14
Rigidity index [J]
= 109.4 x Mmax / ( Efo x tr 3x KL x ln ( K ) )
= 109.4 x 7500591.6 / ( 18786 x 144.3 3 x 0.2 x ln ( 1.103 ) )
= 0.997
Since J < 1.0, design is safe
Assumed flange thickness tr 144.3 mm
Modulus of elasticity for flange Efo 18786 kgf/mm
Rigidity factor KL 0.2
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded 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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
FLANGE DESIGN ( INTERNAL ) Shell Flng (Front)
CODE ASME VIII Div.1, 10 A11
Design pressure P 0.08 kgf/mm g
Design temperature T 180 C
Allowance CA 0 mm
Groove allowance Tg 1.588 mm
M.O.C. SA-240 GR. 316 Plt. [UNS:S31600]
Code allw. stress @ design temp. Sfo 10.46 kgf/mm
Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm
Inside diameter B 1631 mm
Outside diameter A 1786 mm
Hub length h 0 mm
Thickness ( hub end ) g1 0 mmThickness ( pipe end ) g0 0 mm
Thickness provided 158.5 mm
Thickness available 156.9 mm
M.O.C. SA-193 GR. B7 Bolt [UNS:G41400]
Code allw. stress @ design temp. Sb 17.58 kgf/mm
Code allw. stress @ atm. temp. Sa 17.58 kgf/mm
Bolt PCD C 1729 mm
Bolt dia. db 24 mm
No. of bolts nb 68
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 FaceCounter 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/mm
Gasket factor ( from Table 2-5.1 ) m 3
Inside diameter Gi 1631 mm
Outside diameter Go 1695.2 mm
Width of gasket ( as per Table 2-5.2 ) N 32.1 mm
Width of gasket ( as per Table 2-5.2 ) w 32.1 mm
Width of raised face or gasket contact width 38.1 mm
( as per Table 2-5.2 )
Basic gasket seating width ( as per Table 2-5.2 ) b0 16.05 mm
Effective gasket width ( as per Table 2-5.2 ) b 10.1 mm
Dia. at load reaction ( see Table 2-5.2 ) G 1675 mm
M.O.C. --
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6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1)
Total joint - contact surface compression load [Hp]
= 2 x ( x b x G x m + b' x Lp x m' ) x P
= 2 x ( x 10.1 x 1675 x 3 + 0 x 0 x 0 ) x 0.08
= 25499.6 kgfTotal hydrostatic end force [H]
= 0.25 x x G x P
= 0.25 x x 1675 x 0.08
= 176284.5 kgf
Minimum required bolt load for operating condition [Wm1a]
= Hp + H
= 25499.6 + 176284.5
= 201784.1 kgf
Minimum required bolt load for operating condition [Wm1b]
( from mating flange )
= 201784.1 kgf
Governing bolt load for operating condition [Wm1]
= MAX [ Wm1a , Wm1b ]
= MAX [ 201784.1 , 201784.1 ]= 201784.1 kgf
7. BOLT LOAD CALCULATION AS PER APPENDIX 2-5 (b2)
Minimum required bolt load for gasket seating [Wm2]
= ( x b x G x y + b' x Lp x y' )
= ( x 10.1 x 1675 x 7.031 + 0 x 0 x 0 )
= 373499.5 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
= 21249.6 mm
Actual bolt area using root diameter [Ab]
= 21266.9 mm
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
= 373650.9 kgf ( Avg. 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 )
= 21266.9 x 17.58 / ( 2 x x 7.031 x 1675 )
= 5.052 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 x B 2x P
= 0.25 x x 1631 2x 0.08
= 167142.8 kgf
Gasket load (difference between flange design bolt load and total hydrostatic end force) [HG]
= Wm1 - H
= 201784.1 - 176284.5
= 25499.6 kgf
Difference between total hydrostatic end force and hydrostatic end force on area inside of flange [HT]
= H - HD
= 176284.5 - 167142.8
= 9141.7 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 ( 1729 - 1631 ) - 0
Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y' 0 kgf/mm
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
RING FLANGE DESIGN Shell Flng (Front)
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= 49
Radial distance from the bolt circle to the circle on which HD acts [hD]
= R + 0.5 x g1
= 49 + 0.5 x 0
= 49 mm
Radial distance from gasket load reaction to the bolt circle [hG]
= 0.5 x ( C - G )
= 0.5 x ( 1729 - 1675 )
= 27 mm
Radial distance from the bolt circle to the circle on which HT acts [hT]
= 0.5 x ( R + g1 + hG )
= 0.5 x ( 49 + 0 + 27 )= 38 mm
13. FLANGE MOMENTS UNDER OPERATING CONDITION AS PER APPENDIX 2-6
Component of moment due to HD [MD]
= HD x hD
= 167142.8 x 49
= 8189999.4 kgf-mm
Component of moment due to HG [MG]
= HG x hG
= 25499.6 x 27
= 688371.3 kgf-mm
Component of moment due to HT [MT]
= HT x hT
= 9141.7 x 38
= 347363.7 kgf-mmTotal moment acting on the flange for operating condition [MO]
= MD + MG + MT
= 8189999.4 + 688371.3 + 347363.7
= 9225734.4 kgf-mm
14. LOADS AND FORCES DURING GASKET SEATING AS PER APPENDIX 2-3
Gasket load for seating condition [HG]
= W
= 373650.9 kgf
15. MOMENT UNDER GASKET SEATING AS PER APPENDIX 2-6
Total moment acting on the flange for gasket seating [MO']
= W x hG
= 373650.9 x 27
= 10086863.4 kgf-mm
16. SHAPE CONSTANTSFactor [K]
= A / B
= 1786 / 1631
= 1.095
Flange factor from Fig. 2-7.1 [Y]
= 21.32
17. FLANGE THICKNESS REQUIRED AS PER APPENDIX 2-7
Equivalent moment [Mmax]
= MAX [ MO , MO' x Sfo / Sfa ]
= MAX [ 9225734.4 , 10086863.4 x 10.46 / 14.06 ]
= 9225734.4 kgf-mm
Corrected equivalent moment per unit length [M]
= Mmax x Cf / B
= 9225734.4 x 1 / 1631= 5656.5 kgf
Required thickness of flange [t]
= SQRT [ M x Y / Sfo ]
= SQRT [ 5656.5 x 21.32 / 10.46 ]
= 107.4 mm
18. FLANGE RIGIDITY CHECKING AS PER APPENDIX 2-14
Rigidity index [J]
= 109.4 x Mmax / ( Efo x tr 3x KL x ln ( K ) )
= 109.4 x 9225734.4 / ( 18786 x 148.1 3 x 0.2 x ln ( 1.095 ) )
= 0.996Since J < 1.0, design is safe
Assumed flange thickness tr 148.1 mm
Modulus of elasticity for flange Efo 18786 kgf/mm
Rigidity factor KL 0.2
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded 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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
FLANGE DESIGN ( EXTERNAL ) Shell Flng (Front)
CODE ASME VIII Div.1, 10 A11
Design pressure P 0.01055 kgf/mm g
Design temperature T 180 C
Allowance CA 0 mm
Groove allowance Tg 1.588 mm
M.O.C. SA-240 GR. 316 Plt. [UNS:S31600]
Code allw. stress @ design temp. Sfo 10.46 kgf/mm
Code allw. stress @ atm. temp. Sfa 14.06 kgf/mm
Inside diameter B 1631 mm
Outside diameter A 1786 mm
Hub length h 0 mm
Thickness ( hub end ) g1 0 mmThickness ( pipe end ) g0 0 mm
Thickness provided 158.5 mm
Thickness available 156.9 mm
M.O.C. SA-193 GR. B7 Bolt [UNS:G41400]
Code allw. stress @ design temp. Sb 17.58 kgf/mm
Code allw. stress @ atm. temp. Sa 17.58 kgf/mm
Bolt PCD C 1729 mm
Bolt dia. db 24 mm
No. of bolts nb 68
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 FaceCounter 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/mm
Gasket factor ( from Table 2-5.1 ) m 3
Inside diameter Gi 1631 mm
Outside diameter Go 1695.2 mm
Width of gasket ( as per Table 2-5.2 ) N 32.1 mm
Width of gasket ( as per Table 2-5.2 ) w 32.1 mm
Width of raised face or gasket contact width 38.1 mm
( as per Table 2-5.2 )
Basic gasket seating width ( as per Table 2-5.2 ) b0 16.05 mm
Effective gasket width ( as per Table 2-5.2 ) b 10.1 mm
Dia. at load reaction ( see Table 2-5.2 ) G 1675 mm
M.O.C. --
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6. BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1)
Total joint - contact surface compression load [Hp]
= 2 x ( px b x G x m + b' x Lp x m' ) x P
= 2 x ( px 10.1 x 1675 x 3 + 0 x 0 x 0 ) x 0.01055
= 3361.6 kgfTotal hydrostatic end force [H]
= 0.25 x px G x P
= 0.25 x px 1675 x 0.01055
= 23239.4 kgf
Minimum required bolt load for operating condition [Wm1a]
= Hp + H
= 3361.6 + 23239.4
= 26600.9 kgf
Minimum required bolt load for operating condition [Wm1b]
( from mating flange )
= 26600.9 kgf
Governing bolt load for operating condition [Wm1]
= MAX [ Wm1a , Wm1b ]
= MAX [ 26600.9 , 26600.9 ]= 26600.9 kgf
7. BOLT LOAD CALCULATION AS PER APPENDIX 2-5 (b2)
Minimum required bolt load for gasket seating [Wm2]
= ( px b x G x y + b' x Lp x y' )
= ( px 10.1 x 1675 x 7.031 + 0 x 0 x 0 )
= 373499.5 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
= 21249.6 mm
Actual bolt area using root diameter [Ab]
= 21266.9 mm
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
= 373650.9 kgf ( Avg. bolt area and margin factor of 1 )
9. CHECK FOR GASKET CRUSHING
Minimum gasket width required [Nmin]
= Ab x Sb / ( 2 x px y x G )
= 21266.9 x 17.58 / ( 2 x px 7.031 x 1675 )
= 5.052 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 px B 2x P
= 0.25 x px 1631 2x 0.01055
= 22034.2 kgf
Difference between total hydrostatic end force and hydrostatic end force on area inside of flange [HT]
= H - HD
= 23239.4 - 22034.2
= 1205.1 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 ( 1729 - 1631 ) - 0
= 49
Radial distance from the bolt circle to the circle on which HD acts [hD]
= R + 0.5 x g1
= 49 + 0.5 x 0
Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y' 0 kgf/mm
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
RING FLANGE DESIGN Shell Flng (Front)
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= 49 mm
Radial distance from gasket load reaction to the bolt circle [hG]
= 0.5 x ( C - G )
= 0.5 x ( 1729 - 1675 )
= 27 mm
Radial distance from the bolt circle to the circle on which HT acts [hT]
= 0.5 x ( R + g1 + hG )
= 0.5 x ( 49 + 0 + 27 )
= 38 mm
13. FLANGE MOMENTS UNDER OPERATING CONDITION AS PER APPENDIX 2-6
Component of moment due to HD [MD]
= HD x ( hD - hG )= 22034.2 x ( 49 - 27 )
= 484853.9 kgf-mm
Component of moment due to HT [MT]
= HT x ( hT - hG )
= 1205.1 x ( 38 - 27 )
= 13259.3 kgf-mm
Total moment acting on the flange for operating condition [MO]
= MD + MT
= 484853.9 + 13259.3
= 498113.2 kgf-mm
14. LOADS AND FORCES DURING GASKET SEATING AS PER APPENDIX 2-3
Gasket load for seating condition [HG]
= W
= 373650.9 kgf15. MOMENT UNDER GASKET SEATING AS PER APPENDIX 2-6
Total moment acting on the flange for gasket seating [MO']
= W x hG
= 373650.9 x 27
= 10086863.4 kgf-mm
16. SHAPE CONSTANTS
Factor [K]
= A / B
= 1786 / 1631
= 1.095
Flange factor from Fig. 2-7.1 [Y]
= 21.32
17. FLANGE THICKNESS REQUIRED AS PER APPENDIX 2-7
Equivalent moment [Mmax]= MAX [ MO , MO' x Sfo / Sfa ]
= MAX [ 498113.2 , 10086863.4 x 10.46 / 14.06 ]
= 7500591.6 kgf-mm
Corrected equivalent moment per unit length [M]
= Mmax x Cf / B
= 7500591.6 x 1 / 1631
= 4598.8 kgf
Required thickness of flange [t]
= SQRT [ M x Y / Sfo ]
= SQRT [ 4598.8 x 21.32 / 10.46 ]
= 96.83 mm
18. FLANGE RIGIDITY CHECKING AS PER APPENDIX 2-14
Rigidity index [J]
= 109.4 x Mmax / ( Efo x tr 3x KL x ln ( K ) )
= 109.4 x 7500591.6 / ( 18786 x 148.4 3 x 0.2 x ln ( 1.095 ) )
= 0.99
Since J < 1.0, design is safe
Assumed flange thickness tr 148.4 mm
Modulus of elasticity for flange Efo 18786 kgf/mm
Rigidity factor KL 0.2
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded 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 )
= 0.09055 x 800 / ( 13.79 x 0.85 - 0.6 x 0.09055 )
= 6.211 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 5.516 / ( 3 x 120.9 )
= 0.06086 kgf/mm 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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
DESIGN OF SHELL ( INTERNAL AND EXTERNAL PRESSURE ) Main Shell
CODE ASME VIII Div.1, 10 A11
Design pressure ( internal ) Pi 0.09055 kgf/mm g
Design pressure ( external ) Pe 0.06055 kgf/mm g
Design temperature T 180 C
Material of construction SA-240 GR. 316 Plt. [UNS:S31600]
Max. allowable stress at design temp. S 13.79 kgf/mm
Radiography Spot + T Joints
Joint efficiency long. seam Ec 0.85
Outside diameter OD 1628 mm
Inside radius ( corroded ) R 800 mm
Shell length L 2400 mm
Design length L1 2400 mm
Nominal thickness 14 mmNominal thickness required as per TEMA N.A. mm
Internal allowance, corrosion + polishing 0 mm
External allowance, corrosion + polishing 0 mm
Thickness undertolerance 0 mm
Available thickness 14 mm
Assumed te 13.47 mm
L1 / OD 1.474
OD / te 120.9
Factor A ( Refer to Fig. G in Subpart 3 of Sec. II, Part D ) 0.00067
Factor B ( HA-2 ) 5.516 kgf/mm
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded Condition ) :
2. DESIGN CALCULATION AS PER UG 32 e / APPENDIX 1-4 ( d ) :
Factor [M]
= ( 1 / 4 ) x [ 3 + SQRT [ CR / KR ] ]
= ( 1 / 4 ) x [ 3 + SQRT [ 1440 / 272 ] ]
= 1.325
Thickness for internal pressure [t]
= M x Pi x CR / ( 2 x S x E - 0.2 x Pi )
= 1.325 x 0.08 x 1440 / ( 2 x 13.79 x 1 - 0.2 x 0.08 )= 5.54 mm
3. DESIGN CALCULATION AS PER UG 33 e :
Thickness for equivalent external pressure [t]
= M x 1.67 x Pe x CR / ( 2 x S x 1.0 - 0.2 x 1.67 x Pe )
= 1.325 x 1.67 x 0.01055 x 1440 / ( 2 x 13.79 x 1.0 - 0.2 x 1.67 x 0.01055 )
= 1.219 mm
Assumed head thickness, [te]
= 4.454 mm
Assumed outside crown radius, [CRo]
= 1448 mm
Factor [A]
= 0.125 x te / CRo
= 0.125 x 4.454 / 1448
= 0.00038
Factor with reference to chart (HA-2) [B]
= 3.455 kgf/mm
Allowable external pressure [Pa]
= B x te / CRo
= 3.455 x 4.454 / 1448
= 0.01063 kgf/mm
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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
DESIGN OF TORISPHERICAL HEAD ( INT. & EXT. PRESSURE ) Dished End (Rear)
CODE ASME VIII Div.1, 10 A11
Design pressure ( internal ) Pi 0.08 kgf/mm g
Design pressure ( external ) Pe 0.01055 kgf/mm g
Design temperature T 180 C
Material of construction SA-240 GR. 316 Plt. [UNS:S31600]
Max. allowable stress @ design temp. S 13.79 kgf/mm
Radiography Full
Joint efficiency E 1
Outside diameter of head OD 1616 mm
Crown radius CR 1440 mm
Knuckle radius KR 272 mm
Nominal thickness 8 mm
Nominal thickness required as per TEMA N.A mmInternal allowance, corrosion + polishing 0 mm
External allowance, corrosion + polishing 0 mm
Thinning allowance / Under tolerance 0.8 mm
Available thickness 7.2 mm
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS :
2. SHELL DATA :
3. JACKET DATA :
4. MAX. ALLOWABLE WIDTH OF JACKET SPACE
Maximum allowed jacket spacing [Jmax]
= [ 4 x S x ts 2/ ( Pi x ID ) ] - 0.5 x ( ts + tj )
= [ 4 x 12.9 x 14 2/ ( 0.05 x 1728 ) ] - 0.5 x ( 14 + 8 )
= 106.1 mm.
In this case J < Jmax , jacket width is acceptable.
5. DESIGN CALCULATION AS PER 9.5 (c)(5) :
Calculated thickness of closure member for pressure [t1]
= 1.414 x SQRT [ 0.5 x OD1 x Pi x J / S ]
= 1.414 x SQRT [ 0.5 x 1628 x 0.05 x 50 / 12.9 ]
= 17.76 mmRequired minimum thickness of closure member [tr]
= MAX [ t1 , trj ]
= MAX [ 17.76 , 3.951 ]
= 17.76 mm
Since required minimum thickness of closure (tr) < available thickness of jacket closure (tc) , design is safe.
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
DESIGN OF JACKET CLOSURE Jacket Closure (Top)
Code ASME VIII Div.1, 10 A11
Design pressure ( INTERNAL ) Pi 0.05 kgf/mm g
Design temperature T 200 C
Material of construction SA-240 GR. 304 Plt. [UNS:S30400]
Max. allowable stress @ design temp. S 12.9 kgf/mm
Radiography Spot + T Joints
Joint efficiency E 0.85
Jacketing type Shell & Bottom End
Closure type Figure (f2)
Jacket spacing J 50 mm
Nominal closure thickness t 18 mm
Internal allowance, corrosion + polishing 0 mm
External allowance, corrosion + polishing 0 mmAvailable thickness tc 18 mm
Material of construction SA-240 GR. 316 Plt. [UNS:S31600]
Outside diameter OD1 1628 mm
Inside diameter ID1 1600 mm
Provided thickness 14 mm
Nominal thickness ts 14 mm
Material of construction SA-240 GR. 304 Plt. [UNS:S30400]
Outside diameter OD 1744 mm
Inside diameter ID 1728 mm
Provided thickness 8 mm
Nominal thickness tj 8 mm
Required minimum thickness of outer jacket wall trj 3.951 mm
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded 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 )
= 0.05 x 864 / ( 12.9 x 0.85 - 0.6 x 0.05 )
= 3.951 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 284.6 )
= 0.01064 kgf/mm 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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
DESIGN OF SHELL ( INTERNAL AND EXTERNAL PRESSURE ) Jacket Shell
CODE ASME VIII Div.1, 10 A11
Design pressure ( internal ) Pi 0.05 kgf/mm g
Design pressure ( external ) Pe 0.01055 kgf/mm g
Design temperature T 200 C
Material of construction SA-240 GR. 304 Plt. [UNS:S30400]
Max. allowable stress at design temp. S 12.9 kgf/mm
Radiography Spot + T Joints
Joint efficiency long. seam Ec 0.85
Outside diameter OD 1744 mm
Inside radius ( corroded ) R 864 mm
Shell length L 1850 mm
Design length L1 1850 mm
Nominal thickness 8 mmNominal thickness required as per TEMA N.A. mm
Internal allowance, corrosion + polishing 0 mm
External allowance, corrosion + polishing 0 mm
Thickness undertolerance 0 mm
Available thickness 8 mm
Assumed te 6.128 mm
L1 / OD 1.061
OD / te 284.6
Factor A ( Refer to Fig. G in Subpart 3 of Sec. II, Part D ) 0.00026
Factor B ( HA-1 ) 2.272 kgf/mm
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN CONDITIONS ( Design Mode 1 , Uncorroded Condition ) :
2. DESIGN CALCULATION AS PER UG 32 e / APPENDIX 1-4 ( d ) :
Factor [M]
= ( 1 / 4 ) x [ 3 + SQRT [ CR / KR ] ]
= ( 1 / 4 ) x [ 3 + SQRT [ 1728 / 175 ] ]
= 1.536
Thickness for internal pressure [t]
= M x Pi x CR / ( 2 x S x E - 0.2 x Pi )
= 1.536 x 0.05 x 1728 / ( 2 x 12.9 x 1 - 0.2 x 0.05 )= 5.144 mm
3. DESIGN CALCULATION AS PER UG 33 e :
Thickness for equivalent external pressure [t]
= M x 1.67 x Pe x CR / ( 2 x S x 1.0 - 0.2 x 1.67 x Pe )
= 1.536 x 1.67 x 0.01055 x 1728 / ( 2 x 12.9 x 1.0 - 0.2 x 1.67 x 0.01055 )
= 1.812 mm
Assumed head thickness, [te]
= 5.337 mm
Assumed outside crown radius, [CRo]
= 1736 mm
Factor [A]
= 0.125 x te / CRo
= 0.125 x 5.337 / 1736
= 0.00038
Factor with reference to chart (HA-1) [B]
= 3.456 kgf/mm
Allowable external pressure [Pa]
= B x te / CRo
= 3.456 x 5.337 / 1736
= 0.01062 kgf/mm
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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
DESIGN OF TORISPHERICAL HEAD ( INT. & EXT. PRESSURE ) Jacket Dish (Bottom)
CODE ASME VIII Div.1, 10 A11
Design pressure ( internal ) Pi 0.05 kgf/mm g
Design pressure ( external ) Pe 0.01055 kgf/mm g
Design temperature T 200 C
Material of construction SA-240 GR. 304 Plt. [UNS:S30400]
Max. allowable stress @ design temp. S 12.9 kgf/mm
Radiography Full
Joint efficiency E 1
Outside diameter of head OD 1744 mm
Crown radius CR 1728 mm
Knuckle radius KR 175 mm
Nominal thickness 8 mm
Nominal thickness required as per TEMA N.A mmInternal allowance, corrosion + polishing 0 mm
External allowance, corrosion + polishing 0 mm
Thinning allowance / Under tolerance 0.8 mm
Available thickness 7.2 mm
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'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 2107478.2 / ( 1928 x 4 ) ] - 6175 / 4
= -450.7 kgf
Required area of bolts [Am]
= MAX [ ( T / Fs ) , 0 ]
= MAX [ ( -450.7 / 20.88 ) , 0 ]
= 0 mm
Available area of bolts [Ab]
= Ar x Nb ........................................................................................ where, Ar = 217.1 mm, is root area of bolt= 217.1 x 2
= 434.1 mm
Since Ab > Am, bolts provided are sufficient
8. GUSSET DESIGN :
Reaction force at each support [Q]
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
LUG SUPPORT DESIGN Lug Support
CODE P V Design Manual, D.R. Moss
Design Mode 1 , Uncorroded
Condition
M.O.C IS-2062 GR. A Plt.
No. of support N 4
Base plate width b1 42 mm
Base plate depth Lb 220 mm
Thickness of base plate tb 16 mm
Allowable bending stress Sb 22.15 kgf/mm
M.O.C SA-36 / IS-1363,67 Bolt [UNS:K02600]
No. of bolt / lug Nb 2
Bolt diameter db 20 mm
PCD D 1928 mm
Diameter of bolt hole 24 mm
Allowable tensile stress Fs 20.88 kgf/mm
Thickness tg 16 mm
Height h 240 mm
Gusset angle ! 54.69
Gusset depth at top Lc 50 mm
Number of gussets n 1
Distance between gussets b 0 mm
Material SA-240 GR. 316 Plt. [UNS:S31600]
OD diameter OD 1628 mm
Inside diameter ID 1600 mm
Thickness available ts 14 mm
Material SA-240 GR. 316 Plt. [UNS:S31600]
Thickness tp 14 mm
Width W 330 mm
Length L 300 mm
Max. overturning moment M 2107478.2 kgf-mm
Design weight of vessel Wt 6175 kgf
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= [ 4 x M / ( D x N ) ] + Wt / N
= [ 4 x 2107478.2 / ( 1928 x 4 ) ] + 6175 / 4
= 2636.8 kgf
Maximum axial force in gusset [P1]
= Q
= 2636.8
= 2636.8 kgf
Allowable compr. stress in gusset [Sg]
= 1800 / [ ( 1 + 12 / 18000 ) x ( h / tg ) 2] ....................................... where, h = 294.1 mm
= 1800 / [ ( 1 + 12 / 18000 ) x ( 294.1 / 16 ) 2]
= 14690.8 psi
= 10.33 kgf/mm
Required thickness of gusset [tg]
= 2 x P1 x ( 3 x a - Lb ) / [ Sg x Lb 2x ( sin !) 2]
= 2 x 2636.8 x ( 3 x 150 - 220 ) / [ 10.33 x ( 220 ) 2x ( sin 54.69 ) 2]
= 3.644 mm
9. BASE PLATE DESIGN :
Bending moment [Mb]
= Q x b1 / 4
= 2636.8 x 42 / 4
= 27686.9 kgf-mmBearing pressure [bp]
= Q / ( w x b1 ) ............................................................................... where, w = 132 mm
= 2636.8 / ( 132 x 42 )
= 0.476 kgf/mm
Bending moment due to bearing pressure [Mb]
= bp x b 2/ 2
= 0.476 x 0 2/ 2
= 40.19 kgf-mm
Required thickness of base plate between chairs [tb]
= SQRT { 6 x MAX [ Mb , Mb' ] / [ ( Lb - db ) x Sb ] }
= SQRT { 6 x MAX [ 27686.9 , 40.19 ] / [ ( 220 - 20 ) x 22.15 ] }
= 6.186 mm
10. CHECK FOR COMPRESSION PLATE :
Equivalent radial load [f]
= Q x a / h
= 2636.8 x 150 / 240
= 1648 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 1648 x 1628
= 427011.1 kgf-mm
Bending stress induced [fb]
= Mo / Zc
= 427011.1 / 30687.7
= 13.91 kgf/mm ......................................................................... < Sb = 22.15 kgf/mm
Since, induced stress fb < allow. stress Sb in shell material, design is safe.
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'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 1923130.8 / ( 1928 x 4 ) ] - 4385.1 / 4
= -98.79 kgf
Required area of bolts [Am]
= MAX [ ( T / Fs ) , 0 ]
= MAX [ ( -98.79 / 20.88 ) , 0 ]
= 0 mm
Available area of bolts [Ab]
= Ar x Nb ........................................................................................ where, Ar = 217.1 mm, is root area of bolt= 217.1 x 2
= 434.1 mm
Since Ab > Am, bolts provided are sufficient
8. GUSSET DESIGN :
Reaction force at each support [Q]
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
LUG SUPPORT DESIGN Lug Support
CODE P V Design Manual, D.R. Moss
Design Mode 1 , Uncorroded
Condition
M.O.C IS-2062 GR. A Plt.
No. of support N 4
Base plate width b1 42 mm
Base plate depth Lb 220 mm
Thickness of base plate tb 16 mm
Allowable bending stress Sb 22.15 kgf/mm
M.O.C SA-36 / IS-1363,67 Bolt [UNS:K02600]
No. of bolt / lug Nb 2
Bolt diameter db 20 mm
PCD D 1928 mm
Diameter of bolt hole 24 mm
Allowable tensile stress Fs 20.88 kgf/mm
Thickness tg 16 mm
Height h 240 mm
Gusset angle ! 54.69
Gusset depth at top Lc 50 mm
Number of gussets n 1
Distance between gussets b 0 mm
Material SA-240 GR. 316 Plt. [UNS:S31600]
OD diameter OD 1628 mm
Inside diameter ID 1600 mm
Thickness available ts 14 mm
Material SA-240 GR. 316 Plt. [UNS:S31600]
Thickness tp 14 mm
Width W 330 mm
Length L 300 mm
Max. overturning moment M 1923130.8 kgf-mm
Design weight of vessel Wt 4385.1 kgf
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= [ 4 x M / ( D x N ) ] + Wt / N
= [ 4 x 1923130.8 / ( 1928 x 4 ) ] + 4385.1 / 4
= 2093.7 kgf
Maximum axial force in gusset [P1]
= Q
= 2093.7
= 2093.7 kgf
Allowable compr. stress in gusset [Sg]
= 1800 / [ ( 1 + 12 / 18000 ) x ( h / tg ) 2] ....................................... where, h = 294.1 mm
= 1800 / [ ( 1 + 12 / 18000 ) x ( 294.1 / 16 ) 2]
= 14690.8 psi
= 10.33 kgf/mm
Required thickness of gusset [tg]
= 2 x P1 x ( 3 x a - Lb ) / [ Sg x Lb 2x ( sin !) 2]
= 2 x 2093.7 x ( 3 x 150 - 220 ) / [ 10.33 x ( 220 ) 2x ( sin 54.69 ) 2]
= 2.893 mm
9. BASE PLATE DESIGN :
Bending moment [Mb]
= Q x b1 / 4
= 2093.7 x 42 / 4
= 21984.3 kgf-mmBearing pressure [bp]
= Q / ( w x b1 ) ............................................................................... where, w = 132 mm
= 2093.7 / ( 132 x 42 )
= 0.378 kgf/mm
Bending moment due to bearing pressure [Mb]
= bp x b 2/ 2
= 0.378 x 0 2/ 2
= 31.91 kgf-mm
Required thickness of base plate between chairs [tb]
= SQRT { 6 x MAX [ Mb , Mb' ] / [ ( Lb - db ) x Sb ] }
= SQRT { 6 x MAX [ 21984.3 , 31.91 ] / [ ( 220 - 20 ) x 22.15 ] }
= 5.513 mm
10. CHECK FOR COMPRESSION PLATE :
Equivalent radial load [f]
= Q x a / h
= 2093.7 x 150 / 240
= 1308.6 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 1308.6 x 1628
= 339060.9 kgf-mm
Bending stress induced [fb]
= Mo / Zc
= 339060.9 / 30687.7
= 11.05 kgf/mm ......................................................................... < Sb = 22.15 kgf/mm
Since, induced stress fb < allow. stress Sb in shell material, design is safe.
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. SHAFT DATA :
2. IMPELLER TORQUE, FORCES AND MOMENTS :
Formulae used in the above table :
Tm(i) = [ 736 x 60 x HP(i) / ( 9.81 x 2 x px RPM ) ] kgf-m = [ 716440.6 x P(i) / RPM ] kgf-mm
F(i) = Tm(i) / ( 0.75 x Rb ) kgf
M(i) = F(i) x L(i) kgf-mm
M'(i) = F(i) x ( L - L(i) ) kgf-mm
M"(i) = F(i) x ( L - L(i) ) 3kgf-mm 3
3. CHECK FOR EQUIVALENT BENDING MOMENT
Reaction at top bearing [R1]
= [ M" - M' x L 2] / [ 2 x A x L x ( A + L ) ]
= [ 146.8E09 - 424140.7 x 3738.3 2] / [ 2 x 250 x 3738.3 x ( 250 + 3738.3 ) ]
= -775.4 kgf
Reaction at bottom bearing [R2]
= [ - M' - R1 x ( A + L ) ] / L
= [ - 424140.7 - -775.4 x ( 250 + 3738.3 ) ] / 3738.3
= 713.8 kgf
Reaction at bush [R3]
= - [ R1 + R2 + F ]
= - [ -775.4 + 713.8 + 720.9 ]
= -659.3 kgf
Bending moment at the bottom bearing [Mt]
= M + R3 x L
= 2270981.5 + -659.3 x 3738.3
= -193854.1 kgf-mm
Induced equivalent moment in shaft [Me]
= ( Mt 2+ 0.75 x Tm 2) 0.5
= ( -193854.1 2+ 0.75 x 143288.1 2) 0.5
= 230169.6 kgf-mm
Stress induced in shaft [Fy]
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
AGITATOR SHAFT WITH INTERMEDIATE BEARING HOUSING Shaft
Power P 20 hp (MKS)
Pumping capacity (RPM) RPM 100
Service (Duty) factor sf 2
Material of impeller SA-479 GR. 316 Bar [UNS:S31600]
0.2% Proof stress Sy 21.09 kgf/mm
Allowable stress Sa 14.05 kgf/mm
Youngs modulus Es 18786 kgf/mm
Weight density rho 7999.5 kg/m
Shaft OD OD 101 mm
Shaft ID ID 0 mm
Total length 4438.3 mm
Allowance CA 0 mm
Shaft is propped at bottom TrueDistance between bearings A 250 mm
Overhanging length L 3738.3 mm
Type of shaft seal Gland Packing
Distance of packing /seal Y 300 mm
Allowable deflection at packing 0.5 mm
Impeller Length, Power, Radius, Torque, Force, Moment, Moment, Moment,
HubNo
L(i) mmP(i) hp(MKS)
Rb(i) mmTm(i) kgf-mm
F(i) kgf M(i) kgf-mm M'(i) kgf-mmM''(i) kgf-
mm3
1 3150 20 265 143288.1 720.9 2270981.5 424140.7 146.8E09
2
3
4
5
P = 20Tm =
143288.1F = 720.9
M =
2270981.5
M' =
424140.7
M" =
146.8E09
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= ( 32 x sf x Me x D1 ) / [ px ( D1 4 - ID 4) ] .......................... where, assumed D1 = 60.58 mm
= ( 32 x 2 x 230169.6 x 60.58 ) / [ px ( 60.58 4 - 0 4) ]
= 21.09 kgf/mm
Since induced stress (Fy)
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'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in
1. DESIGN DATA :
2. SHAFT DATA :
3. BLADE DATA :
4. CALCULATION OF BLADE THICKNESS
Torsional moment on shaft [Tm]
= 736 x 60 x H.P. / ( 9.81 x 2 x px RPM ) kg-m
= 716440.6 x P / RPM kgf-mm
= 716440.6 x 20 / 100
= 143288.1 kgf-mm
Effective force on blade [Fm]= Tm / ( 0.75 x Rb )
= 143288.1 / ( 0.75 x 265 )
= 720.9 kgf
Minimum blade thickness required [tb]
= SQRT [ 6 x sf x Tm / ( Nb x d x Sa ) ]
= SQRT [ 6 x 2 x 143288.1 / ( 4 x 125 x 21.09 ) ]
= 12.77 mm
Since the calculated thickness 12.77 mm is less that provided thickness 14 mm of blade, blade thickness is adequate.
Licensee :Sunay Wagle, CADEM Services,
Pune, India
Customer ABC Company Ltd.
Project / Equipment Soap Plant / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
DESIGN OF IMPELLER BLADE WITH STIFFENER : Impeller (1)
Power P 20 hp (MKS)
Pumping capacity (RPM) RPM 100
Service (Duty) factor sf 2
Material of impeller SA-240 GR. 316 Plt. [UNS:S31600]
0.2% Proof stress Sy 21.09 kgf/mm
Youngs modulus Es 18786 kgf/mm
Weight density r 7999.5 kg/m
Allowance CA 0 mm
Shaft OD at Impeller OD 101 mm
Total length L 3150 mm
Type of impellerImpellar radius R 265 mm
Distance of impeller from bottom bearing c 3150 mm
No of blades Nb 4 mm
Width of blade w 125 mm
Blade thickness tb 14 mm
Blade angle a 0
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'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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
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 77 mm
Width of lug A 135 mm
Thickness of lug plate TL 28 mm
Straight length B1 10 mm
Radius at tip R3 40 mm
Pin Hole diameter D1 50 mm
Lug to vessel weld size W1 10.22 mm
Min yield stress Sy 24.61 kgf/mm
Allowable tensile stress ( 2 / 3 x Sy ) St 16.4 kgf/mm
Allowable bending stress ( 1.5 x St ) Sb 22.15 kgf/mm
Allowable shear stress (0.6 x St ) Ss 9.843 kgf/mm
Empty weight of equipment Wt 5065.2 kgf
Number of lifting lugs N 2
Jirk load factor j 1.5
Dimension [ L1 ]
= LL - B1 - R3
= 77 - 10 - 40
= 27 mm
Dimension [ L2 ]
= L1 / SIN ( q1 )
= 27 / SIN ( 0.381 )
= 72.7 mm
Dimension [ LT ]= LL - R3
= 77 - 40
= 37 mm
Angle [ q2 ]= ASIN ( R3 / L2 )
= ASIN ( 40 / 72.7 )
= 0.583 radians
Angle [q1 ]
= ATAN ( 2 x L1 / A )
= ATAN ( 2 x 27 / 135 )
= 0.381 radians
Angle [ q3 ]
= q1 + q2
= 0.381 + 0.583
= 0.963 radians
Dimension [ L3 ]
= R3 / SIN ( q3 )
= 40 / SIN ( 0.963 )
= 48.72 mm
Effective design load on each lug [ P ]
= j x Wt / N
= 1.5 x 5065.2 / 2
= 3798.9 kgf
Required min. thickness of lug plate for shear [ t2 ]
= P / [ ( R3 - 0.5 x D1) x ss ]
= 3798.9 / [ ( 40 - 0.5 x 50 ) x 9.843 ]
= 25.73 mm
Required min. thickness of lug plate for bending [ t1 ]
= 6 x P x LT / ( A 2x Sb )
= 6 x 3798.9 x 37 / ( 135 2x 22.15 )
= 2.089 mm
Required min. thickness of lug plate for shear [ t3 ]
= P / [ ( 2 x L3 - D1 ) x ss ]
= 3798.9 / [ ( 2 x 48.72 - 50 ) x 9.843 ]
= 4.881 mm
Bending stress in weld [ f1 ]
= 6 x P x LT / [ 2 x LL2
]= 6 x 3798.9 x 37 / ( 2 x 77 2)
= 71.12 kgf/mm
Max. shear stress in weld [ f2 ]
= P / [ 2 x A ]= 3798.9 / ( 2 x 135 )
= 14.07 kgf/mm
Min. Size of lug plate weld [ w1 ]
= MAX ( f1 , 2 x f2 ) / ( 0.707 x Ss )
= MAX ( 71.12 , 2 x 14.07 ) / ( 0.707 x 9.843 )
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= 10.22 mm
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'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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
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 Uncorroded 5065.2 10988.8 1273.2 1273.2 2107.5 2107.5 1136.8 1534.9
2 Design1 Uncorroded 5065.2 11231.4 1273.2 1273.2 2107.5 2107.5 1161.9 1566.5
3 Hydro Uncorroded 4798.1 10964.4 1273.2 1273.2 2107.5 2107.5 1134.2 1529.2
4 Pneumatic Uncorroded 4798.1 4805.5 1273.2 1273.2 2107.5 2107.5 497.1 822.3
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'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 / Reactor R101
Designed By / Revision and Date / R00 , 06-04-2015 19:23:54
Sr.
No.Mode Condition
Empty Operating / Filled
Wt ( kgf ) C.G. ( mm ) Wt ( kgf ) C.G. ( mm )
1 Operating Uncorroded 5065.2 2111.4 10988.8 1806.42 Design1 Uncorroded 5065.2 2111.4 11231.4 1804.4
3 Hydro Uncorroded 4798.1 2111.4 10964.4 1804.4
4 Pneumatic Uncorroded 4798.1 2111.4 4805.5 2110.2