-
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: [email protected]
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 AND OTHERS AT
www.cadem.in/links
Pressure VesselsReaction VesselsAgitator ShaftsHeat
ExchangersProcess ColumnsStorage TankFloating RoofChimney
ASME Sec. VIII Div. 1TEMAEEUAIS 2825EN 13445API 650API 620IS
6533
-
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.
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
Index
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
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
-
'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 PlantLocation Vapi
SitePlant Refrigeration Plant
Design Code ASME VIII Div.1, 10 A11Equipment Name Gas
FilterEquipment Type Pressure VesselEquipment Class N.A.Equipment
Category N.A.Reference Drawing No ---Service Compressed Gas
ServicesSupport Type Lug Supports
Designed ByDesign Date 30-03-2015 23:35:19Checked ByApproved
ByRevision R00
Inspection Agency ---
Reviewed By ---
Front end Flat EndFront end flanged TrueRear end Dished EndRear
end flanged FalseShell ID 1250 mmShell OD 1270 mmLength, Shell
(W.L. to W.L) / Overall 1650 / 2254.6 mm
Fabricated weight 1898.3 kgfEmpty weight + external weights
1898.3 kgfEstimated operating weight 1926.8 kgfEstimated hydrotest
weight 4439.8 kgf
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
(1) PROCESS DETAILS :
(3) TEST PR. : kgf/mm g
(4) TEMPERATURE : C
(5) ALLOWANCES : mm
(6) RADIOGRAPHY & JOINT EFFICIENCY :
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
VESSEL DESIGN DATA
MEDIA DENSITYkg/m
Operating Process Gas 10Design1 Process Gas
12Design2StartupShutdownUpsetHydrotest Water 1000Pneumatic Process
Gas 1.2
(2) PR. : kgf/mm g INT. EXT.
Operating 0.1 0.12 0.01055Design1 0.12 0.12
0.01055Design2StartupShutdownUpset
Based onInput Pr MAWP MAP
Hydrotest 0.156 0.156 0.169Pneumatic 0.132 0.132 0.143
MIN. MAX.Input MDMT
Operating 20 -14.28 100Design1 20 -11.75
150Design2StartupShutdownUpsetHydrotest 21.67 -11.57 50Pneumatic
21.67 -11.75 50
INT. EXT.Corrosion 3 0Polishing 0 0
RADIOGRAPHY JOINT EFFICIENCYShell Spot + T Joints 0.85Head Full
1.00
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
VESSEL DESIGN DATA1. MATERIAL OF CONSTRUCTION :
2. NOZZLE CONNECTIONS :
3. INSULATION & CLADDING:
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
Shell sideShell 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 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/m / 25
mmMat. / Thk. Al. sheet / 1.191 mm
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
SUMMARY OF EFFECTIVE DESIGN PRESSURES IN kgf/mm g VS TEMPERATURE
IN C
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
Sr. Item name Temp. Inside pr. Liquid pr. Effective pr.No. +ve
-ve +ve -ve1 Cover (Front) 150 0.12 0.01055 0 0.12 0.010552 Shell
Flng (Front) 150 0.12 0.01055 0 0.12 0.010553 Main Shell 150 0.12
0.01055 0 0.12 0.010554 Dished End (Rear) 150 0.12 0.01055 0 0.12
0.010555
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
ITEM WISE WEIGHT SUMMARY
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
Sr.No. Item name Item size Empty wt Volume Filled wt
kgf m 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 10Thk 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 10Thk 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, 4.763Thk 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,
-
27 Lifting Lugs 2 Nos. 1.596 0 1.596
28 Pad (Lifting Lugs) 70 Long x 170 Wide x 8 Thk, 2Nos. 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
-
'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 CalculationsPressure due to hydro liquid column, [
Plh ]= Lh x rh x 1E-09= 0.00225 kgf/mm gHydrotest pressure, [ Ph ]=
1.3 x Pt - Plh= 1.3 x 0.12 - 0.00225= 0.154 kgf/mm gPneumatic test
pressure, [ Pn ]= 1.1 x Pt= 1.1 x 0.12= 0.132 kgf/mm g
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
Design Temperature T 150 COperating Liquid Density r 12 kg/m
Hydrotest Liquid Density rh 1000 kg/mHydrotest Liquid Column Lh
2254.6 mm
Sr.No. Item Name
Pressure ( kgf/mm g ) Stress Correction ( kgf/mm )Pt
Pi Pl Pc Pe Peff Sfo Sfa SfaSfo1 Cover (Front) 0.12 0 0 0.01055
0.12 14.06 14.06 1 0.122 Shell Flng (Front) 0.12 0 0 0.01055 0.12
14.06 14.06 1 0.123 Main Shell 0.12 0 0 0.01055 0.12 14.06 14.06 1
0.124 Dished End (Rear) 0.12 0 0 0.01055 0.12 14.06 14.06 1
0.125
Min. Pr., Pt 0.12
Pi = Internal positive pressurePl = Pressure due to design
liquid columnPe = Internal vacuum pressurePc = External negative
pressurePeff = Pi + Pl + PcSfo = Allowabe stress at design
temperatureSfa = Allowable stress at ambient temperaturePt = MAX [
Peff + Pc, Pe ] x ( Sfa / Sfo )
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
Vessel Inside
Legend :
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
CALC. OF MIN. DESIGN METAL TEMPERATURE Design Mode 1 , Corroded
ConditionCODE ASME VIII Div.1, 10 A11
Design Pressure Pi 0.12 kgf/mm gDesign Temperature T 150 C
Sr.No.
Item Name / Material /Group
Stress (kgf/mm) 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
2Shell 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 ShellSA-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
5Max, MDMT -11.75
Smt = Stress at minimum design metal temperature.Sdt = Pressure
due to design liquid columntn = 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 CorrectionMDMT = Final MDMT for the item =
Tm - Tc.
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
EXTREME FIBRE ELONGATION CALCULATION
Legend :
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
Sr.No.
Item Name MOC Rf t Eqn.No.
e HTmm mm %
1 Main Shell SA-516 GR. 70 Plt. [UNS:K02700] 625 10 1 0.8 False2
Dished End (Rear) SA-516 GR. 70 Plt. [UNS:K02700] 1130 10 2 0.664
False345
Rf = Mean radius after formingRo = Infinityt = Nominal thickness
of the plate before formingEqn. 1 = 50 x t / Rf x [ 1 - Rf / Ro
]Eqn. 2 = 75 x t / Rf x [ 1 - Rf / Ro ]
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
WIND LOAD CALCULATIONCODE Wind [IS:875, 87]
Basic wind speed ( Section 5.2 ) Vb 50 m/sExpected life of
equipment ( Section 5.3.1 ) 25 YearsProbability factor (Risk coeff)
( Section 5.3.1 ) K1 0.902Terrain category ( Section 5.3.2 )
Category 2Structure class ( Section 5.3.2.2 ) Class BTopography
factor ( Section 5.3.3 ) K3 1.3Force coefficient (Shape factor) Cf
0.8
Equivalent diameter De 1820 mmOverall length of equipment L
2254.6 mmHeight of C.G. of equipment Hcg 1807.5 mmSize and height
factor ( Section 5.3.2 ) K2 0.98Effective transverse cross
sectional area
= De x L A 4103343.3 mmEffective wind speed
= K1 x K2 x K3 x Vb Vz 57.44 m/sWind pressure
= 6E-08 x Vz 2 Pz 0.0002 kgf/mm
Longitudinal force= Cf x A x Pz F 649.9 kgf
Support elevation H 372.5 mmTurning moment
= F x ( Hcg - H ) M 932661.5 kgf-mm
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
SEISMIC LOAD CALCULATIONCODE Seismic [IS:1893, 02]
Weight of equipment Wo 1926.8 kgfImportance factor ( Table-6 ,
2002 ) I 1.5Soil profile type Stiff Soil Profile (SD)Foundation
type RCC footings + Tie BeamsDamping factor 5Seismic zone Zone
IIISeismic zone factor ( Table-2 , 2002 ) Z 0.16Response reduction
factor ( Table-7 , 2002 ) R 2.9Spectral accelerations coeff. ( Fig.
2 , 2002 ) Sa / g 2.5, Use max valueDamping correction factor (
Table-3 , 2002 ) Cf 1Seismic 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 mmHeight of C.G. of equipment Hcg
1807.5 mmSeismic 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
-
'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
kgfTotal hydrostatic end force [H]= 0.25 x x G 2 x P= 0.25 x x
1294.4 2 x 0.12= 157907.4 kgfMinimum required bolt load for
operating condition [Wm1]= Hp + H
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
DESIGN OF FLAT BOLTED HEAD ( INTERNAL ) Cover (Front)CODE ASME
VIII Div.1, 10 A11
Design pressure P 0.12 kgf/mm gDesign temperature T 150
CAllowance CA 3 mmGroove allowance Tg 0 mmRadiography Spot + T
JointsJoint efficiency E 1
M.O.C. SA-516 GR. 70 Plt. [UNS:K02700]Code allw. stress @ design
temp. Sfo 14.06 kgf/mmCode allw. stress @ atm. temp. Sfa 14.06
kgf/mmYoungs modulus Ey 19888.4 kgf/mmSelf reinforced FalseFlange
OD A 1420 mmThickness provided 73.41 mmThickness available 70.41
mm
M.O.C. SA-193 GR. B7 Bolt [UNS:G41400]Code allw. stress @ design
temp. Sb 17.58 kgf/mmCode allw. stress @ atm. temp. Sa 17.58
kgf/mmBolt PCD PCD 1363 mmBolt dia. db 24 mmNo. of bolts nb 56
M.O.C.Liner ID mmLiner OD mmLiner thk. mm
M.O.C. Spiral metal wound CAF filled (S.S.)Gasket seating stress
y 7.031 kgf/mmGasket factor m 3Inside diameter Gi 1256 mmOutside
diameter Go 1313.5 mmWidth of gasket N 28.75 mmWidth of gasket ( as
per Table 2-5.2 ) 31.75 mmBasic gasket seating width ( as per Table
2-5.2 ) b0 14.38 mmEffective gasket width ( as per Table 2-5.2 ) b
9.554 mmDia. at load reaction ( see Table 2-5.2 ) G 1294.4 mmPass
partition gasket width Wp 0 mmPass partition gasket length Lp 0
mmEffective pass partition gasket width b' 0 mm
-
= 27973 + 157907.4= 185880.4 kgf7. 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 kgf8. 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 mmActual bolt area using root diameter
[Ab]= 17513.9 mmFlange 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 mm10. 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 mm11. 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 FalseFactor C is user input FalseFactor C taken
from fig. UG 34 or user input 0.3Maximum factor C value C
0.75Factor C (effective) 0.3
C = Min ( 2 x 0.3, 0.75 ) for self reinf.C = 0.3 in other
cases
-
'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
kgfTotal hydrostatic end force [H]= 0.25 x x G 2 x P= 0.25 x x
1294.4 2 x 0.01055= 13877.8 kgfMinimum required bolt load for
operating condition [Wm1]= Hp + H
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
DESIGN OF FLAT BOLTED HEAD ( EXTERNAL ) Cover (Front)CODE ASME
VIII Div.1, 10 A11
Design pressure P 0.01055 kgf/mm gDesign temperature T 150
CAllowance CA 3 mmGroove allowance Tg 0 mmRadiography Spot + T
JointsJoint efficiency E 1
M.O.C. SA-516 GR. 70 Plt. [UNS:K02700]Code allw. stress @ design
temp. Sfo 14.06 kgf/mmCode allw. stress @ atm. temp. Sfa 14.06
kgf/mmYoungs modulus Ey 19888.4 kgf/mmSelf reinforced FalseFlange
OD A 1420 mmThickness provided 73.41 mmThickness available 70.41
mm
M.O.C. SA-193 GR. B7 Bolt [UNS:G41400]Code allw. stress @ design
temp. Sb 17.58 kgf/mmCode allw. stress @ atm. temp. Sa 17.58
kgf/mmBolt PCD PCD 1363 mmBolt dia. db 24 mmNo. of bolts nb 56
M.O.C.Liner ID mmLiner OD mmLiner thk. mm
M.O.C. Spiral metal wound CAF filled (S.S.)Gasket seating stress
y 7.031 kgf/mmGasket factor m 3Inside diameter Gi 1256 mmOutside
diameter Go 1313.5 mmWidth of gasket N 28.75 mmWidth of gasket ( as
per Table 2-5.2 ) 31.75 mmBasic gasket seating width ( as per Table
2-5.2 ) b0 14.38 mmEffective gasket width ( as per Table 2-5.2 ) b
9.554 mmDia. at load reaction ( see Table 2-5.2 ) G 1294.4 mmPass
partition gasket width Wp 0 mmPass partition gasket length Lp 0
mmEffective pass partition gasket width b' 0 mm
-
= 2458.4 + 13877.8= 16336.3 kgf7. 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 kgf8. 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 mmActual bolt area using root diameter
[Ab]= 17513.9 mmFlange 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 mm10. 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 mm11. 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 FalseFactor C is user input FalseFactor C taken
from fig. UG 34 or user input 0.3Maximum factor C value C
0.75Factor C (effective) 0.3
C = Min ( 2 x 0.3, 0.75 ) for self reinf.C = 0.3 in other
cases
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
FLANGE DESIGN ( INTERNAL ) Shell Flng (Front)CODE ASME VIII
Div.1, 10 A11
Design pressure P 0.12 kgf/mm gDesign temperature T 150
CAllowance CA 3 mmGroove allowance Tg 0 mm
M.O.C. SA-105 Frg. [UNS:K03504]Code allw. stress @ design temp.
Sfo 14.06 kgf/mmCode allw. stress @ atm. temp. Sfa 14.06
kgf/mmInside diameter B 1256 mmOutside diameter A 1420 mmHub length
h 30 mmThickness ( hub end ) g1 17 mmThickness ( pipe end ) g0 7
mmThickness provided 128.7 mmThickness available 125.7 mm
M.O.C. SA-193 GR. B7 Bolt [UNS:G41400]Code allw. stress @ design
temp. Sb 17.58 kgf/mmCode allw. stress @ atm. temp. Sa 17.58
kgf/mmBolt PCD C 1363 mmBolt dia. db 24 mmNo. of bolts nb 56
M.O.C.Liner ID mmLiner OD mmLiner thk. mm
M.O.C. Spiral metal wound CAF filled (S.S.)Gasket type Ring
GasketGasket confinement type UnconfinedFlange face type Raised
FaceFlange 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 1BApplicable
gasket column in Table 2-5.2 1Gasket seating stress ( refer to Note
1, Table 2-5.1 ) y 7.031 kgf/mmGasket factor ( from Table 2-5.1 ) m
3Inside diameter Gi 1256 mmOutside diameter Go 1313.5 mmWidth of
gasket ( as per Table 2-5.2 ) N 28.75 mmWidth of gasket ( as per
Table 2-5.2 ) w 28.75 mmWidth 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 mmEffective gasket width ( as per Table 2-5.2 ) b
9.554 mmDia. at load reaction ( see Table 2-5.2 ) G 1294.4 mm
M.O.C. --
-
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 kgfTotal hydrostatic end force [H]= 0.25 x p x G x P= 0.25 x
p x 1294.4 x 0.12= 157907.4 kgfMinimum required bolt load for
operating condition [Wm1a]= Hp + H= 27973 + 157907.4= 185880.4
kgfMinimum required bolt load for operating condition [Wm1b]( from
mating flange )= 185880.4 kgfGoverning bolt load for operating
condition [Wm1]= MAX [ Wm1a , Wm1b ]= MAX [ 185880.4 , 185880.4 ]=
185880.4 kgf7. 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 kgf8. 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 mmActual bolt area using root diameter
[Ab]= 17513.9 mmFlange 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 CRUSHINGMinimum 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 mm10. BOLT SPACING CORRECTION FACTORAs 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
2-3Hydrostatic 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 kgfGasket load
(difference between flange design bolt load and total hydrostatic
end force) [HG]= Wm1 - H= 185880.4 - 157907.4= 27973 kgfDifference
between total hydrostatic end force and hydrostatic end force on
area inside of flange [HT]= H - HD= 157907.4 - 148679.3= 9228.2
kgf12. MOMENT ARMS FOR FLANGE LOADS AS PER TABLE 2-6Radial 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/mmGasket factor ( from Table 2-5.1 ) m' 0Pass partition gasket
width Wp 0 mmPass partition gasket length Lp 0 mmEffective pass
partition gasket width b' 0 mm
INTEGRAL FLANGE DESIGN Shell Flng (Front)
-
= 36.5 mmRadial 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 mmRadial
distance from gasket load reaction to the bolt circle [hG]= 0.5 x (
C - G )= 0.5 x ( 1363 - 1294.4 )= 34.3 mmRadial 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 mm13. FLANGE MOMENTS UNDER
OPERATING CONDITION AS PER APPENDIX 2-6Component of moment due to
HD [MD]= HD x hD= 148679.3 x 45= 6690566.9 kgf-mmComponent of
moment due to HG [MG]= HG x hG= 27973 x 34.3 = 959588.9
kgf-mmComponent of moment due to HT [MT]= HT x hT= 9228.2 x 43.9=
405136.1 kgf-mmTotal moment acting on the flange for operating
condition [MO]= MD + MG + MT= 6690566.9 + 959588.9 + 405136.1 =
8055291.9 kgf-mm14. LOADS AND FORCES DURING GASKET SEATING AS PER
APPENDIX 2-3Gasket load for seating condition [HG]= W= 307837.2
kgf15. MOMENT UNDER GASKET SEATING AS PER APPENDIX 2-6Total moment
acting on the flange for gasket seating [MO']= W x hG= 307837.2 x
34.3= 10560086 kgf-mm16. SHAPE CONSTANTS
17. STRESS FORMULA FACTORSAssumed thickness [t]= 108.7 mmFactor
[a]= t x e + 1= 108.7 x 0.00922 + 1= 2.002Factor [b]= 1.333 x t x e
+ 1= 1.333 x 108.7 x 0.00922 + 1= 2.336Factor [g]= a / T = 2.002 /
1.866= 1.073Factor [d]= t 3 / d
A / B K 1.131Flange factors from Fig. 2-7.1 T 1.866
Z 8.189Y 15.84U 17.41
h0 93.77F / h0 e 0.00922Factor from Fig. 2-7.2 F 0.864Factor
from Fig. 2-7.3 V 0.261g1 / g0 2.429h / h0 0.32
( U / V ) x h0 x g0 2 d 306079.1
Factor from Fig. 2-7.6 f 2.935
-
= 108.7 3 / 306079.1= 4.195Factor [l]= g + d= 1.073 + 4.195=
5.26818. FLANGE STRESSES AS PER APPENDIX 2-7 & 2-8Equivalent
moment [Mmax]= MAX [ MO , MO' x Sfo / Sfa ]= MAX [ 8055291.9 ,
10560086 x 14.06 / 14.06 ] = 10560086 kgf-mmCorrected equivalent
moment per unit length [M]= Mmax x ( Cf / B )= 10560086 x ( 1 /
1256 )= 8407.7 kgfLongitudinal 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 )= 0.996Since J < 1.0, design is safe
= 16.21 kgf/mm .................................... < 1.5 x
Sfo
= 0.316 kgf/mm .................................... < Sfo
= 8.69 kgf/mm .................................... < Sfo
= 12.45 kgf/mm .................................... < Sfo
Modulus of elasticity for flange Efo 19888.4 kgf/mmRigidity
factor KI 0.3
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
FLANGE DESIGN ( EXTERNAL ) Shell Flng (Front)CODE ASME VIII
Div.1, 10 A11
Design pressure P 0.01055 kgf/mm gDesign temperature T 150
CAllowance CA 3 mmGroove allowance Tg 0 mm
M.O.C. SA-105 Frg. [UNS:K03504]Code allw. stress @ design temp.
Sfo 14.06 kgf/mmCode allw. stress @ atm. temp. Sfa 14.06
kgf/mmInside diameter B 1256 mmOutside diameter A 1420 mmHub length
h 30 mmThickness ( hub end ) g1 17 mmThickness ( pipe end ) g0 7
mmThickness provided 128.7 mmThickness available 125.7 mm
M.O.C. SA-193 GR. B7 Bolt [UNS:G41400]Code allw. stress @ design
temp. Sb 17.58 kgf/mmCode allw. stress @ atm. temp. Sa 17.58
kgf/mmBolt PCD C 1363 mmBolt dia. db 24 mmNo. of bolts nb 56
M.O.C.Liner ID mmLiner OD mmLiner thk. mm
M.O.C. Spiral metal wound CAF filled (S.S.)Gasket type Ring
GasketGasket confinement type UnconfinedFlange face type Raised
FaceFlange 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 1BApplicable
gasket column in Table 2-5.2 1Gasket seating stress ( refer to Note
1, Table 2-5.1 ) y 7.031 kgf/mmGasket factor ( from Table 2-5.1 ) m
3Inside diameter Gi 1256 mmOutside diameter Go 1313.5 mmWidth of
gasket ( as per Table 2-5.2 ) N 28.75 mmWidth of gasket ( as per
Table 2-5.2 ) w 28.75 mmWidth 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 mmEffective gasket width ( as per Table 2-5.2 ) b
9.554 mmDia. at load reaction ( see Table 2-5.2 ) G 1294.4 mm
M.O.C. --
-
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 kgfTotal hydrostatic end force [H]= 0.25 x p x G x
P= 0.25 x p x 1294.4 x 0.01055= 13877.8 kgfMinimum required bolt
load for operating condition [Wm1a]= Hp + H= 2458.4 + 13877.8=
16336.3 kgfMinimum required bolt load for operating condition
[Wm1b]( from mating flange )= 16336.3 kgfGoverning bolt load for
operating condition [Wm1]= MAX [ Wm1a , Wm1b ]= MAX [ 16336.3 ,
16336.3 ]= 16336.3 kgf7. 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 kgf8. 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 mmActual bolt area using root diameter
[Ab]= 17513.9 mmFlange 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 CRUSHINGMinimum 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 mm10. BOLT SPACING CORRECTION FACTORAs 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
2-3Hydrostatic 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 kgfDifference between
total hydrostatic end force and hydrostatic end force on area
inside of flange [HT]= H - HD= 13877.8 - 13066.8= 811 kgf12. MOMENT
ARMS FOR FLANGE LOADS AS PER APPENDIX TABLE 2-6Radial 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 mmRadial 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/mmGasket factor ( from Table 2-5.1 ) m' 0Pass partition gasket
width Wp 0 mmPass partition gasket length Lp 0 mmEffective pass
partition gasket width b' 0 mm
INTEGRAL FLANGE DESIGN Shell Flng (Front)
-
= 45 mmRadial distance from gasket load reaction to the bolt
circle [hG]= 0.5 x ( C - G )= 0.5 x ( 1363 - 1294.4 )= 34.3
mmRadial 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
mm13. FLANGE MOMENTS UNDER OPERATING CONDITION AS PER APPENDIX
2-6Component of moment due to HD [MD]= HD x ( hD - hG )= 13066.8 x
( 45 - 34.3 )= 139760.9 kgf-mmComponent of moment due to HT [MT]=
HT x ( hT - hG )= 811 x ( 43.9 - 34.3 )= 7784.2 kgf-mmTotal moment
acting on the flange for operating condition [MO]= MD + MT=
139760.9 + 7784.2= 147545.1 kgf-mm14. LOADS AND FORCES DURING
GASKET SEATING AS PER APPENDIX 2-3Gasket load for seating condition
[HG]= W= 307837.2 kgf15. MOMENT UNDER GASKET SEATING AS PER
APPENDIX 2-6Total moment acting on the flange for gasket seating
[MO']= W x hG= 307837.2 x 34.3= 10560086 kgf-mm16. SHAPE
CONSTANTS
17. STRESS FORMULA FACTORSAssumed thickness [t]= 108.9 mmFactor
[a]= t x e + 1= 108.9 x 0.00922 + 1= 2.004Factor [b]= 1.333 x t x e
+ 1= 1.333 x 108.9 x 0.00922 + 1= 2.338Factor [g]= a / T = 2.004 /
1.866= 1.074Factor [d]= t 3 / d= 108.9 3 / 306079.1= 4.217Factor
[l]= g + d= 1.074 + 4.217= 5.2918. FLANGE STRESSES AS PER APPENDIX
2-7 & 2-8Equivalent moment [Mmax]
A / B K 1.131Flange factors from Fig. 2-7.1 T 1.866
Z 8.189Y 15.84U 17.41
h0 93.77F / h0 e 0.00922Factor from Fig. 2-7.2 F 0.864Factor
from Fig. 2-7.3 V 0.261g1 / g0 2.429h / h0 0.32
( U / V ) x h0 x g0 2 d 306079.1
Factor from Fig. 2-7.6 f 2.935
-
= MAX [ MO , MO' x Sfo / Sfa ]= MAX [ 147545.1 , 10560086 x
14.06 / 14.06 ] = 10560086 kgf-mmCorrected equivalent moment per
unit length [M]= Mmax x ( Cf / B )= 10560086 x ( 1 / 1256 )= 8407.7
kgfLongitudinal 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 )= 0.992Since J < 1.0, design is safe
= 16.14 kgf/mm .................................... < 1.5 x
Sfo
= 0.313 kgf/mm .................................... < Sfo
= 8.669 kgf/mm .................................... < Sfo
= 12.4 kgf/mm .................................... < Sfo
Modulus of elasticity for flange Efo 19888.4 kgf/mmRigidity
factor KI 0.3
-
'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/mm gSince Pa > Pe, design
is safeSince available thickness is more than design thickness,
design is safe.
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
DESIGN OF SHELL ( INTERNAL AND EXTERNAL PRESSURE ) Main
ShellCODE ASME VIII Div.1, 10 A11
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign pressure (
external ) Pe 0.01055 kgf/mm gDesign temperature T 150 CMaterial of
construction SA-516 GR. 70 Plt. [UNS:K02700]Max. allowable stress
at design temp. S 14.06 kgf/mmRadiography Spot + T JointsJoint
efficiency long. seam Ec 0.85Outside diameter OD 1270 mmInside
radius ( corroded ) R 628 mmShell length L 1650 mmDesign length L1
1650 mmNominal thickness 10 mmNominal thickness required as per
TEMA N.A. mmInternal allowance, corrosion + polishing 3 mmExternal
allowance, corrosion + polishing 0 mmThickness undertolerance 0
mmAvailable thickness 7 mm
Assumed te 4.466 mmL1 / OD 1.299OD / te 284.4Factor A ( Refer to
Fig. G in Subpart 3 of Sec. II, Part D ) 0.00021Factor B ( CS-2 )
2.272 kgf/mm
-
'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]= 1Thickness 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 mm3. 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 mmFactor [Ko]= 0.77Assumed
head thickness, [te]= 2.779 mm Factor [A]= 0.125 x te / ( Ko x OD
)= 0.125 x 2.779 / ( 0.77 x 1270 )= 0.00036Factor with reference to
chart (CS-2) [B]= 3.743 kgf/mmAllowable external pressure [Pa]= B /
( Ko x OD / te )= 3.743 x 2.779 / ( 0.77 x 1270 )= 0.01064
kgf/mmSince Pa > Pe, design is safeSince available thickness is
more than design thickness, design is safe.
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
DESIGN OF ELLIPSOIDAL HEAD ( INT. & EXT. PRESSURE ) Dished
End (Rear)CODE ASME VIII Div.1, 10 A11
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign pressure (
external ) Pe 0.01055 kgf/mm gDesign temperature T 150 CMaterial of
construction SA-516 GR. 70 Plt. [UNS:K02700]Max. allowable stress @
design temp. S 14.06 kgf/mmRadiography FullJoint efficiency E
1Outside diameter of head OD 1270 mmInside diameter of shell ID
1256 mmHead shape Elliptical D/2H = 2.0Nominal thickness 10
mmNominal thickness required as per TEMA N.A mmInternal allowance,
corrosion + polishing 3 mmExternal allowance, corrosion + polishing
0 mmThinning allowance / Under tolerance 1 mmAvailable thickness 6
mm
109
-
'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 kgfRequired area of bolts [Am]= MAX [ ( T / Fs )
, 0 ]= MAX [ ( 2.203 / 20.88 ) , 0 ]= 0.106 mmAvailable area of
bolts [Ab]= Ar x Nb
........................................................................................
where, Ar = 217.1 mm, is root area of bolt= 217.1 x 1= 217.1
mmSince Ab > Am, bolts provided are sufficient8. GUSSET DESIGN :
Reaction force at each support [Q]= [ 4 x M / ( D x N ) ] + Wt /
N
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
LUG SUPPORT DESIGN Lug SupportCODE P V Design Manual, D.R.
Moss
Design Mode 1 , Corroded Condition
M.O.C IS-2062 GR. A Plt.No. of support N 4Base plate width b1
242 mmBase plate depth Lb 200 mmThickness of base plate tb 16
mmAllowable bending stress Sb 22.15 kgf/mm
M.O.C Commercial CS BoltNo. of bolt / lug Nb 1Bolt diameter db
20 mmPCD D 1570 mmDiameter of bolt hole 24 mmAllowable tensile
stress Fs 20.88 kgf/mm
Thickness tg 16 mmHeight h 190 mmGusset angle 51.71Gusset depth
at top Lc 50 mmNumber of gussets n 2Distance between gussets b 200
mm
Material SA-516 GR. 70 Plt. [UNS:K02700]OD diameter OD 1270
mmInside diameter ID 1256 mmThickness available ts 7 mm
Material SA-516 GR. 70 Plt. [UNS:K02700]Thickness tp 10 mmWidth
W 270 mmLength L 292 mm
Max. overturning moment M 940925.4 kgf-mmDesign weight of vessel
Wt 2388.5 kgf
-
= [ 4 x 940925.4 / ( 1570 x 4 ) ] + 2388.5 / 4= 1196.4
kgfMaximum axial force in gusset [P1]= Q / n = 1196.4 / 2= 598.2
kgfAllowable 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/mmRequired thickness of gusset [tg]
= 2 x P1 x ( 3 x a - Lb ) / [ Sg x Lb 2 x ( sin ) 2 ] = 2 x
598.2 x ( 3 x 150 - 200 ) / [ 10.98 x ( 200 ) 2 x ( sin 51.71 ) 2 ]
= 1.106 mm9. BASE PLATE DESIGN : Bending moment [Mb]= Q x b1 / 6=
1196.4 x 242 / 6= 48255.9 kgf-mmBearing pressure [bp]= Q / ( w x b1
)
...............................................................................
where, w = 120 mm= 1196.4 / ( 120 x 242 )= 0.0412 kgf/mmBending
moment due to bearing pressure [Mb]
= bp x b 2 / 10= 0.0412 x 200 2 / 10= 164.8 kgf-mmRequired
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 mm10. CHECK FOR COMPRESSION
PLATE :Equivalent radial load [f]= Q x a / h= 1196.4 x 150 / 190=
472.3 kgfAngle between supports [b]= 2 x p / N= 2 x p / 4= 1.571
radInternal bending moment coefficient [Kr]= 0.5 x [ 1 / a - cot (
a ) ]= 0.5 x [ 1 / 1.571 - cot ( 1.571 ) ]= 0.318Internal bending
moment [Mc]= 0.5 x Kr x f x OD= 0.5 x 0.318 x 472.3 x 1270= 95459.3
kgf-mmBending stress induced [fb]= Mo / Zc= 95459.3 / 7785.1= 12.26
kgf/mm
.........................................................................
< Sb = 22.15 kgf/mmSince, induced stress fb < allow. stress
Sb in shell material, design is safe.
-
'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 kgfRequired area of bolts [Am]= MAX [ ( T / Fs )
, 0 ]= MAX [ ( -276.5 / 20.88 ) , 0 ]= 0 mmAvailable area of bolts
[Ab]= Ar x Nb
........................................................................................
where, Ar = 217.1 mm, is root area of bolt= 217.1 x 1= 217.1
mmSince Ab > Am, bolts provided are sufficient8. GUSSET DESIGN :
Reaction force at each support [Q]= [ 4 x M / ( D x N ) ] + Wt /
N
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
LUG SUPPORT DESIGN Lug SupportCODE P V Design Manual, D.R.
Moss
Design Mode 1 , Corroded Condition
M.O.C IS-2062 GR. A Plt.No. of support N 4Base plate width b1
242 mmBase plate depth Lb 200 mmThickness of base plate tb 16
mmAllowable bending stress Sb 22.15 kgf/mm
M.O.C Commercial CS BoltNo. of bolt / lug Nb 1Bolt diameter db
20 mmPCD D 1570 mmDiameter of bolt hole 24 mmAllowable tensile
stress Fs 20.88 kgf/mm
Thickness tg 16 mmHeight h 190 mmGusset angle 51.71Gusset depth
at top Lc 50 mmNumber of gussets n 2Distance between gussets b 200
mm
Material SA-516 GR. 70 Plt. [UNS:K02700]OD diameter OD 1270
mmInside diameter ID 1256 mmThickness available ts 7 mm
Material SA-516 GR. 70 Plt. [UNS:K02700]Thickness tp 10 mmWidth
W 270 mmLength L 292 mm
Max. overturning moment M 288590.5 kgf-mmDesign weight of vessel
Wt 1841.2 kgf
-
= [ 4 x 288590.5 / ( 1570 x 4 ) ] + 1841.2 / 4= 644.1 kgfMaximum
axial force in gusset [P1]= Q / n = 644.1 / 2= 322.1 kgfAllowable
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/mmRequired thickness of gusset [tg]
= 2 x P1 x ( 3 x a - Lb ) / [ Sg x Lb 2 x ( sin ) 2 ] = 2 x
322.1 x ( 3 x 150 - 200 ) / [ 10.98 x ( 200 ) 2 x ( sin 51.71 ) 2 ]
= 0.595 mm9. BASE PLATE DESIGN : Bending moment [Mb]= Q x b1 / 6=
644.1 x 242 / 6= 25979.7 kgf-mmBearing pressure [bp]= Q / ( w x b1
)
...............................................................................
where, w = 120 mm= 644.1 / ( 120 x 242 )= 0.02218 kgf/mmBending
moment due to bearing pressure [Mb]
= bp x b 2 / 10= 0.02218 x 200 2 / 10= 88.72 kgf-mmRequired
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 mm10. CHECK FOR COMPRESSION
PLATE :Equivalent radial load [f]= Q x a / h= 644.1 x 150 / 190=
254.3 kgfAngle between supports [b]= 2 x p / N= 2 x p / 4= 1.571
radInternal bending moment coefficient [Kr]= 0.5 x [ 1 / a - cot (
a ) ]= 0.5 x [ 1 / 1.571 - cot ( 1.571 ) ]= 0.318Internal bending
moment [Mc]= 0.5 x Kr x f x OD= 0.5 x 0.318 x 254.3 x 1270= 51392.7
kgf-mmBending stress induced [fb]= Mo / Zc= 51392.7 / 7785.1= 6.601
kgf/mm
.........................................................................
< Sb = 22.15 kgf/mmSince, induced stress fb < allow. stress
Sb in shell material, design is safe.
-
'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 45Neck 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 mmNeck thickness for
external pressure as per UG 45(a)Neck thickness for external
pressure as per UG 28 Assumed neck thickness , [trn3] = 0.512 mmL /
OD = 0.891OD / trn3 = 328.5Factor A = 0.00025Factor B = 2.679
kgf/mmAllowable external pressure , [Pa]= 4 x B / ( 3 x OD / trn3
)= 4 x 2.679 / ( 3 x 328.5 )= 0.01088 kgf/mm gThickness 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 mmThickness 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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
NOZZLE NECK THICKNESS AND REINFORCEMENT DESIGN N 01CODE ASME
VIII Div.1, 10 A11
Design Mode 1 , Corroded Condition
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign pressure (
external ) Pe 0.01055 kgf/mm gDesign temperature T 150 C
M.O.C. SA-106 GR. B Smls. Pipe[UNS:K03006]Allowable stress @
design temperature Sn 12.02 kgf/mmOutside diameter OD 168.3
mmInside diameter ID 152.3 mmMaximum chord length D 152.3 mmNeck
thickness ( provided ) tnp 10.97 mmInternal allowance , corrosion +
polishing CAI 3 mmExternal allowance , corrosion + polishing CAE
0Neck thickness (tnp - CAI - CAE) tn 7.973 mmMax. under tolerance
on thickness Alw 1.372 mmAvailable neck thickness ( tn - Alw ) ta
6.601 mmNozzle projection outward ( from vessel outer face ) Lo 150
mmTotal length of nozzle ( Lo + Addn for curvature) L 156 mm
Connection type Pipe NozzleApplication type Process
OpeningReinforcement calculation method Isolated OpeningDesign as
large opening False
M.O.C. SA-516 GR. 70 Plt. [UNS:K02700]Allowable stress @ design
temperature Sv 14.06 kgf/mmInside radius R 628 mmThickness t 7
mmMin. thickness for external pressure tr2 4.466 mm
Nozzle outside weld W1 7 mm
-
= 0.01055 x 628 / ( 14.06 x 1.0 - 0.6 x 0.01055 )= 0.471
mmStandard wall thickness as per UG 45(b)(4) , [t3]= 7.112 mmNeck
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 OpeningSince available neck thickness, ta >= trn,
selected neck thickness is adequate.
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
LOCAL STRESS ANALYSIS (EDGE OF ATTACHMENT) N 01
CODE D.R. MOSS (EXTRACT OF WRC 107)Design Mode 1,
CorrodedCondition
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign temperature
T 150 C
M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006]Outside diameter OD
168.3 mmWeld size w 7 mmPad diameter Dp 292.7 mmPad thickness tp 10
mm0.5 x OD C 84.14 mm
Radial force Fr 344.6 kgfLong. moment ML 254724.1 kgf-mmCirc.
moment Mc 254724.1 kgf-mmTorsional moment Mt 254724.1 kgf-mmTotal
eff. shear load Q 487.4 kgf
M.O.C SA-516 GR. 70 Plt. [UNS:K02700]Allowable stress Sv 14.06
kgf/mmInside radius R 628 mmThickness 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/mm
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/mm
Total shear stress , [ t ]= t1 + t2= 0.151 + 0.469= 0.62
kgf/mm
STRESSES FACT FIG. FORCES( kgf ) & MOMENTS( kgf-mm ) STRESS
( kgf/mm )
Radial load
Membrane5-17A 7.023 x FrRm Nf 3.803
Kn x Nft
f 0.312
5-17B 8.616 x FrRm Nx 4.665Kn x Nxt
x 0.382
Bending5-18A 0.117 x Fr Mf 40.25
6 x Kb x Mft 2
f 1.621
6 x Kb x Mx
-
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 Sv2. Membrane + Bending,
Sa = 3 x Sv3. Shear only, Sh = 0.5 x SvDESIGN IS ACCEPTABLE ? :
YES
5-18B 0.0707 x Fr Mx 24.37 t 2 x 0.981
Long. moment
MembraneCL=1 5-19A
3.516 x CL x MLRm 2 x b
Nf 19.11 Kn x Nft
f 1.566
CL=1 5-19B1.697 x CL x MLRm 2 x b
Nx 9.222 Kn x Nxtx 0.756
Bending5-20A
0.03827 x MLRm x b Mf 132.4
6 x Kb x Mft 2
f 5.331
5-20B 0.06937 x MLRm x B Mx 2406 x Kb x Mxt 2
x 9.665
Circ. moment
MembraneCc=1 5-21A
1.893 x Cc x McRm 2 x b
Nf 10.29 Kn x Nft
f 0.843
Cc=1 5-21B2.973 x Cc x McRm 2 x b
Nx 16.16 Kn x Nxtx 1.324
Bending5-22A 0.09066 x McRm x b Mf 313.7
6 x Kb x Mft 2
f 12.63
5-22B0.04678 x McRm x b Mx 161.9
6 x Kb x Mxt 2
x 6.518
Stress due tox f
0 90 180 270 0 90 180 270
Radial load, Fr.(1)
MembraneNf 0.312 0.312 0.312 0.312Nx 0.382 0.382 0.382 0.382
BendingMf 1.621 1.621 1.621 1.621Mx 0.981 0.981 0.981 0.981
Long. moment,
ML.
MembraneNf +( 1.566 ) -( 1.566 )
Nx +( 0.756 ) -( 0.756 )
BendingMf +( 5.331 ) -( 5.331 )
Mx +( 9.665 ) -( 9.665 )
Circ moment,
Mc.
MembraneNf +( 0.843 ) -( 0.843 )
Nx +( 1.324 ) -( 1.324 )
BendingMf + ( 12.63 )
-( 12.63 )
Mx +( 6.518 ) -( 6.518 )
Int. pr., P.
Pi x Rmt
f +( 10.91 )+( 10.91)
+( 10.91 )
+( 10.91 )
Pi x Rm2 x t
x +( 5.456 )+( 5.456 )
+( 5.456 )
+( 5.456 )
Total,
Membrane 6.593 7.162 5.082 4.514 12.86 12.14 9.728 10.45Mem+Bend
17.24 14.66 -3.601 -1.023 19.74 26.32 5.946 -0.631
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
LOCAL STRESS ANALYSIS (EDGE OF PAD) N 01
CODE D.R. MOSS (EXTRACT OF WRC 107)Design Mode 1,
CorrodedCondition
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign temperature
T 150 C
M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006]Outside diameter OD
168.3 mmWeld size w 7 mmPad diameter Dp 292.7 mmPad thickness tp 0
mm0.5 x OD C 146.3 mm
Radial force Fr 344.6 kgfLong. moment ML 254724.1 kgf-mmCirc.
moment Mc 254724.1 kgf-mmTorsional moment Mt 254724.1 kgf-mmTotal
eff. shear load Q 487.4 kgf
M.O.C SA-516 GR. 70 Plt. [UNS:K02700]Allowable stress Sv 14.06
kgf/mmInside radius R 628 mmThickness 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/mm
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/mm
Total shear stress , [ t ]= t1 + t2= 0.151 + 0.27= 0.422
kgf/mm
STRESSES FACT FIG. FORCES( kgf ) & MOMENTS( kgf-mm ) STRESS
( kgf/mm )
Radial load
Membrane5-17A 4.941 x FrRm Nf 2.696
Kn x Nft
f 0.385
5-17B 11.06 x FrRm Nx 6.037Kn x Nxt
x 0.862
Bending5-18A 0.04175 x Fr Mf 14.39
6 x Kb x Mft 2
f 1.762
6 x Kb x Mx
-
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 Sv2. Membrane + Bending,
Sa = 3 x Sv3. Shear only, Sh = 0.5 x SvDESIGN IS ACCEPTABLE ? :
YES
5-18B 0.01857 x Fr Mx 6.398 t 2 x 0.783
Long. moment
MembraneCL=1 5-19A
6.231 x CL x MLRm 2 x b
Nf 19.63 Kn x Nft
f 2.804
CL=1 5-19B3.293 x CL x MLRm 2 x b
Nx 10.38 Kn x Nxtx 1.482
Bending5-20A
0.0128 x MLRm x b Mf 25.46
6 x Kb x Mft 2
f 3.117
5-20B 0.01693 x MLRm x B Mx 33.686 x Kb x Mxt 2
x 4.124
Circ. moment
MembraneCc=1 5-21A
3.869 x Cc x McRm 2 x b
Nf 12.19 Kn x Nft
f 1.741
Cc=1 5-21B7.986 x Cc x McRm 2 x b
Nx 25.16 Kn x Nxtx 3.594
Bending5-22A 0.06043 x McRm x b Mf 120.2
6 x Kb x Mft 2
f 14.72
5-22B0.026 x McRm x b Mx 51.73
6 x Kb x Mxt 2
x 6.334
Stress due tox f
0 90 180 270 0 90 180 270
Radial load, Fr.(1)
MembraneNf ( 0.385 ) ( 0.385) ( 0.385 ) ( 0.385 )Nx ( 0.862 ) (
0.862 ) ( 0.862 ) ( 0.862 )
BendingMf ( 1.762 ) ( 1.762 ) ( 1.762 ) ( 1.762 )Mx ( 0.783 ) (
0.783 ) ( 0.783 ) ( 0.783 )
Long. moment,
ML.
MembraneNf +( 2.804 ) -( 2.804 )
Nx +( 1.482 ) -( 1.482 )
BendingMf +( 3.117 ) -( 3.117 )
Mx +( 4.124 ) -( 4.124 )
Circ moment,
Mc.
MembraneNf +( 1.741 ) -( 1.741 )
Nx +( 3.594 ) -( 3.594 )
BendingMf + ( 14.72 )
-( 14.72 )
Mx +( 6.334 ) -( 6.334 )
Int. pr., P.
Pi x Rmt
f +( 10.83 )+( 10.83)
+( 10.83 )
+( 10.83 )
Pi x Rm2 x t
x +( 5.413 )+( 5.413 )
+( 5.413 )
+( 5.413 )
Total,
Membrane 7.757 9.869 4.793 2.681 14.49 13.43 8.884 9.947Mem+Bend
12.67 16.99 1.452 -2.87 18.89 29.44 7.051 -3.49
-
'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 45Neck 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 mmNeck thickness for
external pressure as per UG 45(a)Neck thickness for external
pressure as per UG 28 Assumed neck thickness , [trn3] = 0.512 mmL /
OD = 0.891OD / trn3 = 328.5Factor A = 0.00025Factor B = 2.679
kgf/mmAllowable external pressure , [Pa]= 4 x B / ( 3 x OD / trn3
)= 4 x 2.679 / ( 3 x 328.5 )= 0.01088 kgf/mm gThickness 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 mmThickness 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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
NOZZLE NECK THICKNESS AND REINFORCEMENT DESIGN N 02CODE ASME
VIII Div.1, 10 A11
Design Mode 1 , Corroded Condition
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign pressure (
external ) Pe 0.01055 kgf/mm gDesign temperature T 150 C
M.O.C. SA-106 GR. B Smls. Pipe[UNS:K03006]Allowable stress @
design temperature Sn 12.02 kgf/mmOutside diameter OD 168.3
mmInside diameter ID 152.3 mmMaximum chord length D 152.3 mmNeck
thickness ( provided ) tnp 10.97 mmInternal allowance , corrosion +
polishing CAI 3 mmExternal allowance , corrosion + polishing CAE
0Neck thickness (tnp - CAI - CAE) tn 7.973 mmMax. under tolerance
on thickness Alw 1.372 mmAvailable neck thickness ( tn - Alw ) ta
6.601 mmNozzle projection outward ( from vessel outer face ) Lo 150
mmTotal length of nozzle ( Lo + Addn for curvature) L 156 mm
Connection type Pipe NozzleApplication type Process
OpeningReinforcement calculation method Isolated OpeningDesign as
large opening False
M.O.C. SA-516 GR. 70 Plt. [UNS:K02700]Allowable stress @ design
temperature Sv 14.06 kgf/mmInside radius R 628 mmThickness t 7
mmMin. thickness for external pressure tr2 4.466 mm
Nozzle outside weld W1 7 mm
-
= 0.01055 x 628 / ( 14.06 x 1.0 - 0.6 x 0.01055 )= 0.471
mmStandard wall thickness as per UG 45(b)(4) , [t3]= 7.112 mmNeck
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 OpeningSince available neck thickness, ta >= trn,
selected neck thickness is adequate.
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
LOCAL STRESS ANALYSIS (EDGE OF ATTACHMENT) N 02
CODE D.R. MOSS (EXTRACT OF WRC 107)Design Mode 1,
CorrodedCondition
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign temperature
T 150 C
M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006]Outside diameter OD
168.3 mmWeld size w 7 mmPad diameter Dp 292.7 mmPad thickness tp 10
mm0.5 x OD C 84.14 mm
Radial force Fr 344.6 kgfLong. moment ML 254724.1 kgf-mmCirc.
moment Mc 254724.1 kgf-mmTorsional moment Mt 254724.1 kgf-mmTotal
eff. shear load Q 487.4 kgf
M.O.C SA-516 GR. 70 Plt. [UNS:K02700]Allowable stress Sv 14.06
kgf/mmInside radius R 628 mmThickness 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/mm
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/mm
Total shear stress , [ t ]= t1 + t2= 0.151 + 0.469= 0.62
kgf/mm
STRESSES FACT FIG. FORCES( kgf ) & MOMENTS( kgf-mm ) STRESS
( kgf/mm )
Radial load
Membrane5-17A 7.023 x FrRm Nf 3.803
Kn x Nft
f 0.312
5-17B 8.616 x FrRm Nx 4.665Kn x Nxt
x 0.382
Bending5-18A 0.117 x Fr Mf 40.25
6 x Kb x Mft 2
f 1.621
6 x Kb x Mx
-
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 Sv2. Membrane + Bending,
Sa = 3 x Sv3. Shear only, Sh = 0.5 x SvDESIGN IS ACCEPTABLE ? :
YES
5-18B 0.0707 x Fr Mx 24.37 t 2 x 0.981
Long. moment
MembraneCL=1 5-19A
3.516 x CL x MLRm 2 x b
Nf 19.11 Kn x Nft
f 1.566
CL=1 5-19B1.697 x CL x MLRm 2 x b
Nx 9.222 Kn x Nxtx 0.756
Bending5-20A
0.03827 x MLRm x b Mf 132.4
6 x Kb x Mft 2
f 5.331
5-20B 0.06937 x MLRm x B Mx 2406 x Kb x Mxt 2
x 9.665
Circ. moment
MembraneCc=1 5-21A
1.893 x Cc x McRm 2 x b
Nf 10.29 Kn x Nft
f 0.843
Cc=1 5-21B2.973 x Cc x McRm 2 x b
Nx 16.16 Kn x Nxtx 1.324
Bending5-22A 0.09066 x McRm x b Mf 313.7
6 x Kb x Mft 2
f 12.63
5-22B0.04678 x McRm x b Mx 161.9
6 x Kb x Mxt 2
x 6.518
Stress due tox f
0 90 180 270 0 90 180 270
Radial load, Fr.(1)
MembraneNf 0.312 0.312 0.312 0.312Nx 0.382 0.382 0.382 0.382
BendingMf 1.621 1.621 1.621 1.621Mx 0.981 0.981 0.981 0.981
Long. moment,
ML.
MembraneNf +( 1.566 ) -( 1.566 )
Nx +( 0.756 ) -( 0.756 )
BendingMf +( 5.331 ) -( 5.331 )
Mx +( 9.665 ) -( 9.665 )
Circ moment,
Mc.
MembraneNf +( 0.843 ) -( 0.843 )
Nx +( 1.324 ) -( 1.324 )
BendingMf + ( 12.63 )
-( 12.63 )
Mx +( 6.518 ) -( 6.518 )
Int. pr., P.
Pi x Rmt
f +( 10.91 )+( 10.91)
+( 10.91 )
+( 10.91 )
Pi x Rm2 x t
x +( 5.456 )+( 5.456 )
+( 5.456 )
+( 5.456 )
Total,
Membrane 6.593 7.162 5.082 4.514 12.86 12.14 9.728 10.45Mem+Bend
17.24 14.66 -3.601 -1.023 19.74 26.32 5.946 -0.631
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
LOCAL STRESS ANALYSIS (EDGE OF PAD) N 02
CODE D.R. MOSS (EXTRACT OF WRC 107)Design Mode 1,
CorrodedCondition
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign temperature
T 150 C
M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006]Outside diameter OD
168.3 mmWeld size w 7 mmPad diameter Dp 292.7 mmPad thickness tp 0
mm0.5 x OD C 146.3 mm
Radial force Fr 344.6 kgfLong. moment ML 254724.1 kgf-mmCirc.
moment Mc 254724.1 kgf-mmTorsional moment Mt 254724.1 kgf-mmTotal
eff. shear load Q 487.4 kgf
M.O.C SA-516 GR. 70 Plt. [UNS:K02700]Allowable stress Sv 14.06
kgf/mmInside radius R 628 mmThickness 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/mm
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/mm
Total shear stress , [ t ]= t1 + t2= 0.151 + 0.27= 0.422
kgf/mm
STRESSES FACT FIG. FORCES( kgf ) & MOMENTS( kgf-mm ) STRESS
( kgf/mm )
Radial load
Membrane5-17A 4.941 x FrRm Nf 2.696
Kn x Nft
f 0.385
5-17B 11.06 x FrRm Nx 6.037Kn x Nxt
x 0.862
Bending5-18A 0.04175 x Fr Mf 14.39
6 x Kb x Mft 2
f 1.762
6 x Kb x Mx
-
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 Sv2. Membrane + Bending,
Sa = 3 x Sv3. Shear only, Sh = 0.5 x SvDESIGN IS ACCEPTABLE ? :
YES
5-18B 0.01857 x Fr Mx 6.398 t 2 x 0.783
Long. moment
MembraneCL=1 5-19A
6.231 x CL x MLRm 2 x b
Nf 19.63 Kn x Nft
f 2.804
CL=1 5-19B3.293 x CL x MLRm 2 x b
Nx 10.38 Kn x Nxtx 1.482
Bending5-20A
0.0128 x MLRm x b Mf 25.46
6 x Kb x Mft 2
f 3.117
5-20B 0.01693 x MLRm x B Mx 33.686 x Kb x Mxt 2
x 4.124
Circ. moment
MembraneCc=1 5-21A
3.869 x Cc x McRm 2 x b
Nf 12.19 Kn x Nft
f 1.741
Cc=1 5-21B7.986 x Cc x McRm 2 x b
Nx 25.16 Kn x Nxtx 3.594
Bending5-22A 0.06043 x McRm x b Mf 120.2
6 x Kb x Mft 2
f 14.72
5-22B0.026 x McRm x b Mx 51.73
6 x Kb x Mxt 2
x 6.334
Stress due tox f
0 90 180 270 0 90 180 270
Radial load, Fr.(1)
MembraneNf ( 0.385 ) ( 0.385) ( 0.385 ) ( 0.385 )Nx ( 0.862 ) (
0.862 ) ( 0.862 ) ( 0.862 )
BendingMf ( 1.762 ) ( 1.762 ) ( 1.762 ) ( 1.762 )Mx ( 0.783 ) (
0.783 ) ( 0.783 ) ( 0.783 )
Long. moment,
ML.
MembraneNf +( 2.804 ) -( 2.804 )
Nx +( 1.482 ) -( 1.482 )
BendingMf +( 3.117 ) -( 3.117 )
Mx +( 4.124 ) -( 4.124 )
Circ moment,
Mc.
MembraneNf +( 1.741 ) -( 1.741 )
Nx +( 3.594 ) -( 3.594 )
BendingMf + ( 14.72 )
-( 14.72 )
Mx +( 6.334 ) -( 6.334 )
Int. pr., P.
Pi x Rmt
f +( 10.83 )+( 10.83)
+( 10.83 )
+( 10.83 )
Pi x Rm2 x t
x +( 5.413 )+( 5.413 )
+( 5.413 )
+( 5.413 )
Total,
Membrane 7.757 9.869 4.793 2.681 14.49 13.43 8.884 9.947Mem+Bend
12.67 16.99 1.452 -2.87 18.89 29.44 7.051 -3.49
-
'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 45Thickness of
head as per UG 37Min. 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 mmNeck 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 mmNeck thickness for external pressure
as per UG 45(a)Neck thickness for external pressure as per UG 28
Assumed neck thickness , [trn3] = 0.279 mmL / OD = 2.487OD / trn3 =
216.3Factor A = 0.00016Factor B = 1.763 kgf/mmAllowable external
pressure , [Pa]= 4 x B / ( 3 x OD / trn3 )= 4 x 1.763 / ( 3 x 216.3
)
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
NOZZLE NECK THICKNESS AND REINFORCEMENT DESIGN N 03CODE ASME
VIII Div.1, 10 A11
Design Mode 1 , Corroded Condition
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign pressure (
external ) Pe 0.01055 kgf/mm gDesign temperature T 150 C
M.O.C. SA-106 GR. B Smls. Pipe[UNS:K03006]Allowable stress @
design temperature Sn 12.02 kgf/mmOutside diameter OD 60.33
mmInside diameter ID 48.85 mmMaximum chord length D 48.85 mmNeck
thickness ( provided ) tnp 8.738 mmInternal allowance , corrosion +
polishing CAI 3 mmExternal allowance , corrosion + polishing CAE
0Neck thickness (tnp - CAI - CAE) tn 5.738 mmMax. under tolerance
on thickness Alw 1.092 mmAvailable neck thickness ( tn - Alw ) ta
4.645 mmNozzle projection outward ( from vessel outer face ) Lo 150
mmTotal length of nozzle ( Lo + Addn for curvature) L 150 mm
Connection type Pipe NozzleApplication type Process
OpeningReinforcement calculation method Isolated OpeningDesign as
large opening False
Allowable stress @ design temperature Sv 14.06 kgf/mmInside
diameter of head @ head skirt Dsf 1256 mmD / 2 H for Ellispoidal
head 2Factor from Table UG-37 K1 0.9Inside diameter of equivalent
sphere, K1 x Dsk x 2 ID1 2260.8 mmThickness t 7 mmMin. thickness
for external pressure tr2 2.779 mm
Nozzle outside weld W1 6.35 mm
-
= 0.01087 kgf/mm gThickness of head as per UG 45(b)(1)Min. head
thickness reqd. as per UG 27(d) , [trn2 = tr1]= 4.828 mmThickness
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 mmStandard wall thickness as per UG
45(b)(4) , [t3]= 3.912 mmNeck 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 OpeningSince available neck thickness, ta >= trn,
selected neck thickness is adequate.
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
LOCAL STRESS ANALYSIS ( ROUND ATTACHMENT ) N 03
CODE D.R. MOSS (EXTRACT OF WRC 107)Design Mode 1,
CorrodedCondition
Design pressure ( internal ) Pi 0.12 kgf/mm gDesign temperature
T 150 C
M.O.C SA-106 GR. B Smls. Pipe [UNS:K03006]Outside diameter OD
60.33 mmWeld size w 7 mm
0.5 x OD Ro = C 30.16 mm
Radial force Fr 74.92 kgfLatitudinal moment ML 29967.5
kgf-mmMeridional moment Mc 29967.5 kgf-mm
Total eff. moment, [ ML 2 + Mc 2 ] 0.5 M 42380.5 kgf-mm
Shear load Q 106 kgfTorsional moment Mt 29967.5 kgf-mm
M.O.C SA-516 GR. 70 Plt. [UNS:K02700]Allowable stress Sv 14.06
kgf/mmInside radius R 1130.4 mmThickness ( 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/mm
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/mm
Total shear stress , [ t ]= t1 + t2= 0.16 + 0.749= 0.909
kgf/mm
STRESS FIGURE VALUE FROM FIGURE STRESS ( kgf/mm )
Radial load
Membrane5-25A Nx x tFr
-0.06044
Kn x Fr t 2
x -0.09241
5-25B Nf x tFr
-0.179Kn x Frt 2
f -0.274
Bending 5-26AMxFr 0.0621
6 x Kb x Frt 2
x 0.57
-
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 Sv2. Membrane + Bending,
Sa = 3 x Sv3. Shear only, Sh = 0.5 x SvDESIGN IS ACCEPTABLE ? :
YES
5-26B MfFr
0.1316 x Kb x Frt 2
f 1.203
Moment , M
Membrane5-27A Nx x t x SQRT [ Rm x t ]M
-0.05621
Kn x M t 2 x SQRT [ Rm x t ]
x -0.546
5-27B Nf x t x SQRT [ Rm x t ]M
-0.159Kn x Mt 2x SQRT [ Rm x t ]
f -1.541
Bending5-28A Mx x SQRT [ Rm x t ] M 0.117
6 x Kb x Mt 2 x SQRT [ Rm x t ]
x 6.794
5-28B Mf x SQRT [ Rm x t ]M 0.436 x Kb x M t 2x SQRT [ Rm x t
]
f 25.07
Stress due tox f
0 90 180 270 0 90 180 270
Radial load, Fr.(1)
MemberaneNx +( -0.274 )
+( -0.274 )
+( -0.274 )
+( -0.274 )
Nf +( -0.09241 )+( -0.09241 )
+( -0.09241 )
+( -0.09241 )
BendingMx +( 1.203 )
+( 1.203 )
+( 1.203 )
+( 1.203 )
Mf +( 0.57 ) +( 0.57 ) +( 0.57 ) +( 0.57 )
Moment, M.
MemberaneNx +( -1.541 )
-( -1.541 )
Nf +( -0.546 )-( -0.546 )
BendingMx +( 25.07 )
-( 25.07 )
Mf +( 6.794 ) -( 6.794 )
Int. pr., P.
Pi x Rmt
f +( 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
0.274Mem+Bend 28.09 1.477 -25.14 1.477 8.002 0.662 -6.678 0.662
-
'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, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
DESIGN OF LIFTING LUG Lifting LugsCODE P V Design Manual, D.R.
Moss
Design Mode 1 , Uncorroded Condition
Material IS-2062 GR. A Plt.Length of lug LL 70 mmWidth of lug A
120 mmThickness of lug plate TL 12 mmStraight length B1 10 mmRadius
at tip R3 35 mmPin Hole diameter D1 40 mmLug to vessel weld size W1
8 mmMin yield stress Sy 24.61 kgf/mmAllowable tensile stress ( 2 /
3 x Sy ) St 16.4 kgf/mmAllowable bending stress ( 1.5 x St ) Sb
22.15 kgf/mmAllowable shear stress (0.6 x St ) Ss 9.843 kgf/mm
Empty weight of equipment Wt 2149.7 kgfNumber of lifting lugs N
2Jirk 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 )
-
= 5.028 mm
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
FOUNDATION LOAD DATA
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
Sr.No. Mode Condition
Weight ( kgf ) Wind Seismic
Empty FilledShear ( 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
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
CENTER OF GRAVITY DATA
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
Sr.No. Mode Condition
Empty Operating / FilledWt ( kgf ) C.G. ( mm ) Wt ( kgf ) C.G. (
mm )
1 Operating Corroded 1898.3 1820.2 1922.1 1809.62 Design1
Corroded 1898.3 1820.2 1926.8 1807.53 Hydro Corroded 1841.1 1820.2
4212.7 1374.54 Pneumatic Corroded 1841.1 1820.2 1843.9 1818.95
Operating Uncorroded 2149.7 1729.8 2173.2 1721.76 Design1
Uncorroded 2149.7 1729.8 2177.9 1720.17 Hydro Uncorroded 2092.5
1729.8 4439.8 1361.38 Pneumatic Uncorroded 2092.5 1729.8 2095.3
1728.8
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
Index
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
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
-
'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 PlantLocation Vapi
SitePlant Refrigeration Plant
Design Code ASME VIII Div.1, 10 A11Equipment Name Gas
FilterEquipment Type Pressure VesselEquipment Class N.A.Equipment
Category N.A.Reference Drawing No ---Service Compressed Gas
ServicesSupport Type Lug Supports
Designed ByDesign Date 30-03-2015 23:35:19Checked ByApproved
ByRevision R00
Inspection Agency ---
Reviewed By ---
Front end Flat EndFront end flanged TrueRear end Dished EndRear
end flanged FalseShell ID 1250 mmShell OD 1270 mmLength, Shell
(W.L. to W.L) / Overall 1650 / 2254.6 mm
Fabricated weight 1841.1 kgfEmpty weight + external weights
1841.1 kgfEstimated operating weight 4212.7 kgfEstimated hydrotest
weight 4439.8 kgf
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
(1) PROCESS DETAILS :
(3) TEST PR. : kgf/mm g
(4) TEMPERATURE : C
(5) ALLOWANCES : mm
(6) RADIOGRAPHY & JOINT EFFICIENCY :
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
VESSEL DESIGN DATA
MEDIA DENSITYkg/m
Operating Process Gas 10Design1 Process Gas
12Design2StartupShutdownUpsetHydrotest Water 1000Pneumatic Process
Gas 1.2
(2) PR. : kgf/mm g INT. EXT.
Operating 0.1 0.12 0.01055Design1 0.12 0.12
0.01055Design2StartupShutdownUpset
Based onInput Pr MAWP MAP
Hydrotest 0.156 0.156 0.169Pneumatic 0.132 0.132 0.143
MIN. MAX.Input MDMT
Operating 20 -14.28 100Design1 20 -11.75
150Design2StartupShutdownUpsetHydrotest 21.67 -11.57 50Pneumatic
21.67 -11.75 50
INT. EXT.Corrosion 3 0Polishing 0 0
RADIOGRAPHY JOINT EFFICIENCYShell Spot + T Joints 0.85Head Full
1.00
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
VESSEL DESIGN DATA1. MATERIAL OF CONSTRUCTION :
2. NOZZLE CONNECTIONS :
3. INSULATION & CLADDING:
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
Shell sideShell 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 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/m / 25
mmMat. / Thk. Al. sheet / 1.191 mm
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
SUMMARY OF EFFECTIVE DESIGN PRESSURES IN kgf/mm g VS TEMPERATURE
IN C
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment Soap Plant / Gas FilterDesigned By
/ Revision and Date / R00 , 30-03-2015 23:35:19
Sr. Item name Temp. Inside pr. Liquid pr. Effective pr.No. +ve
-ve +ve -ve1 Cover (Front) 50 0.12 0 0.00007 0.12 02 Shell Flng
(Front) 50 0.12 0 0.00023 0.12 03 Main Shell 50 0.12 0 0.00188
0.122 04 Dished End (Rear) 50 0.12 0 0.00225 0.122 05
-
'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website
www.cadem.in
ITEM WISE WEIGHT SUMMARY
Licensee : Sunay Wagle, CADEM Services, Pune, IndiaCustomer ABC
Company Ltd.Project / Equipment