Design Of A Large Rectangular Flange-Books Pdf

DESIGN OF A LARGE RECTANGULAR FLANGE
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the head that will be used The actual head being used. for this application has a radius at this juncture and it. PRELIMINARY ENGINEERING DESIGN is in compliance with the ASME code . The pressure vessel design software COMPRESS was used The peak stress of 93 918 psi present in a very tiny. to design the vessel shell jacket nozzles solid unstiffened flat zone in the flange is near the 1 75 thick flat head . welded covers and saddle supports The COMPRESS software This is secondary stress caused by constraints of thick. was also used to design circumferential integral flanges with material and it is self relieving and therefore it is not a. the same design conditions and gasket materials etc The flange concern . dimensions obtained by this method were used as guidelines to. obtain preliminary sizes for the large rectangular flanges and Apart from these two zones discussed above the majority. gasket seating arrangements of the FEA model has following listed values of stress. intensity , FINITE ELEMENT MODEL, The coordinate directions for Finite Elements analysis are Maximum Stress Intensity in the longitudinal flange . as follows Sint 70 479 psi Sallow 71 600 psi OK, Maximum Stress Intensity in the shell . X Along the vessel axis Sint 47 040 psi Sallow 50 100 psi OK. Y Perpendicular to the vessel axis Average Gasket Seating Stress . Z DOWN Vertical GKSX 4156 psi GKSXreqd 3 000 psi OK. Maximum Gasket Compression , The one half 1 2 model of the vessel with rectangular GKD 0 127 GKT 0 300 OK. flange was meshed to generate finite element model for the. analysis Two different cases gasket seating and operating The displacement plot for vessel and flange model is. case of this model were run to perform the analysis The FEA shown in Fig 6 The reaction loads for bolts and gaskets and. cases are covered in this report and are listed as follows gasket closure plot for PRELOAD and PRELOAD . The modeling was done using SOLID45 elements which PRESSURE cases are shown in Fig 7 and 8 The displacement. are 8 noded brick elements with 3 DOF at each node The contours for the model are shown in Fig 9 . pretension elements PRETS179 were used to apply bolt preload The Von Mises stress plots for PRELOAD and PRELOAD. of 25000 psi The mesh plots for the finite element model are PRESSURE cases are shown in Fig 10 11 The Stress. shown in Fig 3 and 4 Intensity plots for PRELOAD and PRELOAD PRESSURE. cases are shown in Fig 12 13 , BOUNDARY CONDITIONS The gasket stress plots for PRELOAD case are shown in. The symmetry boundary conditions were applied to all the Fig 14 and 15 The gasket stress plots for PRELOAD . nodes on the cut surface of the one half 1 2 model Two PRESSURE case are shown in Fig 16 and 17 . additional nodes were constrained in lateral direction for. stability of the model DESIGN SUMMARY, The 50 psig design pressure was applied to all the internal Based on the engineering calculations and finite element.
surfaces of the vessel analysis following are the specific designs based on the. The boundary condition plots are shown in Fig 5 specified design parameters . DISCUSSION Vessel Shell Jacket , The circular cylindrical block at the center of the flat Main Cylinder Mat SA 240 Grade 316L 60 ID X. welded head is 4 5 wide based on the 4 flange width and 150 Length x 0 50 thk . 0 5 thickness of flat head The modeled block was 5 75 Jacket Cylinder Mat SA 240 Grade 316L 0 25 thk . wide with 4 flange width and 1 75 flat head plate . Left and Right flat welded heads Mat SA 240 Grade. 316L 1 75 thk Without stiffeners , STRESS ANALYSIS RESULTS. Please refer to the attached FEA analysis and FEA plots Longitudinal Flange Welded Integral Flange . The following discussion covers the explanation of couple of. Flange Material SA 516 Grade 70, high stress spots in the FEA model . Flange Dimensions 4 0 Wide x 3 0 thk , Approx Bolt Spacing 3 0 . The peak stress intensity of 105 637 psi at the juncture. of thick head FEA model only and shell is due to Bolt Dia 1 00 . stress concentration factor at the sharp discontinuity Gasket Material GARLOCK Style 3535. present there This peak stress will not be present for Gasket Dimensions 0 75 wide x 0 300 thk . 2 Copyright 2006 by ICPVT, Bolts , Bolt Material SA 193 Grade B7.
Split Flange Block Cover Flange Nut Material SA 194 Grade 2H. Material SA 182 Grade F316L Minimum Recommended Bolt Preload 25 000 psi. Size Rating 14 Class 150 Studding Outlet Flat Maximum Recommended Bolt Preload 60 000 psi. faced With Thickness of 6 Please note that this is The vessel digital photographs taken in fabrication shop. different form the standard 2 thickness are shown in Fig 18 19 and 20 . Outside Diameter 21 , Inside Diameter Approximately 15 can be CONCLUSION. customized as per requirement From the detailed plots for gasket stresses it can be seen. Number of Stud holes 12 that the gasket stresses are above 3000 psi at some point across. Stud Circle Diameter 18 75 the gasket width and that is sufficient to seal the gasket for both. Tap Size 1 8 threads per inch the Gasket Seating and Operating conditions . Tap Depth 1 12 Based on the results of the finite element analysis it can be. Cover Flange 14 Class 150 Blind Flange Material concluded that the flanges and the associated gasketed joint are. SA 182 Grade F316L in compliance with ASME Boiler Pressure Vessel Code . Special Request SPLIT the studding outlet in the Section VIII Div 1 . middle to have two semi circular blocks, REFERENCES. Gasket ASME Boiler Pressure Vessel Code Sec VIII Div . Gasket Material GARLOCK Style 3535 1 2001 Edition with 2003 Addenda . Gasket Dimensions 0 75 wide x 0 300 thk ASME Boiler Pressure Vessel Code Sec VIII Div . Recommended gasket seating pressure 3 000 4 000 2 2001 Edition with 2003 Addenda . psi ASME Boiler Pressure Vessel Code Sec II Part D . 2001 Edition with 2003 Addenda , 3 Copyright 2006 by ICPVT. ALLOWABLE STRESS CALCULATIONS , Material SA 240 Grade 316L. Allowable Stress in tension at 70 F per ASME Code Section VIII Div 1 Sma 16 700 psi. Allowable Stress in tension at 300 F per ASME Code Section VIII Div 1 Smo 16 700 psi. Per ASME Section VIII Div 2 Appendix 4 , General Primary Membrane Stress Limit Pm Smo 16 700 psi.
Primary Local Membrane and Bending Stress Limit PL Pb 1 5 Smo 25 050 psi. Primary Local Membrane Bending Secondary Stress Limit . PL Pb Q Larger of 3 Smavg 2 Syavg , Average of allowable stresses Smavg 0 5 16 700 16 700 16 700 psi. Sallow1 3 Smavg 3 16 700 psi 50 100 psi, Yield Strength of SA 240 316L 300 F Syo 19 000 psi. Yield Strength of SA 240 316L 70 F Sya 25 000 psi, Average of Yield Stresses Syavg 0 5 19 000 25 000 22 000 psi. Sallow2 2 Syavg 2 22 000 44 000 psi, Allowable stress per ASME Sec VIII Div 2 Appendix 4 PL PB Q . Sallow Larger of Sallow1 Sallow2 , Sallow Larger of 50 100 psi 44 000 psi .
Sallow 50 100 psi, Material SA 516 Grade 70, Allowable Stress in tension at 70 F per ASME Code Section VIII Div 1 Sma 20 000 psi. Allowable Stress in tension at 300 F per ASME Code Section VIII Div 1 Smo 20 000 psi. Per ASME Section VIII Div 2 Appendix 4 , General Primary Membrane Stress Limit Pm Smo 20 000 psi. Primary Local Membrane and Bending Stress Limit PL Pb 1 5 Smo 30 000 psi. Primary Local Membrane Bending Secondary Stress Limit . PL Pb Q Larger of 3 Smavg 2 Syavg , Average of allowable stresses Smavg 0 5 20 000 20 000 20 000 psi. Sallow1 3 Smavg 3 20 000 psi 60 000 psi, Yield Strength of SA 240 316L 300 F Syo 33 600 psi. Yield Strength of SA 240 316L 70 F Sya 38 000 psi, Average of Yield Stresses Syavg 0 5 33 600 38 000 35 800 psi.
Sallow2 2 Syavg 2 35 800 71 600 psi, Allowable stress per ASME Sec VIII Div 2 Appendix 4 PL PB Q . Sallow Larger of Sallow1 Sallow2 , Sallow Larger of 60 000 psi 71 600 psi . Sallow 71 600 psi, II, 0 5 IHI , J lELL MAT A 24b C 31 L . o 0 0 0 0, i 75 TUK LAT ftAb, MAT SA 2f6 fiR 3 L . b 0 If p o, C 7 JCULA t FL fic , II TO Bt MD Elf .
CYt r J TCAI , I LOCI , 15 NDT TD lJE TA7 Jle 1 . i 0 , o 4, 1 II, IN Z b t 3 TH K , Lt Gc, MAT A 51 70 . o 0 0, Frt l VeSSEL IMCNSTDI JS, Fb R FE A , 1 i 1 rA BOLT J Lf . FoR 1 J rl DfJLT , Fig 3 Mesh Plot Fig 4 Mesh Plot. Dimensions, Fig 5 Boundary Conditions, Fig 6 Fig 7 Reactions.
Displacements for Preload, Fig 8 Reactions for, Preload Pressure Fig 9 Displacement Contours. Fig 10 Fig 11, Fig 12 Fig 13, Fig 14 Fig 15, Fig 16 Fig 17. A mixer vessel Vessel Shell SA 240 Grade 316L was to be designed for a large horizontal agitator with the shaft protruding through the two flat ends of the vessel The horizontal vessel was split in the middle horizontal plane creating a large rectangular opening This rectangular opening was to be sealed using the two

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