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Hi all, I am struggling to understand the correct approach in ASME VIII Div 2 Part 5 2023 Edition for elastic-plastic buckling (Method B). Step 1 is clear. Step 2; is the suggestion that the linear elastic buckling displacements are factored by the manufacturing tolerance (or measured...

Hi TGS4, thanks for your responses so far. Do you have any further thoughts on this?

I'm not at my computer to check, but I've potentially given you values adjusted by E, but I've also ran E = 1. It's 200degC so no derating if I remember correctly.

579 mm OD, 10 mm wt, 3 mm CA, 2:1 elliptical head, 4500 mm between saddle supports, 6445 overall length. One thing I should have been clearer about, this is a FFS of an older vessel using API 579-1. Therefore the Beta load factor is 3.6 (M of 4 x RSFa), which means the benefit of using...

I had run a sub model which was effectively the plain cylinder only. The hoop stress is considerably higher for a given pressure than the hand calc hoop stress, I believe this is purely a function of the non-linear geometry. At high strains the radius increases significantly enough that stresses...

Hi TSG4. Thanks for your response. UTS = 410 MPa, 572 MPa true stress. It is a multi-linear elastic-plastic curve in accordance with ASME VIII Div 2 Annex 3-D.3. Yield is 184 MPa. It is a simple vessel with elliptical heads and saddle supports. Two nozzles, close to the heads at each end. The...

Hi all, I seem to have found an unusual situation (from my experience anyway) whereby Elastic-Plastic results are more onerous than Limit-Load and only slightly better than ASME VIII Div 1 hand calcs. I am using ANSYS and have tried many different solver settings, mesh etc. (and have had...