Does anyone have access to A263 spec published in 1950's? I am dealing with some vessels built in 1958. The shell plates were lined or cladded with 405SS per A263 Gr 0. Based on some details on drawing, I think the the liners were attached to the base metal by spot welding.
This is a follow-up question on thread 794-103201. Dennis Moss's design manual (3rd edition) gave the force in strut or tailing beams, as well as bending moment coefficients. I can totally follow up one point, two points pick or parallel beams. But those beam frames (3-point or four-point) lost...
When we design the lifting lugs, we usually have to calculate the shear stress in the fillet weld caused by twisting load. Pressure vessel design handbook by Bednar recommends using Sshear = TJ/c, where J is the polar moment of inertia. I believe this is the method that everybody is using...
I would like to know how pipe bend (carbon steel material) is handled in Section VIII, Div.1:
1. Is there any requirement on minimum radius?
2. How to calculate minimum required thickness?
3. How to handle the thinning out after bending?
Does ASME Section VIII, Div.2 allow the use of bored bar stock to produce the main body (shell) of a pressure vessel?
I know with Div.1, you can do it with some code cases.
In sketch (l), y looks like the offset between OD of head and OD of shell at tangent line. If a hemi head has the same OD as shell, then y equals 0. Does that mean tapered length l can be 0 (no taper)? In reality, at the weld joint, there is going to be big offset there.
We have a weld overlayed carbon steel vessel. Is it acceptable to weld the tray support rings directly to the weld overlay surface if the calculated stress at weld joint is below the allowable stress of overylay material (304 stainless)? Thanks.
