Hi,
I am dealing with cylindrical vessels (inner diameter=d) with flat unstayed covers at both ends. These covers have central openings (finished diameter=dop). Following UG-39 (b), I already found no reinforcement was needed in cases dop<=0.5 d; but, for the same vessel and cover thicknesses...
Thank you very much, trottiey and TJOrlowski, the situation is clear for me now. Only one last doubt remains: how to deal with specifications such as "Smls. & wld. pipe SA-312 TP316L S31603" on ASME II Ed. 2004, Table 1A, p. 66-68? This case shows the highest stress values among all SA-312...
Hi trottiey, thanks again!
Yes, you got it totally right. The economic reason behind this concern is that for my quite short-d, low-pressure vessels, it is much cheaper to take a thicker plate than adding and welding reinforcement pads. Now I understand better the situation and of course it...
Hi, trottiey, thanks for your fast reply & link!
Yet, I do not fully understand your second paragraph: when talking about welded pipe, I always mean "bought as such" to my raw material supplier, not fabricated by me from plates. I reviewed my 2004 Ed. of ASME VIII Div.1 UW-12(e) and it simply...
Hi,
I usually use pipe (both seamless or longitudinally welded) in the design of pressure vessels, and I do not fully understand UW-12(d) & (e) statements for E value: for the more conservative case of no RT, should I always use E = 0,85 for circumferential stress? Does not it collide with...
Hi,
I am dealing with circular flat unstayed covers that include a female-threaded hole and I am a bit puzzled about application of UG-39(b)(1) & UG-37 rules to check without reinforcemente element added when no welded nozzle is expected: for E1=1 and F=1, these paragraphs always lead to the...
