My suggestion would be to only do one iteration of thickness increasing. Set the MAWP to be equal to either the design pressure OR equal to the MAWP prior to increasing the shell thicknesses. This should resolve your problem. We have taken this approach several times with Div. 1 vessels. I don't...
I don't know of anyway to do that but your questions is better suited for the COADE, Inc.: CAESAR II group since PV Elite is made by the same company as CEASAR.
Good Luck!
I have a shop fabricated API 650 tank that must be "food grade" quality. The nozzles specified by our customer are 150# flanges including both manways. When I asked my customer if we could provide API 650 manways in lieu of 150#, they said we could as long as the manways were food grade API 650...
dhengr,
I appreciate the response. I am quite familiar with how to go about designing support saddles and my questions is only regarding the design of the base plate.
I disagree that if the vessel is tied down above each saddle that the saddle will see lateral and long. loads. These loads...
I am currently designing shipping saddles and was wondering if there were circumstances where the baseplate thickness would not need to be calculated with the shipping loadings. The vessel will be tied down directly over each saddle such that the longitudinal and lateral loads will be translated...
The test pressure is still per UG-99(b). See footnote 36.
UG-99(c) is based on the Maximum Allowable Pressure (MAP) which is calculated from the new and cold condition. The equation for UG-99(c) is PT = 1.3 x MAP.
Keep in mind that if your customer requires a pressure test per UG-99(c), you...
SteamGap,
I believe PV Elite is considering E to be the outside rib to outside rib distance. To work around this, you can change dimension E to be equal to the base plate length if your saddle will be fully supported on the foundation. There should be an input "Dimension E at Base (optional)"...
VTechie79,
ASME Section VIII, Div. 1 does not prohibit the use of a torispherical head with knuckle radius to diameter ratios (r/D) of less than 6%. It simply states that the thickness for a torispherical head that meets that requirement can be determined by formula (2) of UG-32. See excerpt...
I appreciate the replies!
I do not completely agree that FEA is necessarily required but I agree that it would go to a U-2(g) analysis.
The only place I know where to look for a mitered elbow design is B31.3 but I do not see how to go about a mitered elbow with differing IDs at each end...
I am currently designing the bottom of a Reactor that has a "round to round" transition (see attached picture). I was looking at designing it as an eccentric conical transition with an equivalent small end diameter but I am not sure this is the correct approach. Does anyone have any experience...
Jano6924,
The material just needs to be 1 of the following 3 conditions:
1. Fine Grain Practice and Normalized
2. Normalized and Tempered
3. Liquid Quenched and Tempered
If you go with either option 2 or 3, the material does not have to be fine grain practice.
Hope that helps!
Thanks for the correction TomBarsh. My mistake, you must use UG-37 for heads, not 1-7. Hopefully the title of 1-7 was enough of a heads up of my mistake... "1-7 Large Openings in Cylindrical and Conical Shells."
VesselMan,
See UG-36(b)(1): "... The rules in UG-36 through UG-43 apply to openings not exceeding the following: for vessels 60 in. (1 500 mm) inside diameter and less, one-half the vessel diameter, but not to exceed 20 in... [highlight #FCE94F]For openings exceeding these limits, supplemental...
