A pressure vessel is designed, manufactured and certified in accordance with ASME Section VIII, Division 1. This pressure vessel contains a forged proprietary bolting pad that is welded into the pressure boundary of the vessel. The proprietary bolting pad has a gage bolted to it that is designed...
The shell has a long seam in it. I work for a manufacturer that mass produces vessels and I was debating on whether or not there was any benefit to applying the rules of UW-12(d) / UW-11(a)(5)(b) to use an efficiency of E=1.0. I was under the impression that it was required for each seam as well...
My apologies. The head to shell joint is per Figure UW-13.1 sketch (i). The industry name for that type of head is semi-elliptical with a joggled edge.
I tend to agree with you on your statement that the spot cannot be used to satisfy other spot requirements for the rest of the vessel. However...
I have the following design scenario:
Two seamless Type No. 2 joggled heads with one plate offset being welded to a rolled cylindrical shell that has a long seam.
Per UW-12(d), thickness calculations of seamless heads can use a value of E=1.0 when Spot RT per UW-11(a)(5)(b) is met and E=0.85...
Good afternoon,
I am currently completing a design to ASME Section VIII, Division 1 2013 Edition. The vessel is 16" OD, 0.171" thick, 390 psi, 135F and service is propane. Our customer requires a custom fitting with female straight threads machined into the center for a temperature sensor. The...
Corrosion allowance is 0.
The argument made to me was that once your thickness is below the pipe undertolerance, the pipe is no longer acceptable to the material specification. Is this valid?
Thank you,
Ryan
I am currently designing a Category H fitting for use inside of Canada to CSA B51 and ASME Sec VIII, Division 1. The fitting consists of 1/2" Sch 10S pipe, SA-312 TP316L, that is both bent and coiled. The pressure is 300 psi and temperature is 350°F. The required thickness is less than the...
