ASME PV Flange thickness.

[lcatg]

Hi,
I have to validate thickness of flange as per asme.The flange design is as in fig attached.
I considered that the flange comes under 'category 3 class 3(loose type with no hub)' type flange.And first assumed thickeness and proceed with calculations as per appendix Y-6.3 and found no of bolts required. Now to prove that stresses within allwble limit as per rules in app Y-7 need to find radial stresses. But since its no hub type,

1.is it right to consider factor FL as 1. (its reqd to find rad stress)
2.is it right to consider thickness of hub g₀= zero.
3.In ASME are there any rules to design O Ring size. Please tell which chapter to refer.
4.Please suggest any textbooks,study material with enough solved example problems for ASME Pressure vessel.

Thanks.

 

[SnTMan]

lingeshgdvg, not very familar w/ Apx Y, but...
1) FL is found from Fig 2-7.4, based on flange geometry
2) Yes, go, g1, h are taken to be zero in loose type flanges w/o hub
3) Aside from Y-1(b), no, designers' decision

Regards,

Mike

The problem with sloppy work is that the supply FAR EXCEEDS the demand

 

[lcatg]

Hi Mike,

Thanks.. Yes as u said,FL Value is taken from graph and it it depends on factors h and g1/g0.So if those values are zero,what will be FL? bcos in graph least value of g1/g0 is 1 and there's no h=0

Also is that consideration CAT 3 CLASS 3 FLANGE is correct? If its correct,factors C3,C4 and M_SI becomes zero and hence the radial stress in Flange also zero. But practically i felt in PV's circumferential(radial stress) may not be zero.
Any opinion on that?

Thanks..

 

[SnTMan]

lingeshgdvg, I am not familar enough w/ Apx Y to fully answer your question, I'm afraid.

However, in Apx 2, for loose flange w/o hub, radial stress is defined as zero, therefore FL is of no interest. You might confirm whether or not this is the case in Apx Y.

Perhaps another contributor can answer your questions, my apologies.

Regards,

Mike

The problem with sloppy work is that the supply FAR EXCEEDS the demand