Recent content by Minamtungekar

Hi all, I am designing a scraper trap in which I have two shell courses ( pipes ) on either side of eccentric reducer. I am to design the pipes as per ASME code B31.8, which I did. But how am I supposed to calculate the required thickness for the eccentric reduced ? Also the thickness of both...

@MrPDes Thank you. that was very helpful. I believe understanding the principal behind how the formulas are derived gives one a better understanding of the effects of different parameters.

@jte... like you said .. it's a good practise to close the loop which I did. I guess I should have done it earlier. @aidaa2011 .. dear sir, what I believe is that the material is first selected by the process department depending on the service. We have to check the mechanical adequacy of the...

I got the answer. I had given a joint efficiency of 0.85 for the shell welding. That's the reason it showed a lower allowable stress for the shell than the head. For which I had a joint efficiency of 1

Yup got it now ! Thank you Still why 0.78 only is a mystery. Will let you guys know if I get to know the reason for 0.78

Regarding the factor of 0.78, I do not know about it. But as said by MrPDes.. 0.78 is used to compensate for not taking into account bending stresses? How is tha possible ?? If bending stresses are not considered, then should the factor be more that 1 ?

This is what I have found out.. bending stresses due to concentrated external loads, are of high intensity only in close proximity to the area where the load is applied. The attenuation or the decay length, the distance from the load where the stresses are significantly reduced, is limited and...

@TSG4,TonBarsh and JStephen Thank you so much for the replies. I did not get the derivation but by TomBarsh's answer I got an idea of the use of Rt. I am still searching for a copy of WRC 529.

Hi all, I usually tend to understand the principle behind the calculations done by software which brings me back to the code time and again. So while understanding nozzle area calculations in para 4.5 of division 2, I came across formula 4.5.119 and 4.5.120 in which there is an equation showing...

http://www.eng-tips.com/viewthread.cfm?qid=418063 Also please try and reply to the above post

Thank you so much for the input guys.. Pdiculous... Is there an option to use code case 2695 in pv elite?

I am designing a pressure vessel of 1400 diameter and in the output results, internal calculations tab, the allowable stress for the shell is less than that for the ellipsoidal heads. How is that possible? Please help

After studying some on this topic I found that when UG-37 is selected in pv elite as the design basis, the required area formula is as per UG-37(c) - area required under internal pressure, and when 1-10 is selected as the design basis then UG-37(d) formula is selected in the calculations, ie...

Now i have read the related post but it's still unclear to me. My question is simple.. Can I use 1-10 independently in place of UG-37? The reason for me asking this is.. When I read UG-36, it says that when a certain opening diameter limit is exceeded, then you go for the rules of 1-7 in...

Dear all, I have designed an exchanger according to division 2, regarding hydro test pressure, the code writes.. "when a hydrostatic test is performed, the hydrostatic test pressure of a completed vessel shall not exceed that value which results in the following equivalent stress limits: General...