I have similar concerns related to potential future failure points. In addition to shear stress on the studs, I asked if there were any concerns to potential damage to the plate material while torqueing the studs specifically the area of the plate under direct compression where the plate could...
As part of a project in the refining industry, this project recently received from the supplier a seal gas & conditioning auxiliary unit to a centrifugal compressor. Design conditions are 1175 psig @ 200F. Our engineering practices of such auxiliary units to rotating equipment require all...
I have been approached by my process engineer to consider lowering an existing S&T floating head exchanger's shell-side inlet temperature by nearly 250F. Tubeside conditions would stay the same. With this proposed change, the temperature differential between the shell-side and the tube-side...
I guess one question I would ask... is this driven because of metallurgy or is this driven due to process (i.e., aggressive environmental service)?
Do agree what Steve stated concerning NDE prior to and after PWHT. The additional costs to perform NDE could be a plus if a deficiency is found...
Just to clarify, the code equations for B31 are based on two failure theories. As mentioned above, the TRESCA theory (i.e., maximum shear stress failure theory) is one theory used when the maximum shear stress exceeds one-half of the yield strength of the material at temperature, failure will...
There is nothing in the code that prevents a 'spec-break' between two different materials (in your case SS to CS). Sounds like a 316SS spiral wound graphoil gasket could be used at the joint between the flange and valve. Consult with a vendor such as a Garlock representative to discuss your...
