I meant "stress it to 1050°F", which is half the melting point (according to this article - http://www.nationalboard.org/Index.aspx?pageID=181) of A-312-321H, at which I do not need to be concerned about creep.
Thanks all for your great replies. My client just communicated that they have carried out this design before and although they prefer using Incoloy 800 HT, they have designed plants using A312-321H that are still standing after 30 years. Perhaps the actual operating temperature is way lower...
XL83NL is correct, I was referring to pipe stress analysis.
How would the refractory improve the situation TGS4?
The piping is NPS-4 Sch 40 by the way and is actually exhaust piping from an activator through a HEPA filter and to atmosphere.
If it is a time relates issue, then perhaps they...
Thanks all for you input!
I have just been informed that the max pressure (rupture disk burst pressure) is 30" w.c., so pressure will not be an issue, which works in our favor.
The operating conditions are close to the design: Max 1700°F and normal 1600°F. I can use B31.3 up to 1500 °F but...
I am working on a project that involves a short section of piping that is at 1,800°F and 5 psig design conditions. I have been requested to provide the stress analysis. They want the design to B31.3, even though it is not considered pressure pipe. The conundrum is what allowable stresses to use...
The design pressure is 15 psig (vacuum)
The piping is 316L, 42"dia, 3/8" thick and 36" long (connects two vessels)
I have calculated the max external pressure to be 92 psi per ASME Sec VIII DIV I
The forces and moments are yet to be calculated, but I just want to make sure I am on the right track!
TGS4: If I use Pr/2t to convert external pressure to axial force, I get 4 lbs of axial force. I calculated a max. of 92 psig external pressure using Section VIII DIV I and somehow I cannot believe that the external pressure (1 bar) translates to this minimal effect on the axial force. If I...
Thank you all!
TGS4: ASME Section VIII, Division 1, UG-28 through UG-30 only deals with external pressure. How do you convert max. allowable external pressure to compressive force in order to add up all the components (i.e. pure axial force, axial force due to bending moment and axial force...
Does anyone know if there is some type of rough calculations that we can use to verify whether a larger pipe (D/t>100) will buckle if we have a compressive load, bending and external pressure?
Or do we need to carryout FEA on this?
Thanks
FDS2008
I'm going to throw another wrench into the original question, as I spoke to a few more engineers regarding the friciotn question and I am still not convinced about the doubling up of the friction force. I realize my last thread indicated that I was, but now I am not so sure.
The new example is...
I have to apologize for not getting back to this post as I was not set up for e-mail notification and I got busy believing that no one answered the post. Excuse my unfamiliarity with the process. It definitely generated lots of curiosity. I thank you all for your input.
I have acttached a...
I have a physics question that I can't seem to answer using textbooks.
I have a vertical pipe that will be clamped to some structural steel. We are trying to calculate the forces required to restraint the pipe based on friction. The clamp will pull the pipe towards the structural base and...
KBS - Yes I read this post but this was the other extreme, whether slope was required at all.
Unclesyd - I posted the question under Boiler and Pressure Vessels by mistake and am new at this, so i just copied it to the piping. Will keep this in mind.
It appears that there is no restriction to...
