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Sandip, Can you explain to me why you used Simpsons Rule to Calculate The Stress Tensors please? Thanks

Hi metengr Could it be possible though that certain Authorized ASME Inspectors would approve the use of bar with OD greater the 8"? Thanks

I see your point David, I would assume that the values in the mechanical properties table are valid up to 8" bar and the values above that may be lower than stated and would have to be accepted with a concession. Personally I would still want the material over 8" to meet the 50% ROA, and...

Hi DavidC247 Although Code-Case 2156-1 states that the reduction-of-area shall not be less than 30% It also states afterwards 'For those materials for which the material specification requires a reduction-of-area value greater than 30%, the higher value must be met'

You could look at 5.6.1.6 of BS EN 14359:2006 That refers to Tension & Flaring Stress In A Threaded Accumulator Body Hope that is of help

I wouldn't be comfortable with doing it, the stamps will act as stress risers whether they are of the low stress die type or not Increasing stress concentrations is going to have a negative effect on fatigue life. But as metengr says, your AI is the only person who could deem it acceptable or...

Hello, Just wanted to check my understanding of NACE MR0175 correctly. Am I right in saying NACE MR0175 is for materials to be used in sour environments that make the material susceptible to suplhide stress corrosion cracking? Therefore, considering 17-4PH Precipitation Hardened Stainless...

TGS4 Thanks for your reply. I am thinking about the FEA in support of a ASME VIII Div. 1 vessel (over 3000 PSI). So all of the wall thicknesses, end cap lengths and thread lengths are already calculated as per Div. 1. When thinking about the supporting FEA I concluded that the suitability of...

Firstly I'd like to thank all for their input, TGS4 Thanks for pointing out my mistake, I did mean Internal Pressure and I have subsequently changed the title EdStainless & CoryPad The cylinders I'm interested in are all specifically metric screw threads, to investigate this further would you...

Hello, I've got a question as to how the threads would fail when considering a cylinder with threaded end caps when subjected to internal pressure (see top drawing on attached pdf) Would they fail as the second drawing, completely shearing the internal threads of the cylinder (shaded in black)...

Hi Soave, I'm a little confused by the values of L at nodes 1-4. The nodes should be lined up sequentially along the stress classification line, therefore the value of L should increase in from node 0 up until node 48(just like that seen between node 5 and 48). Between node 1-4 your value of...

Hello IRstuff, Maybe I wasn't clear enough... I wasn't asking for any material referring solely to metric threads, More of a way of trying to explain the type and kind of analysis that I am interested in, Basically I am looking for any FEA analysis information regarding the failure of...

Hello all, Just wondering if anyone had any experience of FEA of metric screw threads. For example 2 engaged threads M50 x 3 Pitch with a force applied to one end. Looking into failure due the yielding. Could anyone point me in the direction of any information online as my current searches...

Hi MH500, Unfortunately I cannot think of a suitable alternative to a Rod seal but hopefully another on this forum will... My last suggestion would be to consider the seal material if you haven't already? what was the material of the rod seal you have a good experience with? Maybe consider a...

Have you considered the use of a rod seal? http://hallite.com/products/rod-seals/

Is your shaft essentially a piston? You could have a look at profile seals as an alternative to 'O' Rings. For both 'O' Rings & Profile Seals speak to a few different suppliers as many do manufacture low friction back up rings which for use in low pressure situations like you describe.

TGS4, are you saying the following would be my six stress tensors at end i of my SCL? Snm+Snb, Stm, Shm+Shb, Tntm, Tnhm+Tnhb, Thtm where n= Normal t= Tangential h= Hoop M= Membrane b= Bending

Thanks for your help Prex, Once I have calculated Smx, Syx, Szx Etc... I use these as stress tensors to calculate the membrane stress? I've got a litte confused because I found the following online that seems slightly different to the equation you stated before (Smx=(ΣSx-(Sx[0]+Sx[36])/2)/36)...

Thanks All For Your Input, Advice & Help. Prex Are you saying that dx would be 0.5mm at each node? and not a running addition at each node (0.5, 1.0, 1.5 etc...) as it currently is?

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