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Hi X:83NL, Thanks for the feedback. The problem is the Nitrogen content for S31803 does not match the Nitrogen content for S32205. Basically what I am asking is can I use S32205 inspite of this and if so why? Kind regards

Hi All I am completing pipe design calculations using UNS S31803 (65ksi yield) in an operating temperature range of -4F to 250F. I am trying to account for the shift in Young's modulus and yield strength at the elevated temperatures but need some advice. ASME II Part D table Y-1 gives the...

I think your approach is flawed, because you're not following the typical analysis sequence. I am not posting the entire 294 page design report that shows the whole sequence, I am obviously only posting the specific part I need help with Your approach, as I see it ... 1) sketch the loads...

Hi saplanti, The lug design is not considered here , the sketch is not accurate WRT the lug orientation, that is why I asked the question "When considering the beam, is the way I have added the three stresses together correct (Stress_tot)?" can you answer that question?

Hi JStephan, I dont have any of those codes so I cannot check, thanks though.

Hi rb1957, Figured this was the easiest way to respond, see green text below. Fh will cause a small bending moment on the beam (offset from the NA) I know it will, that is why there is a BM_FH. Is there something wrong with this? I don't like using a -ve sign for the compression bending...

AJoe591 - Fv is the reaction force to the weight, BM due to the weight or BM due to the reaction force is essentially the same thing. So taking the BM due to the weight is all that is needed. why would the direction be opposite?

@3DDave - I left a comment on the video in hopes he would get back to me but emailing him directly seems better, thanks. @rb1957 - thanks for your response @desertfox - Thanks for the info, very helpfull I will update this thread if Dr Yang Cao replies to my email. For now I just going to do...

Hi robyengIT, Thanks for the reply, my main focus is on whether the way I added the bending moments is correct or not. To be honest I would not know how to include shear stress into this example. please feel free to show me how to. Kind regards Mike

Hi, The attached picture shows a scenario where a beam with 2 lifting points is lifted by a crane by a chain with 2 legs. My question is: - When considering the beam, is the way I have added the three stresses together correct (Stress_tot)? Kind regards...

To show you from a different source the question I have: Link at time 0:47:00 he equates the tensile stress to the proof strength Link at time 0:57:00 he works out all the stresses on the threaded member, at time 1:11:15 he equates the VM combination of the stresses to the proof strength Why...

If they are talking about thread bending why do they say "A bending moment could exist in the bolt if there is a gap between the plates (i.e. due to a gasket) or if there are long spacers used in the joint:"? They are calculations that someone else did, I am using them as a method to follow...

Thanks, maybe your follow-up answers to my previous post will help. @desertfox - please give me the formula and the variables you would use to work out the bending stress because I still think there is confusion with the bending stresses we are talking about, I am not talking about the bolt...

Hi desertfox, Thanks for replying. When you say it is the combined stress during tightening, which stresses make up that combination and how are they combined? 2/3 of yield is roughly equal to 75% to 90% of proof strength (which is what I am doing), I think im missing your point with that...

Hi All, Thanks for the feedback @RD1957 - The simpler way is not the more conservative way (unless Im misunderstanding what you are saying) because it does not include stresses that are actually there (ignores bending and shear). @desertfox - The person who did a previous design report...

Thanks again for the feedback @desertfox, yes that is correct majority of the load seen by the threads is pretension. even if I remove all external loads and do von mises using only the pretension the bolt still fails because the bending stress term increases the total (von mises) stress in the...

Thanks for the feedback, I have attached a drawing of what is happening, please let me know if anything is unclear. The below video is of fastener calcs where the axial stress is equated to the allowable yield stress (long video and not necessary to watch as every fastener calc is similar, see...

Hi All, Thank you for the feedback. I am not worried about residual torque in the fastener at all, I am ignoring that aspect. What I still need help with is: 1) For power screws Von Mises is used to combine axial stress, thread bending and thread shear due to rotation. I know that the thread...

Hi RB1957, Thread shear due to rotation is not an issue (as I said I have made it zero in my calcs). Thread shear stress due to the applied load is present as long as there is an applied load, which is the case (note the difference between the blue and purple colours in the pic). Thanks for...

Hi, I am doing pretty standard bolt calculations and noticed a difference between the power screw and regular fastener calcs. The fastener situation I have is bolts holding a pressurized pipe flange together (ie. external load is in the same direction as the preload (or rather opposite...