Hallo guys,
i observed that a smaller expanded length leads to an increased tubesheet thickness.
This is not fully plausible to me...
Now my question is where do i find this in UHX 12 of ASME VIII division 1
Im looking for that equation but i couldnd find something in this chapter
Can...
Hallo,
can anyone explain me how the 75 ksi max allowable bolt stress been calculated or how it is derived?
I do know the 172 allowable form ASME II Part D but dont understand the 75 ksi in the table
Thank you BR Stefan
Hallo guys,
i do have a question i have a flange calculation where i do exceed the limit for g1
i do have g1>5xg0 therefore the calculation uses 5xg0 as a maximum value in the calculation.
But i cannot find this in the ASME Division 1 Appendix 2 Chapter.
Can anyone help me where i do find...
just use the mises calculation to recalculate equivalent stress from tau and then use a safety factor of 1,5
so allowable stress = Yield /(sqrt(3)*1,5) ≥ tau calculated
thats how i would do....
Maybe instead of 1,5 take 2 but it also can then be overconservative...
Hallo,
thank you for the post.
But:
B31.3 Requires a factor of 1,5!
so
Pt = 1,5 x Pd x ratio of St/Sd while St and Sd is allowable at test temperature and design temperature
that is higher compared to other standarts
AD2000 Requires the following:
1,25 factor is from AD2000
pT=max (...
As far as i know the Kellog formula is very conservative so you will like have twice the required wallthickness and nobody want to use / buy this part.... Or am i wrong?
Ok thank you,
but whenn i consider a P355NH and calculate B31.3 test pressure with 1,5 times design pressure times the ratio of the allowable stresses i come to very high values for test pressure
But why then is in B31.3 the test pressure is calculated with the factor of 1,5 and the ratio of...
its for the analytical calculation and be code compliance. I just heard that 90 % is common praxis but i didnt found a source in the Code.
Test Pressure is beeing verified by analytical code calculation for all pressure containing components like branches etc.
We use 90 % because of common...
Hallo guys,
i was asked why i do limit the allowable stress while test pressure to 90 % of yield stress at test temperature.
Now i know that it is common praxis to use 90 % as additional safety factor. But is there a clause in the Norm anywhere so i can add this link?
I cant find this 90 %...
Hallo guys,
i need to perform a calculation to show what is the maximum allowable test pressure without exceeding material minimum yield strength.
According ASME B31.3 How should i perform this.
eventuelle refomring an equation?
Thanks lg Stefan
what diameter of the pipe you have @ 20 bar test pressure and what material ?
Why not verify the hydraulic condition per ASME VIII Div 1 UG-27?
Can do an analytical UG-27 Stress Report in Mathcad and verify that test condition is OK.
Also Excel is OK with 2D Formula Editor for Official...
I do not understand why corrosion allowance should not be considered since this has an influence on the loads.
(Bigger inner diameter due to corrosion allowance leads to bigger required wallthickness due to bigger loaded pressure)
Normaly force should be calculated with nominal and area for...
Ok thank you.
But using corroded thickness is a real szenario because when plant starts up at their final lifetime when inner diameter is bigger due to corrosion I also need to check if stresses are ok.
I use the following:
Thermal force using nominal (without fabric and without...
Hallo,
i have a understanding problem and i hope you guys can help me.
While calculating the maximum occuring displacement Stress (analytical).
according code the Thermal Force is calculated in uncorroded condition using nominal wallthicknesses.
In Detail:
The Area for stresscalculation is...
