Recent content by Chrissy123

Thanks all - I have found the solution - Darcy only applies to fully developed flow so I increased my duct size considerably and now I'm getting good agreement with analytical values - thanks Dave - I've effectively changed it to look at only fully developed flow -

Hello - can anybody help me on this please ? I am modelling a simple cylinder with laminar flow in ABAQUS CFD. I am using Reynolds number of 25 to simulate laminar flow with an inlet velocity of 1m/s using a fluid with density of 1 and kinematic viscosity of 0.012. I have worked out the length...

Hello - can anybody help me on this please ? I am modelling a simple cylinder with laminar flow in ABAQUS CFD. I am using Reynolds number of 25 to simulate laminar flow with an inlet velocity of 1m/s using a fluid with density of 1 and kinematic viscosity of 0.012. I have worked out the length...

Thank you yes. I will be running comparisons also against other head types.

Hi Patrick thanks - Yes I know that C has other factors that need to be considered when calculating it. I also know that E isn't always 1 and further consideration needs to be given to that - so yes I will be refining the calculations based upon further work/investigations etc. I'm also tying...

According to ASME there is a calculation for flat head thickness (t) with the equation shown below. Is this applicable regardless of the ratio of head thickness to cylinder thickness ? I have a pressure vessel where the shell thickness of the cylinder is 100mm and the head thickness is 10mm...

Thank you all for your answers :)

Hi. Sorry just to confirm. I'm using a metal with yield strength of 207Mpa, perfectly plastic. So once I get to yield strength the yield strength doesn't change does it ? Effectively once I get to the yield strength then that's also just about the UTS as because perfectly plastic it will break ...

If a material if perfectly plastic then does this mean that the UTS is effectively the same as the yield stress ? Thanks

thank You :)

Hi - I am modelling a cylindrical pressure vessel. I have carried out a mesh convergence study for smaller pressure loads so I'm happy with that. The material is elastic perfectly plastic. what I need to do now is apply internal pressure and find out what pressure would cause the vessel to...

Hi all - I'm going back to basics with my pressure vessel analysis and starting with ASME to calculate the acceptable operating pressure of a pressure vessel. My model is simple - flat head cylindrical. Length of cylinder 500mm, inside radius 254mm, cylinder shell thickness 100mm, flat head...

Hi to DriveMeNuts - thanks for that information - that is really helpful and yes I don't know a lot you are correct :) I am a trainee and I am trying to learn and I don't have a mentor and I'm doing this to try to learn and just to assure (@TGS4) I will not be building an actual pressure...

Aah - I see so if I follow the approach ASME Section viii Division 2 standard for Pressure vessels, the limit for the hoop stress (away from any discontinuities) is that the material should not experience yielding. So this would be my criterion, when the first element reaches yield point the...

Thanks - I will take a look at what you have suggested. I have assumed that I can apply pressure to the model and then analyse the stresses and the plastic yielding, the 5% results tie in with the Yield stress for the material so I thought this was correct; I'm obviously making a big mistake here -