Hi folks, im new here and im also new at using CREO Simulate, havent really gotten the grabs of this p-element stuff yet.
To the point: I'm performing a static analysis of a lifting lug which is affected by a force acting on a surface inside a hole, this surface models the contact surface between the hole and the lifting tool. The lifting lug is constrained by bolts in holes and i've also constrained it to only move planar for a specified surface (see picture i attached).
I set the solver to MPA where i seartch for convergence of strain energy, von mises and maximal principal stress for the whole model. I set a convergence criteria to 7%.
The current mesh setup allows the solver to find a solution within the specified convergence criteria.. BUT in the "Run status report", in the last pass, it also stated that there are X-number of elements not converged..
The result give me both von mises and max principal stresses that are WAY above the value it should be. The area of interest is the bend and the hole section, stresses at the bolt holes are not of interest. The model material is S55, ive set modulus to 190 000 MPa and poisson to 0.3.
Does anyone have a any tip or tricks to get more accurate stresses? I've also attached the .prt file so that you can try the simulation yourself.
Cheers
Almost there 
ty for taking the time to help me
The surface should be more like this
the angle from the middle of the surface to the midplane is 45 degree. The area is something i got from the lifting tool.
Also had problem running the simulation on that part you sent. It gave large deformaton issue among some.
Hi Steven,
I see, the way to achieve "real" convergence in PTC CREO simulate is quite hard. I haven't really learnt how to see if i get convergence or not, compared to H-elements.
I got some files from Paul which were very good but in his modified model the force from the lifting tool is modelled as a bearing force.. which im not really sure if thats true.. The lifting tool is a "hook" that will have a contact surface in the inner hole of ~84 mm^2. I've attached a part file which ive tried to model this more correctly but i get REALLY REALLY high stresses in the structure... the thickness and geometry of the plate should be able to handle this load according to the company.. the compoents of the force is setup to give a resultant in the direction of the sling. Please see the model
Sorry Paul but i/the company doesnt have the Advanced simulate license.
I've previously modelled using the fasterner feature instead, that i can use with the standard simulate license. I cant open that file sorry 😕
This is the type of lifting tool they use.
And this is how i've drawn the model for my analytical solutions.
The angle "phi" is what i call sling-angle. And alpha is controlled by how the lifting lug is positioned on the structure and how the dimensions of the structure is. Lets say alpha is 71 degree, which is the worst case.
Okay I was thinking more about that coordinate system you introduced, ROTATION. In the 2nd picture i attached, with the definition of force and angles. I could probably use the ROTATION coordinate system, but to "simplify" it more, i could rotate one of the axis to the alpha angle so that i only need to calculate two force components from the sling force. A vertical force and horisontal force.. I dont know if you've done these kind of computations before but do you think its a important factor on where the lifting tool touches the hole ? Because depending on the sling angle phi the tool will be in contact with higher or lower part of the hole. ?
Regards Robin
