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Dear All, I'm trying to evaluate a method to design rectangular flange "according" to ASME PCC-1 and ASME VIII Div.2 What value should I use for pre-load the bolts in Service Criteria and Global Criteria for Elastic-Plastic Stress Analysis ? I'm trying: W = max(Wo;Wgs) Wb = 1.5W (bolt...

Another concept applied to BFJ is Service Criteria. I suppose If I apply factor on pre-tension I will satisfy the Global and Local Criteria (In cases that bolts do not go over ultimate). But I think that the service criteria may not have a satisfactory (consistent) results, like flange rotation...

Dear All I'm here again with other question about Elastic-Plastic Analysis. How should I apply LRFD concepts to bolt pretension for an analysis of bolted joint? Since I will apply the required factored loads to internal pressure... I think I will apply the same factored loads (for internal...

Take a look at ASME VIII Divison 2 Annex 3.D.

Thank you Victor and TGS4 @TGS4 I was thinking of bi-linear to minimize the computing time. But I will continue with the full curve Best regards

Dear All I am running an elastic-plastic analysis for a pressure vessel according to ASME VIII Div.2 - item 5.2.4 and I pretend to use a bilinear material model. But I am in troubling about the value of the Tangent Modulus that I should use. I plotted the stressxstrain curve of the SA-516 70...

Dear Have you read ASME VIII Div.1 Mandatory Appendix 1 - item 1.7 LARGE OPENINGS IN CYLINDRICAL AND CONICAL SHELLS?

Thanks TGS4

Thank you RaymondN, We are considering all requirements for offshore installation.

Thank you all!!

Dear All I'm engaged in a study about bolted flange joint and I need find the flange rotation. Someone knows how I can find the rotation by an analytical calculation? (book, code, article...) At moment I'm using just FEA. Thanks in advance

Tigny, Thank you! I will check some FPSO regulations

inammanj123 I guess not, since we can not model a tangentinal nozzle attached to head. (I just tried to model, but I didn't get it)

As TGS4 replied, you need FEA. Since the WRC 107/297 does not find the actual stress values for your case.

Thank you for your reply SntMan

I have some doubt beucause in ASME VIII Div. 1 and Div.2 state: item 2 of U-1 in ASME VIII Div. 1 states: "...the following classes of vessels are not included in the scope of this Division.....(-a) those within the scope of other Sections" And in ASME VIII Div. 2 item 1.2.1.2 states: "Rules...

Dear All I have a question about the scope of ASME VIII Div. 1: Is included in ASME VIII Div.1 scope a pressure vessel design for operate in a FPSO (floating production storage and offloading)?

DDellmore, Yes, two separate calculations: 1st: If NR-13 shall be applied to your vessel. Item 13.2.1 b) P (kPa) x V (m³), if this product is greater than 8 (kPa.m³), so NR-13 shall be applied 2nd: What is the potencial risk group of your vessel? to classify the vessel you need found the...

ksbhatt Sorry for confusion. That spreadsheet does not refer to ANSYS calculation above (it was used to other vessel). Please, check with any your ANSYS calculation. And as explained by TGS4, the intermediate bending stress values is just calculated by y=mx+b (My spreadsheet dos not consider...

Hi ksbhatt I calculated acc. formula (5-A.2) and described in 5-A.4.1.2(c). The spread sheet is attached. (you can also see peak calculation in this sheet). http://files.engineering.com/getfile.aspx?folder=18cecd49-8870-4e0c-aa08-92e4253efd5e&file=linearização_modelo_2.xls