If I understood correctly your case: the test is always the final best approach and it confirms the design.
If you are talking of a typical flange joint (see the drawings in the standards):
- EN 13445-3 ch 11 it is just the same as ASME VIII-1 apx 2, and many other different design codes, all...
In the scope of TEMA is in RCB-1.11 the design pressure is up to 207 bar, not sure what you mean by high pressure, but I really think you are out of scope if it is above. Generally ASME B16.5 flange (and so also bling flanges, covers) are rated at ambient temperature for maximum around 400 bar...
13CrMo4-5 1.7335 equivalent A387 Gr.12 (UNS K11757) which is listed under ASME BPVC VIII Div 1 table UCS-23 and is P.No 4 (for ASME BPVC IX Table QW/QB-422 or also ISO/TR 20173)
http://www.steelnumber.com/en/steel_composition_eu.php?name_id=445&msclkid=23af22fad05511ec884ab74052c8644c
1) it...
It is:
ISO 15614-1 general
ISO 15614-8 specifally for Tube-To-TubeSheet joint.
The ranges (on materials, diameters, thickness) are quite different , many concepts are different (in 15614-1 there is the deposited thickness for process 's' which is important, while in the 15614-8 is simpler...
Which codes ?
From what said it seems you are basing the analysis on elastic limit theory, because you consider the yielding stress as the limit factor.
Also you said that at 1.5barg there is yielding in the materials, but that does not mean that, by reducing the pressure of 1.5 time, you...
not so common, for PED category III and IV it is required EN 10204 type 3.1 for pressure parts, which is the maximum level that can be required for PED.
A certificate type 3.1 for steel usually comprises mechanical tensile tests and chemical analysis (but to know which tests are required you...
In my point of view from what you said, the QC engineer is asking something unecessary, or maybe, his justification for NDT request is too weak. But he could find many other more important excuses (than the full penetration) to ask for such tests... in any case I would not perform any additional...
it is all useless pieces of paper that some burocrats want in order to keep themselves sure that in the worst case, whenever anything happen wrong, they have no responsibilities for their wrongdoing and their ignorance of everything, but they own a huge amount stock of paper, for the purpose of...
1) I was wrong, you right.
2) check the tab. 2-5.2 and definitions in 2-3:
N and w is the width according to both the definition and the scheme, while b is called the seating width and it is generally half of the real width.
You are right if you consider only the formula (2) in calculating...
Any code is different. ASME VIII div. 1 Apx. 2 is based on Taylor Forge method and it was used for long time and has given good results, but it is not good to calculate actual bolt stress and preload or torque for that matter follow PCC. Taylor Forge method shall be used for the joint design...
the material is suitable according to EN 10269 up to 500°C.
For the flange 2"1500# and 3"1500# the bolt sizes are indicated in ASME B16.5. The Pressure-Temperature rating depends on the material of the flange (check tables 2-... in ASME B16.5), but with class 1500# at 415°C it is for sure more...
Fluoro polymer like PTFE (and also FKM, NBR, etc) is an elastomer according to table 2-5.1, thus only the toughness of the material is of importance: if it is below 75 Shore A, m=0.5 and y=0; otherwise m=1 and y=1.4MPa; this at least in case you are talking about a flat circular gasket of...
You should not do these kind of comparisons and calculations in my opinion. The allowable stress values (indicated by capital letter 'S') for bolting, reported in BPVC II part D tab. 3, shall be used only as it is prescribed by the code, for example in ASME VIII div. 1 apx. 2 (which is according...
I do not know what "WCC" stands for, but in no case; there are no such materials where you can used #600 flange at any temperature for 125bar according to ASME B16.5.
Maybe, the only way is to try to use some different calculation methods than the normal Taylor Forge (ASME VIII Div 1 Apx 2, or...
it is ITERATIVE.
Consider that for a bolter flat cover you have 2 kind of thickness (fig 10.5-1):
- thickness (e)
- flanged extension thickness (e1) which could be lower (see 10.5.1.2 and fig 10.5-1, 2 to 4) for a raised face or a grooved face.
The word "analysis" (referred to the thickness...
I have seen the sketch, and I do not think that the gasket metallic rib contact surface and the gasket spiral wound plates can be considered as a uniform material. Not to say about the thickness: even in the sketch the thickness of the partition rib of the gasket and that of the spiral wound...
According to the Taylor-Forge method both the constant m and y are independent of the pressure ! m and y are only a function of the type and material of the gasket and are tabled in tab. 2-5.1 of ASME BPVC VIII-1 or EN 13445-3 annex H.
y value is for the seating / assembly / bolting condition...
In EN 13445-3 tab. 6-1 the 'f_test' nominal design stress for test or nominal test stress (in ASME BPVC it is called 'S' maximum allowable stress) to be considered for the test condition is roughly 1/1.05=95% of the yield strength at ambient (or test) temperature (except for bolts, see 11.4.3.1...
@r6155
You can find the definition in words in the vocabulary.
For ISO 25901-1
- (2007 2.55, 2016 2.1.6.3) butt weld (groove weld): weld other than a fillet weld (2.131) made in a groove or in a square preparation
- (2007 2.54, 2016 2.1.4.5) butt joint : type of joint where the parts lie in...
