I just called our typical code AI about the issue. The entire piping system includes any flanges. It is also a pressure weld, and I drew it out to explain. Typically what they do is weld another cap on it that has a hole to put the water in the system with a air valve to the side. The unit...
@Btrueblood: "ASME B31 would have you hydro test the flanges"
The way I read this statement means that all flanges are required to be hydro tested. Is this correct?
I recently argued with my QA department about hydro testing Slip-On flange to a pipe. It is my understanding that all welds must be hydro tested, even though the slip-on flanges partially cover the pipe and one of the welds isn't a boundary weld, while the other is a fluid boundary weld. (We...
@XL83NL: I talked with my AI. If vessel has been stamped the nameplate is a code plate and the AI would have looked at it. The AI must witness the nameplate being taken off and the new one put on. You will need to fill out a form in section 5 (PART 2) of the National Board Inspection Code...
Hello,
My company recently bought the books for WRC 537, which is identical to WRC 107, and I am familiarizing myself with the calculations.
My question is during the selection of Nx*T/P and Mx/P, ect...which graphs are appropriate to use? The table listed gives graphs for some standard...
No,
If the vessel is designed to VIII there is no difference at all in the calculations/thickness between building it and building it code stamped (U-Stamped). The difference comes from the inspection/quality procedures to be done to the vessel and the items the Authrozied Inspector needs to...
I actually am acting like the engineering senior. I've layed-out the department plans for the year, have started looking at document control programs and implementations. I'm looking at re-writing the design standards (most because they no longer exist).
However, I've asked for more people...
I deal with VIII and B31.1 a lot.
The way you can look at it is this.
Calculate the required thickness for the pressure boundary of the pipe.
T = (P*OD)/(2(S*E*W+P*Y)) + CA where CA is corrosion allowance
Add in the mill tolerance (12.5%). This can be done to either side.
Tr = T/0.875...
Hello,
I was hired at my company about a year ago as a mechanical/thermal design engineer. Long story short, there was a good engineering department of the company 3 years ago. Then management had the idea of moving the engineering to overseas, which has proven to be a very bad decision. So...
I am looking over a proposal for our company regarding a pressure vessel. The customer is stating that A516 Gr.70 does not need to be Charpy tested with a thickness less than 25mm for a design temperature of -50°C. I look at VIII Fig. UCS-66M and the lowest that A516 Gr.70 goes is to curve B...
My only help with the perforated plate thickness would be ASME VIII ligament patterns. It has the efficiencies for hole spacing, and I would assume you could apply those efficiencies to the plate thickness calculations. However, you might not be able to.
My company makes desuperheaters, and there is a difference only in the way you wish it to be. It is basically saying, all desuperheaters are attemperators, but not all attemperators are desuperheaters. It is just how the individual wishes to classify the product.
It does not sound like a pressure vessel. A pressure vessel as a general meaning is any pressurized container (ie, piping or container) that has an internal/external pressure over 15psi. 15 psi (or generally one atmosphere) is what most technical standards use as a pressure minimum.
My company that works with team has found that PWHT up to about 3 times until the hardness starts to fall off in that area. At that point, you have to re-normalize the material. We mainly deal with making piping parts (desuperheaters) for power plants, which are rolled and welded pieces of 91...
I agree with SnTMan, I would as for a quote of the pipe as you normally do, and then specify on your request for it to have the ID you wish by swage. See who quotes it and who doesn't.