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No, it`s not listed as an acceptable material in table UCS-23.

The allowable stress for SA-240 304 at atmospheric temperature is 138 MPa not 206.9 MPa. There are increased low temperature allowables in table ULT-23.

Depending on the amount of torque applied, that would control how far the threads are engaged. I am not sure how you can predict where the pressure actually seals in a tapered pipe thread joint. Depending where the effective seal occurs, would determine the effective minimum wall occurs. For...

For the female thread set your inside diameter to 'D' and for the male thread set your outside diameter to the minor diameter at the small end of the pipe 'Ko'. This creates the least material condition.

Yes it is required. See CSA B51 Part 1, paragraph 5.1.

What design code are you using?

Per UG-44 they are calculated as equivalent size and schedule straight seamless pipe. B16.9 only specifies the thickness at the butt weld end. The profile and crown thickness is up to the manufacturer.

You may also want to review ASME BTH-1: Design of Below-the-Hook Lifting Devices. This will provide you with an appropriate factor of safety and address the possible failure modes in your design.

I am looking at table II-6 example (1) it seems to indicate that the hub height is based on the larger flange size.

Have you read code case 2244? Please be more specific about which part of it you don't understand.

Try doing a search! There are a plethora of threads on this topic. Just to list a few: http://www.eng-tips.com/viewthread.cfm?qid=344256 http://www.eng-tips.com/viewthread.cfm?qid=230734 http://www.eng-tips.com/viewthread.cfm?qid=318004 http://www.eng-tips.com/viewthread.cfm?qid=138163...

Usually plate and frame heat exchangers can be calculated as non-round bolted flat heads per UG-34 and then nozzle calculations to justify the openings. If this particular design cannot be calculated with those rule, you can use the U-2(g) clause which allows alternate methods of analysis such...

It basically comes down to the manufacturer's quality control program. Most pressure vessel shops are certified by ASME and use the U-1A form. ABSA in Alberta issues their own quality control certification which does not permit the manufacturer to use the U-1A form and instead use the AB-25...

You're looking at the von Mises stress while calculating the basic torsional shear. You need to define a radial shear stress plot or you could also look at the first principal stress.

You will have to know in which Canadian province the vessel will be installed. You will have to submit the vessel design to the appropriate provincial regulatory body who will review the design and then issue a CRN number. If it is located in Ontario, then an Ontario P. Eng. stamp is required on...

Under ASME section VIII division 1 the calculations use factor of safety that is based on the minimum of tensile strength/3.5 or yield strength * 2/3. When performing a proof test according to UG-101 the burst pressure is divided by 4. My question is why the difference in safety factors? Is this...

Not anymore, they've removed this in SolidWorks 2012. You only get a callout but it no longer models the weld bead.

You don't have any restraint set in the y direction. Your model is also missing a pressure balancing force at the flange.

Look at your displacement. You should be able to see if the parts are pulling away from each other. Also look at your contact pressure plot. If you have contact pressure between the parts, they are still in contact. No contact pressure means they have separated.

Do you perform a heat treatment or work hardening procedure on the material after it arrives from the mill? These manufacturing processes alter the tensile strength.