Search results for query: *

Apologies, my initial query was somewhat rushed being late on a Friday. My query is whether we run a risk of yielding the tubesheet if the stress limit is set to 2 * 90% of Sy? My understanding is that this is a primary bending stress and therefore I would typically limit this stress to 90% of...

We are currently fabricating replacement u-tube bundles. The bundles are Figure UHX-12.1 Configuration D with extended flange, the gaskets either side of the tubesheet are the same configuration and as such no bolt load gets transferred into the tubesheet during normal operation. The intent...

WRC-538 is based on ASME VIII Division 1 Appendix 2 with some small differences that are detailed therein. Simplistically it replaces the ASME material allowable stress with yield (or multiples there of depending on type of stress) and calculates max assembly load using Appendix 2 methods. It's...

ASME PCC-1 Appendix O gives a joint component approach to assessing the assembly stud stress for a flanged joint. It states the minimum permissible bolt stress must be selected by the user and then goes on to say its typically in the range of 20-40% of ambient bolt yield stress. My employer has...

ASME PCC-1 Appendix O provides guidance for the determination of an appropriate assembly bolt stress for flanged joints. However, it doesn't explicitly cover blind flanges. For weld neck flanges bolted to a blind flange (including heat exchanger cover flanges), a basic summary of how I've been...

@doct9960 With regards to calculating rotation of flange, the rigidity factor formula in ASME VIII Table 2-14 can be modified to do just this. By simply removing the K factor the result will be rotation in degrees. So in essence, ASME VIII rigidity limits rotation on integral flanges to 0.3...

Thanks for the response TGS4, appreciate it. So when the code refers to Other Than Ring Joints (ie in Appendix B-1 & B-2) am I correct in assuming this refers to tongue-in-groove and other types? For info I've always mandated Appendix 2 calcs for any change in standard flange gasket dimension...

Firstly, I understand there has been a number of queries submitted previously on similar topics, however, I couldn't find the ultimate answer I was looking for plus I also wanted to add some further code clauses, etc to the question to ensure no ambiguity. ASME VIII-1 (Clauses UG-11 & UG-44)...

The scope of ASTM A333/A333M specifically states "Some product sizes may not be available under this specification because heavier wall thicknesses have an adverse effect on impact properties." We currently have an issue where we have identified longitudinal cracks in DN300 47mm thick A333 Gr6...

Similar questions seem to have been asked in the past but nothing I can find for lifting activities. We are looking at possibly tapping the outer diameter of some large blind flanges to attach a lifting eyebolt. I'm trying to understand if there is a minimum edge distance between the tapped...

Thanks SnTMan, this is most helpful.

Thanks for the responses so far guys gr2vessels, I understand the spacing between transverse baffles and shell ID as per the TEMA code which allows a certain amount of bypassing, however, in our case we have a somewhat non-standard exchanger where we need to ensure there is zero (or as close to...

Gday Forum Members My question is a simple one today (or so I hope). I'm familiar with longitudinal baffle seals (ie, kempchen, etc) for Shell and Tube Heat Exchangers, however, I'm not familiar with any transverse baffle sealing systems. We need something for a couple of baffles and they need...

Thankyou for all your responses SnTMan, I believe the issue with HTRI is that because this is a baffled construction the program doesn't like the large dome space. For kettles and similar this is not an issue. marty007, we investigated the options you have put forward. Increasing outlet nozzle...

Gday Forum Members We have a current issue where we are having to replace existing undersized TEMA AES S&T Coolers (air compressor inter-stage coolers). The existing have a demister pad installed in the DN400 outlet nozzle and we intended to keep this configuration, however, during the design...

Gday Forum Members My question relates to ASME VIII-1 2015 UG-140(b), specifically the interpretation of UG-140(b)(2) which reads: (2) The decision to limit the overpressure by system design is the responsibility of the user. The user shall request that the Manufacturer’s data report state...

Forum Members My question relates to the final affixing of NBIC R-Stamp nameplates after re-rating an item of equipment. We have a vessel which we may require to re-rate from 170degC to 180degC, this will reduce the MAWP from 890kPa to something closer to 850kPa. The expectation is that we...

Thanks TGS4. This is a weird circumstance where we haven't actually started up the refinery yet so this equipment is installed but not yet commissioned. It's not expected to start up until end of year, maybe early next year (we all know how schedules go). The plan going forward was to carry...

Sorry guys Just to confirm, the vessel I am looking at is an ASME VIII Division 1 vessel. My undertanding is that Div 1 does not expressly cover cyclic loading and fabrication/design requirements and that the cyclic fatigue analysis in Div 2 is generally used in this case. Based on this, are...

Thanks a lot for the responses guys, they are all very much appreciated. One further question on this issue. We have a project specification for cyclic loading and it states (verbatim): A "cyclic service" is defined as one in which the equipment will be subjected to periodic changes in stress...