×
INTELLIGENT WORK FORUMS
FOR ENGINEERING PROFESSIONALS

Log In

Come Join Us!

Are you an
Engineering professional?
Join Eng-Tips Forums!
  • Talk With Other Members
  • Be Notified Of Responses
    To Your Posts
  • Keyword Search
  • One-Click Access To Your
    Favorite Forums
  • Automated Signatures
    On Your Posts
  • Best Of All, It's Free!
  • Students Click Here

*Eng-Tips's functionality depends on members receiving e-mail. By joining you are opting in to receive e-mail.

Posting Guidelines

Promoting, selling, recruiting, coursework and thesis posting is forbidden.

Students Click Here

Jobs

Pressure vessel Body flange calculation DIV 2
2

Pressure vessel Body flange calculation DIV 2

Pressure vessel Body flange calculation DIV 2

(OP)
Need your help.i got datasheet from client need to design Division 2 vessel.

ID : 2320
length shell : 6245
Internal pressure : 165 Bars
External Pressure : FV
Temperature : 70/70
Head Type : Body flange (Top),Hemispherical Head (Bottom)
material head and shell : SA 516 GR.70
body flange material " SA.350 LF.2 CL.1

When i come out in PV elite. requirement thickness body flange is 500 mm thickness. have other way how to reduced thickness of body flange?

Thank You so much if can help me to solve this problem

RE: Pressure vessel Body flange calculation DIV 2

You are leaving out a lot of information. What type of flange? Weld neck? Slip On? What type gasket are you using? Dimensions? bolt size and material?

What part is driving the thickness requirement? Seating condition? Operating condition? Flange rigidity?

RE: Pressure vessel Body flange calculation DIV 2

I'm not very familiar with ASME VIII-2 Part 4, but this is going to be a monster flange at that pressure and diameter.

The best way to reduce flange thickness in general is to make your bolt circle diameter as small as possible.

Because of your pressure however, you're going to be running into bolt spacing issues. Really the only thing you can do is try to find the strongest bolts allowable by code, and use them to reduce your bolt circle diameter as much as possible.

Other than that, you'd have to step outside of the rules of Part 4 and design a specialised closure. One example would be something like a Greyloc closure, but I don't know if that's practical at your diameter.

Another option could be some sort of breech-lock style threaded closure? Depends on the geometry of your equipment...

Good luck!
Marty

RE: Pressure vessel Body flange calculation DIV 2

(OP)
cbPVme

Sorry if i miss information.
Orientation : Vertical
flange type : proposed to used weld neck type
gasket : ring joint ss and nickel base alloy
dimension and bolt size : depend what the design calculation can pass
material of bolt and nuts : SA-193-B7M/SA 194-2HM

Thank You sir for your reply

Marty007

Yes your right.
i will get monster flange. but if i changed to used quick opening closure type i will step out from design code also?

RE: Pressure vessel Body flange calculation DIV 2

Also be aware that depending on the bolt size that you're using you might need
hydraulic tensioning therefore your studs should be longer by the thickness
of one extra nut on one side.
Usually bolting of 1.5" and higher requires the use of hydraulic tensioners.

You could also try and use alternative design codes for flange design like:
BS EN 1591-1:2013
https://shop.bsigroup.com/ProductDetail/?pid=00000...

or
EN 13445 Annex G

but what the outcome would be in comparison to ASME VIII-2 - I have absolutely no idea.

RE: Pressure vessel Body flange calculation DIV 2

Quote (pepiji)

if i changed to used quick opening closure type i will step out from design code also?

ASME VIII-2 addresses quick opening closures in paragraph 4.8. Unfortunately this paragraph doesn't provide specific design formulas, so you're probably left with Part 5 (FEA).

RE: Pressure vessel Body flange calculation DIV 2

I suggest design for top head similar to ASME VIII Div 1 Figure 1-6 (d)
Stud screwed through shell flange and fitted with single nut in top head flange.
Hydraulic tensioner shall be applied in set of four studs (minimum) at same time . Particular specification is required.
My experience was: Reactor Pressure Vessel (nuclear), 76 stud 220 mm diameter with special design of nuts (no hexagonal).

Regards

RE: Pressure vessel Body flange calculation DIV 2

Double check the B7M stud bolt material, as that material doesn't seem to make sense for external bolting.

B7M studs have a lower allowable stress than B7 studs, so using them will result in a larger diameter/more expensive flange.


-Christine

RE: Pressure vessel Body flange calculation DIV 2

I prefer the standard EN 1591-1 or EN13445 Annex G.
Or we should push the ASME BPVC adopting the methord " the leakage Behavior of Gaskets in Flanged Connections".
Unfortunately, after so many years, nothing has happened. Leaving us behind the europeans.

RE: Pressure vessel Body flange calculation DIV 2

Quote:

Leaving us behind the europeans.

I wouldnt say that, but: have you considered becoming a voluntary ASME committee member, such to participate and help in making changes?

RE: Pressure vessel Body flange calculation DIV 2

Dear XL83NL ,
Sorry my schedule is always full. I just hope our association can absorb some foreign more advanced experience.

Red Flag This Post

Please let us know here why this post is inappropriate. Reasons such as off-topic, duplicates, flames, illegal, vulgar, or students posting their homework.

Red Flag Submitted

Thank you for helping keep Eng-Tips Forums free from inappropriate posts.
The Eng-Tips staff will check this out and take appropriate action.

Reply To This Thread

Posting in the Eng-Tips forums is a member-only feature.

Click Here to join Eng-Tips and talk with other members! Already a Member? Login


Resources

White Paper - The Criticality of the E/E Architecture
Modern vehicles are highly sophisticated systems incorporating electrical, electronic, software and mechanical components. Mechanical systems are giving way to advanced software and electronic devices, driving automakers to innovate and differentiate their vehicles via the electric and electronic (E/E) architecture. As the pace of change accelerates, automotive companies need to evolve their development processes to deliver and maximize the value of these architectures. Download Now
White Paper - Model Based Engineering for Wire Harness Manufacturing
Modern cars, trucks, and other vehicles feature an ever-increasing number of sophisticated electrical and electronic features, placing a larger burden on the wiring harness that enables these new features. As complexity rises, current harness manufacturing methods are struggling to keep pace due to manual data exchanges and the inability to capture tribal knowledge. A model-based wire harness manufacturing engineering flow automates data exchange and captures tribal knowledge through design rules to help harness manufacturers improve harness quality and boost efficiency. Download Now
White Paper - Modeling and Optimizing Wire Harness Costs for Variation Complexity
This paper will focus on the quantification of the complexity related costs in harness variations in order to model them, allowing automated algorithms to optimize for these costs. A number of real world examples will be provided as well. Since no two businesses are alike, it is the aim of this paper to provide the foundational knowledge and methodology so the reader can assess their own business to model how variation complexity costs affect their business. Download Now

Close Box

Join Eng-Tips® Today!

Join your peers on the Internet's largest technical engineering professional community.
It's easy to join and it's free.

Here's Why Members Love Eng-Tips Forums:

Register now while it's still free!

Already a member? Close this window and log in.

Join Us             Close