There is no mention of a fabrication tolerance in the thickness in DVS 2205 (nor in EN12573 I believe).
So the thickness to be used in the calculations is the minimum available/required thickness.
Out-of-roundness is another issue altogether and is mentioned in DVS2205-2.
I have a question regarding API 650 appendix P figures P.4a and P.4b.
These figures tend to be log-log graphs based on the numeric scale given on both axis.
However both axis in figure P.4a have a numbered scale which is logaritmic, but has intermediate scales which are linear.
How to deal...
Thanks for your reply. As this is already an old part of the code, I hoped someone with longer experience had an answer to the question.
I cannot imagine no one has an answer or thought about this and everybody is just doing what they seem fit. :-)
Dear,
in API650 appendix P all formulas refer to t, which is the shell thickness at the opening connection.
To calculate the stiffness of the connection, the code differentiates between nozzles with reinforcement on shell (figures P.2a to P.2f) or reinforcement in the nozzle neck (figures P.2g...
Dear all,
an existing tank has to be equipped with an intermediate wind girder.
Tank cooling is however provided by a water free flow from the top of the fixed cone roof.
If we want to attach an intermediate wind girder without having to add a sprinker ring for cooling just underneath the new...
A dome roof is also a fixed roof design, but with a different shape than a cone roof.
For larger diameter fixed roof tanks it is more economical to use a dome roof.
Thanks for the replies.
@MikeHalloran: Where to use this coefficient? Is it in velocity = (2*g*Head)^0.5, becoming velocity = (2*g*Head*coefficient)^0.5?
Thanks for the replies.
@Latexman:
I didn't do anything more then using above three formulas (velocity = (2*g*Head)^0.5, droptime = (2*height of defect / g)^0.5 and distance=velocity*droptime) to calculate the distance for multiple defect locations. Then took the highest value from these...
Dear,
I don't exactly know where to post this question, but as it actually is a fluid flow issue, I thought I post it here.
I have to calculate the spray distance resulting from a small defect (say 10 or 20 mm) in a storage tank shell.
My first assumption was to calculate the outlet velocity...
Dear,
I don't know if I should ask this question here, or in the proccess engineering forum, but let me start by asking it here.
I have to calculate the spray distance resulting from a small defect (say 10 or 20 mm) in a storage tank shell.
My first assumption was to calculate the outlet...
Just for information to all of you.
I made a finite element model with a U-bolt with both ends fixed on the steel structure. In this situation the bending moment for my layout with a 16" pipe is approx 0.38*F*R, where F is the lateral force and R is the pipe radius.
I think it will not bend, because the wall of the pipe will prevent the U-bolt from bending. The client thinks the U-bolt will bend due to the lateral (sideways) force from the piping such that the legs of the U-bolt will not be vertical anymore. The mechanical model client is proposing is a...
Dear,
a 16" pipe (heavy wall thickness) is supported on a beam and held in place using a U-bolt.
Normally I design the U-bolt based on tensile stress due to possible upward force and shear stress based on lateral force. For easy calculation I divide the pipe force by 2 to get the force for each...
Mike,
that's also how I consider it. Two separate calculations with a lot of margin in both of them.
I hoped that someone would come up with a code case or other reference on how to address this issue in such a way that one can make the design as thin as possible (and still within code limits...
My issue is that if I carry out both calculations independently that I am using the material 2 times.
First I fully utilize the material for the opening reinforcement giving me maximum allowable stress in the flange.
Secondly I fully utilize the material as a flange, giving me maximum allowable...
Dear all,
In a lot of situations a reverse flange is also acting as opening reinforcement, for example a 48" head with a 10" reverse flange in the top.
I tried to find a reference in ASME VIII how to handle such a situation.
The flange will see stresses due to the fact that is acts as opening...
PD5500 is officially replaced by the BS EN 13445.
I know it is still updated and can still be used. But EN 13445 will be leading in this case (vessel to be delivered in Europe). Is there no real EN code for titanium pressure vessels?
I think I go for ASME VIII making it a worldwide accepted...
I have to design a titanium pressure vessel (ASTM B-338 or equivalent), but the client insists that it must be designed according to a European code.
EN 13445 is the European code for unfired pressure vessels, but is only applicable to vessels manufactured from steels, spheroidal graphite cast...
