Thank you for your answer , another question in fixed roofs we use the details of appendix F and calculate its area that must be same or greater than area in item 5.1.5.9 e , does this mean that if we use any detail that have top angle of the minimum thickness so we don't need to calculate the...
In API 650 according to item 5.1.5.9 e , the fixed roof tanks require top angle of minimum sizes and this angle is a curb angle that is attached to both shell and roof , now item 5.9.3.1 say that when the angle is located 0.6 m below the top of shell , so we must put angle at the top , so I am...
I can't put drawings as it is confidential to my company if they discover there are penalties ,, the skirt is not the part that support the pressure vessels as saddles but it is a shell , which mean the drawing is divided shell part 1 welded to shell part 2 welded to skirt and then welded to...
When our supplier provides the drawing of high pressure and low pressure feedwater heaters , there is a part of shell called skirt , its position is after tubesheet in LP heater and its position is at steam inlet in HP heater , so what is the skirt ? IS it a part of shell ? what is its function...
I need to know if the secondary stresses is different from residual stresses ? , also is the secondary stresses in the pressure vessel important ? AS i know that the secondary stresses comes combined with the primary stresses not alone so can we neglect the secondary stress and if not why ...
I have a heat exchanger of material SA516-70 , I need to know the creep range of this material and other material , where can I find such a data whether in a code or website ?
I was reading in ansi hi standards for pumps and there is a table called pump test acceptable grades , what i understand is that if we have a specific design of a pump say head of 10 bar at rated flow ,, so when the tests are made and due to fluctuations and vibrations , the readings foe example...
I know that centrifugal pumps produces head which has a value equals to the system resistance ,, but what is the case of compressors ? do they have curves like pumps ? Does their head or pressure changes with the system resistance ? How the compressibility factor of gases is involved ?
ok , actually i searched more in a heat exchanger text book and both equations determines the rate of heat transfer , i don't know from where you get the heat capacity which is only the term " Cp " not the equation i wrote !!
In heat transfer equations sometimes they use Q=m*Cp*deltaT = m* delta H ,, and sometimes uses Q=U*A*delta T ,, so when to use each equation ? in heat exchangers they use the first equation then the second one so i got confused a little , AT last does the two equations equals each other ?
It is a practical solution that when we have a branch of high pressure and we need to decrease the pressure so the pressure reaches the end user at the pressure needed so we use a restricted orfice in that branch , so my question was since the Q from pump is the same , does adding this orfice...
The pressure decreases from 8 bars to 6 bars by using an orfice for example , the pressure drop in branch 2 due to friction and static head is 1 bar and we added an orfice of pressure drop 2 so the fluid pressure decreases from 9 bars to 6 bars at the end user , why it is not possible ?
I edit the question sorry for that its 8 bars ,, The artificial resistance drops the pressure 2 bars and branch 2 resistance is 1 bar so pressure drops from 9 bars at point 3 to 6 bars at the end of branch 2 ,, so i don't get "Normally that doesn't happen" ? in my previous thread someone told me...
On the left we have a system with a pump and two branches , a pump produces head of 10 bars and Q of 5 m3/h according to the system requirments. On the left the pressure came uot of the pump 10 bars it drops to reach 9 bars at point 3 then the 9 bars drops in branch 1 to reach 1 bar at its end...
If the branch you are talking about is not critical branch , so the pump will produce head and flow rate as determined and since head doesn't change , so the point of the flow rate on the pump curve will not change also , so it will produce same flow rate , now you have two paths the critical...
But as you can see if this is a pump curve , the flow rate of 15 will never match with head of 3.2 even if we use a control valve , so we need to work on point 3 so we need a pump with variable speeds , so is it better to determine the 3 points i need of the 3 modes so that the supplier can find...
