This curve works well for cooling / heating water only, while the stainless steel dimple jacket has. Here is what Mueller suggests based on their experiments. Other companies have published similar data. Don’t forget to consider the static pressure difference at inlet and outlet points (here 4.33 psi). Is the 24' x 24' sample enough for the proof test if we maintain the same material specs, thicknesses and dimple spacing? If so would the proof test sample need to be rolled to the same radius as the vessel or can it be flat? Thanks in advance. The total pressure drop would be 6.7 psi. 5) Check tube pattern - HTEX with 30 triangular pattern cost less per m heat transfer area (due to highest tube densities) and transfer more heat per m heat transfer area (due to the high shell-side heat transfer coefficients). We are struggling with UG-101(d) which allows the proof test of similar geometry to be used. The objective of the present work is to perform thermal design of a shell and tube heat exchanger that using HTRI software to makes the process energy efficient. 4) Check for vibration warnings, if there are vibration warnings you need to look at design carefully. 17-5 sends you to UG-101 but mentions the test may be part of the test in 17-7. 17-7 states not less than 5 pitches an 24' x 24', but 17-7 is concerning welding qualifications. My question is the size of the sample for the proof test.

Welds are being looked at per UW-19 (c)and the plain plate as a stayed surface per. It will be an embossed plate, plug welded to a plain plate. We are fabricating a pressure vessel to Section VIII Div 1 which will have a dimple jacket. We will calculate the required burst pressure per UG-101(m)(2)(-a)adjusted per UG-101(k) for max temp, to obtain the 150 PSI MAWP we need. MDS N SONS (Industrial) (OP) 17 Nov 21 16:50. Welds are being looked at per UW-19(c)and the plain plate as a stayed surface per UG-47.

Htri software dimpled jacket