Bending stress on horizontal pressure vessel saddle wear plate

[kos1]

Does anyone knows the equation to Bending stress on wear plate on horizontal pressure tank?

I am trying to analyze the loads on saddle using Pressure Vessel Design Manual by Dennis Moss. He gave details on all the saddle parts, but didn't include anything on the wear plates. Any tips or direction to where I can find this info, would be greatly appreciated.

 

[JStephen]

Reference 4th Edition, Page 260, see definitions of ts in the left-hand column.
Specifically, the wear plate is not designed as a separate element, but its thickness is combined with the shell thickness for certain design checks.
This also requires the wear plate to extend beyond the saddles a certain amount on the sides and on the ends of the saddles.
Note that "wear plate" as used is here is separate from the top flange plate of the saddle.

Saddles are discussed in Moss's book, also in Bednar's, Megyesy's handbooks, as well as the original Zick paper. Combining those sources will help to understand some of the approaches more than just using one of them.

 

[kos1]

Thanks for reply JStephen,

I did read that definitions and followed the calculation, but the number im getting it seems too high. I thought there might be a different approach to it, hence the reason for posting it here.

Here is the equation i have derived based on my understanding:

r=radius (in)
b=wear plate width (in)
ts= ts+tw (in)
Q=load per saddle (lbs)
K5=0.760 for 120D saddle angle

 

[JStephen]

How the numbers work out depends on vessel size, pressure, etc.
Typically, higher-pressure vessels are easier to design for due to having thicker shells anyway.
Lower pressure or atmospheric vessels can be a challenge.
Most of the vessels I work with are around 100 psi, and they will nearly always require a greater saddle angle than 120 degrees.