A double saddle is considered unqualified even if a triple saddle passes the test. . .
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I currently have a device of model DN3800, with a head tangent distance of 7300, a design pressure of 1.0, and it operates with water at normal temperature. Actually, two saddles are sufficient, but the client wants three. Here comes the problem! ! ! With a saddle angle of 150 degrees, when calculating the stress at the edge of the δ6 shimming plate, the end cap provides no reinforcement, so the value of K6 must be set to 0.025. . . How to break it? Thicker wall panels? Add a reinforcement ring?
Since the calculation for the double saddle is acceptable, we can consider the intermediate saddle as a supplementary support and skip its calculation... Alternatively, you might want to study HG/T 20582-2011 \"Specifications for Strength Calculation of Steel Chemical Storage Vessels\" regarding the design and calculation of horizontal vessels with multiple saddles...
This post was last edited by star72 on 2015-8-27 08:43. From a formula perspective, in the absence of a reinforcement ring, the stress value is related to the effective thickness of the shell. I conducted calculations using a reinforcement ring, and it was found that I126x74x5 is required. From an economic standpoint, it is advisable to use a reinforcement ring