The objective of this paper is to analyze an existing American Petroleum Institute (API) 620 Tank [10]. The API Tank had failed in the field. The tank is analyzed without reinforcement and with an optimum I-Beam reinforcement. The API Tank is used to store chemicals used in today’s industry. The initial over-all dimensions of the API Tank are determined from the capacity of the stored chemicals. The design function is performed using the ASME Code See VIII Div 1. The API Tank design is broken up into (a) bottom plate, (b) shell section with 9 mm thickness, (c) shell section with 8 mm thickness, (d) shell section with 7 mm thickness, (e) shell section with 6 mm thickness, (f) shell section with 5 mm thickness, (g) top head with 5mm thickness, (h) bolts, and (i) reinforcement ring. The designed dimensions are used to recalculate the stresses for the complete API Tank. The dimensioned API Tank without reinforcement is modeled first using STAAD III finite element software. The stresses from the finite element software are obtained. Next the API Tank with I-Beam reinforcement was modeled using STAAD III finite element software. Ten different I-Beams were considered for the present analysis. The main objective of this paper was to find the optimum I-Beam that resulted in safe reinforced configuration. Optimum I-Beam was considered to be the one that resulted in similar stresses for the beam as well as the tank. This assures elastic matching between the beam and the tank. The design is found to be safe for the I-Beam reinforced configuration considered.

The main objective of this paper is to improve a jacketed vessel. The jacketed vessel is usually chosen to heat the contents of the vessel. The chamber or annulus contains fluid under pressure to heat the inner vessel contents. The initial over-all dimensions of the vessel are based on the capacity of the stored liquid. The design was in accordance with the ASME Boiler & Pressure Vessel Code, Section VIII, Div 1. The jacketed vessel bottom head and jacket bottom head are being improved to withstand internal and external design pressures. Bottom head of the jacket can be reinforced in one of the three ways, namely: (1) rings which are radial (these rings also create flow for the fluid); (2) attachment of the rings to the bottom jacket head with stays, since rings cannot be physically welded to the bottom jacket; or (3) there is a possibility, the new bottom head and jacketed head combination can be cast, but that would not be economically feasible. This leads to the following six configurations considered in this paper and they are: (1) internal pressure of 50 psi, (2) external pressure + vacuum pressure of 65 psi, (3) reinforcement with 5 rings with external pressure of 65 psi, (4) rings welded with the bottom jacket head with external pressure of 65 psi, (5) welded with stays on ring location (stay diameter of 1 inch) with external pressure of 65 psi, and (6) welded with stays on ring location (stay diameter of 1.5 inch) with external pressure of 65 psi. The pattern of stays chosen for this analysis is one of uniform distribution on ring locations, which are radially situated. The design dimensions based on Code sizing are used to recalculate the stresses for the jacket vessel. The dimensional jacketed vessel is modeled using STAAD III Finite Element Analysis (FEA) software. The design is found to be safe for the specific configuration considered herein with stays.