As mentioned before, if applying internal pressure only, the yielding zones occur in the cylindrical shell as shown in Figure 6. Clearly, the decrease of the limit-load is owing to the application of the earthquake load and pipe-loads. Figure 7 shows that the limit load is 4.9В MPa which is smaller than above obtained 6.63вЂ‰MPa. As an example, supposing that the acceleration for the earthquake loading is 0.142 g which corresponds about seismic intensity level 8 and the external pipe-loads acted on the end of the tube in the bottom of the conical shell are F zвЂ‰=вЂ‰20вЂ‰000вЂ‰N and M zвЂ‰=вЂ‰12вЂ‰000вЂ‰N.m, the load-displacement curve with changing the internal pressure is shown in Figure 7 and Mises distribution is shown in Figure 8 at the last convergent pressure loading. The design parameters for the jacketed vessel are listed in Table 1.Д¬ontours of von Mises stress distribution for internal pressure only 4.2 Acted by comprehensive loadingsДifferent from the codes ASME VIII-1 and ASME VIII-2, by applying limit-load analysis, other loadings such as dead weight, earthquake, and external pipe-loads can also be considered beside the internal pressure. The half-pipe jacketed vessel studied here consists of the cylindrical shell, elliptical head, half-pipe jackets, and supporters. 2 INITIAL CALCULATION OF STRUCTURAL THICKNESS Scheme and advantages of the method will be presented through a design of half-pipe jacketed vessel which cannot be performed with codes ASME VIII-1 and ASME VIII-2. In this paper, a new design method based on limit-load analysis is proposed to design half-pipe jacketed vessels. Any other half-pipe jacketed vessels not in the specified range or acted by comprehensive loadings cannot be designed according to codes ASME VIII-1 and VIII-2. The other is that only pressure loading is considered in the calculation of the vessel thickness. and the outside diameter of the half-pipe should be 60вЂ‰mm or 89вЂ‰mm or 114вЂ‰mm. 10 One is that the internal diameter of the vessel should be within the range of 760вЂ“4300вЂ‰mm. Regarding the design of half-pipe jacketed vessels, there are two clear limitations in codes ASME VIII-1 9 and ASME VIII-2. 2 (or ASME VIII-2) and verified that the half-pipe jacket has a strengthening effect on the shell. conducted buckling analysis and plasticity evaluation on the half-pipe jacketed vessel that did not meet the requirements of ASME Sec. 7 conducted experiments on the heat transfer of the fluid in the half-pipe jacket, fitted the correlation equation of the heat transfer coefficient, developed a mathematical model for predicting the heat transfer of the half-pipe jacket, and found that the model predicts are in good agreement with the experimental data. 5 studied the residual stress and deformation caused by the welding of the half-pipe jacket on the shell, which provided a reference for the safety assessment of the half-pipe jacket.

4 investigated the effect of Dean and Prandtl numbers on the fluid flow and heat transfer in the inner and outer half-coil jackets. 2 Pydi studied the heat transfer of the half-coil jacket. 1 Jawad gave the background information for the derivation of the half-pipe jacket design rules formulated by the ASME Subgroup on Design of Section VII, and various assumptions were made in developing the rules. proposed a calculation method based on thin shells connection for the design of large-diameter half-pipe jacketed vessels operating under high pressure. Due to the above advantages, the application of half-pipe jackets in industrial production is becoming more and more widespread. As a kind of jacketed container, the half-pipe type jacketed vessel has the advantages of high heat transfer efficiency, good stress distribution on the cylinder, energy saving, and steel consumption of the vessel compared with other jackets. Jacketed vessels are widely used in petroleum, chemical, pharmaceutical, and food processing fields.

Goldencheetah half pipe method