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这是我从ANSYS的算法验证文件转换过来的，同样适用于CosmosWorks。在计算实际的工程问题以前应该先计算一个类似的验证文件，比较计算结果以验证自己算法的正确性。也可以作为有限元例题使用。
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" r/ {( _& @9 c S& u6 t* Q y3 A标题 Cylindrical Shell Under Pressure& {7 I1 ?% N; Y8 S9 K2 P- h L
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Overview
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| Reference: | | S. Timoshenko, Strength of Material, Part I, Elementary Theory and Problems, 3rd Edition, D. Van Nostrand Co., Inc., New York, NY, 1955, pg. 45, article 11. | | A. C. Ugural, S. K. Fenster, Advanced Strength and Applied Elasticity, Elsevier, 1981. |
| | Analysis Type(s): | Static Analysis |
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( h. s/ F1 u. MA long cylindrical pressure vessel of mean diameter d and wall thickness t has closed ends and is subjected to an internal pressure P. Determine the axial stress σy and the hoop stress σz in the vessel at the midthickness of the wall., {. g# G4 z& ^( `
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Figure 13.1 Cylindrical Shell Problem Sketch5 I, Z, _6 }% n/ m) q% k' j* Z# Q
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| Material Properties | | E = 30 x 106 psi | | υ = 0.3 |
| | Geometric Properties | | t = 1 in | | d = 120 in |
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2 V7 F5 I5 o: r& W6 j7 F9 K, LAnalysis Assumptions and Modeling NotesAn arbitrary axial length of 10 inches is selected. Nodal coupling is used in the radial direction. An axial force of 5654866.8 lb ((Pπd2)/4) is applied to simulate the closed-end effect.
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Results Comparison | Target | ANSYS | Ratio | | Stressy , psi | 15,000. | 15,000 | 1.000 | | Stressz , psi | 29,749. | 29,750. | 1.000 |
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[ 本帖最后由 tigerdak 于 2007-11-5 10:48 编辑 ] |
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发表于 2007-11-5 09:41:21