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/ |0 i) T" f# g8 n. v8 S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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标题 Cylindrical Shell Under Pressure
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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 |
& L) H) H) V" U, dTest Case% x8 A9 D+ n" x4 @, T2 O
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A 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.1 ~$ p# o1 H7 j3 [4 ~, ~9 T
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Figure 13.1 Cylindrical Shell Problem Sketch( C/ Z4 J+ X: i1 l
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" Z* I$ d% l3 V. D| Material Properties | | E = 30 x 106 psi | | υ = 0.3 |
| | Geometric Properties | | t = 1 in | | d = 120 in |
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8 p6 G6 Z8 y" _% k5 D' ]% UAnalysis 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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/ ~3 j5 Q4 D8 H5 rResults Comparison | Target | ANSYS | Ratio | | Stressy , psi | 15,000. | 15,000 | 1.000 | | Stressz , psi | 29,749. | 29,750. | 1.000 | 5 x" u) }% B2 F5 v7 z8 R
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[ 本帖最后由 tigerdak 于 2007-11-5 10:48 编辑 ] |
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