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& v+ Q+ u. A6 E+ k& K* j% L6 Z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。* P' u$ w2 C& @# k2 q
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标题 Cylindrical Shell Under Pressure
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, Z! m/ l' j4 |0 [( u* ?1 ^| 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 |
0 R2 u0 G' W% \, ~! s0 @% o+ PTest Case
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+ e2 O! _4 J6 ]5 Y& q+ ^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.
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% E+ G: R% N' v7 ?9 T8 o" i rFigure 13.1 Cylindrical Shell Problem Sketch
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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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( m J# {$ W. e2 s TAnalysis 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 | , ~$ s. n" y% h& \' Q
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[ 本帖最后由 tigerdak 于 2007-11-5 10:48 编辑 ] |
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