复合材料压力容器含凹陷内胆屈曲的有限元分析

张国; 朱海洋; 蔡雅琪; 任明法; 李刚

doi:10.13801/j.cnki.fhclxb.20210518.004

复合材料压力容器含凹陷内胆屈曲的有限元分析

doi: 10.13801/j.cnki.fhclxb.20210518.004

张国^{1, 2,},
朱海洋^1,,
蔡雅琪^3,,
任明法^{1, 4, ,},
李刚^{1, 4,}

1.
大连理工大学　工程力学系，大连 116024
2.
北京科泰克科技有限责任公司，北京 100024
3.
中车大连机车研究所有限公司，大连 116021
4.
大连理工大学工业装备结构分析国家重点实验室，大连 116024

基金项目: 国家自然科学基金 (U1837204)；国家重点研发计划(2019YFA0706803)

详细信息

通讯作者:
任明法，博士，教授，研究方向为复合材料结构力学和复合材料工艺力学分析　E-mail：renmf@dlut.edu.cn

中图分类号: TB331
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出版历程
- 收稿日期: 2021-03-17
- 修回日期: 2021-04-27
- 录用日期: 2021-05-09
- 网络出版日期: 2021-05-18
- 刊出日期: 2021-03-01

Finite element analysis of the buckling of the liner of composite pressure vessel with depression

ZHANG Guo^{1, 2
,},
ZHU Haiyang^1
,,
CAI Yaqi^3
,,
REN Mingfa^{1, 4
, ,},
LI Gang^{1, 4
,}

1.
Faculty of Engineering Mechanics, Dalian University of Technology, Dalian 116024, China
2.
Beijing Chinatank Industry Co. Ltd., Beijing 100024, China
3.
CRRC Dalian Institute Co. Ltd., Dalian 116021, China
4.
State Key Laboratory of Structural Analysis for Industrial Equipment, Dalian University of Technology, Dalian 116024, China

摘要

摘要: 提出了一种复合材料压力容器含凹陷金属内胆屈曲的三维有限元分析方法。基于平面应变假设，建立了含凹陷半圆环收缩屈曲分析模型，通过修改有限元模型中内胆的节点坐标，将内胆初始凹陷引入模型中，采用非线性迭代法逐步增大面内载荷，实现了含凹陷半圆环的收缩屈曲分析。在此基础上，建立复合材料压力容器含凹陷内胆的三维有限元分析模型，同时考虑自紧工艺后内胆残余应力的环向分量与轴向分量，实现了复合材料压力容器自紧工艺后含凹陷内胆的屈曲分析。以130 L球形封头薄壁铝合金内胆全缠绕复合材料压力容器为例，分析了含凹陷内胆的临界屈曲载荷以及屈曲发生时内胆的应力及变形。结果显示，含初始缺陷的内胆在自紧工艺之后屈曲模式为局部屈曲；初始凹陷深度越大，临界屈曲载荷越低；与直筒段中部的距离为凹陷轴向宽度1/2的区域和直筒段靠近封头的金属内胆区域存在凹陷易发生屈曲，是金属内胆的薄弱环节。
- 复合材料 /
- 压力容器 /
- 内胆 /
- 屈曲 /
- 有限元
Abstract: A method for buckling analysis of liner of composite pressure vessel with depression was proposed. Based on the assumption of plane strain, the shrinkage buckling analysis model of the semicircular ring with depress-ion was established, and the depression was introduced into the finite element analysis model by modifying the coordinates of nodes. The nonlinear iterative method was used to gradually increase the in-plane load, and the shrinkage buckling analysis of the semicircular ring with depression was analyzed. On this basis, a three-dimensional finite element analysis model of composite pressure vessel containing a liner with depression was established, the hoop and axial components of the residual stress of the liner after autofrettage was considered to analysis the buckling of the liner with depression after autofrettage of composite pressure vessel. Taking a 130 L spherical head and thin-walled aluminum alloy liner full-wound composite pressure vessel as an example, the critical buckling load of the liner and the stress and deformation of the liner when buckling occurred were analyzed. The results show that the buckling mode of the liner with initial depression after autofrettage is local buckling; the greater the initial depression depth, the lower the critical buckling load; the area where the distance from the middle of the straight section is 1/2 of the axial width of the depression and near the head of the straight section is prone to buckling, which is the weakness zone of the metal liner.
- composite materials /
- pressure vessels /
- liner /
- buckling /
- finite element analysis

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图 1 金属圆环收缩屈曲简化模型图

Figure 1. Simplified model of shrinkage buckling of metal ring

R—Radius of the liner; P—Pressure

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图 2 半圆环有限元分析模型

Figure 2. Finite element model of the semi-circle

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图 3 含初始凹陷的半圆环有限元分析模型

Figure 3. Finite element model of the semi-circle with initial depression

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图 4 半圆环凹陷中心的载荷-位移曲线

Figure 4. Load-displacement curve in the center of the depression of the semi-circle

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图 5 半圆环结构径向位移云图

Figure 5. Cloud image of radial displacement of the semi-circle

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图 6 本文含凹陷内胆有限元模型计算结果与Vasilikis^[13]的分析结果对比

Figure 6. Relationship between the buckling load and the defect amplitude corresponding to the finite element calculation results in this paper and Vasilikis^[13] calculation results

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图 7 含凹陷内胆局部屈曲计算流程图

Figure 7. Flow chart of local buckling calculation of inner liner with depression

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图 8 压力容器有限元分析模型

Figure 8. Finite element model of the pressure vessel

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图 9 压力容器自紧工艺后内胆轴向、环向应力分布

Figure 9. Axial and circumferential stress distribution of the liner of the pressure vessel after autofrettage

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图 10 含凹陷内胆压力容器有限元模型

Figure 10. Finite element model of the pressure vessel with depression of the liner

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图 11 压力容器自紧后内胆径向应力分布

Figure 11. Radial stress distribution of liner of the pressure vessel after autofrettage

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图 12 压力容器自紧后内胆环向应力分布

Figure 12. Circumferential stress distribution of liner of the pressure vessel after autofrettage

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图 13 压力容器自紧后内胆等效塑性应变分布

Figure 13. Equivalent plastic strain distribution of liner of the pressure vessel after autofrettage

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图 14 三种凹陷深度对应的压力容器凹陷中心位置的载荷-位移曲线

Figure 14. Load-displacement curves of the center of the depression corresponding to the three depression depths for the pressure vessel

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图 15 三种凹陷深度对应的压力容器内胆与缠绕层之间的界面压力分布

Figure 15. Pressure distribution between the inner liner and the winding layer corresponding to the three depression depths for the pressure vessel

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图 16 不同凹陷轴向宽度对应的压力容器内胆临界屈曲载荷

Figure 16. Critical buckling load of liner corresponding to different axial widths of depressions for the pressure vessel

Δ—Depth of the depression

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图 17 不同凹陷周向宽度对应的压力容器内胆临界屈曲载荷

Figure 17. Critical buckling load of liner corresponding to different circumferential direction widths of depressions for the pressure vessel

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图 18 凹陷不同位置对应的压力容器内胆临界屈曲载荷

Figure 18. Critical buckling load of the liner corresponding to different positions of the depression for the pressure vessel

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表 1 金属内胆材料的力学性能

Table 1. Mechanical properties of the metal liner material

Young’s modulus/GPa	Poisson’s ratio	Yield strength/MPa	Ultimate strength/MPa
74	0.28	300	320

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表 2 T300碳纤维/环氧树脂缠绕层的力学性能

Table 2. Mechanical properties of the winding T300 carbon fiber/epoxy layers

E_X/GPa	E_Y/GPa	E_Z/GPa	μ_X	μ_Y	μ_Z	G_XY/GPa	G_YZ/GPa	G_XZ/GPa
135	10	10	0.32	0.32	0.32	7	5	5
Notes: E, μ, G—Elastic modulus, Poisson’s ratio and shear modulus, respectively.

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