工业管道系统流致疲劳寿命的数值模拟

尹晓文; 田泽; 韩阳; 李志强

doi:10.11858/gywlxb.20180559

工业管道系统流致疲劳寿命的数值模拟

doi: 10.11858/gywlxb.20180559

尹晓文^1,,
田泽¹,
韩阳¹,
李志强^{1, 2, 3,*, ,}

1.
太原理工大学应用力学与生物医学工程研究所, 山西太原 030024
2.
太原理工大学力学学院材料强度与结构冲击山西省重点实验室, 山西太原 030024
3.
力学国家级实验教学示范中心(太原理工大学), 山西太原 030024

基金项目:

国家自然科学基金 11672199

山西省自然科学基础研究项目 201601D011011

详细信息

作者简介:
尹晓文(1990-), 男, 硕士研究生, 主要从事冲击动力学研究. E-mail:yinxiaowen1002@link.tyut.edu.cn

通讯作者:
李志强(1973-), 男, 博士, 教授, 博士生导师, 主要从事冲击动力学研究. E-mail:lizhiqiang@tyut.edu.cn

中图分类号: O346.2;U173
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出版历程
- 收稿日期: 2018-05-10
- 修回日期: 2018-05-25

Numerical Simulation on Fluid Causing Fatigue of Industrial Pipeline System

YIN Xiaowen^1
,,
TIAN Ze¹,
HAN Yang¹,
LI Zhiqiang^{1, 2, 3,*
, ,}

1.
Institute of Applied Mechanics and Biomedical Engineering, Taiyuan University of Technology, Taiyuan 030024, China
2.
Shanxi Key Laboratory of Material Strength & Structural Impact, College of Mechanics, Taiyuan University of Technology, Taiyuan 030024, China
3.
National Demonstration Center for Experimental Mechanics Education(Taiyuan University of Technology), Taiyuan 030024, China

摘要

摘要: 鉴于目前对整个管道系统的疲劳分析和相应数值模拟比较缺乏，基于ANSYS软件，利用Workbench和nCode DesignLife完成了管道系统从建模到流固耦合再到疲劳分析的完整模拟计算过程，得到了一般高压工业输水管道系统在正常流速及管内高压工况下的模拟计算结果，探究了入口速度和随机激振力作用下管道系统和各组件的疲劳响应。结果表明：对于实际运用的工业高压管道，需要对各部分管内流速进行监控，保证其处于合理可控范围；管道系统内的连接部是发生疲劳失效的重点区域，并且多发生于相贯线处；管道系统有助于增加各法兰管件在极限状态下的疲劳寿命。研究结果可为高压工业管道系统的设计和疲劳失效防护提供指导。
- 流固耦合 /
- 管道系统 /
- 疲劳分析 /
- 激振力
Abstract: The fatigue analysis for a whole pipeline system is rather rare to date, while in this paper, we accomplished an integrated computational fatigue analysis of the pipeline system based on model constructing and fluid-solid coupling by using Workbench and nCode DesignLife method.And the high pressure industrial water pipeline is studied under normal interior flow velocity and high working pressure conditions respectively.The fatigue response of the system and individual part is affected by various inlet velocities and random excitation forces.The results indicate that the interior flow velocity of each part in industrial high-pressure pipeline should be monitored for the system health.The fatigue failures generally occur on the connecting parts, especially at the interior intersecting line segments.Piping system can extend the fatigue life of flanged pipe at extreme states.This work provides a significant reference for the design of the high pressure industrial piping system in preventing the fatigue failure.
- fluid-solid coupling /
- pipeline system /
- fatigue analysis /
- excitation force

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图 1 管道系统几何模型

Figure 1. Geometrical model of pipeline system

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图 2 网格正交品质统计

Figure 2. Statistics for orthogonal quality of meshing

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图 3 网格倾斜度统计

Figure 3. Statistics for inclination of meshing

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图 4 白噪声载荷时程曲线

Figure 4. Load-time curve of white noise

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图 5 标准S-N曲线

Figure 5. Standard S-N curve

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图 6 不同入口速度下管路子系统流速

Figure 6. Flow rate of pipeline subsystem for different inlet velocities

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图 7 四通的应力云图

Figure 7. Stress nephogram of four-way

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图 8 三通出口的应力云图

Figure 8. Stress nephogram of tee-out

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图 9 管道系统整体疲劳寿命云图

Figure 9. Fatigue life nephogram of pipeline system

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图 10 四通的疲劳寿命云图

Figure 10. Fatigue life nephogram of four-way

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图 11 出流三通的疲劳寿命云图

Figure 11. Fatigue life nephogram of tee-out

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图 12 支座三通的疲劳寿命云图

Figure 12. Fatigue life nephogram of tee-support

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图 13 A类弯头的应力-疲劳寿命曲线

Figure 13. Stress-life curve of A class elbows

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图 14 B类弯头的应力-疲劳寿命曲线

Figure 14. Stress-life curve of B class elbows

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图 15 支座三通的应力-疲劳寿命曲线

Figure 15. Stress-life curve of tee-support

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图 16 出流三通的应力-疲劳寿命曲线

Figure 16. Stress-life curve of tee-out

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图 17 四通的应力-疲劳寿命曲线

Figure 17. Stress-life curve of four-way

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图 18 不同法兰管件的应力-疲劳寿命曲线

Figure 18. Stress-life curve of various flanges

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表 1 管道系统内流体对结构的映射力

Table 1. Mapping force of fluid in pipeline system to structure

Component	v₀/(m·s^-1)	Mapping force/N
Component	v₀/(m·s^-1)	x	y	z
Elbow A	3	1.86	124.00	-147.94
	5	282.56	39.96	-332.05
	7	561.72	142.27	-707.51
	10	5 677.60	-2 269.10	-797.02
Elbow B	3	-0.32	-44.00	2.26
	5	865.42	-1 068.40	0.24
	7	1 745.20	-2 095.90	-9.68
	10	18 628.00	-18 369.00	580.01
Tee-support	3	136.32	-0.23	-3.15
	5	682.44	0.04	-3.56
	7	1 093.30	-1.14	-0.15
	10	2 715.60	-6.83	-32.04
Tee-out	3	472.57	-0.01	343.97
	5	1 707.60	-0.65	1 092.30
	7	3 031.30	-0.24	2 002.40
	10	13 840.00	-20.37	9 474.50
Four-way	3	-8.02	0.25	-186.31
	5	-7.74	1.70	-615.87
	7	-19.67	3.66	-1 173.30
	10	126.58	13.93	-2 455.70

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表 2 计算结果

Table 2. Calculated results

v₀/(m·s^-1)	σ_max/MPa	ε_max/10^-3	Position with maximum stress
3	285.34	2.28	Tee-out
5	285.37	2.28	Tee-out
7	285.30	2.28	Tee-out
10	287.11	2.29	Tee-out

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