磁流变阻尼器悬架系统非线性振动行为分析

韩刚; 刘瑞; 吕鹤

doi:10.13433/j.cnki.1003-8728.20200412

磁流变阻尼器悬架系统非线性振动行为分析

doi: 10.13433/j.cnki.1003-8728.20200412

齐齐哈尔大学机电工程学院, 黑龙江齐齐哈尔 161006

基金项目:

黑龙江省教育厅基本业务专项 135109218

详细信息

作者简介:
韩刚(1971-), 副教授, 博士, 研究方向为结构动力学与控制, hgjxx@163.com

中图分类号: O322;TH113.1
计量
- 文章访问数: 84
- HTML全文浏览量: 68
- PDF下载量: 24
- 被引次数: 0
出版历程
- 收稿日期: 2020-09-21
- 刊出日期: 2022-05-01

Analysis on Nonlinear Vibration Behavior of Suspension System with Magnetorheological Damper

School of Mechanical & Electrical Engineering, Qiqihar University, Qiqihar 161006, Heilongjiang, China

摘要

摘要: 建立了简化的整车系统振动模型, 研究汽车车身垂直振动非线性响应行为。利用SolidWorks与SimMechanics联合仿真方法, 分析悬架系统的几何非线性和非线性磁流变阻尼力对其振动行为的影响, 讨论其垂直振动位移响应的二次及以上谐波成分随系统参数变化的规律。结果表明: 系统响应出现二次及以上的谐波成分, 甚至在特定的外激励频率和幅值下, 会产生二次和三次超谐波共振, 表现出明显的非线性振动行为, 导致车辆乘坐舒适性不佳。该工作对带有磁流变阻尼器的悬架系统优化设计, 具有一定的理论参考意义。
- 磁流变阻尼器 /
- 悬架系统 /
- 非线性振动 /
- 联合仿真方法
Abstract: The simplified vibration model of the vehicle was developed to study the nonlinear response behavior of vertical vibration of automobile body. The influence of geometric nonliearity and nonliear magnetorheological damping force of the suspension system on the vehicle vertical vibration behavior are analyzed with the combined simulation method of SolidWorks and SimMechanics, and the variation of the second and higher superharmonic components with system parameters in vertical displacement response of automobile body are discussed. The simulation results show that the second and higher superharmonic components appear in the system responses, the second and the third superharmonic resonance will be generated under the specific excitation frequencies and amplitudes. These show obvious nonlinear vibration behaviors that will lead to poor ride comfort. The work will be helpful to the optimization design of suspension system with magnetorheological damper.
- magnetorheological damper /
- suspension system /
- nonlinear vibration /
- combined simulation method

HTML全文

图 1 前麦弗逊与后多连杆悬架模型

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图 2 SolidWorks实体模型向SimMechanics仿真模型的转化过程

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图 3 SimMechanics动力学仿真模型

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图 4 外激励A=0.02 m时车身位移-时间历程曲线、相平面图和频谱图

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图 5 外激励f=0.51 Hz时车身位移-时间历程曲线、相平面图和频谱图

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图 6 车身频谱图

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图 7 磁流变阻尼器仿真模型

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图 8 磁流变阻尼力随速度变化曲线

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图 9 外激励f=0.2 Hz、A=0.05 m、F_m=200 N时车身位移-时间历程曲线、相平面图和频谱图

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图 10 外激励f=0.2 Hz、A=0.05 m、β=200时车身位移-时间历程曲线、相平面图和频谱图

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图 11 外激励A=0.05 m、β=300、F_m=400 N时车身位移-时间历程曲线、相平面图和频谱图

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图 12 不同β值时车身垂直位移响应幅频曲线

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图 13 不同F_m值时车身垂直位移响应幅频曲线

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表 1 几何与动力学特性参数

参数	数值
车身长度/m	4.15
车身宽度/m	1.85
车身高度/m	1.35
轴距/m	2.7
轮距/m	1.8
质心距前轴距离/m	1.17
质心距后轴距离/m	1.53
质心距地面高度/m	0.6
麦弗逊弹簧刚度/(N·m^-1)	45 000
麦弗逊减振器阻尼/(N·(m·s^-1)^-1)	1 500
多连杆弹簧刚度/(N·m^-1)	34 180
多连杆减振器阻尼/(N·(m·s^-1)^-1)	1 350
轮胎刚度/(N·m^-1)	400 000

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参考文献(15)

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