磁流变阻尼器参数对座椅悬架系统减振效果的影响

胡国良; 刘前结; 李刚; 徐明

doi:10.19818/j.cnki.1671-1637.2018.01.010

磁流变阻尼器参数对座椅悬架系统减振效果的影响

doi: 10.19818/j.cnki.1671-1637.2018.01.010

华东交通大学载运工具与装备教育部重点实验室机构, 江西南昌 330013

基金项目:

国家自然科学基金项目 51475165

国家自然科学基金项目 51765016

江西省主要学科学术和技术带头人培养计划项目 20162BCB22019

详细信息

作者简介:
胡国良(1973-), 男, 江西南昌人, 华东交通大学教授, 工学博士, 从事磁流变智能器件与结构研究

中图分类号: U463.83
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出版历程
- 收稿日期: 2017-09-02
- 刊出日期: 2018-02-25

Influence of parameters of magnetorheological damper on vibration attenuation effect of seat suspension system

Key Laboratory of Conveyance and Equipment of Ministry of Education, East China Jiaotong University, Nanchang 330013, Jiangxi, China

More Information

Author Bio:
HU Guo-liang(1973-), male, professor, PhD, glhu2006@163.com

摘要

摘要: 应用Bingham本构力学模型, 得到了磁流变阻尼器(MRD) 的结构尺寸参数(缸体内径、活塞直径、活塞杆直径、活塞有效长度)、线圈匝数和磁流变液表观黏度与输出阻尼力的关系, 利用力学模型分析了MRD的6个参数对输出阻尼力和动态范围的影响; 建立了基于MRD的半主动座椅悬架系统模型, 以驾驶人加速度和座椅软垫动行程的均方根作为减振效果的评价指标, 采用百分比斜率均方根评价MRD参数的影响程度; 结合Bingham本构力学逆模型, 分析了MRD的6个参数对减振效果的影响及MRD磨损对减振效果的影响。分析结果表明: 活塞直径对驾驶人加速度和座椅软垫动行程的影响因子分别为4.83、5.46, 缸体内径的影响因子分别为4.45、4.75, 线圈匝数的影响因子分别为0.61、0.67, 活塞杆直径的影响因子分别为0.53、0.59, 活塞有效长度的影响因子分别为0.51与0.56, 因此, 活塞直径对减振效果的影响最大, 其次为缸体内径, 随后依次为线圈匝数、活塞杆直径与活塞有效长度, 而磁流变液表观黏度对减振效果几乎没有影响; 为了获得较好的减振效果, 应使MRD的最大输出阻尼力与动态范围足够大。
- 汽车工程 /
- 磁流变阻尼器 /
- 座椅悬架 /
- 力学模型 /
- 参数设计 /
- 减振效果
Abstract: The relationships among the output damping force and the structural dimension parameters (cylinder inner diameter, piston diameter, piston rod diameter, effective piston length), coil turn, and apparent viscosity of magnetorheological fluid of magnetorheological damper (MRD) were obtained based on the Bingham constitutive mechanical model.The effects of the six parameters of MRD on the output damping force and the dynamic range were analyzed by using the obtained mechanical model.A semi-active seat suspension system model based on MRD was established, and the RMSs of driver acceleration and dynamic displacement of seat cushion were used as the evaluation indexes of vibration attenuation effect, and the RMS of percentage-based slope was put forward to evaluate the influence degrees of MRD parameters.The influences of the six parameters of MRD on the vibration attenuation effect were investigated, and the influence of MRD wear on the vibration attenuation effect was analyzed simultaneously by using the Bingham constitutive inverse mechanical model.Analysis resultshows that the influence factors of piston diameter on the driver acceleration and the dynamic displacement of seat cushion are 4.83 and 5.46, respectively.The influence factors of cylinder inner diameter are 4.45 and 4.75, respectively.The influence factors of coil turn are 0.61 and0.67, respectively.The influence factors of piston rod diameter are 0.53 and 0.59, respectively.The influence factors of effective piston length are 0.51 and 0.56, respectively.So piston diameter has the most important influence on the vibration attenuation effect, the second is cylinder inner diameter, and then followed by coil turn, piston rod diameter and effective piston length.However, the apparent viscosity of magnetorheological fluid has little influence on the vibration attenuation effect.Besides, in order to obtain a better vibration attenuation effect, the maximal output damping force and dynamic range of MRD should be larger enough.
- automotive engineering /
- magnetorheological damper /
- seat suspension /
- mechanical model /
- parameter design /
- vibration attenuation effect

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图 1 剪切阀式MRD结构

Figure 1. Structure of shear-valve mode MRD

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图 2 力学性能试验系统

Figure 2. Test system of mechanical performance

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图 3 试验用MRD

Figure 3. MRD used for test

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图 4 阻尼力-位移曲线比较

Figure 4. Comparison of damping force-displacement curves

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图 5 阻尼力-速度曲线比较

Figure 5. Comparison of damping force-velocity curves

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图 6 参数D、d₂、d₁、L对输出阻尼力的影响

Figure 6. Influence of parameters D, d₂, d₁and L on output damping force

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图 7 参数η、N对输出阻尼力的影响

Figure 7. Influence of parameters η and N on output damping force

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图 8 参数D、d₂、d₁对动态范围的影响

Figure 8. Influence of parameters D, d₂ and d₁ on dynamic range

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图 9 参数η、N对动态范围的影响

Figure 9. Influence of parameters η and N on dynamic range

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图 10 阻尼性能影响因子

Figure 10. Influence factors of damping performances

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图 11 基于MRD的半主动座椅悬架系统简化模型

Figure 11. Simplified model of semi-active seat suspension system based on MRD

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图 12 半主动座椅悬架系统控制原理

Figure 12. Control principle of semi-active seat suspension system

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图 13 期望阻尼力与MRD产生的阻尼力比较

Figure 13. Comparison between expected damping force and damping force produced by MRD

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图 14 参数D、d₂、d₁、L对驾驶人加速度的影响

Figure 14. Influence of parameters D, d₂, d₁and L on driver acceleration

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图 15 参数η、N对驾驶人加速度的影响

Figure 15. Influence of parameters η and N on driver acceleration

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图 16 参数D、d₂、d₁、L对座椅软垫动行程的影响

Figure 16. Influence of parameters D, d₂, d₁and L on dynamic displacement of seat cushion

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图 17 参数η、N对座椅软垫动行程的影响

Figure 17. Influence of parameters η and N on dynamic displacement of seat cushion

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图 18 驾驶人加速度影响因子

Figure 18. Influence factors of driver acceleration

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图 19 座椅软垫动行程影响因子

Figure 19. Influence factors of dynamic displacement of seat cushion

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图 20 驾驶人加速度功率谱对比

Figure 20. Comparison of power spectrums of driver acceleration

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图 21 座椅软垫动行程功率谱对比

Figure 21. Comparison of power spectrums of dynamic displacement of seat cushion

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表 1 MRD主要参数值

Table 1. Main parameter values of MRD

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