负刚度结构的座椅悬架优化及隔振分析

时培成; 李云龙; 肖平; 李静

doi:10.13433/j.cnki.1003-8728.20200054

负刚度结构的座椅悬架优化及隔振分析

doi: 10.13433/j.cnki.1003-8728.20200054

安徽工程大学汽车新技术安徽省工程技术研究中心，安徽芜湖　241000

基金项目: 国家自然科学基金项目（51575001，51605003）、安徽高校科研平台创新团队建设项目（2016-2018）与安徽工程大学中青年拔尖人才项目（2016BJRC010）

详细信息

作者简介:
时培成（1976−），教授，博士，研究方向为机械/汽车振动控制技术、汽车轻量化设计，shipeicheng@126.com

中图分类号: TB535; O322
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- 被引次数: 0
出版历程
- 收稿日期: 2019-10-08
- 刊出日期: 2021-02-02

Optimization and Vibration Isolation Analysis of Vehicle Seat Suspension with Negative Stiffness Structure

Automotive New Technology Anhui Engineering and Technology Research Center, Anhui Polytechnic University, Wuhu 241000, Anhui, China

摘要

摘要: 为进一步提升车辆座椅悬架的隔振性能，利用连杆弹簧负刚度结构与正刚度弹性元件并联的方式，设计了一种具有准零刚度的座椅悬架系统。基于多目标参数协调优化原理，进行了结构参数优化，获得了使座椅悬架刚度动刚度趋于准零刚度的最佳值。通过对座椅悬架隔振系统的动力学响应分析，以及仿真实验，验证了座椅悬架隔振系统优化的有效性。研究结果表明，采用连杆弹簧负刚度结构的座椅悬架系统能有效提升座椅的隔振效果，并可降低系统本身的固有频率，实现低频和超低频隔振。
- 负刚度结构 /
- 座椅悬架 /
- NSGA-Ⅱ算法 /
- 准零刚度
Abstract: In order to further improve the vibration isolation performance of the vehicle seat suspension, a seat suspension system with quasi-zero stiffness is designed by using the negative stiffness structure of the connecting rod spring and the positive stiffness elastic element in parallel. Based on the multi-objective parameter coordination optimization principle, the structural parameters are optimized, and the optimal value for making the seat suspension dynamic stiffness tend to quasi-zero stiffness is obtained. The effectiveness of the seat suspension vibration isolation system is verified by the dynamic response analysis of the seat suspension vibration isolation system and the simulation experiment. The research results show that the seat suspension system with the negative stiffness of the connecting rod spring can effectively improve the vibration isolation effect of the seat, and can reduce the natural frequency of the system itself, and achieve low frequency and ultra low frequency vibration isolation.
- negative stiffness structure /
- seat suspension /
- NSGA-II algorithm /
- quasi-zero stiffness

HTML全文

图 1 连杆弹簧负刚度机构

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图 2 负刚度机构无量纲力${\hat F_h}$-垂向位移$\hat y$曲线

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图 3 负刚度调节机构无量纲刚度${\hat K_h}$-垂向位移$\hat y$曲线

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图 4 基于负刚度结构的座椅悬架机构图

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图 5 并联后无量纲刚力-位移特性曲线图

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图 6 并联后无量纲刚度-位移特性曲线图

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图 7 优化后座椅悬架无量纲刚度、无量纲力与无量纲位移$\hat y$特性曲线（k = 0.415, β₁ = 1, β₂ = 1.8）

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图 8 “座椅-车”三自由度模型

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图 9 被隔振物体m₁的加速度响应及对应的快速傅里叶变换（1 Hz、2 Hz）

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图 10 不同路面激励频率下被隔振物体m₁加速度均方根值

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图 11 脉冲路面激励函数

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图 12 被隔振物体m₁运动响应曲线

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图 13 多频率组合路面激

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图 14 多频率组合激励被隔振物体m₁运动响应曲线

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图 15 随机激励位移随时间变化曲线

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图 16 随机激励下隔振物体m₁运动响应曲线

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图 17 隔振物体m₁加速度功率谱密度

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表 1 “座椅-车”三自由度参数定义^[14]

参数	数值
座椅负载质量m₁/kg	60
悬架质量m₂/kg	300
轮胎质量m₀/kg	35
座椅阻尼c₁/(Ns·m⁻¹)	150
悬架阻尼c₂/(Ns·m⁻¹)	980
座椅悬架垂向刚度K_v/(N·m⁻¹)	12000
车辆悬架刚度k₂/(N·m⁻¹)	16000
轮胎刚度k₀/(N·m⁻¹)	160000

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参考文献(18)

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