• CN:11-2187/TH
  • ISSN:0577-6686

机械工程学报 ›› 2018, Vol. 54 ›› Issue (5): 105-112.doi: 10.3901/JME.2018.05.105

• 机械动力学 • 上一篇    下一篇

齿轮系统振动响应信号调制边频带产生机理

李永焯, 丁康, 何国林, 林慧斌   

  1. 华南理工大学机械与汽车工程学院 广州 501641
  • 收稿日期:2016-10-27 修回日期:2017-06-07 出版日期:2018-03-05 发布日期:2018-03-05
  • 通讯作者: 李永焯(通信作者),男,1990年出生,博士研究生。主要研究方向为机械振动信号处理与故障诊断、车辆振动噪声测试与分析。E-mail:liyongzhuo123@foxmail.com
  • 作者简介:丁康,男,1957年出生,博士,教授,博士研究生导师。主要研究方向为离散频谱校正技术、机械振动信号处理与故障诊断、车辆振动噪声测试与分析。E-mail:kding@scut.edu.cn
  • 基金资助:
    国家自然科学基金(51475169,51475170)和广东省自然科学基金团队(S2013030013355)资助项目。

Modulation Sidebands of the Vibration Signal of Gearbox

LI Yongzhuo, DING Kang, HE Guolin, LIN Huibin   

  1. School of Mechanical and Automotive Engineering, South China University of Technology, Guangzhou 501641
  • Received:2016-10-27 Revised:2017-06-07 Online:2018-03-05 Published:2018-03-05

摘要: 齿轮传动系统的振动频率成分复杂多变,许多频率成分难于进行力学解释。建立定轴齿轮系统啮合点处的单自由度动力学模型,并将模型激励划分为线性激励和非线性激励,分别推导正常状态和平稳型故障下的频率响应特性及诱导因素。正常状态下,齿轮振动响应频率成分为啮合频率及其倍频,由齿轮受载后产生的静弹性变形位移和啮合动刚度共同诱发,并由非线性反馈进一步形成更高阶啮合频率成分。平稳型故障下,响应频率成分除正常运行特有的频率成分外,还包括:故障齿轮转频及其倍频,由平稳型位移误差函数与系统参数作用产生的惯性激励力、阻尼激励力和弹性激励力共同诱发;啮合频率及其倍频两侧间隔为转频的调制边频带,是由位移误差函数与啮合动刚度产生的弹性激励力引起的,并经非线性反馈进一步形成更高阶啮合频率及调制边带。有限元仿真和试验均有效地验证了推导和分析的振动响应频率特征规律。

关键词: 齿轮系统, 调制边频带, 频率特征, 平稳型故障, 正常啮合

Abstract: Vibration response of the gear system is complicated, and some frequency components are hard to analyze with mechanics. Kinetic models of the fixed-shaft gearbox under healthy state and steady-type fault are established, whose excitation forces are divided into linear and nonlinear parts, and the vibration response derivations are obtained, as well as the induction factors. Due to the interaction between the static elastic deformation and the dynamic mesh stiffness, a healthy gearbox generates vibration response of the mesh frequency and its higher harmonics. When a steady-type fault exists in the gear pair, in addition to the frequency components under healthy state, the gearbox's vibration response also contains two other parts. One part is the rotational frequency of the fault gear and its higher harmonics exited by the inertia force, the damping force and the elastic force, which are generated from the interactions between the displacement error function and the system parameters such as mass, damping and stiffness. The other part is the modulation sidebands, whose carriers are the mesh frequency harmonics and their modulation frequencies are the rotational frequency harmonics of the fault shaft or gear. This part is the result of convolution between the displacement error function and the dynamics mesh stiffness. Frequency characteristics of the fixed-shaft gearbox obtained from both the finite element simulations and experimental tests effectively demonstrate the correctness of the theory derivation and analysis of the vibration response.

Key words: frequency feature, gear system, healthy state, modulation sidebands, steady-type fault

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