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某型叶片缘板阻尼器结构设计与减振分析

吕启航 陈成 邓丽君 周泽堂 董军帅 谢宇航 漆文凯 邹励戬

吕启航, 陈成, 邓丽君, 等. 某型叶片缘板阻尼器结构设计与减振分析[J]. 航空动力学报, 2026, 41(2):20240122 doi: 10.13224/j.cnki.jasp.20240122
引用本文: 吕启航, 陈成, 邓丽君, 等. 某型叶片缘板阻尼器结构设计与减振分析[J]. 航空动力学报, 2026, 41(2):20240122 doi: 10.13224/j.cnki.jasp.20240122
LYU Qihang, CHEN Cheng, DENG Lijun, et al. Structure design and vibration reduction analysis of a certain type of un-derplatform damper[J]. Journal of Aerospace Power, 2026, 41(2):20240122 doi: 10.13224/j.cnki.jasp.20240122
Citation: LYU Qihang, CHEN Cheng, DENG Lijun, et al. Structure design and vibration reduction analysis of a certain type of un-derplatform damper[J]. Journal of Aerospace Power, 2026, 41(2):20240122 doi: 10.13224/j.cnki.jasp.20240122

某型叶片缘板阻尼器结构设计与减振分析

doi: 10.13224/j.cnki.jasp.20240122
基金项目: 研究基金
详细信息
    作者简介:

    吕启航(1994-),男,工程师,硕士,主要研究方向为航空发动机振动设计。E-mail:1598459487@qq.com

  • 中图分类号: V231.1

Structure design and vibration reduction analysis of a certain type of un-derplatform damper

  • 摘要:

    为了研究叶片缘板阻尼装置对某型发动机燃气涡轮叶片振动的动力响应的影响,基于整体-局部统一滑动模型理论建立摩擦模型,结合有限元分析软件ANSYS和谐响应计算程序,对成组三齿涡轮叶片进行了仿真分析,当阻尼器和叶片缘板之间正压力与叶片受到的激振力比值在合适范围内,叶片第2阶共振幅值仿真结果可降至无阻尼状态下的25%以下,依据仿真分析结果,完成了两种涡轮叶片的缘板阻尼器结构设计。针对某型涡轮叶片高频振动模态,设计高频减振特性试验方案,搭建高频减振特性试验系统,开展成组涡轮叶片高阶模态减振试验,叶片第1阶共振幅值相对无阻尼状态可降至70.72%。结合仿真计算结果和实际试验结果,得到涡轮叶片减振特性影响参数,形成了一套针对危险模态下涡轮叶片缘板阻尼器的结构设计和试验验证方法。

     

  • 图 1  整体-局部统一滑动模型的力-位移迟滞回线

    Figure 1.  Force-displacement hysteresis loop of global-local unified sliding model

    图 2  带摩擦阻尼装置叶片振动响应计算流程图

    Figure 2.  Flow chart of vibration response calculation of blade with friction damping device

    图 3  涡轮叶片前4阶振型图

    Figure 3.  The first four order vibration patterns of turbine blade

    图 4  不同正压力下涡轮叶片组幅频特性曲线

    Figure 4.  Amplitude-frequency characteristics of turbine blades under different positive pressures

    图 5  涡轮叶片相对共振幅值随无量纲正压力的变化曲线

    Figure 5.  Curve of relative common amplitude of turbine blade with dimensionless positive pressure

    图 6  阻尼器结构设计流程

    Figure 6.  Damper structure design flow

    图 7  三齿涡轮叶片阻尼装置结构及安装示意图

    Figure 7.  Structure and installation diagram of three-tooth turbine blade damping device

    图 8  阻尼器在工作状态下等效应力云图

    Figure 8.  Equivalent stress diagram of the damper in working condition

    图 9  涡轮叶片摩擦阻尼高频减振试验系统

    Figure 9.  High frequency vibration damping test system for turbine blade friction damping

    图 10  试验系统基础台架结构形式

    Figure 10.  Test system base bench structure form

    图 11  加载装置结构示意图

    Figure 11.  Loading device structure

    图 12  三齿涡轮叶片第2阶加速度幅频曲线

    Figure 12.  Amplitude-frequency curve of the second order acceleration of a three-tooth turbine blade

    图 13  试验系统安装

    Figure 13.  Test system installation

    图 14  不同正压力下三齿涡轮叶片第1阶模态减振试验幅频曲线

    Figure 14.  Amplitude-frequency curves of the first mode vibration attenuation test of three-tooth turbine blades under different positive pressure

    图 15  相对共振幅值随无量纲正压力变化曲线

    Figure 15.  Relative common amplitude with dimensionless positive pressure

    表  1  DZ125材料属性

    Table  1.   Material properties of DZ125

    参数 数值
    密度/(kg/m3 8570
    弹性模量/1011 Pa Ex 1.765
    Ey 1.765
    Ez 1.27
    切变模量/1010 Pa Gxy 7
    Gyz 1.07
    Gxz 1.07
    泊松比 Uxy 0.26
    Uyz 0.49
    Uxz 0.49
    下载: 导出CSV

    表  2  涡轮叶片前4阶固有频率计算结果

    Table  2.   Calculation results of the first four natural frequencies of turbine blades

    阶次固有频率/Hz
    第1阶7942
    第2阶13012
    第3阶17716
    第4阶23891
    下载: 导出CSV

    表  3  三齿涡轮叶片自由模态试验数据与仿真数据对比

    Table  3.   Comparison of modal test data and simulation data of three-tooth turbine blades

    参数 仿真数据 试验数据 相对误差/%
    第1阶固有频率/Hz 12753 12080 −5.28
    下载: 导出CSV

    表  4  三齿涡轮叶片试验数据对比

    Table  4.   Comparison of test data of three-tooth turbine blades

    阶次频率/Hz相对
    误差/%
    模态试验减振特性试验
    第1阶570057200.35
    第2阶12300130706.26
    第3阶17500173101.09
    下载: 导出CSV

    表  5  三齿涡轮叶片第1阶减振试验中不同正压力下加速度共振幅值及共振频率变化

    Table  5.   Changes of acceleration co-amplitude and resonance frequency under different positive pressure in the first order vibration reduction test of three-tooth turbine blades

    正压力/N a/g 共振频率/Hz 相对共振幅值
    0 77.16 5600 1
    5 65.04 0.8429
    10 59.99 0.7775
    20 63.07 0.8174
    40 55.03 0.7132
    60 54.57 0.7072
    100 68.95 0.8936
    下载: 导出CSV
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  • 收稿日期:  2024-03-03
  • 网络出版日期:  2025-11-10

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