Structure design and vibration reduction analysis of a certain type of un-derplatform damper
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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。
Abstract:To investigate the impact of blade platform damping devices on the dynamic response of vibration in a certain type of aero-engine gas turbine blades, a friction model was established based on the global-local unified slip model theory. By integrating the finite element analysis software ANSYS and harmonic response calculation procedures, simulation analysis was conducted on grouped three-tooth turbine blades. When the ratio of the normal pressure between the damper and the blade platform to the excitation force acting on the blade fell within an appropriate range, the simulated resonance amplitude of the second-order mode of the blade can be reduced to below 25% of the undamped state. Based on the simulation results, structural designs for two types of turbine blade platform dampers were completed. For high-frequency vibration modes of a certain turbine blade, a high-frequency vibration reduction test plan was designed, and a corresponding test system was constructed. High-order modal vibration reduction tests were carried out on grouped turbine blades, and the first-order resonance amplitude was reduced to 70.72% of the undamped state. By combining simulation results with experimental data, key parameters influencing the vibration reduction characteristics of turbine blades were identified, leading to the development of a comprehensive methodology for the structural design and experimental validation of turbine blade platform dampers under critical modal conditions.
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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 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 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 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 5700 5720 0.35 第2阶 12300 13070 6.26 第3阶 17500 17310 1.09 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 -
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