时变正压力弹支干摩擦阻尼器对发动机转子减振分析

王胜朔; 范雨; 胡誉; 高钱; 吴亚光

doi:10.13224/j.cnki.jasp.20250023

时变正压力弹支干摩擦阻尼器对发动机转子减振分析

doi: 10.13224/j.cnki.jasp.20250023

王胜朔^1,,
范雨^{1, 2},
胡誉¹,
高钱^1,*, ,,
吴亚光^{1, 3}

1.
北京航空航天大学能源与动力工程学院，北京 100191
2.
北京航空航天大学航空发动机结构强度北京市重点实验室，北京 100191
3.
北京航空航天大学中法工程师学院，北京 100191

基金项目: 国家科技重大专项（J2022-Ⅳ-0005-0022）

详细信息

作者简介:
王胜朔（2000-），男，博士生，研究领域为航空发动机结构振动分析与抑制。E-mail：wangshengshuo@buaa.edu.cn

通讯作者:
高钱（1995-），男，助理研究员，博士，研究领域为非线性振动与叶盘阻尼技术。E-mail：gaoqian04@buaa.edu.cn

中图分类号: V231.96
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出版历程
- 收稿日期: 2025-01-14
- 网络出版日期: 2026-05-11

Analysis of vibration reduction in engine rotors using elastic-support dry friction dampers with time-varying normal force

Wang Shengshuo^1
,,
Fan Yu^{1, 2},
Hu Yu¹,
Gao Qian^{1,*
, ,},
Wu Yaguang^{1, 3}

1.
School of Energy and Power Engineering，Beihang University，Beijing 100191，China
2.
Beijing Key Laboratory of Aero-Engine Structure and Strength，Beihang University，Beijing 100191，China
3.
Sino-French Engineering School，Beihang University，Beijing 100191，China

摘要

摘要:
针对航空发动机转子通过临界转速时的振动问题，提出了在常值正压力基础上引入谐波分量的时变正压力弹支干摩擦阻尼器。首先根据转子系统的运动特点，以简化的二维干摩擦动力学模型为对象，通过扩展傅里叶全局参数敏感性分析方法，研究了时变正压力在典型二维运动轨迹下对干摩擦阻尼的影响机制。结果表明：对于圆形运动轨迹，时变正压力会削弱常值正压力的减振性能；而对于椭圆形运动轨迹，正压力的2阶谐波分量能够进一步增强减振效果，可使振动响应峰值进一步下降24.7%。在此基础上，将弹支干摩擦阻尼器应用于某型航空发动机的低压转子系统，采用2阶谐波时变正压力控制策略，基于高保真有限元模型和谐波平衡法开展动力学仿真分析。结果显示，对2阶谐波分量进行有效控制后，相较于常正压力，时变正压力弹支干摩擦阻尼器使得转子系统的2阶反进动、2阶正进动和3阶反进动的共振峰值分别进一步降低35.6%、10.6%和5.1%。
- 弹支干摩擦阻尼器 /
- 时变正压力 /
- 参数敏感性分析 /
- 谐波平衡法 /
- 转子动力学
Abstract:
To address the vibration issues encountered by aero-engine rotors when passing through critical speeds, a time-varying normal force elastic-support dry friction damper, incorporating a harmonic component alongside a constant normal force, was proposed. A simplified two-dimensional dry friction dynamic model, representing the rotor system's motion characteristics, was analyzed. Using an extended Fourier global parameter sensitivity analysis method, the influence of time-varying normal force on dry friction damping under typical two-dimensional motion trajectories was investigated. The results indicated that for circular motion trajectories, time-varying normal force diminished the vibration reduction performance compared with constant normal force. In contrast, for elliptical motion trajectories, the inclusion of a second-order harmonic component enhanced vibration reduction, achieving a 24.7% reduction in peak vibration response. Based on these findings, the elastic-support dry friction damper was applied to the low-pressure rotor system of an aero-engine, utilizing a second-order harmonic time-varying normal force control strategy. Dynamic simulations were conducted using a high-fidelity finite element model and harmonic balance method, revealing significant improvements. Compared with constant normal force, the proposed damper reduced the resonance peak values of the second-order backward whirl, second-order forward whirl, and third-order backward whirl of the rotor system by 35.6%, 10.6%, and 5.1%, respectively.
- elastic-support dry friction damper /
- time-varying normal force /
- parameter sensitivity analysis /
- harmonic balance method /
- rotor dynamics

HTML

图 1 某型涡轮风扇发动机低压转子结构简图

Figure 1. Schematic diagram of the low-pressure rotor structure in a turbofan engine

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图 2 时变正压力弹支干摩擦阻尼器构型

Figure 2. Configuration of a time-varying normal force elastic-support dry friction damper

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图 3 二自由度干摩擦系统模型示意图

Figure 3. Schematic diagram of a two-dimensional dry friction system model

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图 4 不同常值正压力下的频响曲线

Figure 4. Frequency response curves under different constant normal forces

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图 5 时变正压力的频响分布

Figure 5. Frequency response distribution under time-varying normal forces

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图 6 参数敏感性分析结果

Figure 6. Results of parameter sensitivity analysis

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图 7 振动响应下降百分比

Figure 7. Percentage reduction in vibration response

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图 8 常值正压力和时变正压力的频响曲线和滑移状态占比（圆形运动轨迹）

Figure 8. Frequency response curves and slip ratios of constant normal forces and time-varying normal forces （circular）

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图 9 频率为31.8 Hz时质量块、阻尼器和迟滞弹簧轨迹

Figure 9. Trajectory of mass, damper and hysteresis spring at frequency of 31.8 Hz

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图 10 频率为32.1 Hz时质量块、阻尼器和迟滞弹簧轨迹

Figure 10. Trajectory of mass, damper and hysteresis spring at frequency of 32.1 Hz

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图 11 常值正压力和时变正压力的频响曲线和滑移状态占比（椭圆形运动轨迹）

Figure 11. Frequency response curves and slip ratios of constant normal forces and time-varying normal forces （elliptical）

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图 12 频率为32.0 Hz时质量块、阻尼器和迟滞弹簧轨迹

Figure 12. Trajectory of mass, damper and hysteresis spring at frequency of 32.0 Hz

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图 13 频率为32.1 Hz时质量块、阻尼器和迟滞弹簧轨迹

Figure 13. Trajectory of mass, damper and hysteresis spring at frequency of 32.1 Hz

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图 14 WS-X-LR有限元模型

Figure 14. Finite element model of WS-X-LR

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图 15 WS-X-LR有限元模型及测点示意图

Figure 15. Finite element model and measurement point diagram of WS-X-LR

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图 16 WS-X-LR的坎贝尔图

Figure 16. Campbell diagram for WS-X-LR

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图 17 WS-X-LR的前3阶模态振型

Figure 17. First three-order mode shapes of WS-X-LR

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图 18 WS-X-LR的不平衡响应图

Figure 18. Unbalanced response diagram of WS-X-LR

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图 19 算法框架

Figure 19. Algorithm framework

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图 20 风扇测点在不同常值正压力下长轴的频响曲线

Figure 20. Frequency response curve of the long axis of the fan measuring point under different constant normal forces

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图 21 风扇测点在时变正压力作用下长轴的频响分布

Figure 21. Frequency response distribution of the long axis of the fan measurement point under time-varying normal force

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图 22 滑移状态占比随转速的变化

Figure 22. Variation of slip ratio with rotational speed

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图 23 轴心、阻尼器和迟滞弹簧的运动轨迹

Figure 23. Trajectory of the axis, damper and hysteresis spring

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表 1 二自由度干摩擦系统的参数

Table 1. Parameters of two-dimensional dry friction system

参数	数值	含义
$ m $/kg	1	质量
$ {c}_{x} $/（N·s/m）	1	x方向阻尼系数
$ {c}_{y} $/（N·s/m）	1	y方向阻尼系数
$ {k}_{x} $/10⁴ （N/m）	4	x方向刚度系数
$ {k}_{y} $/10⁴ （N/m）	4	y方向刚度系数
$ f_{{x}}^{\text{ext}} （t） $/N	$ 10\cos （\omega t） $	x方向激振力（圆形）
$ f_{{x}}^{\text{ext}} （t） $/N	$ 10\cos （\omega t） $	x方向激振力（椭圆形）
$ f_{y}^{\text{ext}} （t） $/N	$ 10\sin （\omega t） $	y方向激振力（圆形）
$ f_{y}^{\text{ext}} （t） $/N	$ 5\sin （\omega t） $	y方向激振力（椭圆形）
$ \mu $	0.3	摩擦因数
$ {k}_{\text{t}} $/10³ （N/m）	1	接触刚度

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表 2 前3阶临界转速和振型特点

Table 2. First three-order critical speeds and vibration characteristics

阶次	临界转速/（r/min）	振型特点
1阶反进动	2507	涡轮主导的整体俯仰
1阶正进动	3089	涡轮主导的整体俯仰
2阶反进动	3395	风扇主导的局部摆动
2阶正进动	4312	风扇主导的局部摆动
3阶反进动	4483	转轴弯曲与涡轮摆动
3阶正进动	6155	转轴弯曲与涡轮摆动

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表 3 时变正压力的取值和转速计算区间

Table 3. Values of time-varying normal force and speed range

参数	数值
参数	2阶反进动	2阶正进动	3阶反进动
转速区间/（r/min）	[3180, 3860]	（3860, 4460]	（4460, 4850]
常值正压力/N	800	1000	900
谐波振幅/N	[160, 480]	[200, 600]	[180, 540]
谐波相位/rad	$ [0,2{\text{π}} ] $	$ [0,2{\text{π}}] $	$ [0,2{\text{π}}] $

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