直升机主传动系统共振能量传递特性研究

许华超; 秦大同; 徐志良; 王勇; 罗宏林; 延依芹

doi:10.13224/j.cnki.jasp.20230623

直升机主传动系统共振能量传递特性研究

doi: 10.13224/j.cnki.jasp.20230623

许华超^{1, 2,},
秦大同²,
徐志良³,
王勇^{1, 2},
罗宏林¹,
延依芹¹

1.
重庆电子科技职业大学智能制造与汽车学院，重庆 401331
2.
重庆大学机械传动国家重点实验室，重庆 400044
3.
季华实验室超滑工程中心，广东佛山 528251

基金项目: 国家自然科学基金（52305052）；重庆市自然科学基金面上项目（CSTB2023NSCQ-MSX0813）；重庆市教育委员会科学技术研究计划项目（KJZD-M202403101，KJZD-K202203105）

详细信息

作者简介:
许华超（1990-），男，讲师，博士，主要从事直升机主传动系统动力学设计与分析的研究。E-mail：xuhuachao@cqcet.edu.cn

中图分类号: V275；TH113
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- 被引次数: 0
出版历程
- 收稿日期: 2023-10-01
- 网络出版日期: 2025-03-21

Research on resonance energy transfer characteristics of helicopter main transmission system

1.
Intelligent Manufacturing and Automobile School，Chongqing Polytechnic University of Electronic Technology，Chongqing 401331，China
2.
State Key Laboratory of Mechanical Transmission，Chongqing University，Chongqing 400044，China
3.
Engineering Center for Superlubricity，Ji Hua Laboratory，Foshan Guangdong 528251，China

摘要

摘要:
为使力学模型更好与物理模型相匹配，采用集中参数/有限元混合建模法构建计及轴与机匣结构柔性的直升机主传动系统动力学模型。基于所建模型开展了固有特性分析，并综合采用坎贝尔图与模态能量法对系统共振能量传递特性进行了研究。结果表明：直升机主传动系统的振型可归为全局纯扭转振动模式、定轴-行星轮系耦合振动模式、局部行星轮系振动模式和局部定轴传动振动模式；输入转速在5210 r/min附近时低速级啮频易引发该系统共振，振动能量可能主要通过齿轮6、轴5、轴承10和轴承座10传递，其中齿轮6和轴承10模态能量较大，视为危险构件。
- 直升机 /
- 传动系统 /
- 齿轮 /
- 共振 /
- 传递路径 /
- 振动能量
Abstract:
To make the mechanical model better match the physical model, a dynamic model of the helicopter main transmission system considering the structural flexibility was constructed by using the hybrid lumped parameter/finite element modeling method. Based on the established model, the inherent characteristics were analyzed, and the resonance energy transfer characteristics of the system were comprehensively studied using Campbell diagram and modal energy method. The results showed that the vibration modes of the helicopter main transmission system can be classified into global pure torsional vibration mode, fixed shaft-planetary gear coupling vibration mode, local planetary gear vibration mode and local fixed shaft transmission vibration mode. When the input speed was close to 5210 r/min, the meshing frequency of low-speed stage was easy to cause the resonance of the system, and the vibration energy may be mainly transmitted through gear 6, shaft 5, bearing 10 and bearing seat 10. Among them, gear 6 and bearing 10 were considered dangerous components due to their large modal energy.
- helicopter /
- transmission system /
- gear /
- resonance /
- transfer path /
- vibration energy

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图 1 直升机主传动系统行星轮系级建模

Figure 1. Modeling of planetary gear for helicopter main transmission system

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图 2 直升机主传动系统高速斜齿轮级建模

Figure 2. Modeling of helical gear for helicopter main transmission system

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图 3 锥齿轮啮合副模型

Figure 3. Bevel gear meshing pair model

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图 4 系统整体矩阵组装示意图

Figure 4. Assembly schematic diagram of system overall matrix

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图 5 直升机主传动系统动力学模型

Figure 5. Dynamic model of helicopter main transmission system

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图 6 全局纯扭转振动模式（0 Hz）

Figure 6. Global pure torsional vibration mode （0 Hz）

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图 7 定轴-行星轮系耦合振动模式（130.9 Hz）

Figure 7. Fixed shafts-planetary gear coupling vibration mode （130.9 Hz）

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图 8 局部行星轮系振动模式（563.3 Hz）

Figure 8. Local planetary gear vibration mode （563.3 Hz）

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图 9 局部定轴传动振动模式（1158.5 Hz）

Figure 9. Local fixed shafts transmission vibration mode （1158.5 Hz）

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图 10 直升机主传动系统各阶模态动能分布

Figure 10. Modal kinetic energy distribution of each vibration mode of helicopter main transmission system

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图 11 直升机主传动系统各阶模态应变能分布

Figure 11. Modal strain energy distribution of each vibration mode of helicopter main transmission system

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图 12 坎贝尔图（600～1600 Hz）

Figure 12. Campbell diagram （600—1600 Hz）

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图 13 低速级啮合振动的传递路径

Figure 13. Transmission path of mesh vibration at low-speed stage

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图 14 输入转速为5210 r/min时直升机主传动系统低速级的振动能量分布

Figure 14. Vibration energy distribution of low-speed stage of helicopter main transmission system at input speed 5210 r/min

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表 1 齿轮参数

Table 1. Gear data

传动级	齿轮名称	齿数	模数/mm	压力角/（°）	螺旋角/（°）
高速级	锥齿轮1	15	4.2	22	32
高速级	锥齿轮2	59	4.2	22	32
中间级	锥齿轮3	42	3.2	22	32
中间级	锥齿轮4	19	3.2	22	32
低速级	斜齿轮5	30	4.6	20	16
低速级	斜齿轮6	35	4.6	20	16
行星级	太阳轮	37	5.1	20	0
	行星轮	39
	内齿圈	115

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表 2 齿轮啮合刚度

Table 2. Gear meshing stiffness

传动级	啮合刚度/（MN/m）
高速级	647
中间级	821
低速级	260
行星级外啮合	897
行星级内啮合	813

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表 3 系统固有频率及振型

Table 3. Natural frequency and vibration mode of system

阶数	频率/Hz	振动模式	阶数	频率/Hz	振动模式
1	0	A	15	401.8	B
2	130.9	B	16	474.2	B
3	131.0	B	17	503.8	A
4	137.5	B	18	503.8	A
5	140.7	B	19	563.3	C
6	164.3	B	20	587.8	B
7	187.6	B	21	591.7	B
8	191.9	B	22	603.6	B
9	201.4	B	23	615.6	B
10	228.5	B	24	666.5	B
11	294.3	B	25	680.8	B
12	309.1	B	26	706.8	B
13	371.3	B	27	739.7	B
14	395.3	A

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表 4 各阶固有频率下能量集中构件与之相交的激励频率

Table 4. Excitation frequency at which the energy concentrating member intersects at each order of intrinsic frequency

共振点	激励频率/Hz	固有频率/Hz	转速/ （r/min）	动能集中构件（占比超8%）
A	f_m56	f₃₆=1428.8	5210	齿轮6（低速级）
B	f_msp	f₂₅=739.7	6188	齿圈（行星级）

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