Journal of Jilin University(Engineering and Technology Edition) ›› 2024, Vol. 54 ›› Issue (4): 890-901.doi: 10.13229/j.cnki.jdxbgxb.20221107

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Analysis of nonlinear vibration response characteristics of hybrid transmission system with dual-planetary gear sets

Shao-hua WANG1,2(),Qi-rui ZHANG1,De-hua SHI1,2(),Chun-fang YIN3,Chun LI4   

  1. 1.Automotive Engineering Research Institute，Jiangsu University，Zhenjiang 212013，China
    2.Jiangsu Province Engineering Research Center of Electric Drive System and Intelligent Control for Alternative Vehicles，Zhenjiang 212013，China
    3.School of Electrical and Information Engineering，Jiangsu University，Zhenjiang 212013，China
    4.Higer Bus Company Limited，Suzhou 215026，China
  • Received:2022-12-08 Online:2024-04-01 Published:2024-05-17
  • Contact: De-hua SHI E-mail:shwang@ujs.edu.cn;dhshi@ujs.edu.cn

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Abstract:

Aiming at the hybrid transmission system with dual-planetary gear sets， the purely axial-torsional nonlinear dynamic model considering the internal excitations， including the comprehensive time-varying meshing stiffness and meshing error， and the external excitations， including the load torque and output torque of different power sources， is established. On this basis， the fourth-order Runge-Kutta method is applied to study the nonlinear high-frequency vibration characteristics of the system in the pure electric and hybrid driving modes with different torque excitations. The impacts of the torque allocation of different power sources on each component of the planetary gear sets are obtained. Research results demonstrate that in the pure electric driving mode with dual motors， the vibration response of the front planetary gear set is greater than that of the rear one， and the vibration fluctuation of the rear planetary row is greater than that of the front planetary row. The motor MG2 should preferentially work in the working range with large and constant torque； In the hybrid drive mode， the front planetary row is greatly affected by the motor MG1， and the vibration response amount and vibration response fluctuation range are larger than those of the rear planetary row. The motor MG1 should be kept in a relatively constant working range， and the motor MG2 should preferentially work in a larger torque range. The research results will provide a theoretical basis for the dynamic behavior analysis and torque allocation optimization of the power-split HEV based on the dual-planetary gear sets configuration.

Key words: vehicle engineering, dual-planetary gear sets, dynamic model, vibration response characteristics, torque distribution

CLC Number: 

  • U463.2

Fig.1

Structure diagram of the transmission system"

Table 1

Specifications of the dual-planetary gear sets"

参数前行星排后行星排
行星架c1内齿圈r1太阳轮s1行星轮p1行星架c2内齿圈r2太阳轮s2行星轮p2
模数/mm1.51.51.51.52.52.52.52.5
压力角/（°）2020202020202020
螺旋角/（°）27.08827.08827.08827.08827.08827.08827.08827.088
齿数-964824-964824
基圆直径/mm105.572135.31667.65833.829162.549197.33598.66849.334

Fig.2

Dynamic model of the dual-planetary gear sets"

Fig.3

Integrated internal and external time-varying meshing stiffness of front planetary gear set"

Fig.4

Integrated internal and external time-varying meshing stiffness of rear planetary gear set"

Table 2

Specifications of the hybrid electric vehicle"

参数含义数值单位
mv整车整备质量18 000kg
R车轮半径0.51m
ρair空气密度1.23g/m3
CD空气阻力系数0.3-
Af车辆迎风面积4.746m2
i0主减速比5.3-
K1前行星排特征参数2-
K2后行星排特征参数3-
ωmaxE发动机最大转速2 300r/min
PmaxE发动机峰值功率151kW
ωmaxG电机MG1最大转速6 000r/min
PmaxG电机MG1峰值功率100kW
ωmaxM电机MG2最大转速3 500r/min
PmaxM电机MG2峰值功率120kW

Fig.5

Lever model of the planetary gear set"

Table 3

Vehicle driving mode"

工作模式发动机MG1MG2锁止机构
单电机驱动关关开锁止
双电机驱动关开开锁止
混合驱动开开开分离

Fig.6

Angular displacement of the carrier gear of the rear planetary gear set in MG2 driving mode"

Fig.7

Peak to peak angular displacement of the carrier gear of the rear planetary gear set in MG2 driving mode"

Fig.8

Vibration angular displacement of different components of front planetary gear set in the dual-motor driving mode"

Fig.9

Vibration angular displacement of different components of rear planetary gear set in the dual-motor driving mode"

Fig.10

Peak to peak angular displacement of different components of front planetary gear set in dual-motor driving mode"

Fig.11

Peak to peak angular displacement of different components of rear planetary gear set in dual-motor driving mode"

Fig.12

Vibration angular displacement of different components of front planetary gear set in the hybrid driving mode"

Fig.13

Vibration angular displacement of different components of rear planetary gear set in hybrid driving mode"

Fig.14

Peak to peak angular displacement of different components of front planetary gear set in the hybrid driving mode"

Fig.15

Peak to peak angular displacement of different components of rear planetary gear set in the hybrid driving mode"

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