Journal of Jilin University(Engineering and Technology Edition) ›› 2025, Vol. 55 ›› Issue (10): 3141-3150.doi: 10.13229/j.cnki.jdxbgxb.20231402

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Clearance design of taper roller bearings for reducing drive axle whine

Ji-xuan YANG1(),Gui-hui ZHANG2,Zhi-yong CHEN1(),Wen-ku SHI1,Jian LIU3,Ren-fei YUAN3,Yan-yan ZHAO3   

  1. 1.National Key Laboratory of Automotive Chassis Integration and Bionics,Jilin University,Changchun 130022,China
    2.Dahua Machine Manufacturing Co. ,Ltd. ,Changchun 130103,China
    3.Automotive Research Institute,China National Heavy Duty Truck(Group Corp. ),Jinan 250100,China
  • Received:2024-03-26 Online:2025-10-01 Published:2026-02-03
  • Contact: Zhi-yong CHEN E-mail:yangjx22@mails.jlu.edu.cn;chenzy@jlu.edu.cn

Abstract:

A proposed analytical process aims to reduce vibration and noise by adjusting the clearance of the taper bearings for the systematic issue of whine in the drive axle. This process is based on a simulation model of the dynamics of the mid-axle assembly, which includes the gear, axle, bearings, and housing. The accuracy of the model is verified by the transmission error test of the bevel gears. By considering the clearances of five taper bearings that support the input shaft, pinion shaft, and differential as design variables, the response surface method was employed to establish a surrogate model for the vibration response of the axle case and the fatigue life of the pinion shaft ball bearings. Through multi-objective optimization, an improvement plan for addressing the drive axle whistling issue was obtained, considering the bearing life. The results show that this process yields better outcomes and demonstrates high adaptability.

Key words: automotive engineering, loaded transmission error, bearing clearance, bearing fatigue life, response surface method

CLC Number: 

  • TH133.33

Table 1

Macro parameters for helical gears"

项 目主动齿轮被动齿轮
法向模数/mm5.755.75
齿数/个3838
螺旋角/(°)1515
旋向左旋右旋
法向压力角/(°)2020
齿宽/mm4646

Table 2

Parameters for hypoid gear blanks"

项目主动齿轮被动齿轮
轴交角/(°)9090
偏置距/mm3030
旋向右旋左旋
齿数/个1037
名义压力角/(°)22.522.5

Fig.1

Simulation model of gear-shaft system in drive axle assembly"

Fig.2

Power flow diagram of the simulation model"

Fig.3

Condensation node unit for bearing mounting points"

Fig.4

Dynamic model of the middle axle assembly"

Fig.5

User interface of KIMoS"

Fig.6

Simulation result of loaded transmission error for hypoid gear"

Fig.7

Loaded transmission error test system for hypoid gear"

Fig.8

Spectrum of hypoid gear LTE for 100 N·m load condition"

Fig.9

Time-domain curve of hypoid gear LTE for 100 N·m load condition"

Fig.10

Comparison of test and simulation of the first-order components of hypoid gear LTE"

Table 3

Verification of hypoid gear LTE simulation accuracy"

参 数转矩工况/(N·m)
50100200400600
测试值/μm16.16314.56113.09413.1129.269
仿真值/μm12.99413.15212.92612.23210.940
仿真精度/%80.4090.3398.7293.2984.73

Fig.11

Taper roller bearings studied in this paper"

Table 4

Table of levels for each factor"

因素对应轴承水平
-11
A输入轴前轴承-300300
B差速器壳右轴承-300300
C差速器壳左轴承-300300
D小齿轮轴后轴承-300300
E小齿轮轴前轴承-300300

Fig.12

Normalized effects on vibration responseat axle housing"

Fig.13

Plot of main effect of bearing clearance onvibration response"

Fig.14

Fatigue life of bearings in their original state"

Fig.15

Normalized effects on fatigue life of ball bearing"

Fig.16

Plot of main effect of bearing clearance on fatigue life of ball bearing"

Fig.17

Interaction of clearance of bearings 2 and 3"

Table 5

Results of optimization of AFSA"

轴承游隙代号ABCDE
取值/μm30023520423-50.6

Table 6

Validation of result of AFSA"

参数拟合值仿真值
10阶振动RMS值/(m·s-212.0513.21
球轴承寿命 L10 h/h100 000.2105 521.8

Fig.18

10th-order vibration section on main drivehousing before and after optimization"

Fig.19

Fatigue life of bearings before and after optimization"

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