Analysis of contact stress of Hypoid Gear of micro- car rear axle

Abstract

Abstract.Established a finite element model of hypoid gear of a micro-car rear final drive, analysis of the hypoid gear mode and static contact by means of finite element analysis , obtained the surface of gear contact stress distribution in the different installation position,The results show that the finite element simulation exactly reflects the impact of the installation location of the hypoid gear to contact fatigue strength of gear,providing a theoretical basis for the design and installation of the gear.

Computational analysis of the longevity of drive gear bearings in the primary reduction unit

“…While mini-MPV vehicles have seen a marked improvement in ride comfort compared to their micro-car counterparts, issues related to noise and vibrations in the primary gearbox continue to persist, as evidenced by real-world tests and analyses [1][2][3][4]. This study employs Adams simulation to investigate the lifespan of support bearings at varying distances between them.…”

Numerical Analysis and Demonstration: Transmission Shaft Influence on Meshing Vibration in Driving and Driven Gears

“…This work focuses on the drive shaft-rear axle main reducer and gear [5,6] system of the vehicle, creates a torsional vibration model, and solves its equations by the lumped mass method. Influences of transmission shaft angle and intermediate support stiffness on the meshing vibration of both driving and driven gears are studied [7,8], and the installation angle and intermediate support stiffness are quantified.…”

A Study on Effects of Gear Backlash on Differential Vibration

“…In order to make the acceleration process smoother, set time function of the speed in ADAMS as STEP (TIME, 0, 0, 0.2, 3600d). Two groups of load torque of 2.5×10 5 N• mm were respectively applied to half axle gear 1 and half axle gear 2 [5][6] .…”

“…Set the time function as STEP (TIME, 0, 0, 0.2, 200d). Two groups of load torque of 2.5×10 5 N•mm were respectively applied to half axle gear 1 and half axle gear 2 [5][6] . A load torque of 2.5×10 5 N•mm was applied to half axle gear 1 [5][6] .…”

“…Two groups of load torque of 2.5×10 5 N•mm were respectively applied to half axle gear 1 and half axle gear 2 [5][6] . A load torque of 2.5×10 5 N•mm was applied to half axle gear 1 [5][6] . Under this condition, an additional internal friction torque should be added on the planetary gears.…”