Computational Design of Rolling Bearings by Hung Nguyen-Schäfer

By Hung Nguyen-Schäfer

This publication comprehensively provides the computational layout of rolling bearings facing many interdisciplinary tough operating fields. They surround elastohydrodynamics (EHD), Hertzian touch conception, oil-film thickness in elastohydrodynamic lubrication (EHL), bearing dynamics, tribology of floor textures, fatigue failure mechanisms, fatigue lifetimes of rolling bearings and lubricating greases, Weibull distribution, rotor balancing, and airborne noises (NVH) within the rolling bearings. moreover, the readers are supplied with hands-on crucial formulation according to the up to date DIN ISO norms and worthy examples for computational layout of rolling bearings.

The subject matters are meant for undergraduate and graduate scholars in mechanical and fabric engineering, study scientists, and practising engineers who are looking to comprehend the interactions among those operating fields and to understand easy methods to layout the rolling bearings for car and lots of different industries.

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Extra resources for Computational Design of Rolling Bearings

Sample text

2). Contrary to the two-bearing rotor system, the rotor shaft is bent with a small deflection angles at the bearings. The bending centerline of the three-bearing rotor system is shown in Fig. 2. In this case, the computation of the bearing forces F1 a1 a2 P1 Bending centerline F2 F3 P2 Pa M1 T1 Fa M2 G x M3 Rotor Gearbox Bearing G y Bearing B Bearing A l1 Fig. 2 Computing Loads Acting upon Bearings 23 is quite complicated because the deformation of the rotor axis caused by the acting forces must be taken into account.

22, the curvature difference of the roller and inner raceway results as À 1 Á 2 2 Dw AÀ1 Fr=IR ðρÞ ¼ þ À A Á¼1 Dw D2w AÀ1 ð1:24aÞ Similarly, substituting Eqs. 21b into Eq. 2, where the parameter A is defined in Eq. 527, and α ¼ 10 . The factor A for the ball bearing is calculated using Eq. 20 as A¼ Dpw 44:6 ¼ % 4:388 Dw cos α 10:32  cos 10 Using Eqs. 5 Bearing Speeds The speed number of bearings is defined as A ¼ N Á Dpw ð1:25Þ where N is the rotor speed in rpm and Dpw is the pitch diameter in mm and A in mm/min.

Similar to Eq. 39, the operating contact angle under the combined load is calculated as [1] δa sin α0 þ ρ0 sin α ¼ rffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi     iγ cos α0 þ δr cos ρ 0 2 þ sin α0 þ ρδa 2 0 sin α0 þ ρa  qffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi ð cos α0 þ ρr cos iγ Þ2 þ ð sin α0 þ ρa Þ2 where iγ is the angular angle position of the ball i. ð2:44Þ 40 2 Design of Rolling Bearings For the sake of simplicity, the operating contact angle of the lowest position of the ball (iγ ¼ 0) is chosen for all balls in the bearing.

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