Analysis of bearing stiffness variations, contact forces and vibrations in radially loaded double row rolling element bearings with raceway defects

An extensive review of vibration modelling of rolling element bearings with localised and extended defects

“…In order to present a review of the nonlinear multi-body dynamic analytical models [53][54][55][56][57][58][59][60][61][62][63][64][65][66][67][68][69] for predicting 297 the vibration response of rolling element bearings having localised defects, the models are segregated into 298 three categories based on the characteristic shape of the defects being considered: 299 1. Point spall [53,56,57,59,61,62] 2.…”

“…Circular and elliptical spall [60,64,66] 3. Line (rectangular) spall [54,55,58,63,65,[67][68][69] 303 Building on the 2-DOF model of Fukata et al [40], Feng et al [53] presented a 4-DOF model corre- 304 sponding to the two translational degrees of freedom, in the radial plane, each for the two lumped masses: 305 the rotor and pedestal masses. No other component was included in the model except the outer ring, which 306 was assumed to be stationary and rigidly connected to the pedestal.…”

“…Extending the work of Sawalhi et al [58,80], in 2014, Petersen et al [68] reported on the development of 503 an analytical multi-body dynamic model to predict the vibration response of a bearing having raceway defects 504 that include line and extended spalls. Most of the assumptions considered in the model [68] are similar to 505 those in references [58,80]; however, a few modifications were made to the model to improve the prediction 506 of the vibration response of the bearing.…”

“…Most of the assumptions considered in the model [68] are similar to 505 those in references [58,80]; however, a few modifications were made to the model to improve the prediction 506 of the vibration response of the bearing. Compared to a single resonance-changer in the earlier model 507 [58] that predicts a high-frequency response of the bearing in one radial direction only (global Cartesian 508 y-direction), an additional mass-spring-damper system attached to the outer raceway was incorporated in 509 the model presented in reference [68] to enable predicting the resonant response in x-and y-directions. The 510 global damping included in the model by Sawalhi et al [58] via a viscous damper attached to the inner 511 ring was replaced by lubrication film damping at the rolling element-to-raceway contact interfaces in the 512 model by Petersen et al [68].…”

“…Compared to a single resonance-changer in the earlier model 507 [58] that predicts a high-frequency response of the bearing in one radial direction only (global Cartesian 508 y-direction), an additional mass-spring-damper system attached to the outer raceway was incorporated in 509 the model presented in reference [68] to enable predicting the resonant response in x-and y-directions. The 510 global damping included in the model by Sawalhi et al [58] via a viscous damper attached to the inner 511 ring was replaced by lubrication film damping at the rolling element-to-raceway contact interfaces in the 512 model by Petersen et al [68]. The model [68] also presents an extension of the previously developed model 513 of a defective single-row bearing [58,80] to a double-row bearing.…”