With the development of high-speed, low-friction, and light-weight rotating parts of power and transmission systems, the slipping problem of high-speed ball bearings has attracted more and more attention. Slippage causes frictional heating and wear, which can lead to bearing damage and premature failure. The theory, mechanism, experimental research progress, influencing factors and the determination of bearing preload to prevent slipping are systematically reviewed, and the influence of the current research on the viscous resistance of the lubricant, the impact of the ball and the raceway under the combined load is pointed out. Due to the lack of research on slippage and slippage measurement under time-varying conditions, future research directions should focus on slippage mechanism and experimental research considering actual lubrication and special operating conditions, as well as preload optimization combined with bearing operating conditions. With the improvement of the efficiency requirements of the power system and transmission system in the fields of aerospace, high-speed precision machine tools, and new energy vehicles, the requirements for the bearing speed and life of the host are also getting higher and higher. In high-speed ball bearings, the relative sliding between the ball and the raceway and the stability of the cage are important factors that affect the dynamic performance and working life of the bearing, and are also the hotspot and difficulty in the research of high-speed ball bearings. 1. Ball bearing slip mode Angular contact ball bearing balls run on the channel differential sliding, spin sliding and gyroscopic sliding. The angular velocity vector of the ball in the azimuth coordinate system is shown in Figure 1. In the figure: Oixiyizi is the inertial coordinate system; Obxbybzb is the azimuth coordinate system of the ball; Ob is located at the geometric center of the ball and rotates with the center of the ball; the xb axis is along the axial direction of the bearing; the zb axis is always radially outward of the bearing; αi, αe are the contact angles between the ball and the inner and outer rings, respectively; Ψ is the azimuth angle of the ball; ωb is the rotation angular velocity of the ball; ωbx, ωby, ωbz are the rotation angular velocity of the ball in the azimuth The velocity component in the coordinate system; ωby is the gyro sliding velocity component; ωbx, ωbz and the ferrule angular velocity in the contact coordinate system between the ball and the inner and outer channels can be decomposed into the spin sliding perpendicular to the contact surface (ωse, ωsi) and The pure scroll velocity component along the scroll direction. Fig.1 Diagram of angular velocity vector of ball in an angular contact ball bearing Under high-speed conditions, the centrifugal force and gyroscopic moment increase significantly, and the motion of the ball is more complicated. The slip of the ball bearing is divided into the following 4 modes: 1) Gyroscopic slip. When the rotation axis of the ball is not parallel to the revolution axis, a gyroscopic moment will be generated. When the frictional moment provided by the contact area of ​​the inner and outer rings is less than the gyroscopic moment, the ball will produce gyroscopic sliding. Gyroscopic sliding is the overall sliding of the ball relative to the inner and outer channels, and its direction is perpendicular to the rolling direction, that is, along the long axis of the contact ellipse. In the quasi-static model, gyroscopic slip is usually suppressed, whereas in the dynamical view, gyroscopic slip is unavoidable. 2) Drag and slide. Under the action of centrifugal force, the contact load between the ball and the inner ring is reduced, and the ball even separates from the inner ring, resulting in a reduction in the drag force between the ball and the inner ring. When there is resistance, the ball will drag and slide on the inner ring channel. The drag sliding is the overall sliding of the ball relative to the inner ring channel, and its direction is along the direction of the minor axis of the contact ellipse. 3) Scroll and slide. During the operation of the bearing, due to the change of the contact angle or drag coefficient of the ball at different angular positions, the speed component of the ball spin or gyroscopic motion increases, while the rotational speed component parallel to the rolling direction decreases, resulting in a decrease in the ball's revolution speed. 4) Momentary sliding. Under the combined load condition or variable speed condition, the sudden change of the contact load or drag force between the ball and the raceway, and the impact collision between the ball and the cage lead to the instantaneous sliding of the ball on the raceway. Influenced by parameters such as geometry, lubrication, and working conditions during the actual operation of the bearing, there are often several sliding modes between the ball and the raceway at the same time. The shearing of the oil film caused by the ball slipping on the channel generates a large amount of frictional heat, and due to the increase in oil temperature, the viscosity of the lubricating oil and the thickness of the oil film decrease, which may lead to metal contact, which may cause scratches or wear on the channel and lead to bearing accuracy. Reduce or fail early, and even cause the host to freeze.