Abstract
Mechanical model with detailed design parameters of a rotor slewing bearing with the structure type of double-row tapered roller for supporting the rotor of the wind turbine was presented. The internal geometrical relationships of the rotor slewing bearing were established in the Cartesian coordinate system. The elastic contact deformations between each tapered roller and the raceways were expressed through the geometrical transformation. The mechanical model was established using the equilibrium relations in the rotor slewing bearing. The safety factor and the fatigue life which represents, respectively, the ability of resisting the rolling contact plastic deformation failure and the rolling contact fatigue failure of the rotor slewing bearing were obtained based on the solution of the mechanical model. Effects of the detailed design parameters such as axial clearance, contact angle, and roller semi-cone angle on the carrying capacity of the rotor slewing bearing were analyzed. The results show that right amount of small negative axial clearance, increase in contact angle, and decrease in roller semi-cone angle are advantageous for enhancing the carrying capacity of the rotor slewing bearing. This provides the basis for the reasonable value selection of the design parameters of the double-row tapered roller slewing bearing for supporting the rotor of the wind turbine.
Highlights
In recent years, utilization of renewable energy represented by wind power by countries around the world reached a climax
As the contact angle increases from 40° to 60°, the safety factor and the fatigue life of the rotor slewing bearing increase with it
The internal geometrical relationships of a rotor slewing bearing in wind turbine were described in Cartesian coordinate system; this is different from the traditional description of internal geometrical relationships of the slewing bearing in the polar coordinates
Summary
Utilization of renewable energy represented by wind power by countries around the world reached a climax. Before the rotor slewing bearing being loaded, the distances between the center points of the inner raceway and the outer raceway at the arbitrary roller azimuth angle c are qffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi A1, c = (x1i, c À x1e, c)2 + (y1i, c À y1e, c)2 + (z1i, c À z1e, c)[2]
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