Rolling and sliding velocities of a hypoid gear set along the path of contact

The crowning seen in the ease-off results in the contact zone is located within the boundaries of the gear tooth. A less tooth contact area generally results from large amounts in the ease-off and graph motion and vice versa. Figure 4 shows 20 potential contact lines isolated, their individual crowning amounts along their length (touch-scan line). Can the gap geometry towards touch-line impact of changing ease-off topography, and maximize on the cases kinematic gap (see also “General Explanation Theoretical Analysis Bevel Gear”).

The geometry does not gap direction perpendicular to the line of contact (not exactly the same path of contact direction) depends largely on the ease-off topography but mostly more of the geometry of the mating tooth profiles. Hypoid gears typical for the lubrication gap is changed from contact line to connect online. Effects are similar to those discussed in the 5 and 6 cases likely to be applicable in hypoid gears and can also be controlled to some extent in hypoid easy-off developments. Figure 5 shows the sliding- and rollingvelocity vectors of typical hypoid gear set for each path point-of-contact for the panel discussed 20 jobs; Each vector is projected to the plane tangential to the point – the vector initiatives. The velocity vectors to draw inside the projection plane gear tooth.

The points of origin vectors rolling- and sliding velocity grouping the path-of-contact, which is available as the connection of the minima of the individual lines in the graphic touch-scan line (Fig. 4). The vectors can be separated velocity jointly towards the touch-line and vertical component to that in order to investigate the hydrodynamic lubrication properties by applying the information from the touch-line scan (curvature and curvature change) and the tooth surface curvatures direction perpendicular to the contact-line (see also “General Explanation Bevel Gear Theoretical Analysis,” Figure 8, 1-6 cases). For the hypoid gear sets discussed, the sliding velocity vectors to lengthoriented due to the high screw motion component. In the top field (top left) the vectors point slides to the left and slightly up (drive pinion gear on the drive-side). Moving along the path-of-contact from bottom to top (from left to right, Figure 5), reduces the sliding velocity component profile and long reach single amount on the line oriented park.

Beneath the park line develops the sliding velocity component positive profile. The maximum amount of the sliding velocities depending on the online site of the park in the direction of the profile at one extreme ends of the path of contact (top heel or toe root). The top-line oriented park in this example as a result of the largest sliding velocities in the root area. The rolling vectors point down and right and are basically all the same direction. The small change in orientation leads to the spiral angle that changes along the face width. The shrinking size of the rolling velocity (moving from heel to toe-top-up) caused by the reduced circumferential speed toward the inner diameter. It thus becomes clear that complex and evaluate velocity gap in the area of ​​discrete points, and considering the two main curvature directions, important in order hypoid equipment reliable results for achieving lubrication mechanics.

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