Given the distortions mentioned systems tapereddepth tooth flanks feel compared to conjugate coupling, can define a possible contact lines would apply where the distortions removed or where load-bearing deflections allow for the spread of contact. In order to allow for deflection of tooth surfaces, shafts, bearings and gear box housing without unwanted edge contact is face width and direction crowning application profile. Tooth contact analysis is theoretical (TCA) before the appliance manufacturing to do to look at the effect of the crowning in connection with the basic characteristic of the particular gear set.
This also allows the possibility of returning to the basic features to optimize them if analysis results show any deficiencies. Figure 3 shows the result of TCA of typical hypoid gear sets. Represents the two columns in Figure 3 the results of analysis on both sides coupling combinations (see also “General Explanation Theoretical Analysis Bevel Gear”). The use of the drive-side guide transmission main burden for hypoid gears in place a binding rule. Transmission torque and speed and all the forces as a result of additional slides on a coast-side deflection pinion toward the ring gear, which reduces the backlash in extreme cases to zero.
This situation occurs already under moderate load and interrupts any lubrication that results in surface damages and may be followed by breaking a tooth. The graphics show the topographies easy tip-off. Shows the surface over the grid at the consolidation of the pinion and gear crowning. These easy-offs in Figure 3 mixture of crowning length, profile crowning and twist side, and as a result of clearance along the boundary of the teeth being established. Beneath all easy-off, the transmission graphs offer the unique pair mating side shown. The graphs show the motion transmission angular change the pinion gear driven for that rotates with constant angular velocity. The graphs for the rotation and mesh of three consecutive pairs of teeth.
While the ease-off requires a sufficient amount of crowning in order to prevent edge contact and allow for load-bearing deflections, causing the crowning turn angular motion diversity proportionate amounts of about 50 micro radians in this example. This value is a measure for the affected tooth mesh as well as noise emission. At the bottom of Figure 3, tooth contact pattern is plotted inside of the gear tooth projection. The contact patterns are calculated for zero load and marking film-virtual merger of 6 m thickness. This basically doubled the tooth contact one could look real rolling version of the gear set under light load analysis on roll tester, although the gear member layer coated with com-pound mark. The lines on the angle of contact with the face width direction, depending essentially on the spiral angle. The contact path connects the beginning and end of the meshing. Its orientation is nearly perpendicular to the contact lines.