To make sure that the new incoming contacts which are the main excitation source are properly simulated, the necessary deformation of the gears is determined by using the true geometry and positions of the gears for every time step of the dynamic calculation.
The characteristic parameters of the planetary gear were determined based on the rotational speed space of the planet.
Both strength with respect to bending and contact pressure are found, and the torque transmission capacity of the gear is determined by the lower value of the two.
Dynamic behaviour of an individual draft pad and a draft gear is determined and characterized with exciting frequencies and corresponding mode shapes.
Assuming that the load capacity of a gear is determined by load capacity with respect to bending or load capacity with respect to contact pressure whichever is lower the greatest torque load capacity can be expected at α 1 = 45° for all forms in the case of flame-hardened MQ class steel.
As presented in this section, the catch composition for each gear was determined by sampling.
The failed gear was examined, the reasons for the failure were determined and preventive methods were explained.
The layout and geometry for a pair of meshing spur gears can be determined by the procedure, which assumes access to a computer aided design (CAD) drawing package.
Based on Hertz contact hypothesis, the contact region of pinion-gear teeth was determined, and the computerized simulation program for tooth contact was developed.
The correct gear selection is determined by the on-board computer which calculates the bike's speed.
