For involute spur fixed-drive and planetary gear drive respectively, a nonlinear dynamic model of yaw-torsion coupling was established by Lagrange method, in which the plane force system acting between gear pairs along the meshing surface was equivalent to meshing force and offset load torque.
In the past, gear meshing models used to calculate dynamic meshing force generally neglected the influence of actual gear movement on meshing parameters such as tooth side clearance and meshing rigidity.Among them, the backlash of tooth side is mostly fixed value, and meshing stiffness is obtained by quasi-static method and presents periodic time-varying characteristics.In actual gear transmission, the meshing parameters such as tooth side clearance and meshing rigidity are affected by the gear movement state.For example, the change of center distance will cause the dynamic change of tooth side clearance, while the change of speed, center distance and meshing state of tooth surface and back will cause the position change of meshing point, thus causing the dynamic change of meshing rigidity.
Non-linear dynamic meshing model is put forward for involute spur fixed-shaft gear drive and planetary gear drive respectively. The model takes into account the influence of center distance change on tooth side clearance and the influence of tooth profile modification, speed change, center distance change, tooth surface and back meshing state change on meshing rigidity.
The non-linear dynamic engagement model can be used to realize feedback calculation with the yaw-torsion coupling non-linear dynamic model of gear transmission established in Chapter 2. It can be used to analyze the coupling effect between dynamic changes of engagement parameters and vibration response during gear transmission.