S High Speed Punch To Study The Dynamic Precision Compensation Of Dynamic Balance Design And Bottom Dead Center

With the increasing of the speed or the SPM of high-speed presses and demanding on quality of stampings, the study of dynamic balancing and dynamic precision for high-speed presses is increasingly important. In this paper, a multi-link high-speed press is studied on dynamic balancing and the dynamic precision of the bottom dead centre.When the dynamic balancing of the multi-link high-speed press is designed, the kinematics and dynamics are discussed respectively to simplify the problem and weaken the coupling parameters. Firstly, Kinematic equations are established of each part. Based on this, the problems concerned with the set-up and optimization of the kinematics parameters of each component of the press is discussed, if the shortest crank is chosen as the target. Then, on the basis of the optimization of the kinematics parameters, dynamic equations and supplement equation are established of each component. The mechanical property of each component and the structural parameters are got. Secondly, a synthetic optimization model of dynamic balancing was proposed to reduce shaking force and shaking moment of high-speed press, and the counterweight’s masses are designed. Besides that, by using the Lagrange Equation,1-Dof equivalent rotary inertia on the fluctuation of crank rotational velocity. The fluctuation of crank rotational velocity is reduced by designing a flywheel.To get the control model, that is the relational function of the error of the bottom dead center and distance of the compensation, the kinematics calibration model of the press is set up. The parameter identification model of the mechanism of the pres is built based on least square method to get the parameters of the the mechanism of the high-speed press.The CAD model of each part and whole body of the press were established according to the SOLIDWORKS platform. The simulation of the motion of the calculated model and the control model is carried out. The kinematics states and the figures of the compensation is presented. The result of kinematic analysis and the control model are proved.