The vehicle impact test is one of the most important research methods of passive safety protection technology for rail vehicles.In order to ensure the accuracy of the impact speed of the test rig,multiple tests and debugging are required.The test rig under debugging conditions needs non-destructive braking,so it is an important research content to realize the stable,non-destructive and repeated braking of the rail vehicle test rig within a limited installation distance.In this paper,combined with the friction energy absorption method,a two-stage tensile composite friction braking scheme and a design method of main parameters are proposed,the corresponding braking device is developed,and the non-destructive braking test is carried out for the rail vehicle crash test rig.The two-stage tensile compound friction braking device is composed of two-stage friction pairs,movable guide rails,fixed guide rails,disc springs,and preloaded bolts.The theoretical derivation of the motion process of the braking scheme is carried out,and the dynamic theoretical model of the two-stage friction pair exists at the same time and the twostage friction pair exists in sequence is obtained.Further analysis was carried out to obtain the value range of the braking force of the driving trolley and the impact trolley under the working condition of 30 m/s.The overall structure of the two-stage tensile composite friction braking device is designed,and two ways of realizing positive pressure are determined:the interference fit between the movable guide rail and the impact shoe,and the compression of the disc spring.The two realization methods are analyzed and studied,and the mechanical relationship between them is obtained.A finite element model is established,and the rationality of the finite element model and the reliability of the simulation results are verified through experiments;the influencing factors of the dynamic response of the braking process of the train crash test rig are studied by the simulation analysis method,and the pre-compression of the disc spring is obtained.The relationship between the amount of interference between the impact shoe and the movable guide rail and the braking response characteristics.After further analysis,the optimal parameter matching of the braking device of the driving trolley and the impacting trolley was obtained: the single-side interference of the braking device of the driving trolley was 0.8mm,the compression amount of the disc spring was 1.1 mm,and the braking device of the impacting trolley was 0.8 mm.The interference on one side is 3 mm,and the compression of the disc spring is 2.3 mm.83 Figures,7 Tables,90 References... |