Thermal Analysis And Experimental Research Of Woven Liner Spherical Plain Bearing

By taking GE20ET-2RS woven liner spherical plain bearing as the research object, static thermal elastic model and thermal-mechanical coupled model of woven liner spherical plain bearing were built by ABAQUS simulation software. Distribution and transmission rule about friction temperature on the contact surface were analyzed, and the influence of friction heat on the deformation and stress of the spherical plain bearing was discussed. Liner and inner maximum heat flow is 50 k W and 550 k W respectively, in the static thermal elastic model, in the condition of the maximum temperature on contact center surface is 50 oC. The heat inner ring transfer accounts for 90% of that the total model transfer. The inner ring transfers heat obviously at the position of 1mm deep on the inner surface compare with others. Liner heat flow distribution is relatively smooth, and the maximum heat flow on the contact center. The two parts of liner and inner ring have heat flow on the half up circle(between contact area).Because of the thermal stress, inner ring stress distribution is uniform when the contact center temperature range 50 oC to 90 oC compare with the normal temperature. It makes the inner ring has minor contact stress under the same load capacity and has well mechanical properties. At the temperature range, spherical plain bearing has longer and more smoothly service time. When contact center surface temperature is higher than 100 oC, however, caused by the temperature and stress deformation on the inner ring surface, it makes the surface abnormalities and no longer smooth. Accelerated liner wear, eventually leading to spherical plain bearing failure.Assembly clearance value is changed by change the size of the ball size for the inner ring in the model. Contact stress between the contact pair of woven liner spherical plain bearing is analyzed by simulation. It is concluded that, at the clearance of 100 um, inner ring maximum stress of woven liner spherical plain bearing is smaller than other clearance. The location of maximum stress is inside of the inner ring, and has the strongest load capacity at the clearance of 100 um.Maximum heat flow reach 63.04 k W about liner surface under 35 k N radial force and in the progress of rotary oscillation, and it is located on the contact center surface. Inner ring maximum heat flow is 200.9k W on the location of the contact surface adjacent liner face. Between friction surface heat transfer direction is all along the contact surface normal direction to the internal. Liner maximum heat flow and the inner ring are 200.9 k W and 63 k W respectively in axis direction. The maximum heat flow reaches 63 k W and 180 k W respectively along the circumferential direction. Because of lowing thermal conductivity about liner materials, the heat generated by the friction passed on to the liner is less than the bearing steel. The liner transfer heat is equal to 30% of the heat inner ring transfer. The liner maximum temperature rise reach 27.12 oC, less than inner ring temperature rise 37.65 oC. Both two parts of maximum temperature rise are at their contact centre interface. In the depth direction, the overall difference in temperature of inner ring at about 6.65 oC. In the case with frictional heat, the Mises stress of liner is greater than the Mises stress absence of friction heat, the equivalent stress of joint bearing inner ring in all directions is smaller. Maximum equivalent stress of inner ring is inside of bearing inner ring, located in the depth of the friction surface 3mm distance.Spherical plain bearing friction temperature test was implemented by using spherical plain bearing life test machine. The friction temperature variation tendency when working was measured. The friction temperature rise increased dramatically within 30 minutes at the beginning of the test. It keeps stable after 30 minutes until the end of the test. The liner contact wear region distribution is close to the simulation stress distribution, compared with test and simulation. The point friction temperature rise and the temperature distribution curve by experiment measuring are close to the simulation. The temperature rise of the contact edge is equal. A simulation result was slightly greater than the test results on the contact center. Comprehensive analysis it can be thought of that the simulation calculation results is accord with the actual situation.