First, cut the outer ring of the GEZ101ES radial spherical plain bearing sample before and after optimization into two pieces with a central angle of 170. The bearing shell is fixed on the shaft connected with the friction and wear testing machine. The friction and wear test was carried out using the bearing friction and wear testing machine developed by Nanjing University of Aeronautics and Astronautics (see Figure 3). First, the frequency is 0.12 Hz and the swing angle is 30. , MoS lithium grease lubrication, the friction coefficient was measured under different positive pressure conditions. First, the positive pressure was loaded to 150 kN, and the corresponding friction coefficient was measured. Then, the positive pressure was loaded at 250 kN, 357 kN, 500 kN, and 607 kN in turn, and the corresponding friction coefficient was measured. A total of 19 groups of friction coefficients under different positive pressure conditions were measured, and the average value of friction coefficients under different positive pressure conditions was taken as the basis for the design, calculation and use of spherical plain bearings. Since the frictional force in the swinging process of the friction and wear testing machine is related to the swinging angle, from the tribological point of view, as long as the swinging can pass through the position of the maximum frictional force, it must be able to pass through other positions. In view of this, we measure the maximum friction force and convert it into the friction coefficient, that is, the maximum friction coefficient is obtained. Secondly, we use the GEZ101ES spherical plain bearing specimens before and after optimization to conduct a wear comparison test. The test conditions are: positive pressure of 607 kN, swing frequency of 0.12 Hz, and swing angle of 30. , swing around the contact point of the inner and outer rings of the bearing. It is stipulated that one of three conditions, such as temperature rise ≥ 150 ℃, wear amount of inner ring or outer ring ≥ 150 m, or ferrule burn, shall be used as the basis for judging wear failure. No ferrule burn was found in the whole test process, and the temperature rise of the specimen did not exceed 40℃ after 12 hours of continuous wear test. Therefore, the wear amount of 150 m was used as the basis for judging the termination of the test. Use a digital thermometer to monitor the temperature of the bearing, and use a dial gauge to measure the thickness of the outer ring of the bearing every 4 to 6 hours during the wear test, and use a micrometer to measure the ball diameter of the inner ring of the bearing. The wear thickness is equal to the initial thickness minus the wear. Thickness measured after the test. Scanning electron microscope (SEM) was used to observe the wear surface morphology of the outer ring of GEZ101ES spherical plain bearing, and the results and analysis of Acta Tribology. It can be seen that the friction coefficient of GEZ101ES joint support before and after optimization does not change much. Under regular lubrication conditions, when the positive pressure is in the range of 150 to 607 kN. The corresponding friction coefficient is 0.089~0.067, and the friction coefficient decreases with the increase of positive pressure, which is in line with the normal law of friction and separation. Wear performance Figure 5 shows the wear of GEZ1 01ES spherical bearing before and after optimization. Figure 5 Wear depth of spherical bearing: s. The relationship curve of wear curve depth of sliding dista rwe ring 5 joint auxiliary bearing with the change of wear stroke. visible. When the bearing capacity is 607 kN and the wear amount of the outer ring is 150 m, the wear amount of the two outer rings of the bearing is similar. The wear stroke of the unoptimized spherical plain bearing is 1 3 847 1TI, while that of the optimized spherical plain bearing is 15 760 m. At the same time, under proper lubrication conditions, the temperature rise of the bearing does not change much during the continuous wear process. Generally, the temperature rise of the bearing is less than 30°C for 12 hours of continuous operation (room temperature is 5-1 ℃ in volume 24). The measured friction coefficient is about 0.070, indicating that the friction coefficient of the bearing is relatively stable. 2.3 Wear surface morphology Figure 6 shows the SEM photo of the bearing outer ring wear surface morphology. F 6 SEM images 0f wDrn su rface of GEZ101ES (500 ] Fig. 5 The worn surface morphology of GEZ101ES SEM film (500) shows that there are pitting pits on the surface. It can be speculated that under the swing bar, the main damage of the joint bearing is It is caused by surface fatigue and wear. Conclusion The maximum energy error of the corresponding finite element analysis is 7.5, indicating that the selected homogeneity accuracy meets the requirements. The result is reliable. b. The stress on the optimized spherical plain bearing is the same as before The friction coefficient of the joint sleeve before and after optimization has no significant change, but the wear life after optimization is significantly improved than that before optimization. The corresponding calculation and test results are consistent.