First, cut the outer ring of the optimized GEZ101ES radial spherical plain bearing sample into two pieces with a center angle of 170. The bearing shell is fixed to the shaft connected with the friction and wear tester. 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-based grease lubrication, the friction coefficient is measured under different positive pressure conditions. First load the positive pressure to 150 kN, measure the corresponding friction coefficient, and then load the positive pressure 250 kN, 357 kN, 500 kN, and 607 kN in turn to determine the corresponding friction coefficient. A total of 19 sets of friction coefficients under different positive pressure conditions were measured, and the average value of the friction coefficients under different positive pressure conditions was taken as the basis for the design, calculation and use of joint bearings. Since the frictional force during the swinging process of the friction and wear tester is related to the swing angle, from a tribological point of view, as long as it can pass the position of the maximum frictional force when swinging, it must be able to pass other positions. In view of this, we measured the maximum friction force and converted it into the friction coefficient to obtain the maximum friction coefficient. Secondly, we use GEZ101ES joint bearing specimens before and after optimization to carry out a wear comparison test. The test conditions are: positive pressure 607 kN, swing frequency 0.12 Hz, swing angle ±30. , Swing near 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℃, inner ring or outer ring wear ≥150 m, or ferrule burn, shall be used as the basis for judging wear failure. No ring burn was found during all the tests. The temperature rise of the test piece after 12 hours of continuous abrasion test did not exceed 40℃, so 150 m of abrasion was used as the criterion for the termination of the test. Use a digital thermometer to monitor the temperature of the bearing. Use a dial indicator to measure the thickness of the outer ring of the bearing every 4-6 hours during the wear test. 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. The thickness measured after the test. A scanning electron microscope (SEM) was used to observe the wear surface morphology of the outer ring of the GEZ101ES joint bearing. The results and analysis of the Journal of Tribology It can be seen that 0¨u lIna LJ-k Fig. 4 Relationship between GEl01ES positive pressure and friction coefficient Fig. 4 Relationship between frictior, coeKicient and normal load for GEL0IES GEZ101ES joint support has little change in friction coefficient before and after optimization. Under the condition of regular lubrication, when the positive pressure is in the range of 150～607 kN. The corresponding friction coefficient is 0.089~0.067, and the friction coefficient decreases with the increase of positive pressure, which conforms to the normal law of friction loss. Wear performance Figure 5 shows the wear depth of spherical bearing before and after optimization. Sliding dista rwe ring 5 The relationship curve of the wear curve depth of the joint support with the change of the wear stroke. visible. When the bearing capacity is 607 kN and the wear of the outer ring is 150 m, the wear of the two outer rings of the bearing is similar. The unoptimized joint bearing wear stroke is 13 847 1TI, and the optimized joint bearing meal loss stroke is 15 760 m. At the same time, under proper lubrication conditions, the temperature rise of the bearing during continuous wear does not change much. Generally, the temperature rise is only 30°C for 12 hours of continuous operation (the room temperature is 5 to 1 ℃ in volume 24). The measured friction coefficient is about 0.070, indicating that the friction coefficient of the Lou bearing is relatively stable. 2.3 Wear surface morphology Figure 6 shows the SEM photo of the wear surface morphology of the outer ring of the bearing. F 6 SEM images 0f wDrn su rface of GEZ101ES (500×) Fig. 5 GEZ101ES worn surface SEM fuselage (×500) shows that there are pitting pits on the surface. Based on this, it can be inferred that under the swing bar, the joint bearing The damage is mainly caused by the surface fatigue and wear. Conclusion The maximum energy error of the corresponding finite element analysis is 7.5, indicating that the selected grid accuracy meets the requirements. The result is reliable. b. The stress on the optimized joint bearing is the same as before. Compared with the reduction of 29.2.c. The friction coefficient of the joint sleeve bearing before and after optimization has no significant change, but the wear life after optimization is significantly improved compared with that before optimization. The corresponding calculation and test results are consistent.