High temperature sleeve friction and wear test device

Abstract

The present application provides a high-temperature bushing friction and wear testing device. The high-temperature bushing friction and wear testing device may include a heating furnace, a rotary actuator and a radial force loading mechanism. The heating furnace is used to provide a closed high-temperature cavity, and includes a first sample opening located in the horizontal direction and a second sample opening located on the top surface. In the rotary actuator, the first sample fixture extends into the heating furnace through the first sample opening in the form of a cantilever. In the radial force loading mechanism, the linear bearing is fixedly connected to the top of the heating furnace, the adjusting plate nut is fixedly connected to the top of the linear bearing, the adjusting plate is formed into a cylindrical shape and is threadedly connected to the adjusting plate nut, the compensation spring is arranged on the top of the adjusting plate, the weight plate is arranged on the top of the compensation spring, and the weight plate is pressed on the loading shaft, so that the compression degree of the compensation spring can be adjusted by rotating the adjusting plate.

Description

Technical Field

[0001] The present invention belongs to the technical field of friction and wear testing equipment, and is used to test the friction and wear performance of a pin-bushing kinematic pair and its coating at high temperatures (e.g., up to 1100°C), and specifically relates to a high-temperature bushing friction and wear testing device. Background Art

[0002] Aeroengines contain numerous pin-bushing kinematic pairs, operating at temperatures ranging from room temperature to as high as 1100°C. These pairs can experience severe wear due to thermal-mechanical coupling. The friction and wear behavior of these kinematic pairs exhibits distinct patterns at different temperatures. Especially at high temperatures, oxidation of the structural materials used in aircraft engines can alter the friction and wear mechanisms at the kinematic pair interfaces. Therefore, experimental research is needed to investigate the friction and wear performance of these kinematic pairs at high temperatures.

[0003] Pin-bushing revolving pairs are linear contact pairs, and current standard testing machines generally use ring-block friction and wear testers. For example, Chinese patent application publication number CN108344654A discloses a ring-block friction and wear tester that achieves infinite adjustment of the loading force by adjusting the spring compression, enabling ring-block friction and wear testing under various lubrication and temperature conditions. However, the curvature radius of the block specimen in ring-block contact is infinite, resulting in a significant difference in contact stress distribution from pin-bushing contact, making it difficult to effectively simulate the friction and wear of the bushing under actual operating conditions.

[0004] Reference 1 reports on experimental research on the friction and wear properties of aviation metal fluoroplastic bushings. The experimental setup uses a bushing to connect a core shaft to a support seat. A radial load is applied to the core shaft via a loading plate, and a swing cylinder drives the core shaft back and forth, thereby measuring the friction and wear between the bushing and the core shaft. While this setup simulates the actual operating conditions of friction and wear between the shaft and bushing, it cannot measure the actual friction force and can only be used to evaluate bushing wear after multiple cycles.

[0005] Chinese patent application publication number CN118641198A discloses a multi-condition friction and wear test simulation device suitable for rotating pairs. The test device primarily consists of a rigid frame, a rotary drive actuator, a bending moment loading actuator, a heating actuator, and a radial positive pressure loading actuator. By driving a pin specimen at the end of the rotary actuator to rotate, it wears against an attached sleeve specimen under conditions of radial positive pressure, bending moment, and heating, thereby meeting the requirements of multi-condition friction and wear testing. Although the device achieves heating and temperature detection of the test specimen through a heating rod, an outer baffle, a mounting plate, and a temperature-measuring thermocouple attached to the outer surface of the sleeve specimen, the semi-open heating mechanism results in uneven temperature distribution of the test specimen. Furthermore, at high test temperatures, the temperature in the area of ​​the moment loading actuator on one side will also rise significantly. Limited by the operating temperatures of precision components such as motors and sensors, the maximum temperature that the device can heat is limited.

[0006] Chinese patent publication number CN117589622B discloses a high-temperature vacuum ring-shaft friction and wear testing system. This testing system constrains the sample position by installing a ring sleeve outside the assembled shaft sleeve sample. When the shaft sample rotates, the friction between the ring and the shaft drives the ring sleeve to rotate, which is then transmitted by the baffle to the static torque sensor for measurement. However, the friction force measured by this system is also affected by the friction between the ring sleeve and the plane bearing, and the friction between the ring sleeve and the curved loading block of the sliding bearing during the process of being transmitted from the ring-shaft contact surface to the static torque sensor, resulting in certain measurement errors. Generally speaking, the operating temperature of bearings is limited. High-temperature resistant bearings made of special materials have been reported to have an operating temperature of around 300°C. The plane bearings and sliding bearings of this testing system are both arranged in a heating furnace, which reduces the reliability and operating temperature of the device.

[0007] At present, the high-temperature friction and wear test device for the pin-bushing kinematic pair has problems such as large difference between the sample shape and the actual situation, insufficient maximum test temperature, large friction force measurement error, and insufficient device reliability.

[0008] Reference 1: Lin Jing, Zhao Yingchun. Experimental study on friction and wear properties of aviation metal fluoroplastic bushings[J]. Aviation Standardization and Quality, 2019, (05): 23-26. DOI: 10.13237 / j.cnki.asq.2019.05.005. Summary of the Invention

[0009] In order to solve or alleviate at least one of the problems mentioned in the background technology, the present application provides a high-temperature shaft sleeve friction and wear testing device.

[0010] The high-temperature sleeve friction and wear testing device provided in the embodiment of the present application includes:

[0011] A heating furnace, configured to provide a closed high-temperature cavity, the heating furnace comprising a first sample opening in a horizontal direction and a second sample opening on a top surface;

[0012] a rotary actuator comprising a first rotating shaft, a torque sensor, a second rotating shaft, and a first sample holder connected in sequence, wherein the first rotating shaft is configured to provide rotational power, and the first sample holder extends into the heating furnace through the first sample opening in the form of a cantilever;

[0013] A radial force loading mechanism includes a linear bearing, an adjusting piece nut, an adjusting piece, a compensation spring, a loading shaft, a weight disk and a second sample fixture. The linear bearing is fixedly connected to the top of the heating furnace, the adjusting piece nut is fixedly connected to the top of the linear bearing, the adjusting piece is formed into a cylindrical shape and is threadedly connected to the adjusting piece nut, the compensation spring is arranged on the top of the adjusting piece, and the weight disk is arranged on the top of the compensation spring. The weight disk is pressed onto the loading shaft so that the compression degree of the compensation spring can be adjusted by rotating the adjusting piece. One end of the loading shaft extends into the heating furnace through the linear bearing and the first sample opening, and one end of the loading shaft is also connected to the second sample fixture.

[0014] In at least one embodiment, a heat insulation sheet is installed outside the first sample opening, and the heat insulation sheet includes a heat insulation sheet opening communicating with the first sample opening, and the second rotating shaft extends into the heating furnace through the heat insulation sheet opening.

[0015] In at least one embodiment, the rotary actuator includes a transition shaft having a diameter smaller than a diameter of the second rotating shaft, one end of the transition shaft is connected to the second rotating shaft, and the other end of the transition shaft is connected to the first sample holder.

[0016] In at least one embodiment, a cooling water coil is disposed outside the second rotating shaft.

[0017] In at least one embodiment, the rotary actuator includes a motor, a reducer, and a coupling. The motor is connected to the first rotating shaft through the reducer and the coupling, and the coupling is a diaphragm coupling.

[0018] In at least one embodiment, the second specimen fixture includes a curved surface, and the second specimen for testing has a curved surface. The curved surface of the second specimen is adapted to fit against the curved surface of the second specimen fixture. The second specimen fixture is provided with a second fixture threaded hole, and the second specimen can be secured to the second specimen fixture via a fastener and the threaded hole.

[0019] In at least one embodiment, the second sample holder includes a flat surface adjacent to the arc surface in a circumferential direction. When the second sample has a flat surface, the flat surface of the second sample is adapted to fit the flat surface of the second sample holder.

[0020] In at least one embodiment, a cylindrical recess or protrusion is provided at one end of the loading shaft, and a cylindrical protrusion or recess is provided at one end of the second sample grip, and the loading shaft and the second sample grip are pluggable.

[0021] In at least one embodiment, the radial force loading mechanism also includes a weight column and a weight, the weight column is connected to the loading shaft, the axes of the weight disk, the loading shaft and the weight column coincide, the center of the weight has a hole that cooperates with the weight column, and the weight is installed on the weight disk through the weight column.

[0022] In at least one embodiment, the high-temperature bushing friction and wear testing device further includes a horizontal displacement mechanism, which is configured to drive the rotary actuator to horizontally displace and enable the first sample fixture to enter and exit the heating furnace through the first sample opening.

[0023] This application directly places the torque sensor between the first and second rotating shafts. This shortens the torque transmission path between the torque sensor and the specimen, reduces friction loss, and improves reliability. The rotary actuator extends the first specimen fixture into the heating furnace in the form of a cantilever. This cantilever configuration facilitates interaction with the radial force loading mechanism, enabling the loading direction of the radial force loading mechanism to be perpendicular to the rotational direction of the cantilever, effectively enabling the radial force loading mechanism to be applied. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 An axonometric view of a high-temperature shaft sleeve friction and wear device according to an embodiment of the present application is shown.

[0025] Figure 2 A cross-sectional view of a high-temperature shaft sleeve friction and wear device according to an embodiment of the present application is shown.

[0026] Figure 3 Shown Figure 2 A partial enlarged view of the sample location.

[0027] Figure 4 Shown Figure 2 A partial enlarged view of the location of the radial force loading mechanism.

[0028] Figure 5 FIG1 shows an isometric view of a second sample holder of a high-temperature bushing friction and wear apparatus according to an embodiment of the present application.

[0029] Description of Reference Numerals

[0030] 100 Heating Furnace

[0031] 110 First sample opening

[0032] 120 Second sample opening

[0033] 130 thermal insulation sheet

[0034] 140 Heating furnace upper plate

[0035] 150 furnace body

[0036] 160 furnace door

[0037] 170 Thermocouple

[0038] 200 Rotary Actuator

[0039] 201 First Rotating Axis

[0040] 202 Torque Sensor

[0041] 203 Second Rotating Axis

[0042] 204 First specimen fixture

[0043] 210 transition shaft

[0044] 220 cooling water coil

[0045] 231 Motor

[0046] 232 reducer

[0047] 233 Coupling

[0048] 234 motor bracket

[0049] 241 bearings

[0050] 242 bearing spacer

[0051] 300 Radial force loading mechanism

[0052] 301 linear bearings

[0053] 302 Adjustment plate nut

[0054] 303 Adjustment Plate

[0055] 304 compensation spring

[0056] 305 Loading Shaft

[0057] 3051 Depression

[0058] 306 weight plate

[0059] 307 Second sample fixture

[0060] 3071 Camber

[0061] 3072 Second clamp threaded hole

[0062] 3073 Plane

[0063] 3074 protrusion

[0064] 310 weight column

[0065] 320 weights

[0066] 400 horizontal displacement mechanism

[0067] 401 Workbench

[0068] 402 rigid bracket

[0069] 403 bracket upper plate

[0070] 404 linear guide

[0071] 405 Slider

[0072] 406 Slide

[0073] 407 Support Column

[0074] 408 support plate

[0075] 510 First Sample

[0076] 520 Second Sample DETAILED DESCRIPTION

[0077] The following describes exemplary embodiments of the present application with reference to the accompanying drawings. It should be understood that these specific descriptions are only used to teach those skilled in the art how to implement the present application, and are not intended to exhaust all possible embodiments of the present application, nor to limit the scope of the present application.

[0078] The present invention provides a high-temperature sleeve friction and wear test device (hereinafter sometimes referred to as "test device"). It should be understood that the test device can be applied to high temperatures (eg, about 1100°C) or any temperature condition from room temperature to high temperature.

[0079] "Shaft sleeve" should be understood as a shaft and a sleeve, that is, the first specimen used for the test can be a pin, and the second specimen can be a bushing. Of course, the first and second specimens can also be various parts that meet the characteristics of the shaft and sleeve.

[0080] See also Figure 1The sample device may include a heating furnace 100 , a horizontal displacement mechanism 400 , a rotation actuator 200 and a radial force loading mechanism 300 .

[0081] Heating furnace 100

[0082] See also Figure 2 The heating furnace 100 is used to provide a closed high-temperature cavity. The heating furnace 100 may include a furnace body 150 , a furnace door 160 , a heat insulating sheet 130 , a heating furnace upper plate 140 and a thermocouple 170 .

[0083] A furnace door 160 may be provided on one horizontal side of the furnace body 150 and hinged to the furnace body 150. Self-locking buckles may be provided at the four corners of the furnace door 160 to facilitate locking the furnace door 160 to the furnace body 150. The furnace door 160 may be provided with a first sample opening 110 for inserting the first sample 510 into the heating furnace 100.

[0084] A second sample opening 120 may be provided on the top surface of the furnace body 150 for the second sample 520 to pass through.

[0085] Depending on the test requirements, the temperature inside the furnace may be higher, and heat may diffuse outward through the first sample opening 110. Threaded holes can be provided around the first sample opening 110 to secure the thermal insulation sheet 130. The thermal insulation sheet 130 includes an opening that communicates with the first sample opening 110, through which the second rotating shaft 203 extends into the heating furnace 100. The thermal insulation sheet 130 can be made of materials such as alumina ceramic or biotite, providing excellent thermal insulation.

[0086] The heating furnace 100 further includes a heating furnace upper plate 140 , and the linear bearing 301 is fixed to the heating furnace upper plate 140 . The heating furnace upper plate 140 is disposed on the top of the heating furnace 100 .

[0087] Thermocouple 170 may extend into heating furnace 100 from the side wall opposite to furnace door 160 to monitor the temperature inside the furnace.

[0088] Horizontal displacement mechanism 400

[0089] See also Figure 1 、 Figure 2 The horizontal displacement mechanism 400 may include a workbench 401, a rigid bracket 402, a bracket upper plate 403, a linear guide rail 404, a slider 405, a slide 406, a support column 407 and a support plate 408.

[0090] The workbench 401 has threaded holes on its upper surface for securing the rigid bracket 402. The rigid bracket 402 also has threaded holes for securing the bracket upper plate 403, allowing the linear guide 404 to have a certain height to match the position of the heating furnace 100. The bracket upper plate 403 also has threaded holes for securing the linear guide 404. The slider 405, which has built-in ball bearings and can move horizontally on the linear guide 404, is threadedly connected to the slide 406, support column 407, and support plate 408. The support plate 408 has threaded holes for securing the rotary actuator 200. The support column 407 ensures that the rotary actuator 200 has a certain height to match the position of the first specimen opening 110.

[0091] Rotary actuator 200

[0092] See also Figures 1 to 3 The rotary actuator 200 may include a motor 231 , a reducer 232 , a coupling 233 , a motor bracket 234 , a first rotating shaft 201 , a torque sensor 202 , a second rotating shaft 203 , a cooling water coil 220 , a transition shaft 210 , a first sample holder 204 , a bearing 241 and a bearing pad 242 .

[0093] The motor 231 can be a servo motor, the reducer 232 can be a planetary reducer, and the coupling 233 can be a diaphragm coupling. The motor 231 and reducer 232 can be connected to a motor bracket 234, which can be connected to the support plate 408. The output shaft of the reducer 232 is connected to the first rotating shaft 201 via the coupling 233.

[0094] The first rotating shaft 201 can be secured to the torque sensor 202 via a threaded flange, and the torque sensor 202 can be secured to the second rotating shaft 203 via a threaded flange. The second rotating shaft 203 passes through a bearing 241 (e.g., a seated outer spherical bearing), which can be threadedly connected to the support plate 408 via a bearing spacer 242. A cooling water coil 220 can be positioned outside the first rotating shaft 201 to cool the shaft by supplying cooling water.

[0095] The end of the second rotating shaft 203 ( Figure 2 The first sample holder 204 has a threaded hole at its right end for mechanically mating with the transition shaft 210. One end of the first sample holder 204 is mounted on the transition shaft 210, and the other end is mounted with the first sample 510. The first sample 510 and the first sample holder 204 can be fastened together by screws.

[0096] It should be understood that the present application directly sets the torque sensor 202 between the first rotating shaft 201 and the second rotating shaft 203. The torque transmission path between the torque sensor 202 and the sample is short, the friction loss is small, and the reliability is higher.

[0097] The rotary actuator 200 extends the first sample holder 204 into the heating furnace 100 in the form of a cantilever. This cantilever structure facilitates cooperation with the subsequent radial force loading mechanism 300 loaded by weights, so that the loading direction of the radial force loading mechanism 300 can be perpendicular to the rotation direction of the cantilever, that is, the radial force loading mechanism 300 can successfully load the radial force.

[0098] To ensure cantilever rigidity, the second rotating shaft 203 is relatively thick. To facilitate connection with the smaller first specimen holder 204, a transition shaft 210 with a smaller diameter than the second rotating shaft 203 is provided. Compared to directly providing a thinner second rotating shaft 203, the present invention employs a thicker second rotating shaft 203 and then a transition shaft 210, which allows for both securing the smaller first specimen holder 204 and maintaining system rigidity.

[0099] Furthermore, multiple first specimen fixtures 204 with various clamping apertures can be prepared to meet the clamping requirements of first specimens 510 with different outer diameters. For special first specimens 510, the required clamping aperture can be machined into the unopened fixture replacement to meet special needs.

[0100] The temperature in the furnace may be higher depending on the test requirements. The first sample fixture 204 and its locking screws may be made of high-temperature alloy or high-temperature resistant stainless steel, which can maintain sufficient mechanical properties at high temperatures.

[0101] Radial force loading mechanism 300

[0102] See also Figure 4 The radial force loading mechanism 300 may include a linear bearing 301, an adjusting piece nut 302, an adjusting piece 303, a compensation spring 304, a loading shaft 305, a weight plate 306, a second sample holder 307 (see Figure 3 ) and weight column 310.

[0103] The linear bearing 301 is fixedly connected to the top of the heating furnace 100, for example, to the upper plate 140 of the heating furnace. The adjusting piece nut 302 is fixedly connected to the top of the linear bearing 301. The adjusting piece 303 is formed in a cylindrical shape and is threadedly connected to the adjusting piece nut 302. The compensation spring 304 is arranged on the top of the adjusting piece 303. The weight plate 306 is arranged on the top of the compensation spring 304, and the weight plate 306 is pressed against the loading shaft 305. By rotating the adjusting piece 303, the axial distance between the adjusting piece 303 and the adjusting piece nut 302 can be adjusted, and the compression degree of the compensation spring 304 can be adjusted.

[0104] It should be understood that in addition to the support force of the loading shaft 305, the weight plate 306 is also supported by the compensation spring 304. By adjusting the compression degree of the compensation spring 304, the support force of the compensation spring 304 on the weight plate 306 can be adjusted, thereby offsetting the influence of the radial force loading mechanism 300's own weight.

[0105] See also Figure 2 The weight column 310 can be disposed at the axis of the weight disk 306 and can be threadedly connected to the loading shaft 305. A corresponding load can be applied to the second specimen 520 by placing a weight 320 of corresponding weight in the weight disk 306. The weight 320 can be a commercially available Newtonian weight with a hole, the hole of which can fit into the weight column 310. The axes of the weight disk 306, the loading shaft 305, and the weight column 310 can coincide. The weight 320 can be mounted on the weight disk 306 via the weight column 310.

[0106] One end (lower end) of the loading shaft 305 extends into the heating furnace 100 through the linear bearing 301 and the first sample opening 110. One end of the loading shaft 305 is also connected to the second sample holder 307. Figure 5 The second sample fixture 307 may include a curved surface 3071, and the second sample 520 may also have a curved surface. The curved surface of the second sample 520 is adapted to fit the curved surface 3071 of the second sample fixture 307, and the loading force may be transmitted to the second sample 520 via the curved surface 3071. The second sample fixture 307 is provided with a second fixture threaded hole 3072, which can be fastened to the second sample fixture 307 and the second sample 520 using a fastener, such as a locking screw.

[0107] Furthermore, the second sample holder 307 may include a flat surface 3073 adjacent to the arc surface 3071 in the circumferential direction of the arc surface 3071. When the second sample 520 has a flat surface (for example, the cylindrical second sample 520 is trimmed), the flat surface of the second sample 520 is attached to the flat surface 3073 to prevent rotation.

[0108] Furthermore, multiple second sample fixtures 307 with various camber radii can be prepared to meet the clamping requirements of second samples 520 with different outer diameters. For second samples 520 with special outer diameters, the required camber radius can be machined into the fixture replacement.

[0109] See also Figure 3The loading shaft 305 can be provided with a cylindrical recess 3051, and the second sample grip 307 can be provided with a cylindrical protrusion 3074, so that the loading shaft 305 and the second sample grip 307 can be plugged together. Alternatively, a cylindrical protrusion can be provided on the loading shaft 305, and a cylindrical recess can be provided on the second sample grip 307. This allows the second sample grip 307 to rotate along its axis to fine-tune the coaxiality between the first sample 510 and the second sample 520. A set screw can also be provided to secure the loading shaft 305 and the second sample grip 307.

[0110] According to the test requirements, the temperature in the furnace may be relatively high. The second sample fixture 307 and its locking screw may be made of high-temperature alloy, high-temperature resistant stainless steel or alumina ceramic, which can maintain sufficient mechanical properties at high temperatures.

[0111] In one embodiment, the working process of the test device provided by the present application is as follows.

[0112] Before the test begins, use a spirit level to calibrate the support plate 408 and the upper plate 140 of the heating furnace, fine-tune the circumferential position of the second sample fixture 307, ensure that the coaxiality of the first sample 510 and the second sample 520 is within the specified standard, and record the height of the loading shaft 305 at this time; rotate the adjusting plate 303 to adjust the compression of the compensation spring 304 so that the second sample 520 hovers at the corresponding height. At this time, the supporting force provided by the compensation spring 304 just offsets the deadweight of the radial force loading device; close the furnace door 160, and move the slide 406 to make the first sample 510 and the second sample 520 cooperate with each other.

[0113] The heating furnace 100 is programmed to raise the temperature in the chamber to the target temperature and maintain the temperature; a specific weight combination is added to the weight disk 306 to load the radial force on the outer surface of the second sample 520; the first sample 510 is controlled by the motor 231 to rotate back and forth at a specific speed and angle; the friction torque between the first sample 510 and the second sample 520 is transmitted to the torque sensor 202 by the long rotating shaft for collection and measurement, and can be output and displayed on the computer.

[0114] The friction coefficient of the first sample 510 and the second sample 520 can be obtained by converting the weight, friction torque, and sample radius, that is, the friction force F of the contact surface is obtained by multiplying the friction torque M by the radius r of the first sample 510, and then the friction coefficient μ is obtained by dividing the friction force F by the weight G. The torque sensor (202) can also convert the friction torque M on the shaft into an electrical signal, and display it on a computer through the acquisition instrument output.

[0115] The test device provided in this application can effectively simulate the friction and wear behavior of the pin-bushing kinematic pair under high temperature and radial load conditions, solving the problem of limited maximum test temperature of existing devices.

[0116] In addition, the dimensions and fitting tolerances of the first specimen 510 and the second specimen 520 can be determined based on the actual components being evaluated, which can better simulate the actual situation. The mechanical properties and temperature resistance of the materials used in the device have been calibrated and can meet the test requirements within 1100°C. The maximum test temperature is higher than that of existing devices. The torque sensor 202 is directly mounted on the rotating shaft to measure the torque directly. The load transfer path is short and the test error is smaller. The layout of components such as bearings and electrical components is far away from the heating furnace 100, and the rotating shaft is cooled by the cooling water coil 220, which makes the performance more stable and reliable. The device uses weights to apply radial loads, which is more reliable and simpler than traditional force feedback electronic control loading.

[0117] It should be understood that fixed connection includes fixing one part to another part by a fastener, which does not limit whether the two parts are detachable.

[0118] The above is a preferred embodiment of the present application. It should be pointed out that for those skilled in the art, several improvements and modifications can be made without departing from the principles of the present application. These improvements and modifications should also be regarded as within the scope of protection of the present application.

Claims

1. A high temperature sleeve friction and wear testing device, characterized in that: include: A heating furnace (100) is used to provide a closed high-temperature cavity, wherein the heating furnace (100) comprises a first sample opening (110) located in a horizontal direction and a second sample opening (120) located on a top surface; A rotary actuator (200) comprising a first rotating shaft (201), a torque sensor (202), a second rotating shaft (203), and a first sample holder (204) connected in sequence, wherein the first rotating shaft (201) is configured to provide rotational power, and the first sample holder (204) extends into the heating furnace (100) through the first sample opening (110) in the form of a cantilever; A radial force loading mechanism (300) comprises a linear bearing (301), an adjusting piece nut (302), an adjusting piece (303), a compensation spring (304), a loading shaft (305), a weight plate (306) and a second sample fixture (307), wherein the linear bearing (301) is fixedly connected to the top of the heating furnace (100), the adjusting piece nut (302) is fixedly connected to the top of the linear bearing (301), the adjusting piece (303) is formed into a cylindrical shape and is threadedly connected to the adjusting piece nut (302), and the compensation spring (304) is fixedly connected to the top of the heating furnace (100). 4) is arranged on the top of the adjusting plate (303), the weight plate (306) is arranged on the top of the compensation spring (304), and the weight plate (306) is pressed on the loading shaft (305), so that the compression degree of the compensation spring (304) can be adjusted by rotating the adjusting plate (303), one end of the loading shaft (305) extends into the heating furnace (100) through the linear bearing (301) and the first sample opening (110), and one end of the loading shaft (305) is also connected to the second sample fixture (307).

2. The high-temperature sleeve friction and wear testing device according to claim 1, characterized in that: A heat insulation sheet (130) is installed outside the first sample opening (110), and the heat insulation sheet (130) includes a heat insulation sheet opening connected to the first sample opening (110), and the second rotating shaft (203) extends into the heating furnace (100) through the heat insulation sheet opening.

3. The high-temperature sleeve friction and wear testing device according to claim 1, characterized in that: The rotary actuator (200) comprises a transition shaft (210), the diameter of the transition shaft (210) being smaller than the diameter of the second rotating shaft (203), one end of the transition shaft (210) being connected to the second rotating shaft (203), and the other end being connected to the first sample holder (204).

4. The high-temperature sleeve friction and wear testing device according to claim 1, characterized in that: A cooling water coil (220) is provided outside the second rotating shaft (203).

5. The high-temperature sleeve friction and wear testing device according to claim 1, characterized in that: The rotary actuator (200) comprises a motor (231), a reducer (232) and a coupling (233); the motor (231) is connected to the first rotating shaft (201) via the reducer (232) and the coupling (233); and the coupling (233) is a diaphragm coupling.

6. The high-temperature sleeve friction and wear testing device according to claim 1, characterized in that: The second sample fixture (307) includes a curved surface (3071), and the second sample (520) used for the test has a curved surface. The curved surface of the second sample (520) is used to fit the curved surface (3071) of the second sample fixture (307). The second sample fixture (307) is provided with a second fixture threaded hole (3072). The second sample (520) can be fixed to the second sample fixture (307) through a fastener and the second fixture threaded hole (3072).

7. The high-temperature sleeve friction and wear testing device according to claim 6, characterized in that: The second sample fixture (307) includes a plane (3073) adjacent to the arc surface (3071) in the circumferential direction. When the second sample (520) has a plane, the plane of the second sample (520) is used to fit the plane (3073) of the second sample fixture (307).

8. The high-temperature sleeve friction and wear testing device according to claim 1, characterized in that: One end of the loading shaft (305) is provided with a cylindrical recessed portion (3051) or a protruding portion, and one end of the second sample fixture (307) is provided with a cylindrical protruding portion (3074) or a recessed portion. The loading shaft (305) and the second sample fixture (307) can be plugged into each other.

9. The high-temperature sleeve friction and wear testing device according to claim 1, characterized in that: The radial force loading mechanism (300) further includes a weight column (310) and a weight (320), wherein the weight column (310) is connected to the loading shaft (305), the axes of the weight disk (306), the loading shaft (305) and the weight column (310) coincide with each other, the center of the weight (320) has a hole that matches the weight column (310), and the weight (320) is installed on the weight disk (306) through the weight column (310).

10. The high temperature bushing friction and wear testing device according to claim 1, characterized in that: The high-temperature shaft sleeve friction and wear testing device further comprises a horizontal displacement mechanism (400), wherein the horizontal displacement mechanism (400) is configured to drive the rotary actuator (200) to horizontally displace and enable the first sample fixture (204) to enter and exit the heating furnace (100) through the first sample opening (110).

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