Clutch bearing high temperature testing device

Abstract

A high-temperature testing device for clutch bearings includes a worktable with a drive mechanism, a radial loading mechanism, an axial loading mechanism, and a bearing under test. It also includes a transmission shaft and a loading shaft respectively positioned on opposite axial sides of the bearing under test. The transmission shaft is the output end of the drive mechanism and is engaged with the outer ring of the bearing under test. The loading shaft is fixed to the inner diameter surface of the inner ring of the bearing under test. The loads applied by the radial and axial loading mechanisms act on the loading shaft. The load applied by the axial loading mechanism on the loading shaft causes the inner ring of the bearing under test to tend to separate from the outer ring. The beneficial effect of this invention is that by engaging the transmission shaft with the outer ring and fixing the loading shaft to the inner ring, it simulates a working condition where the outer ring rotates actively while the inner ring remains stationary. This is completely consistent with the actual state of a clutch release bearing in use, where the outer ring rotates with engine-side components while the inner ring is fixed to the release sleeve.

Description

Technical Field

[0001] This invention relates to a testing device, and more particularly to a high-temperature testing device for clutch bearings. Background Technology

[0002] In automotive transmission systems, the clutch release bearing, as a critical component, typically employs an angular contact ball bearing structure to withstand the axial loads and some radial loads generated during clutch engagement and disengagement. In actual vehicle operation, this bearing operates for extended periods in the high-temperature environment of the engine compartment, and due to its often cantilevered mounting configuration, the load application point is offset from the bearing center, generating additional bending moments. Simultaneously, the outer ring of the clutch release bearing rotates with the clutch diaphragm spring, while the inner ring is fixed or relatively stationary. This condition of outer ring rotation and inner ring stress places stringent demands on the bearing's dynamic performance, temperature rise, and lifespan. To verify the bearing's reliability under the coupled effects of high temperature, cantilever load, and outer ring rotation, a specialized testing device is needed to simulate these actual operating boundaries. This involves driving the outer ring to rotate at high speed and applying controllable axial and radial loads, while real-time monitoring of parameters such as temperature and vibration to evaluate the bearing's durability and performance degradation patterns.

[0003] Currently, most devices used for testing the performance of clutch release bearings employ traditional test schemes with the inner ring rotating and the outer ring fixed, or only capable of applying a single axial load. These methods fail to accurately reproduce the complex stress state resulting from the combined effects of outer ring rotation and cantilever load. While some devices can simulate high-temperature environments, their temperature field control precision is insufficient, and the fixed loading position prevents flexible adjustment of the loading point to simulate bending moments generated by different offset distances. This leads to significant deviations between the obtained bearing life and performance data and actual usage conditions. Furthermore, existing devices lack stability under prolonged high-speed operation and the ability to simultaneously acquire multiple parameters, making it difficult to meet the requirements for high-precision bearing performance verification. Summary of the Invention

[0004] To address the shortcomings of existing technologies, this invention provides a high-temperature testing device for clutch bearings that can reproduce the coupling loading of outer ring rotation and cantilever load, as well as high-temperature testing.

[0005] To achieve the above objectives, the technical solution of the present invention is as follows: A high-temperature testing device for clutch bearings includes a worktable, on which a drive mechanism, a radial loading mechanism, an axial loading mechanism, and a bearing to be tested are arranged. It also includes a transmission shaft and a loading shaft respectively disposed on both axial sides of the bearing to be tested. The transmission shaft is the output end of the drive mechanism and is engaged on the outer ring of the bearing to be tested. The loading shaft is fixed to the inner diameter surface of the inner ring of the bearing to be tested. The loads applied by the radial and axial loading mechanisms act on the loading shaft. The load applied to the loading shaft by the axial loading mechanism causes the inner ring of the bearing to be tested to tend to separate from the outer ring of the bearing to be tested.

[0006] The beneficial effects of this invention are as follows: By fixing the drive shaft to the outer ring and the loading shaft to the inner ring, a simulation of the working condition where the outer ring rotates actively while the inner ring remains stationary is achieved. This is completely consistent with the actual state of the clutch release bearing in use, where the outer ring rotates with the engine-side components and the inner ring is fixed to the release sleeve. The radial loading mechanism applies the load to the loading shaft. Due to the cantilever distance between the loading point and the center of the bearing inner ring, a cantilever bending moment is generated on the inner ring, realistically replicating the radial cantilever load of the release fork acting on the inner ring of the release bearing. The axial loading mechanism applies an axial force to the inner ring corresponding to the separation tendency of the outer ring, simulating the separation load under the action of the diaphragm spring. This scheme is the first to simultaneously couple and apply three loads: outer ring rotation, cantilever radial bending moment, and axial separation force. It can comprehensively reproduce the complex stress state of the clutch release bearing under high temperature and high speed operation, making up for the shortcomings of traditional devices that can only achieve inner ring rotation or no cantilever load. This ensures that the measured bearing friction torque, temperature rise, and life data are highly consistent with actual use, providing an accurate basis for bearing performance evaluation and failure analysis. As a preferred embodiment, the output end of the drive shaft is machined with a stepped cylindrical hole to accommodate the outer ring of the bearing. Several axial slits are formed along the circumferential direction of the inner wall of the hole to create elastic grippers. A locking nut is fitted onto the outer conical surface of the grippers. When the locking nut is tightened, the grippers radially contract to evenly grip the outer ring, while the steps within the hole abut against the end face of the outer ring, achieving torque transmission without relative slippage. The loading shaft uses a tapered expansion sleeve that fits with the inner diameter of the inner ring. An axial tension bolt is installed inside the expansion sleeve. When the bolt is tightened, the expansion sleeve radially expands and forms an interference fit with the inner ring, ensuring that the inner ring does not loosen under axial and radial loads and allowing for quick assembly and disassembly. As another preferred embodiment, the drive shaft uses multi-lobed grippers and an axial pressure cap to axially press the outer ring. The end of the loading shaft is machined into a threaded section, and a round nut and a locking washer are used to tighten the inner ring, providing an adjustable preload fixing effect.

[0007] Furthermore, the device also includes a temperature control mechanism. The bearing to be tested is disposed within the temperature control mechanism. The temperature control mechanism has through holes at both ends along the axial direction of the bearing to be tested, which respectively cooperate with the drive shaft and the loading shaft. A seal is provided at the through hole to isolate the interior of the temperature control mechanism from the outside.

[0008] By placing the bearing under test entirely inside the temperature control mechanism, the bearing's ambient temperature can be actively controlled, realistically simulating the high-temperature working environment of the clutch release bearing near the gearbox, thus compensating for deviations in room-temperature test data. Through holes at both ends allow the drive shaft and loading shaft to pass through normally, while the seals form a dynamic isolation under shaft rotation conditions, preventing hot air leakage and external cold air ingress, maintaining a uniform and stable temperature field inside the temperature control mechanism, improving temperature control accuracy, and avoiding the impact of bearing clearance changes and lubrication failures caused by temperature fluctuations on the test results. As a preferred method, the temperature control mechanism consists of a hollow cylindrical heating furnace. The inner wall of the furnace is arranged with spiral resistance wires and filled with thermally conductive ceramic fibers. Insulating end plates are fixed at both ends, with through holes located in the center of the end plates. The seals are high-temperature resistant fluororubber skeleton oil seals, with the main lip in interference contact with the drive shaft or loading shaft, and the secondary lip serving as a dustproof seal. A graphite heat insulation ring is added to the outside of the oil seal to reduce heat conduction along the shaft. As another preferred method, the seal is a non-contact stepped labyrinth ring. The labyrinth ring is filled with low-pressure dry air to form an air curtain, which not only ensures zero friction during rotation, but also effectively isolates the exchange of internal and external airflow, thus extending the seal life.

[0009] Furthermore, the temperature control mechanism includes a heating element and a fixing plate disposed on both sides of the heating element along the axial direction of the bearing to be tested. The through hole is disposed on the fixing plate, and the fixing plate has a plurality of fixing holes spaced circumferentially on its end face facing away from the heating element. Fixing members are inserted into the fixing holes to fix the fixing plate and the heating element.

[0010] The heating element is stacked and fixed to two side mounting plates, making the temperature control mechanism modular and easy to assemble and maintain. The through holes on the mounting plates directly provide a positioning reference for the drive shaft and loading shaft, ensuring coaxiality of the shaft insertion. Multiple circumferentially arranged mounting holes and fasteners ensure that the heating element is evenly and tightly clamped between the two mounting plates, eliminating gaps, increasing the contact area, and allowing heat to be efficiently conducted to the mounting plates and radiated to the bearing space, thereby improving heating efficiency and temperature uniformity, while preventing the heating element from loosening or shifting under vibration. As a preferred method, the heating element is a ring-shaped mica heating plate with an inner hole larger than the bearing outer diameter. The mounting plates are circular stainless steel plates with eight through holes evenly distributed along the same pitch circle. The fasteners are bolts and lock nuts. During assembly, thermally conductive adhesive is applied to both sides of the heating element, and the bolts are tightened diagonally to ensure a full fit between the heating element and the mounting plates. As another preferred method, the heating element can be assembled from multiple arc-shaped heating units, and the fixing holes on the fixing plate are located in the arc-shaped groove, allowing the heating element to be finely adjusted in the circumferential direction, further ensuring symmetrical heat distribution.

[0011] Furthermore, the transmission shaft is provided with a sleeve hole on the side facing the bearing to be tested for mating with the outer ring of the bearing to be tested. The sleeve hole is provided with an abutment step, which abuts against the outer diameter surface and one axial end face of the bearing outer ring respectively.

[0012] The abutment step inside the bushing simultaneously limits the outer diameter surface and axial end face of the outer ring, not only reliably transmitting drive torque but also providing back support for the outer ring under axial load, preventing it from being pulled out or experiencing axial movement. This ensures that the outer ring and drive shaft maintain a consistent relative position, thus guaranteeing the stability of rotational accuracy, especially under high speeds and conditions of superimposed axial separation forces. As a preferred embodiment, the bushing includes a large-diameter section and a small-diameter section. The large-diameter section has a small clearance fit with the outer ring's outer diameter, its depth slightly less than the outer ring's width. The inner end face of the small-diameter section forms an abutment step. A set of disc springs is installed at the bottom of the bushing. After the outer ring is installed, the threaded end cap at the front end presses against the other end face of the outer ring, using the disc springs to compensate for the axial clearance caused by thermal expansion, maintaining smooth transmission. As another preferred embodiment, a spiral oil groove is provided on the inner wall of the bushing to store a small amount of grease, reducing fretting wear between the outer ring and the bushing. The abutment step contacts the bearing end face through the embedded replaceable wear-resistant washer, improving service life.

[0013] Furthermore, the radial loading mechanism includes a radial base fixed on the worktable, a radial load sensor fixed on the radial base, and a radial sleeve sleeved on the loading shaft, wherein the sleeve sleeve is sleeved on the portion of the loading shaft located outside the temperature control mechanism.

[0014] The radial sleeve is fitted onto the portion of the loading shaft extending beyond the temperature control mechanism, placing the radial loading point outside the high-temperature zone. This protects the radial load sensor from thermal radiation and conduction, ensuring its measurement accuracy and long-term stability. It also allows for flexible selection of the loading position along the axial direction, enabling bending moment adjustment at different cantilever distances and simulating radial load conditions with varying offsets. The radial base provides rigid support for the sensor, ensuring high rigidity of the radial force transmission chain. As a preferred embodiment, the radial sleeve is a fork-shaped component with self-aligning roller bearings at the ends of its two fork arms. The inner rings of the bearings are transition-fitted to the loading shaft and secured by locking sleeves. A hydraulic loading cylinder is mounted on the radial base. The output end of the loading cylinder is connected in series with the radial load sensor and hinged to the crossbeam of the fork-shaped component. The applied tension or pressure is accurately measured by the sensor and then applied to the loading shaft, generating a cantilever bending moment. Alternatively, the radial sleeve employs an open semi-circular clamp structure, bolted to the loading shaft. A radially extending loading pin is installed on the clamp, allowing for gravity loading via connection to a spring scale or weight lever mechanism. This design is simple and easy to calibrate.

[0015] Furthermore, the axial loading mechanism includes a slidable axial base, an axial rotating screw fixed on the worktable, a connecting shaft disposed on the axial base, and an axial load adjustment assembly disposed between the connecting shaft and the loading shaft. The axial base cooperates with the axial rotating screw to drive the axial base to move along the bearing to be tested axially on the worktable when the axial rotating screw rotates. The axial load adjustment assembly includes a fixed sleeve fixed on the portion of the loading shaft located outside the temperature regulating mechanism and a sliding sleeve fixed on the connecting shaft. The fixed sleeve and the sliding sleeve can move relative to each other, and the axial load acting on the loading shaft by the fixed sleeve changes accordingly during the relative movement.

[0016] By rotating the axial screw, the axial base moves linearly, causing the connecting shaft to drive the sliding sleeve to generate axial displacement relative to the fixed sleeve fixed on the loading shaft. This changes the compression of the elastic element between the two, achieving stepless adjustment of the axial force on the loading shaft. This mechanism converts rotational motion into precise axial force control, is labor-saving to operate, and has good self-locking performance after positioning. It can accurately simulate separation loads with different degrees of compression and can be dynamically adjusted during testing to examine the performance changes of the bearing under different axial forces. As a preferred method, the fixed sleeve is fixed to the end of the loading shaft by a flat key and a set screw. The sliding sleeve is sleeved on the outside of the fixed sleeve via a linear bearing, and a helical compression spring is installed between the two. The connecting shaft is connected to the end of the sliding sleeve via a thrust ball bearing. When the axial screw moves the axial base forward, the sliding sleeve compresses the spring. The spring force is transmitted to the loading shaft through the fixed sleeve, ultimately pulling the inner ring to generate an axial force that separates it from the outer ring. The compression of the spring can be calibrated by a displacement sensor. As another preferred method, a small hydraulic bladder is provided between the fixed sleeve and the sliding sleeve in the axial load adjustment assembly. The pressure inside the bladder is adjusted by a micro manual pump to directly generate axial force hydraulically. The force value is calculated by a pressure sensor, which has a fast response and does not require complex mechanical transmission.

[0017] Furthermore, the axial load adjustment assembly also includes a linear bearing disposed between the sliding sleeve and the fixed sleeve, and springs at both ends of the bearing being connected to the sliding sleeve and the fixed sleeve, respectively.

[0018] Linear bearings provide low-friction guidance for the relative axial movement between the sliding sleeve and the fixed sleeve, significantly reducing friction during adjustment. This allows the spring force to be converted into axial load with almost no loss, improving the adjustment sensitivity and repeatability of the load. Simultaneously, linear bearings can withstand a certain radial force, keeping the sleeves concentric and preventing spring bending and additional bending moments due to uneven loading. The spring, as an energy storage element, smoothly applies axial force, absorbs high-frequency vibrations and thermal displacement generated during operation, and protects the bearing from overload impacts. As a preferred method, the linear bearing is a self-lubricating metal-polymer composite sliding bearing, requiring no additional lubrication. The outer diameter of the fixed sleeve is precision ground, and the bearing is press-fitted into the inner hole of the sliding sleeve. The spring is a rectangular cross-section mold spring, with both ends ground flat and fitted with locating sleeves to prevent radial slippage. The initial spring preload is set by adjusting the thread length between the connecting shaft and the sliding sleeve. As another preferred method, the linear bearing adopts a circulating ball sleeve type linear guide pair. The guide groove is machined on the fixed sleeve, and a double row of ball sliders are installed in the sliding sleeve. The spring is placed on the outside of the sleeve and connected by tie rods at both ends, which facilitates visual observation and replacement.

[0019] Furthermore, the sliding sleeve is provided with a travel limiting groove, and a limiting pin connected to the fixed sleeve is provided in the travel limiting groove.

[0020] The stroke limiting groove and the limiting pin work together to not only provide a physical stop for the axial movement of the sliding sleeve, preventing over-compression of the spring or disengagement of the linear bearing, but also constrain the relative rotation between the sliding sleeve and the fixed sleeve. This ensures that the spring end does not twist during the rotation of the loading shaft and the adjustment of the axial force, and that the axial force always follows the bearing axis, eliminating lateral disturbances and additional bending moments caused by deflection, thus ensuring the accuracy of axial load measurement. As a preferred embodiment, the stroke limiting groove is a slotted through hole machined into the wall of the sliding sleeve, and the limiting pin is an internal hexagonal head screw. Its threaded section is screwed into a radial threaded hole on the fixed sleeve, and the smooth section passes through the slotted through hole. A nylon spacer is fitted on the smooth section to reduce impact and wear. The length of the slotted through hole is determined according to the spring's working stroke and safety margin. As another preferred embodiment, the limiting groove and the limiting pin are arranged symmetrically in pairs. The limiting pin adopts a stepped shaft structure, is axially fixed by a snap ring, and a buffer pad is installed in the limiting groove to achieve soft limiting and reduce limiting collision noise.

[0021] Furthermore, the driving mechanism includes a driving base and a driving rotating screw, which cooperate with the driving base to drive the driving base to move radially along the bearing to be tested on the worktable when the driving rotating screw rotates.

[0022] By setting a radially movable drive base, the rotation of the drive screw is converted into precise radial sliding of the base, which allows for flexible adjustment of the relative position between the drive shaft axis and the loading shaft axis, achieving coaxiality correction of the two shafts. This effectively compensates for misalignment caused by machining errors, installation deviations, or high-temperature thermal expansion, reduces additional radial force and vibration inside the bearing, makes the outer ring rotate more smoothly, and avoids abnormal bearing wear and test data distortion caused by eccentricity, which is particularly important for high-speed life testing. As a preferred method, two parallel guide rails are laid on the worktable, a slider is installed on the bottom surface of the drive base, and the drive screw is a trapezoidal lead screw. Both ends of the lead screw are supported on the worktable by bearing seats, and its threaded section engages with a nut fixed on the drive base. The end of the lead screw is equipped with a handwheel and a dial. After adjustment, the base and guide rails are locked with locking blocks to ensure positional stability during operation. As another preferred method, the drive base adopts a differential thread pair adjustment mechanism, that is, the rotating screw has two threads with different pitches, which respectively cooperate with the fixed nut and the adjusting nut on the base. Micro-feeding is achieved through differential operation, and a dial indicator is set to display the radial displacement in real time. The coaxiality adjustment accuracy can reach the micrometer level. Attached Figure Description

[0023] Figure 1 This is a three-dimensional structural diagram of an embodiment of the present invention; Figure 2 This is a schematic diagram of the temperature control mechanism and radial loading mechanism in an embodiment of the present invention; Figure 3 This is a partial enlarged view of the axial load adjustment component in an embodiment of the present invention; Figure 4 This is a partial cross-sectional view of the axial load adjustment component in an embodiment of the present invention; Figure 5 This is a partial cross-sectional view of the bearing under test in an embodiment of the present invention. Detailed Implementation

[0024] An embodiment of the present invention provides a high-temperature testing device for clutch bearings, such as... Figure 1-5 As shown: The device includes a workbench 1 as the mounting base, on which a drive mechanism 2, a radial loading mechanism 3, an axial loading mechanism 4, a temperature control mechanism 6, and a bearing 5 to be tested are integrated. This embodiment aims to simulate the outer ring rotation and the inner ring bearing cantilever radial load and axial separation load of a clutch bearing in actual operation, and to conduct durability and performance tests under high temperature conditions.

[0025] The drive mechanism 2 is fixed on the worktable 1 and includes a drive base 21 and a drive rotating screw 22. The drive base 21 is slidably mounted on the worktable 1, and the drive rotating screw 22 is rotatably mounted on the worktable 1 and threadedly engaged with the drive base 21. When the drive rotating screw 22 is rotated, the entire drive base 21 can be driven to move radially along the bearing 5 to be tested on the worktable 1 to precisely adjust the concentricity between the subsequent transmission shaft 7 and the loading shaft 8, ensuring test accuracy. The output end of the drive mechanism 2 is a transmission shaft 7, which is rotatably supported on the drive base 21 by bearings and driven to rotate by a power source such as a motor.

[0026] The drive shaft 7 is connected to the outer ring 51 of the bearing 5 under test, thereby transmitting rotational motion. Specifically, the drive shaft 7 has a sleeve hole 71 at one end facing the bearing 5 under test, and the bottom of the sleeve hole 71 forms an annular abutment step 72. During assembly, the outer ring 51 of the bearing 5 under test is press-fitted into the sleeve hole 71, the outer diameter surface of the outer ring 51 is tightly fitted with the inner wall of the sleeve hole 71, and at the same time, one axial end face of the outer ring 51 is tightly fitted with the abutment step 72, so that the rotation of the drive shaft 7 drives the outer ring 51 of the bearing 5 under test to rotate synchronously.

[0027] A loading shaft 8 is fixed to the inner ring 52 of the bearing under test 5, and the axis of the loading shaft 8 coincides with the axis of the transmission shaft 7. One end of the loading shaft 8 is machined with a connecting part, which is fixedly connected to the inner diameter surface of the inner ring 52 of the bearing under test 5 by means of key connection or interference fit, so that the inner ring 52 remains stationary during the test. The other end of the loading shaft 8 extends outward along the axial direction, passes through the temperature control mechanism 6 in sequence, and serves as the force application point of the radial loading mechanism 3 and the axial loading mechanism 4. This constitutes a test configuration in which the outer ring 51 rotates and the inner ring 52 is fixed. Both radial and axial loads are applied through the cantilevered loading shaft 8, which realistically simulates the cantilever working force condition of the clutch bearing.

[0028] To simulate the axial tensile force experienced by the bearing during clutch disengagement, the axial loading mechanism 4 applies a load in a direction that tends to cause the inner ring 52 of the bearing under test 5 to separate axially from the outer ring 51. The axial loading mechanism 4 includes a sliding axial base 41, an axial rotating screw 42, a connecting shaft 43, and an axial load adjustment assembly 44. The axial rotating screw 42 is rotatably fixed to the worktable 1 via a bearing housing, and its screw portion is threadedly engaged with a nut on the axial base 41. When the axial rotating screw 42 is rotated, the axial base 41 translates along the surface of the worktable 1 in the axial direction of the bearing under test 5. One end of the connecting shaft 43 is fixed to the axial base 41, and the other end extends towards the loading shaft 8. The axial load adjustment assembly 44 is located between the end of the connecting shaft 43 and the portion of the loading shaft 8 that passes through the outside of the temperature control mechanism 6. It mainly consists of a fixed sleeve 441, a sliding sleeve 442, a linear bearing 443, and a spring 444. The fixed sleeve 441 is coaxially fixed to the end of the loading shaft 8, and the sliding sleeve 442 is coaxially fixed to the end of the connecting shaft 43. The two are axially slidingly engaged through the inner hole of the linear bearing 443. The two ends of the spring 444 are hooked or abutted against the end faces of the fixed sleeve 441 and the sliding sleeve 442, respectively. When the axial base 41 moves away from the bearing 5 under test, the connecting shaft 43 pulls the sliding sleeve 442, and the sliding sleeve 442 applies a pulling force to the fixed sleeve 441 through the spring 444. This pulling force is transmitted to the loading shaft 8 through the fixed sleeve 441, and finally manifests as an axial test load that pulls the inner ring 52 outward and separates it from the outer ring 51. In order to accurately guide and limit the movement process and prevent circumferential deflection from causing axial torque deviation, the sliding sleeve 442 is provided with a stroke limiting groove 445 extending along the axial direction. A limiting pin 446 passes through the stroke limiting groove 445 and is fixedly connected to the fixed sleeve 441, thereby limiting relative rotation while ensuring axial sliding stroke.

[0029] The radial loading mechanism 3 is used to simulate the cantilever radial force borne by the clutch bearing. Its point of application is also located on the part of the loading shaft 8 that extends beyond the temperature regulating mechanism 6, to avoid interference from high temperature on the sensor accuracy. The radial loading mechanism 3 consists of a radial base 31, a radial load sensor 32, and a radial sleeve 33. The radial base 31 is fixed on the worktable 1, and the radial load sensor 32 is mounted on the mounting surface of the radial base 31. The force-bearing end of the sensor 32 is connected to the radial sleeve 33, and the body of the radial sleeve 33 is fitted onto the loading shaft 8. By pushing the radial sleeve 33 with an external hydraulic or pneumatic actuator, the loading shaft 8 can be subjected to a radial force perpendicular to the axis. The magnitude and direction of this force can be accurately obtained by the sensor 32.

[0030] To achieve a high-temperature testing environment, the entire device, including the temperature control mechanism 6, the bearing under test 5, and the mating parts of the drive shaft 7 and the loading shaft 8, is encapsulated within it. The temperature control mechanism 6 is assembled from a heating element 61 and two fixing plates 62. The two fixing plates 62 are respectively attached to the two axial end faces of the heating element 61. Bolts or other fasteners are inserted through fixing holes 63 spaced apart circumferentially on the fixing plates 62 to fasten the fixing plates 62 and the heating element 61 into a box or cylindrical structure, which can enclose the heating element 61 to form a heating cavity. A through hole 64 is opened at the center of each fixing plate 62, allowing the drive shaft 7 and the loading shaft 8 to extend into the temperature control mechanism 6 from both sides and connect to the bearing under test 5. To achieve dynamic sealing to maintain the internal high temperature, a sealing element 65, such as a high-temperature oil seal or a labyrinth seal, is installed at each through hole 64, so that the drive shaft 7 and the loading shaft 8 can maintain the isolation between the inside of the temperature control mechanism 6 and the external environment whether the drive shaft 7 and the loading shaft 8 are rotating or stationary.

[0031] During testing, the outer ring 51 of the bearing under test 5 is first pressed into the sleeve hole 71 of the drive shaft 7, fixing the inner ring 52 to the loading shaft 8. Next, the position of the drive mechanism 2 is finely adjusted by rotating the drive screw 22 to achieve high concentricity between the drive shaft 7 and the loading shaft 8. Then, the temperature control mechanism 6 is closed and the heating element 61 is activated to raise the internal temperature to and maintain it at the set value. Afterward, the drive mechanism 2 is activated, causing the drive shaft 7 to rotate the outer ring 51 at a specified speed. Finally, under high temperature and rotational conditions, a radial force is applied to the cantilevered loading shaft 8 by the radial loading mechanism 3, while simultaneously, by rotating the axial rotation screw 42, an axial separation load is applied to the loading shaft 8 via the axial load adjustment assembly 44, pulling the inner ring 52 outward. This scheme achieves comprehensive performance testing of the clutch bearing under high-temperature separation conditions of "outer ring rotation, inner ring fixation" and cantilever radial load.

[0032] The above embodiments are merely one preferred embodiment of the present invention. Ordinary variations and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are all included within the protection scope of the present invention.

Claims

1. A high-temperature testing device for clutch bearings, comprising a worktable, wherein a drive mechanism, a radial loading mechanism, an axial loading mechanism, and a bearing to be tested are arranged on the worktable, characterized in that: It also includes a drive shaft and a loading shaft set on both sides of the bearing under test. The drive shaft is the output end of the drive mechanism and is clamped on the outer ring of the bearing under test. The loading shaft is fixed to the inner diameter surface of the inner ring of the bearing under test. The load applied by the radial loading mechanism and the axial loading mechanism is applied to the loading shaft.

2. The load applied to the loading shaft by the axial loading mechanism causes the inner ring of the bearing under test to tend to separate from the outer ring of the bearing under test.

3. The high-temperature testing device for clutch bearings according to claim 1, characterized in that: The device also includes a temperature control mechanism. The bearing to be tested is disposed inside the temperature control mechanism. The temperature control mechanism has through holes at both ends along the axial direction of the bearing to be tested, which respectively cooperate with the drive shaft and the loading shaft. A seal is provided at the through hole to isolate the inside of the temperature control mechanism from the outside.

4. The high-temperature testing device for clutch bearings according to claim 2, characterized in that: The temperature control mechanism includes a heating element and a fixing plate disposed on both sides of the heating element along the axial direction of the bearing to be tested. The through hole is disposed on the fixing plate, and the fixing plate has a plurality of fixing holes spaced circumferentially on its end face facing away from the heating element. Fixing members are inserted into the fixing holes to fix the fixing plate and the heating element.

5. The high-temperature testing device for clutch bearings according to claim 1, characterized in that: The drive shaft has a sleeve hole on the side facing the bearing to be tested for mating with the outer ring of the bearing to be tested. The sleeve hole has an abutment step, which abuts against the outer diameter surface and one axial end face of the bearing outer ring.

6. The high-temperature testing device for clutch bearings according to claim 2, characterized in that: The radial loading mechanism includes a radial base fixed on the worktable, a radial load sensor fixed on the radial base, and a radial sleeve sleeved on the loading shaft. The sleeve sleeve is fitted on the portion of the loading shaft located outside the temperature control mechanism.

7. The high-temperature testing device for clutch bearings according to claim 2, characterized in that: The axial loading mechanism includes a slidable axial base, an axial rotating screw fixed on the worktable, a connecting shaft disposed on the axial base, and an axial load adjustment assembly disposed between the connecting shaft and the loading shaft. The axial base cooperates with the axial rotating screw to drive the axial base to move along the bearing to be tested axially on the worktable when the axial rotating screw rotates. The axial load adjustment assembly includes a fixed sleeve fixed on the part of the loading shaft located outside the temperature control mechanism and a sliding sleeve fixed on the connecting shaft. The fixed sleeve and the sliding sleeve can move relative to each other, and the axial load of the fixed sleeve acting on the loading shaft changes accordingly when they move relative to each other.

8. The high-temperature testing device for clutch bearings according to claim 6, characterized in that: The axial load adjustment assembly also includes a linear bearing disposed between the sliding sleeve and the axial sleeve, and springs at both ends of the linear bearing connected to the sliding sleeve and the axial sleeve respectively.

9. The high-temperature testing device for clutch bearings according to claim 7, characterized in that: The sliding sleeve is provided with a travel limit groove, and the travel limit sleeve is provided with a limit pin that is connected to the fixed sleeve.

10. The high-temperature testing device for clutch bearings according to claim 1, characterized in that: The driving mechanism includes a driving base and a driving rotating screw. The driving rotating screw and the driving base cooperate to drive the driving base to move radially along the bearing to be tested on the worktable when the driving rotating screw rotates.

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