CN209945717U

CN209945717U - Fatigue life testing device for high-speed oscillating bearing

Info

Publication number: CN209945717U
Application number: CN201920167437.2U
Authority: CN
Inventors: 卓耀彬; 叶晓平; 林云峰
Original assignee: Lishui University
Current assignee: Lishui University
Priority date: 2019-01-30
Filing date: 2019-01-30
Publication date: 2020-01-14
Anticipated expiration: 2029-01-30

Abstract

The utility model discloses a fatigue life test device for a high-speed oscillating bearing, which comprises an operation platform, and a driving motor, a rotating and oscillating conversion module, a plurality of test modules and a test bearing which are positioned on the operation platform, wherein the test bearing is sleeved with an outer sleeve; the test modules comprise radial sine pulse loading modules, friction torque monitoring modules, temperature detection modules and bearing support modules, wherein the radial sine pulse loading modules in the test modules are connected with one another, and the bearing support modules in the test modules are connected with one another; the rotating swing conversion module is provided with a flywheel and is directly connected with a driving motor, and the rotating swing conversion module drives the test bearing to rotate and swing in a reciprocating mode and simultaneously drives the radial sine pulse loading module to provide pulse radial loads for the test bearing; through the technical scheme, the friction torque change condition of the plurality of test bearings under different test conditions can be monitored in real time, so that whether the bearing fails or not is judged.

Description

Fatigue life testing device for high-speed oscillating bearing

Technical Field

The utility model belongs to bearing life test field especially relates to a high-speed oscillating bearing fatigue life test device.

Background

The existing bearing swing life test device mainly aims at a sliding knuckle bearing, has lower swing frequency which is generally less than 30 times/minute, and is not suitable for a high-speed swing bearing.

For example, patent document CN205981688U discloses a joint bearing life tester, which comprises an operation table and a test main body part arranged on the operation table, wherein the test main body part comprises a test main shaft and a bearing clamp, the device comprises a load loading device, a torque sensor and a transmission shaft, wherein two ends of a test main shaft are respectively rotatably supported by a left supporting component and a right supporting component, the transmission shaft is connected with one end of the test main shaft through the torque sensor, an angle encoder is installed at the other end of the test main shaft, a test bearing is installed in a bearing fixture, an inner ring of the test bearing is fixed on the test main shaft, two end faces of the inner ring of the test bearing are respectively clamped between the left supporting component and the right supporting component through a left lantern ring and a right lantern ring which are sleeved on the test main shaft, the transmission shaft is driven by a crank rocker mechanism and drives the test bearing to reciprocate and rotate and swing through the test main shaft, and the. The utility model discloses a can high-efficiently detect joint bearing's life-span, assess joint bearing's reliability. But also has the following disadvantages: a. the crank rocker mechanism is adopted to realize swinging motion, and the dynamic load is large and the vibration noise is large during operation, so that the crank rocker mechanism is not suitable for high-speed operation; b. the static spring or the oil cylinder is adopted to realize loading, so that the following change of the load in the running process of the bearing cannot be realized, or the following change of the load can be realized only in the low-speed swinging process; c. the function of monitoring the change of the friction torque of the bearing is not available, so that the running condition of the bearing cannot be reflected in real time; d. only a single bearing can be tested, and the test cost is high.

Disclosure of Invention

In order to solve the technical problem, the utility model aims at providing a high-speed oscillating bearing fatigue life test device, this test device can carry out the high-speed swing life test of a plurality of bearings, and the vibration that reduces when the swing motion disturbs, applys the cycle radial load that corresponds with the swing angle, still can monitor the change condition of bearing friction torque, load and temperature simultaneously.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

a fatigue life test device for a high-speed oscillating bearing comprises an operation table, a driving motor, a rotating and oscillating conversion module, a plurality of test modules and a test bearing, wherein the driving motor, the rotating and oscillating conversion module, the test modules and the test bearing are positioned on the operation table;

the test modules comprise radial sine pulse loading modules, friction torque monitoring modules, temperature detection modules and bearing support modules, wherein the radial sine pulse loading modules in the test modules are connected with one another, and the bearing support modules in the test modules are connected with one another;

the rotation swing conversion module is provided with a flywheel and is directly connected with the driving motor, the rotation swing conversion module drives the test bearing to perform reciprocating rotation swing, and simultaneously drives the radial sine pulse loading module to provide pulse radial load for the test bearing.

Preferably, the rotation-oscillation converting module includes a first supporting side plate, a second supporting side plate, a crankshaft and a guide rod shaft between the first supporting side plate and the second supporting side plate, a crank fixed on the crankshaft, and a guide rod fixedly connected to the guide rod shaft and connected to the crank, and the crankshaft is connected to the driving motor and is coaxial with the flywheel. By the arrangement, the rotational inertia of the crank shaft can be increased, the additional dynamic load interference caused by the crank and the guide rod is reduced, the motion conversion from rotation to swinging is realized by the crank guide rod mechanism, and meanwhile, the rotating speed is adjusted by the driving motor, so that the swing frequency with different frequencies is realized.

More preferably, the guide rod is provided with a long hole, the crank shaft is provided with a plurality of connecting holes, the connecting holes are respectively positioned on concentric circles with different radiuses, and the crank is in threaded fit with the connecting holes and penetrates through the long hole. The length adjustment of the crank can be realized through different connecting hole positions at the end of the crank shaft, so that the adjustment of the swing amplitude of the bearing is realized.

Preferably, the radial sinusoidal pulse loading module comprises a push rod, a spring assembly, a sliding block assembly, a first force sensor, a loading ball, an upper base and a lower base, the lower base is fixed on the operating platform, the sliding block assembly comprises a sliding block, a plurality of guide rails and linear bearings sleeved on the guide rails, the guide rails are fixed between the upper base and the lower base, the sliding block can move up and down on the guide rails, one end of the push rod is of a frame-shaped structure and is sleeved on a crank, the other end of the push rod is fixedly connected with the sliding block, the spring assembly penetrates through the lower base and the sliding block and is fixed on the sliding block, the first force sensor is fixed on the spring assembly, and the loading ball is embedded on the first. According to the arrangement, the rotary motion of the crank is converted into the up-and-down movement of the sliding block through the push rod, the spring assembly is driven to move up and down, sinusoidal regular pulse radial loads are generated, and the sinusoidal regular pulse radial loads are applied to the test bearing through the load first force sensor, the loading ball and the outer sleeve; and the loading ball is arranged at the position, so that the influence of the friction force on the friction torque monitoring at the force loading position can be reduced.

More preferably, the spring assembly comprises a spring, a spring housing and a spring adjusting sleeve, the spring adjusting sleeve is sleeved inside the spring housing, the spring housing is fixed on the sliding block through a fastener, and the first force sensor is fixed on the spring housing through a fastener. The arrangement is that the rotating motion of the crank is converted into the up-and-down movement of the sliding block through the push rod, so that pulsating force is applied to the test bearing, and if the reciprocating point and the starting point of the spring assembly are unchanged, the range value of the pulsating force applied to the test bearing is always fixed and unchanged no matter the rotating speed of the driving motor; therefore, the spring assembly is provided with the spring adjusting sleeve, and pulsating force in different ranges can be output by adjusting the position of the spring adjusting sleeve.

Preferably, the bearing support module comprises a third support side plate, a fourth support side plate, a first support bearing embedded in the third support side plate, a second support bearing embedded in the fourth support side plate, a left half shaft penetrating through the third support side plate and abutting against the test bearing, and a right half shaft penetrating through the fourth support side plate and the test bearing and abutting against the test bearing, wherein the third support plate and the fourth support plate are fixed on the upper base, the left half shaft and the right half shaft are connected through threads or in interference fit, the right half shaft is in interference fit with the test bearing, and the service life of the first support bearing and the service life of the second support bearing are far longer than that of the test bearing.

Preferably, the friction torque monitoring module comprises a second force sensor, a connecting rod and a connecting block, one end of the connecting block is vertically embedded into the outer sleeve, the other end of the connecting block is in threaded fit or interference fit with the connecting rod, the connecting block is perpendicular to the connecting rod, and the second force sensor is fixedly connected to the connecting rod and fixed to any one of the third supporting side plate, the fourth supporting side plate and the upper base. So arranged, the tangential force F can be measured_TAnd meanwhile, the distance from the center of the test bearing to the central shaft of the connecting rod is d, so that the friction torque from the inner ring to the outer ring is M-F when the test bearing swings_T·d。

Preferably, the temperature detection module is fixed on the upper base and aligned with the outer sleeve, and the temperature detection module is an infrared temperature sensor. The arrangement is to monitor the temperature change condition when the bearing generates heat by friction.

Preferably, the left half shaft is connected with the guide rod shaft through a coupler, the left half shaft is in interference fit with the coupler, the guide rod shaft is in interference fit with the coupler, and the coupler is a rigid coupler. So set up, through the shaft coupling with the swing motion transmission of guide rod axle to experimental bearing.

Preferably, the left half shaft and the right half shaft coupler between the adjacent test modules are connected, the left half shaft is in interference fit with the coupler, the right half shaft is in interference fit with the coupler, and the coupler is a rigid coupler. So set up, will test the oscillating motion transmission of bearing to next test bearing through the shaft coupling.

Preferably, the sliding blocks between the adjacent test modules are fixedly connected through a connecting plate. The setting can realize synchronous reciprocating of the slider in a plurality of test modules, guarantees the uniformity of applying load.

The utility model has the advantages that: a. the conversion from rotary motion to swing motion is realized by adopting a crank guide rod mechanism with a flywheel, and the crank guide rod mechanism has small dynamic load and small vibration noise during operation, so that the crank guide rod mechanism is suitable for high-speed operation; b. bearing realized by spring adjusting sleeveThe position of the spring changes in the operation process, so that the following change of the radial pulsating force load is realized; c. monitoring the tangential restraining force F of the test bearing during oscillation through a second force sensor_TBy the formula M ═ F_TD, obtaining the change condition of the friction moment M when the bearing swings, thereby judging whether the bearing fails or not, wherein d is F_TDistance to the center of the test bearing; d. on the premise of ensuring the connection rigidity of each part, a plurality of test bearings can be tested simultaneously, and the test cost is reduced.

Drawings

FIG. 1 is a schematic view of the overall structure of the fatigue life testing device for the high-speed oscillating bearing of the present invention;

fig. 2 is a schematic structural diagram of the rotation and swing conversion module of the present invention;

fig. 3 is a schematic structural view of a rotating crank shaft according to the present invention;

FIG. 4 is a schematic diagram of the friction torque monitoring module and the temperature detecting module of the present invention;

fig. 5 is a schematic structural diagram of the radial sinusoidal pulse loading module of the present invention;

FIG. 6 is a schematic view of the connection of adjacent test modules of the present invention;

fig. 7 is an enlarged view of a portion of fig. 6 according to the present invention;

fig. 8 is a schematic diagram of the overall structure of the fatigue life testing apparatus for a high-speed oscillating bearing of the present invention.

Description of reference numerals: 1. an operation table; 2. a drive motor; 3. a rotation swing conversion module; 4. a test module; 5. testing the bearing; 51. a jacket; 41. a sine pulse loading module; 42. a friction torque monitoring module; 43. a temperature detection module; 44. a bearing support module; 31. a flywheel; 32. a first support side plate; 33. a second support side plate; 34. a crank shaft; 35. a guide rod shaft; 36. a crank; 37. a guide bar; 371. a long hole; 341. connecting holes; 411. a push rod; 412. a spring assembly; 413. a slider assembly; 414. a first force sensor; 415. loading a ball; 4131. an upper base; 4132. a lower base; 4133. a slider; 4134. a guide rail; 4135. a linear bearing; 4121. a spring; 4122. a spring housing; 4123. a spring adjusting sleeve; 441. a third support side plate; 442. a fourth supporting side plate; 443. a first support bearing; 444. a second support bearing; 445. a left half shaft; 446. a right half shaft; 421. a second force sensor; 422. a connecting rod; 423. connecting blocks; 6. a coupling; 7. a connecting plate.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present invention, and should not be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and to simplify the description, but do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be construed as limiting the present invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, unless otherwise specified, "a plurality" means two or more unless explicitly defined otherwise.

In the present invention, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

In the present disclosure, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may comprise direct contact between the first and second features, or may comprise contact between the first and second features not directly. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.

The fatigue life testing device for the high-speed oscillating bearing shown in fig. 1 comprises an operating platform 1, a driving motor 2, a rotating and oscillating conversion module 3, two testing modules 4 and two testing bearings 5, wherein the driving motor 2, the rotating and oscillating conversion module 3, the two testing modules 4 and the two testing bearings 5 are positioned on the operating platform 1, an outer sleeve 51 is sleeved on each testing bearing 5, and the outer sleeve 51 is tightly matched with the testing bearings 5;

the test modules 4 comprise radial sine pulse loading modules 41, friction torque monitoring modules 42, temperature detection modules 43 and bearing support modules 44, wherein the radial sine pulse loading modules 41 in the test modules 4 are connected with one another, and the bearing support modules 44 in the test modules 4 are connected with one another;

the rotation swing conversion module 3 drives the test bearing 5 to perform reciprocating rotation swing, and simultaneously drives the radial sine pulse loading module 41 to provide pulse radial load for the test bearing 5.

The rotational-oscillation converting module 3 shown in fig. 2 includes a first supporting side plate 32, a second supporting side plate 33, a crankshaft 34 and a guide rod shaft 35 between the first supporting side plate 32 and the second supporting side plate 33, a crank 36 fixed to the crankshaft 34, a guide rod 37 fixedly connected to the guide rod shaft 35 and connected to the crank 36, and a flywheel 31 coaxial with the crankshaft 34, wherein the crankshaft 34 is directly connected to the driving motor 2; the guide rod 37 is provided with a long hole 371, the crank 36 passes through the long hole 371, and the long hole 371 is a rectangular hole. By means of the arrangement, the rotational inertia of the crank shaft 34 can be increased, the additional dynamic load interference caused by the crank 36 and the guide rod 37 is reduced, the motion conversion from rotation to swinging is achieved by the aid of the mechanism of the crank 36 and the guide rod 37, and meanwhile, the swing frequency of different frequencies is achieved by adjusting the rotating speed of the driving motor 2.

In the embodiment, the rotating speed range of the driving motor 2 is 50-2000 rpm, and the energy storage and speed regulation functions of the flywheel 31 coaxial with the crank 36 are utilized to reduce the overall speed fluctuation of the system, so that the maximum swing frequency of the test bearing 5 can be more than 1000 times/min.

As shown in fig. 3, the crank shaft 34 is provided with 3 connecting holes 341, the 3 connecting holes 341 are respectively located on concentric circles with different radii, and the crank 36 is in threaded fit with the connecting holes 341. The length adjustment of the crank 36 can be realized through different connecting holes 341 at the end of the crank shaft 34, so that the adjustment of the bearing swinging amplitude is realized, in the embodiment, the change of the motion from rotation to swinging is realized through the guide rod 37 mechanism of the crank 36, and the maximum swinging amplitude of the test bearing 5 is larger than 13 degrees by adjusting the position of the crank 36.

The radial sine pulse loading module 41 shown in FIG. 5 comprises a push rod 411, a spring assembly 412, a slide block 4133 assembly 413, a first force sensor 414, a loading ball 415, an upper base 4131 and a lower base 4132, wherein the first force sensor 414 has a measuring range of 0-200N, the lower base 4132 is fixed on the operation table 1, the slide block 4133 assembly 413 comprises a slide block 4133, four guide rails 4134 and linear bearings 4135 sleeved on the guide rails 4134, the guide rails 4134 are fixed between the upper base 4131 and the lower base 4132 and evenly distributed at four corners of the upper base 4131 and the lower base 4132, the slide block 4133 can move up and down on the guide rails 4134, one end of the push rod 411 is in a frame-shaped structure and sleeved on a crank 36, the other end of the push rod 411 is fixedly connected with the slide block 4133, the spring assembly 412 penetrates through the lower base 4132 and the slide block 4133 and is fixed on the slide block 4133, the first force sensor 414 is fixed on the spring, the loading ball 415 is embedded in the first force sensor 414 and is mounted to ensure centering accuracy. So configured, the rotation of the crank 36 is converted into the up-and-down movement of the slider 4133 through the push rod 411, and drives the spring assembly 412 to move up and down, generating a sinusoidal regular pulse radial load, which is applied to the test bearing 5 through the load first force sensor 414, the loading ball 415 and the outer sleeve 51; and the presence of the loading balls 415 at this location may reduce the effect of friction on friction torque monitoring at the force loading location.

Specifically, the spring assembly 412 includes a spring 4121, a spring housing 4122, and a spring adjustment sleeve 4123, the spring adjustment sleeve 4123 is sleeved inside the spring housing 4122, the spring housing 4122 is fixed to the slider 4133 by bolts, and the first force sensor 414 is fixed to the spring housing 4122 by bolts. This arrangement is made in consideration of the fact that the rotational movement of the crank 36 is converted into the up-and-down movement of the slider 4133 by the push rod 411 to apply a pulsating force to the test bearing 5, and if the reciprocation point and the starting point of the spring assembly 412 are not changed, the range of the pulsating force applied to the test bearing 5 is always fixed regardless of the rotation speed of the driving motor 2; therefore, the spring assembly 412 is provided with the spring adjusting sleeve 4123, pulsating force in different ranges can be output by adjusting the position of the spring 4121 force adjusting sleeve, and in addition, the change of the radial load amplitude can be realized by changing the rigidity of the spring 4121.

In the test, the spring adjusting sleeve 4123 is arranged at the initial position which does not affect the elasticity of the spring 4121 in the test process, the push rod 411 drives the slide block 4133 to move up and down, so that the pressing force range of the pulsating spring 4121 is output to be 0-120N, and then the position of the spring adjusting sleeve 4123 is adjusted to output the pulsating force of 0-60N to 60-120N.

The friction torque monitoring module 42 shown in fig. 4 includes a second force sensor 421, a connecting rod 422, and a connecting block 423, one end of the connecting block 423 is vertically embedded in the outer casing 51, and the other end of the connecting block 423 is connected with the connecting rod422, in this embodiment, the other end of the connecting block 423 is in threaded fit with the connecting rod 422, the connecting block 423 and the connecting rod 422 are perpendicular to each other, the second force sensor 421 is fixedly connected to the connecting rod 422 and fixed to the upper base 4131, and the measurement range of the second force sensor 421 is as follows. So arranged, the tangential force F can be measured_TMeanwhile, if the distance from the center of the test bearing 5 to the center axis of the connecting rod 422 is d, the friction torque from the inner ring to the outer ring when the test bearing 5 swings is M ═ F_T·d。

Specifically, the temperature detection module 43 is fixed on the upper base 4131 and aligned with the outer casing 51, and the temperature detection module 43 is an infrared temperature sensor that performs non-contact temperature measurement.

The bearing support module 44 shown in fig. 6 and 7 includes a third support side plate 441, a fourth support side plate 442, and a first support bearing 443 embedded in the third support side plate 441, and a second support bearing 444 embedded in the fourth support side plate 442, and a left half shaft 445 penetrating the third support side plate 441 and abutting against the test bearing 5, and a right half shaft 446 penetrating the fourth support side plate 442 and the test bearing 5 and abutting against the test bearing 5, the third support plate and the fourth support plate being fixed to the upper base 4131, the left half shaft 445 and the right half shaft 446 being connected by screw threads or interference fit, in this embodiment, the left half shaft 445 and the right half shaft 446 being connected by screw threads, the right half shaft 446 being interference fit with the test bearing 5, the first support bearing 443 and the second support bearing 444 having a life much longer than that of the test bearing 5, the distance between the first support bearing 443 and the second support bearing 444 should be minimized when mounting, to ensure support rigidity.

Specifically, the left half shaft 445 is connected with the guide rod shaft 35 through the coupler 6, the left half shaft 445 is in interference fit with the coupler 6, the guide rod shaft 35 is in interference fit with the coupler 6, and the coupler 6 is a rigid coupler 6. With this arrangement, the oscillating movement of the guide rod shaft 35 is transmitted to the test bearing 5 via the coupling 6.

Specifically, a left half shaft 445 and a right half shaft 446 between adjacent test modules 4 are connected through a coupling 6, the left half shaft 445 is in interference fit with the coupling 6, the right half shaft 446 is in interference fit with the coupling 6, and the coupling 6 is a rigid coupling 6. So configured, the oscillating movement of the test bearing 5 is transmitted to the next test bearing 5 via the coupling 6.

Specifically, the sliding blocks 4133 between the adjacent test modules 4 are fixedly connected by the connecting plate 7. The arrangement can realize synchronous up-and-down movement of the sliding blocks 4133 in the plurality of test modules 4, and ensure the consistency of applied load.

On the premise of ensuring the connection rigidity of all parts, the test station can be continuously expanded, as shown in fig. 8, 6 test modules 4 are provided, and the test cost is greatly saved.

It is worth explaining that, the swing motion of the test bearing 5 in each test module 4 is kept unanimous, and the up-and-down motion of the slider 4133 in each test module 4 is kept unanimous, but can also exert different ranges of radial pulsating force to the test bearing 5 in different test modules 4 through adjusting the position of the spring adjusting sleeve 4123 in each test module 4, promptly the utility model discloses still can carry out the high-speed swing bearing fatigue life test of a plurality of different conditions in a test process, very big improvement efficiency of software testing.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

Although embodiments of the present invention have been shown and described, it is to be understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that changes, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art without departing from the principles and spirit of the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. The fatigue life testing device for the high-speed oscillating bearing is characterized by comprising an operating platform (1), a driving motor (2), a rotating and oscillating conversion module (3), a plurality of testing modules (4) and a testing bearing (5), wherein the driving motor, the rotating and oscillating conversion module, the plurality of testing modules and the testing bearing (5) are positioned on the operating platform (1), and an outer sleeve (51) is sleeved on the testing bearing (5);

the test modules (4) comprise radial sine pulse loading modules (41), friction torque monitoring modules (42), temperature detection modules (43) and bearing support modules (44), the radial sine pulse loading modules (41) in the test modules (4) are connected with one another, and the bearing support modules (44) in the test modules (4) are connected with one another;

the rotation swing conversion module (3) is provided with a flywheel (31) and is directly connected with a driving motor (2), the rotation swing conversion module (3) drives the test bearing (5) to swing in a reciprocating rotation mode, and meanwhile, the rotation swing conversion module drives a radial sine pulse loading module (41) to provide pulse radial loads for the test bearing (5).

2. A high-speed oscillating bearing fatigue life testing device according to claim 1, wherein the rotary oscillating converting module (3) comprises a first supporting side plate (32), a second supporting side plate (33), a crank shaft (34) and a guide shaft (35) between the first supporting side plate (32) and the second supporting side plate (33), a crank (36) fixed on the crank shaft (34), and a guide rod (37) fixedly connected with the guide shaft (35) and connected with the crank (36), wherein the crank shaft (34) is directly connected with the driving motor (2) and is coaxial with the flywheel (31).

3. The fatigue life testing apparatus for the high-speed oscillating bearing according to claim 2, wherein the guide rod (37) is provided with a long hole (371), the crank shaft (34) is provided with a plurality of connecting holes (341), the connecting holes (341) are respectively located on concentric circles with different radii, and the crank (36) is in threaded engagement with the connecting holes (341) and passes through the long hole (371).

4. The fatigue life testing device for the high-speed oscillating bearing according to claim 2, wherein the radial sine pulse loading module (41) comprises a push rod (411), a spring assembly (412), a slider assembly (413), a first force sensor (414), a loading ball (415), an upper base (4131) and a lower base (4132), the lower base (4132) is fixed on the operating platform (1), the slider assembly (413) comprises a slider (4133), a plurality of guide rails (4134) and linear bearings (4135) sleeved on the guide rails (4134), the guide rails (4134) are fixed between the upper base (4131) and the lower base (4132), the slider (4133) can move up and down on the guide rails (4134), one end of the push rod (411) is of a frame-shaped structure and sleeves the crank (36), and the other end of the push rod (411) is fixedly connected with the slider (4133), the spring assembly (412) penetrates through the lower base (4132) and the sliding block (4133) and is fixed on the sliding block (4133), the first force sensor (414) is fixed on the spring assembly (412), and the loading ball (415) is embedded on the first force sensor (414).

5. A high speed oscillating bearing fatigue life testing apparatus according to claim 4 wherein the spring assembly (412) comprises a spring (4121), a spring housing (4122) and a spring adjustment sleeve (4123), the spring adjustment sleeve (4123) is sleeved inside the spring housing (4122), the spring housing (4122) is fixed to the slider (4133) by fasteners, and the first force sensor (414) is fixed to the spring housing (4122) by fasteners.

6. A high speed oscillating bearing fatigue life test apparatus according to claim 4, the bearing support module (44) comprises a third support side plate (441), a fourth support side plate (442), and a first support bearing (443) embedded in the third support side plate (441), and a second support bearing (444) embedded in the fourth support side plate (442), and a left half shaft (445) passing through the third support side plate (441) and abutting against the test bearing (5), and a right half shaft (446) passing through the fourth support side plate (442) and the test bearing (5) and abutting against the test bearing (5), the third support plate and the fourth support plate are fixed on the upper base (4131), the left half shaft (445) and the right half shaft (446) are connected through threads or in interference fit, and the right half shaft (446) is in interference fit with the test bearing (5).

7. The high-speed oscillating bearing fatigue life testing device according to claim 4, wherein the friction torque monitoring module (42) comprises a second force sensor (421), a connecting rod (422) and a connecting block (423), one end of the connecting block (423) is vertically embedded into the outer sleeve (51), the other end of the connecting block (423) is in threaded fit or interference fit with the connecting rod (422), the connecting block (423) and the connecting rod (422) are perpendicular to each other, and the second force sensor (421) is fixedly connected to the connecting rod (422) and fixed to any one of a third supporting side plate (441), a fourth supporting side plate (442) and an upper base (4131).

8. A high speed oscillating bearing fatigue life testing apparatus according to claim 1, wherein the temperature sensing module (43) is fixed on the upper base (4131) and aligned with the outer sleeve (51), the temperature sensing module (43) being an infrared temperature sensor.

9. The high-speed oscillating bearing fatigue life testing device according to claim 6, wherein the left half shaft (445) is connected with the guide rod shaft (35) through a coupler (6), the left half shaft (445) between the adjacent test modules (4) is connected with the right half shaft (446) coupler (6), the left half shaft (445) is in interference fit with the coupler (6), the right half shaft (446) is in interference fit with the coupler (6), the guide rod shaft (35) is in interference fit with the coupler (6), and the coupler (6) is a rigid coupler (6).

10. A high speed oscillating bearing fatigue life test apparatus according to claim 4, characterized in that the sliders (4133) between adjacent test modules (4) are fixedly connected by springs (4121).