Lubrication mechanism of bearing testing machine and bearing testing machine

Abstract

We provide a lubrication mechanism for a bearing testing machine. [Solution] The present invention discloses a bearing testing machine lubrication mechanism and a bearing testing machine, comprising a flange, a flange end cap, an outer sleeve member and an inner sleeve member, wherein the first end face of the flange is provided with an oil drain port I, the flange end cap comprises an end cap and a flange portion I provided circumferentially in the direction of the center hole of the end cap, and a lubricating oil hole is further provided along the axial direction of the flange end cap, the lubricating oil hole is located on one side of the center hole of the end cap, the outer sleeve member is provided with a cavity II that penetrates along the axial direction, the two ports of the cavity II of the outer sleeve member are each fitted into the flange portion I of the flange end cap, the outer sleeve member is provided with a lubricating oil passage I along the axial direction, one end of the lubricating oil hole is connected to the oil drain port I, and the other end of the lubricating oil hole is connected to the lubricating oil passage I, and by optimizing the structure, this device rationally simplifies the structure of the bearing testing machine, facilitates the disassembly, assembly and replacement of test bearings, and solves the problem of difficulty in replacing bearings in existing testing machines.

Description

Technical Field

[0001] The present invention belongs to the technical field of testing machines, and specifically relates to a lubrication mechanism of a bearing testing machine and a bearing testing machine.

Background Art

[0002] With the rapid development of China's modern industry, rolling bearings have become generally used basic components. High-speed rolling bearings are core components of high-end mechanical equipment, and their fatigue life has a great impact on performance indicators such as the use performance and service life of the main body. Since the operating conditions of high-speed bearings affect the safety of equipment, engineering technicians have always been interested in their operating conditions. If a small bearing is damaged, it may lead to many accidents. For example, China's railway transportation is developing rapidly, and the operating speed of electric locomotives is constantly increasing. Currently, the motor of the 300 km / h electric locomotive developed in China has abnormal wear on the motor bearing during operation, resulting in increased vibration of the motor and inability to operate. Therefore, in order to solve these problems and study the operating conditions of the motor bearing at 300 km / h, it is necessary to analyze and solve these problems using a high-speed bearing life testing machine.

[0003] Furthermore, even when bearings operate under good mounting, lubrication, and maintenance conditions, the periodically changing stress can cause small pieces or lumps to peel off from each load-bearing element, forming pits or depressions and potentially leading to fatigue pitting corrosion. This can cause components to generate noise, wear, vibration, and temperature rise during operation, leading to component failure. Various failure modes such as fatigue pitting corrosion, plastic deformation, wear, and adhesion seriously affect the lifespan of high-speed bearings. The dynamic performance of bearings at high rotational speeds is not only affected by preload but also greatly related to the rotational speed and the characteristics of the ball material. If a bearing problem occurs during the production process, it can cause failure of the entire mechanical transmission system, affecting production efficiency and resulting in enormous economic losses. Therefore, it is essential to perform reliability testing on bearings during the production process. For high-speed rolling bearings, a friction-damping elastic support structure can be adopted to suppress excessive vibration when the rotor system passes the critical speed. Bearing life testers can achieve the objective of evaluating bearing life by simulating various loads, vibrations, temperatures, lubrication, and other environmental conditions that bearings experience under actual operating conditions and conducting long-term operation tests. Bearing life testing machines allow for a comprehensive and systematic understanding of bearing performance, lifespan, and reliability, providing a scientific basis for the design and manufacture of bearing products. Simultaneously, by performing timely replacements or repairs based on test results during future maintenance and servicing processes, the service life of bearings can be extended, failure rates reduced, and production efficiency and product quality improved. Therefore, research into bearing life testing machines has significant practical and economic value.

[0004] Conventional technologies still fail to meet the requirements for safety, stability, and accuracy of testing machines. Furthermore, to increase test loads and improve test effectiveness, some companies are intensifying test conditions by using heavier working fluids or altering bearing surface deformation. While simulation testing techniques can quickly evaluate bearing reliability, they struggle to effectively address issues such as high cost, long cycles, and complex couplings. [Overview of the project] [Problems that the invention aims to solve]

[0005] The object of the present invention is to provide a lubrication mechanism for a bearing testing machine and a bearing testing machine in order to solve the problems that exist in the prior art described above. This device rationally simplifies the structure of the bearing testing machine by optimizing its structure, facilitates the disassembly, assembly, and replacement of test bearings, and solves the problem that existing testing machines make it difficult to replace bearings. [Means for solving the problem]

[0006] One of the objects of the present invention is to provide a lubrication mechanism for a bearing testing machine, which includes a flange, a flange end cap, an outer sleeve member, and an inner sleeve member, wherein an oil drain port I is provided on the first end face of the flange. The flange end cap includes an end cap and a flange portion I provided in the circumferential direction of the end cap's central hole, and further, lubricating oil holes are provided along the axial direction of the flange end cap, with the lubricating oil holes located on one side of the end cap's central hole. The outer sleeve member is provided with a cavity II that penetrates axially, and the two ports of the cavity II of the outer sleeve member are each fitted into the flange I of the flange end cover, and the outer sleeve member is provided with a lubricating oil passage I axially, one end of the lubricating oil hole is connected to the drain port I, and the other end of the lubricating oil hole is connected to the lubricating oil passage I. The inner sleeve member is installed in the cavity II, and the inner sleeve member is provided with a lubricating oil passage II along the axial direction. A connecting oil hole I communicating with the lubricating oil passage I is formed in the inner wall of the outer sleeve member, and a connecting oil hole II communicating with the lubricating oil passage II is provided in the outer wall of the inner sleeve member. The connecting oil hole I and the connecting oil hole II are provided facing each other on the inside and outside, enabling communication between the lubricating oil passage I and the lubricating oil passage II. The lubricating oil passage II is arranged to supply oil to a pair of bearings located in the middle of the rotor, and an oil drain port II is provided on the second end face of the flange. The oil drain port II is arranged to supply oil to a pair of bearings located at both ends of the rotor.

[0007] As a preferred solution, the circumferential surface of the flange is further provided with oil inlets that communicate with oil drain port I and oil drain port II.

[0008] A second object of the present invention is to provide a bearing detection testing machine that includes a lubrication mechanism for the bearing testing machine described in any one of the above items.

[0009] A preferred solution further includes a rotor, a test bearing assembly, a test auxiliary bearing assembly, and a radial load sleeve, wherein the rotor includes a large diameter portion and small diameter portions located at both ends of the large diameter portion, the large diameter portion and the small diameter portion are provided coaxially, and a mounting step is formed at the connection point between the large diameter portion and the small diameter portion. The test bearing assembly includes a first test bearing and a second test bearing, each mounted on the smaller diameter portions on both sides, with one end of the inner ring of the first and second test bearings abutting against the mounting step of the rotor, the inner rings of the first and second test bearings fitted to the rotor, an outer sleeve member fitted to the outside of the outer rings of the first and second test bearings, a radial load sleeve fitted to the outside of the outer sleeve member, and both ends of the radial load sleeve fixed and connected to the flange end caps. The test auxiliary bearing assembly includes a first test auxiliary bearing and a second test auxiliary bearing, the first and second test auxiliary bearings located on the small diameter portion of the rotor, and the first and second test auxiliary bearings located on either side of the test bearing assembly, Or, The rotor includes a large-diameter section and small-diameter sections located at both ends of the large-diameter section, the large-diameter section and the small-diameter section are arranged coaxially, and a mounting step is formed at the connection point between the large-diameter section and the small-diameter section. The test auxiliary bearing assembly includes a first test auxiliary bearing and a second test auxiliary bearing, each mounted on the smaller diameter portions on both sides, with one end of the inner ring of the first and second test auxiliary bearings abutting against the mounting step of the rotor, the inner rings of the first and second test auxiliary bearings fitted to the rotor, an outer sleeve member fitted to the outside of the outer ring of the first and second test auxiliary bearings, a radial load sleeve fitted to the outside of the outer sleeve member, and both ends of the radial load sleeve fixed and connected to the flange end caps. The test bearing assembly includes a first test bearing and a second test bearing, the first and second test bearings located on the small diameter portion of the rotor, and the first and second test bearings located on either side of the test auxiliary bearing assembly, respectively.

[0010] A preferred solution further includes an axial loading mechanism, the axial loading mechanism comprising an axial loading hydraulic cylinder and an axial loading body, the axial loading hydraulic cylinder being located on a third bracket, the axial loading body being detachably connected to the piston rod of the axial loading hydraulic cylinder, and the axial loading body being positioned to enter the internal cavity of the loading inner sleeve in the second bushing to apply an axial loading force to the test bearing.

[0011] As a preferred solution, a first bushing is fitted to the outside of the first test auxiliary bearing, the first end of the first bushing is fixed in the mounting cavity of the flange, and the other end of the first bushing is connected to the first bearing through cover. The first bush is provided with a cavity V along the axial direction, and the first bearing through cover includes an end plate and a flange portion II provided at the center of the end plate, the flange portion II entering the cavity V and forming an axial stopper for one end of the first test auxiliary bearing or the first test bearing. The second test auxiliary bearing or the second test bearing is provided inside the load inner sleeve, the second bush has a cavity VI along the axial direction, the load inner sleeve is provided inside the cavity VI of the second bush, one end of the second bush and the load inner sleeve is fixed inside the mounting cavity of the flange, and the first bush and the second bush are each connected to the second bracket via a support frame.

[0012] A preferred solution further includes shaft sleeves I and II, wherein both ends of shaft sleeve I abut against the inner ring of the first test auxiliary bearing and the inner ring of the first test bearing, respectively, and both ends of shaft sleeve II abut against the inner ring of the second test bearing and the inner ring of the second test auxiliary bearing, respectively, and the other end of the second test auxiliary bearing or the inner ring of the second test bearing abuts against a shaft end cap, which is fixed to the rotor.

[0013] A preferred solution further includes a radial load hydraulic cylinder, the piston rod of which can be fixedly connected to the outer wall of the radial load sleeve via a stud.

[0014] A preferred solution is that the rotor further includes a coupling portion, the coupling portion being connected to a smaller diameter portion on one side thereof, and the coupling portion being connected to the rotating shaft of a drive motor via the coupling. [Effects of the Invention]

[0015] Compared to the prior art, the present invention has at least the following beneficial effects.

[0016] Firstly, the lubrication mechanism of this solution improves the structure, coordinating the flange, flange end cap, outer sleeve member, and inner sleeve member, and combining this with the design of the lubrication oil passages to realize oil supply to the test bearing and test auxiliary bearing. Of these, drain ports I and II are provided on both end faces of the flange, respectively. Drain port I realizes oil supply to a pair of bearings located in the middle of the rotor via lubrication oil passage I, connecting oil hole I, connecting oil hole II, and lubrication oil passage II, while drain port II is positioned to directly supply oil to a pair of bearings located at both ends of the rotor. As a result, the test bearing and test auxiliary bearing are lubricated by a single set of oil passage systems, realizing lubrication of the entire rotor system, ensuring lubrication during the testing process, and improving the reliability of the lubrication effect of the entire system.

[0017] Secondly, the bearing testing machine of this solution, through optimization and improvement, has a simpler and more rational structure, making it easier to replace the test bearings, solving the problem of difficulty in replacing test bearings due to the complex structure of the testing machine. Axial load can be applied to the test bearing by an axial load hydraulic cylinder, a first frame, and an axial load load body, and radial load can be applied to the test bearing by a radial load hydraulic cylinder, a second frame, a radial load load sleeve, an outer sleeve member, and an inner sleeve member. This solution has a simple and rational design structure, is easy to install, provides stable and reliable load application, and is easy to maintain. The axial load load body is replaceable, expanding the range of axial load application when loading bearings of different types. By expanding the range of application of the axial load load body, the equipment can simultaneously meet axial load requirements under different operating conditions, becoming more stable and reliable during use. Expanding the range of application of the axial load load body helps reduce the cost of equipment replacement and maintenance, improving equipment utilization and economic benefits. Furthermore, expanding the application range of axial load loaders can improve the production efficiency and quality of equipment, allowing the equipment to maintain efficient and stable operation under different operating conditions, thereby enhancing the competitiveness of companies. Therefore, expanding the application range of axial load loaders is of great importance, improving the adaptability and flexibility of test equipment, enhancing production efficiency and quality, reducing maintenance costs, and bringing about significant economic benefits.

[0018] Thirdly, this solution takes into account the large amount of heat and frictional force generated during the prolonged operation of the testing machine. These factors cause a certain amount of wear and damage to the test bearings and transmission devices inside the testing machine. (In the prior art, the testing machine needs to clamp and fix the test bearings when performing tests, and the fixtures and fixing devices of the testing machine often generate a certain amount of frictional force and pressure on the test bearings, and further cause wear or deformation on their surfaces.) This solution reduces damage to the test bearings by adding auxiliary test bearings on the outside or inside of the test bearings, thereby ensuring the reliability and accuracy of the test results.

Brief Description of the Drawings

[0019] To more clearly explain the technical solutions in the embodiments of the present invention or the prior art, the drawings necessary for the description of the embodiments or the prior art will be briefly described below. Obviously, the drawings described below are only some embodiments of the present invention, and those skilled in the art can obtain other drawings based on these drawings without creative effort.

[0020] [Figure 1] It is a perspective view of the testing machine of the present invention. [Figure 2] It is a front view of the testing machine of the present invention. [Figure 3] It is a plan view of the testing machine of the present invention. [Figure 4] It is a cross-sectional view of the testing machine of the present invention. [Figure 5] It is a schematic diagram of the installation of the test bearing in the first embodiment of the present invention. [Figure 6] It is a schematic diagram of the installation of the test bearing in the second embodiment of the present invention. [Figure 7] It is a structural cross-sectional view of the third embodiment of the present invention. [Figure 8] It is an internal structure diagram of the hydraulic cylinder of the present invention. [Figure 9] It is a structural diagram of the radial load sleeve of the present invention. [Figure 10] It is a structural diagram of the flange end cover of the present invention. [Figure 11] It is a structural diagram of the rotor of the present invention. [Figure 12] It is a structural diagram of the axial load body of the present invention. [Figure 13] It is a structural diagram of the bush of the present invention. [Figure 14] It is a structural diagram of the flange of the present invention. [Figure 15] It is a structural diagram of the outer sleeve member of the present invention.

Modes for Carrying Out the Invention

[0021] The present invention will be described in detail below with reference to exemplary embodiments. However, it should be understood that elements, structures, and features of one embodiment may be usefully incorporated into other embodiments without further detail.

[0022] Unless otherwise defined, technical or scientific terms used herein should have the ordinary meaning understood by those skilled in the art. Similar terms such as “one,” “one,” or “the said” used in the patent application and claims of the present invention do not limit the quantity but indicate that there is at least one. Similar terms such as “equipment” or “includes” indicate that the element or article appearing before “equipment” or “includes” covers the elements or articles and their equivalents listed after “equipment” or “includes,” but do not exclude other elements or articles having the same function.

[0023] Example 1 This embodiment provides a lubrication mechanism for a bearing testing machine, comprising a flange end cover 2, an outer sleeve member 3, and an inner sleeve member 4. Both the outer sleeve member 3 and the inner sleeve member 4 are shaft sleeve structures and are coaxially fitted. The outer sleeve member 3 is provided with a cavity II3-3 along the axial direction for housing the inner sleeve member 4, and the inner sleeve member 4 is located in the middle part inside the cavity II3-3. The flange end cover 2 comprises a flange end cover I210 and a flange end cover II220. Each end cover II220 includes an end cover and a flange portion I2-2 located on one end face of the end cover. An end cover central hole 2-1 is formed in the center of the flange end cover 2, and the flange portion I2-2 is circumferentially arranged in the direction of the end cover central hole 2-1. The flange portion I2-2 of the flange end cover I210 enters the interior of the first port of the cavity II3-3 and abuts against the first end of the outer ring of the first test bearing 7, and the flange portion I2-2 of the flange end cover II220 enters the interior of the second port of the cavity II3-3 and abuts against the first end of the outer ring of the second test bearing 8.

[0024] In this solution, the outer sleeve member 3 is further provided with a lubricating oil passage I3-1 along the axial direction, and the lubricating oil passage I3-1 is located on the outer peripheral side wall of the cavity II3-3, and a connecting oil hole I3-2 is further provided on the inner wall of the cavity II3-3. Felt rings 27 are provided between both ends of the outer sleeve member 3 and the radial load sleeve 6 and the flange end caps I210 and II220, respectively.

[0025] In this solution, the inner sleeve member 4 is provided with a cavity III 4-3 along the axial direction, and the rotor 5 is passed through the inside of the cavity III 4-3, forming a gap fit between the cavity III 4-3 and the rotor 5, that is, the inner sleeve member 4 functions as a spacer. The inner sleeve member 4 is further provided with a lubricating oil passage II 4-1 along the axial direction, and the lubricating oil passage II 4-1 is located on one side of the cavity III 4-3. The outer wall of the inner sleeve member 4 is further provided with a connecting oil hole II 4-2, and the connecting oil hole I 3-2 and the connecting oil hole II 4-2 are abutted against each other on the inside and outside, arranged to enable communication between the lubricating oil passage I 3-1 and the lubricating oil passage II 4-1. Both ends of the inner sleeve member 4 abut against the outer rings of the first test bearing 7 (test bearing 1) and the second test bearing 8 (test bearing 2), respectively, while the inner sleeve member 4 does not contact the inner rings of the first test bearing 7 and the second test bearing 8, and the inner rings of the first test bearing 7 and the second test bearing 8 abut against the mounting step 5-4 of the rotor 5.

[0026] In this solution, both flange end caps I210 and II220 are provided with lubrication oil holes 2-3 along the axial direction, flange I110 is located outside flange end cap I210, and an oil drain port I1-3 is provided on the end face of flange I110 facing flange end cap I210, and the oil drain port I1-3 of flange I110 abuts against the first end of lubrication oil passage I3-1 via lubrication oil hole 2-3, and an oil drain port I1-3 is provided on the end face of flange II120 facing flange end cap II220, and the oil drain port I1-3 of flange II120 abuts against the second end of lubrication oil passage I3-1 via lubrication oil hole 2-3. As a result, oil is supplied simultaneously into lubrication oil passage I3-1 through the flanges at both ends. A first test bearing 7 and a second test bearing 8 are provided at both ends of the lubrication oil passage II4-1, respectively, and the lubrication oil passage II4-1 is arranged to supply oil to the first test bearing 7 and the second test bearing 8, respectively.

[0027] In this embodiment, an oil drain port II1-4 is further provided on the end face of flange I110 opposite to the flange end cover I210, and a first test auxiliary bearing 9 (test auxiliary bearing 1) is provided correspondingly at the end of the oil drain port II1-4 of flange I110, and an oil drain port II1-4 is further provided on the end face of flange II120 opposite to the flange end cover II220, and a second test auxiliary bearing 10 (test auxiliary bearing 2) is provided correspondingly at the end of the oil drain port II1-4 of flange II120, and is arranged to supply oil to the first test auxiliary bearing 9 and the second test auxiliary bearing 10, respectively.

[0028] In this embodiment, oil inlets 1-2 are provided on the outer circumferential surfaces of flange I110 and flange II120, and nozzle joints 1-6 for supplying oil to the inside of the lubrication mechanism are provided in each of the oil inlets 1-2. The first test bearing 7, the second test bearing 8, the first test auxiliary bearing 9, and the second test auxiliary bearing 10 are arranged coaxially.

[0029] In this embodiment, there is another embodiment which is the same as the other configuration described above, except that the positions of the first test bearing 7 and the first test auxiliary bearing 9 are swapped, and the positions of the second test bearing 8 and the second test auxiliary bearing 10 are swapped. In this embodiment, the oil drain ports I1-3 are arranged to supply oil to the first test auxiliary bearing 9 and the second test auxiliary bearing 10, respectively, and the oil drain ports II1-4 are arranged to supply oil to the first test auxiliary bearing 9 and the second test auxiliary bearing 10, respectively.

[0030] Example 2 This embodiment provides a bearing testing machine comprising a rotor 5, a test bearing assembly, a test auxiliary bearing assembly, a radial load sleeve 6, and a lubrication mechanism as in Embodiment 1. The test bearing assembly includes a first test bearing 7 and a second test bearing 8, and the test auxiliary bearing assembly includes a first test auxiliary bearing 9 and a second test auxiliary bearing 10. The first test auxiliary bearing 9 and the second test auxiliary bearing 10 are located on the outside of both ends of the test bearing assembly, and the first test auxiliary bearing 9, the first test bearing 7, the second test bearing 8, and the second test auxiliary bearing 10 are fitted to the rotor 5 in order and are provided coaxially.

[0031] In this solution, the rotor 5 includes a large diameter portion 5-1, a small diameter portion 5-2, and a coupling portion 5-3. The small diameter portion 5-2 has two parts, each located at both ends of the large diameter portion 5-1. The large diameter portion 5-1, the small diameter portion 5-2, and the coupling portion 5-3 are arranged coaxially. A mounting step 5-4 is formed at the connection point between the large diameter portion 5-1 and the small diameter portion 5-2. The first test bearing 7 and the second test bearing 8 are each attached to the two small diameter portions 5-2. One end of the inner ring of the first test bearing 7 and the second test bearing 8 fits with the mounting steps 5-4 on both sides to form an axial stopper. The other end of the inner ring of the first test bearing 7 abuts against the shaft sleeve I18 to form the axial position of the first test bearing 7, and the other end of the inner ring of the second test bearing 8 abuts against the shaft sleeve II19 to form the axial position of the second test bearing 8. The coupling portion 5-3 of the rotor 5 is connected to the power output shaft of the drive motor 60 via the coupling 70 and bolt I101. Specifically, the coupling portion 5-3 of the rotor 5 is connected to the coupling 70 via key 5-6 and keyway 5-5, and the coupling 70 is connected via bolt I. The drive motor 60, the coupling 70, and the third bracket 50 supporting the drive motor 60 constitute a rotational speed control unit.

[0032] In this embodiment, a cavity I1-1 is formed in the flange I110 along its axial center, one end of the shaft sleeve I18 is mounted in the central hole of the flange end cap I210, and the other end extends through the cavity I1-1 of the flange I110, with the end of the cavity I1-1 abutting against one end of the inner ring of the first test auxiliary bearing 9, a central boss is formed at the first end of the flange I110 that contacts the flange end cap I210, and a mounting cavity for connecting the first bush 11 is formed at the second end of the flange I110, with one end of the first bush 11 fixed inside the mounting cavity of the flange I110 by a stud. An annular mounting groove 24 is provided in the inner ring of the central hole of the flange end cap I210, and an O-ring 26 is mounted in the mounting groove 24 and positioned to achieve a seal between the shaft sleeve I18 and the flange end cap I210.

[0033] In this solution, a cavity V is formed in the first bush 11 along the axial direction, the first bush 11 is fitted to the outside of the first test auxiliary bearing 9, the flange portion of the through cover I13 penetrates the inside of the cavity V of the first bush 11, and positions the first test auxiliary bearing 9 axially from the other end, and the through cover I13 and the first bush 11 are fixed and connected by bolts II102. A slinger I24 is further provided between the first test auxiliary bearing 9 and the through cover I13, and the slinger I24 is positioned to seal the lubricating oil of the first test auxiliary bearing 9 and to position and stop the first test auxiliary bearing 9 axially. After the first bush 11 and the through cover I13 are butted together, a groove region is formed on its outer circumference for connection to the support frame 15.

[0034] In this embodiment, a cavity is formed along the axial center of the flange II120 at the other end of the testing machine body, one end of the shaft sleeve II19 is mounted in the central hole of the flange end cover II220, the other end extends through the cavity of the flange II120, the end of the shaft sleeve II19 abuts against one end of the inner ring of the second test auxiliary bearing 10, a central boss is formed at the first end of the flange II120 that contacts the flange end cover II220, a mounting cavity for connecting the second bush 12 is formed at the second end of the flange II120, one end of the second bush 12 is fixed inside the mounting cavity of the flange II120 by a stud, an annular groove is provided in the inner ring of the central hole of the flange end cover II220, an O-ring 26 is mounted in the mounting groove 24 and arranged to achieve a seal between the shaft sleeve II19 and the flange end cover II220. The other end and the through cover II21 are fixed and connected by bolt IV104, and the internal cavity of the through cover II21 is interlocked with the load inner sleeve 23, loading the inner sleeve. One end of the second bush 12 is fixed inside the mounting cavity 1-5 of the flange II120 and is screwed into the threaded blind hole 123 of the second bush 12 and fixed by screw, and a stop boss 122 that engages with the flange II120 is provided on the circumferential side of the second bush 12. A cavity VI121 is formed in the second bush 12 along the axial direction, and the cavity VI121 of the second bush 12 is fitted to the outside of the second test auxiliary bearing 10. An end cap 22 is provided at the other end of the second test auxiliary bearing 10, and the end cap 22 is fixed and connected to the rotor 5 by a screw 105, and contacts the inner ring of the second test auxiliary bearing 10, stopping and positioning the second test auxiliary bearing 10 in the axial direction.

[0035] In this embodiment, a lubrication mechanism for supplying lubricating oil to the test machine body is further included. The lubrication mechanism is provided on the outer circumference of the rotor 5, the test bearing assembly, and the test auxiliary bearing assembly, and is used to lubricate the test bearing assembly and the test auxiliary bearing assembly.

[0036] The lubrication mechanism can employ the following embodiment: It includes a flange end cap 2, an outer sleeve member 3, and an inner sleeve member 4, both of which are axial sleeve structures and are fitted coaxially, the outer sleeve member 3 is provided with a cavity II3-3 along the axial direction for housing the inner sleeve member 4, and the inner sleeve member 4 is located in the middle part inside the cavity II3-3, the flange end cap 2 includes a flange end cap I210 and a flange end cap II220, both of which include an end cap and a flange portion I2-2 located on one end face of the end cap, and the center of the flange end cap 2 has an end cap central hole 2-1 A flange portion I2-2 is formed, and the flange portion I2-2 is provided circumferentially in the direction of the end cover central hole 2-1. The flange portion I2-2 of the flange end cover I210 enters the interior of the first port of the cavity II3-3 and abuts against the first end of the outer ring of the first test bearing 7. The flange portion I2-2 of the flange end cover II220 enters the interior of the second port of the cavity II3-3 and abuts against the first end of the outer ring of the second test bearing 8. The outer sleeve member 3 is further provided with a lubricating oil passage I3-1 along the axial direction, and the lubricating oil passage I3-1 is located on the outer peripheral side wall of the cavity II3-3. The inner wall of the cavity II3-3 is further provided with a connecting oil hole I3-2.

[0037] In this solution, the inner sleeve member 4 is provided with a cavity III 4-3 along the axial direction, and the rotor 5 is passed through the inside of the cavity III 4-3, forming a gap fit between the cavity III 4-3 and the rotor 5. The inner sleeve member 4 is further provided with a lubricating oil passage II 4-1 along the axial direction, and the lubricating oil passage II 4-1 is located on one side of the cavity III 4-3. The outer wall of the inner sleeve member 4 is further provided with a connecting oil hole II 4-2, and the connecting oil hole I 3-2 and the connecting oil hole II 4-2 are abutted against each other on the inside and outside, and are arranged to enable communication between the lubricating oil passage I 3-1 and the lubricating oil passage II 4-1.

[0038] In this solution, a radial load sleeve 6 is provided on the outside of the outer sleeve member 3, and a cavity IV6-1 is provided in the radial load sleeve 6 along the axial direction to accommodate the outer sleeve member 3. Both ends of the radial load sleeve 6 are fixed and connected to the flange end cap I210 and flange end cap II220 by bolts III103, respectively. Screw holes 6-2 connected to bolts III103 are provided at both ends of the radial load sleeve 6, and through holes 2-5 corresponding to the screw holes 6-2 are provided in the flange end cap I210 and flange end cap II220, respectively. Screw through holes 6-3 are provided in the outer wall of the radial load sleeve 6, and the screw through holes 6-3 are connected to the piston rod of the radial load hydraulic cylinder 20. By applying a radial force to the radial load sleeve 6 with the piston rod of the radial load hydraulic cylinder 20, a radial load test is performed on the first test bearing 7 and the second test bearing 8.

[0039] In this solution, both flange end caps I210 and II220 are provided with lubrication oil holes 2-3 along the axial direction, flange I110 is located outside flange end cap I210, and an oil drain port I1-3 is provided on the end face of flange I110 facing flange end cap I210, and the oil drain port I1-3 of flange I110 abuts against the first end of lubrication oil passage I3-1 via lubrication oil hole 2-3, and an oil drain port I1-3 is provided on the end face of flange II120 facing flange end cap II220, and the oil drain port I1-3 of flange II120 abuts against the second end of lubrication oil passage I3-1 via lubrication oil hole 2-3. As a result, oil is supplied simultaneously into lubrication oil passage I3-1 through the flanges at both ends. A first test bearing 7 and a second test bearing 8 are provided at both ends of the lubrication oil passage II4-1, respectively, and the lubrication oil passage II4-1 is arranged to supply oil to the first test bearing 7 and the second test bearing 8, respectively.

[0040] In this embodiment, an oil drain port II1-4 is further provided on the end face of flange I110 opposite to the flange end cover I210, and a first test auxiliary bearing 9 is provided correspondingly at the end of the oil drain port II1-4 of flange I110, and an oil drain port II1-4 is further provided on the end face of flange II120 opposite to the flange end cover II220, and a second test auxiliary bearing 10 is provided correspondingly at the end of the oil drain port II1-4 of flange II120, and is arranged to supply oil to the first test auxiliary bearing 9 and the second test auxiliary bearing 10, respectively.

[0041] In this embodiment, oil inlets 1-2 are provided on the outer circumferential surfaces of flange I110 and flange II120. They are positioned to supply oil to the inside of the lubrication mechanism. The first test bearing 7, the second test bearing 8, the first test auxiliary bearing 9, and the second test auxiliary bearing 10 are provided coaxially. The first test auxiliary bearing 9 and the second test auxiliary bearing 10 employ angular contact ball bearings.

[0042] In this solution, in order to perform an axial load test on the test bearing, the first test bearing 7 and the second test auxiliary bearing 9 need to swap positions based on the lubrication mechanism, and the second test bearing 8 and the third test auxiliary bearing 10 need to swap positions. As a result, the axial load body 17 directly applies the axial load force to the test bearing. In this solution, the axial load body 17 enters the cavity VI of the second bush 12, and the axial load body 17 applies an axial load to the second test bearing 8 via the slinger II 25. An end face cavity 171 is formed on one side of the axial load body 17 facing the rotor 5, and the end face cavity 171 is arranged to accommodate and retract the shaft end of the rotor 5. The axial load body 17 is provided with a positioning screw hole 172, and a positioning screw 106 is installed in the positioning screw hole 172. The axial load body 17 and the piston rod of the axial load hydraulic cylinder 16 are fixed and connected by bolts. This design allows for the replacement and adaptation of different axial loads 17 depending on the bearing. An inner load sleeve 23 is provided on the outer circumference of the axial load 17, and a cavity is provided in the inner load sleeve 23 along the axial direction, and the axial load 17 is mounted within the cavity of the inner load sleeve 23. A limit stop groove 107 is formed in the inner load sleeve 23 along the axial direction, and a positioning screw 106 of the axial load 17 engages with the limit stop groove 107. As the positioning screw 106 moves along the axial direction toward the second test bearing 8 together with the axial load 17, the limit stop groove 107 limits the maximum movement limit position of the axial load 17.

[0043] In this solution, the axial load hydraulic cylinder 16 is a core component of the axial load loading portion, and the axial load hydraulic cylinder 16 can adopt the following embodiments. The cylinder body 161 includes a cavity formed in the cylinder body 161 through which a piston 166 moves axially. A cylinder head end cover 162 and a cylinder bottom end cover 163 are fixedly connected to both ends of the cavity of the cylinder body 161, respectively. A central hole is formed in the center of the cylinder head end cover 162 through which the first end of the piston rod 165 extends. A step seal 164 is provided circumferentially around the central hole, positioned to ensure a seal between the piston rod 165 and the inner wall of the central hole. The second end of the piston rod 165 is fixedly connected to the piston 166. A guide sleeve 167 is attached circumferentially around the outer circumference of the piston 166, and the guide sleeve 167 contacts the inner wall of the cavity of the cylinder body 161. A seal ring I 168 is further provided circumferentially around the piston 166, positioned to ensure a seal of hydraulic fluid on this side. A seal ring II 169 is provided circumferentially around the cylinder bottom end cover 162, positioned to ensure a seal of hydraulic fluid on this side. A lubrication passage is provided in the cylinder bottom end cover 163, and an oil chamber space for hydraulic fluid is formed between the piston 166 and the cylinder bottom end cover 163. The oil chamber space automatically expands or contracts by promoting the movement of the piston according to the amount of lubrication supplied, and at the same time realizes the extension and contraction function of the piston rod 165. During operation, hydraulic fluid is introduced from the oil passage at the bottom of the hydraulic cylinder, pressure is applied to the piston 166, and the piston 166 begins to move along the cylinder body 161 of the hydraulic cylinder. The internal structure of the radial load hydraulic cylinder 20 is the same as or similar to the structure of the axial load hydraulic cylinder 16.

[0044] In another embodiment of the present invention, elastic support rings 28 are provided at positions corresponding to the bearings in the cavity of the first bush 11 and at positions corresponding to the bearings in the cavity of the load inner sleeve 23, with the elastic support rings 28 in contact with the outer rings of the first test auxiliary bearing 9 and the second test auxiliary bearing 10, respectively. Alternatively, the elastic support rings 28 are in contact with the outer rings of the first test bearing 7 and the second test bearing 8, respectively. The elastic support rings 28 provided on the testing machine can reduce vibration and noise, improve stability, reduce friction, and improve accuracy. Their friction-damping elastic support effectively reduces the energy transmitted by mechanical vibrations to the bearings and other components, thereby reducing noise and vibration generated by the testing machine. This helps protect the bearings and other critical components from damage due to vibration and shock, extending their service life. The elastic support structure improves the stability and balance of the testing machine, making it more stable during high-speed operation. This helps ensure that the bearings are accurately tested and evaluated, and that errors due to instability of the testing machine itself are avoided. Friction-damping elastic supports reduce friction between the bearing and the support structure, thereby reducing energy loss and heat generation. This helps improve the efficiency of the testing machine, which is especially important for tests that operate for long periods, as it reduces wear and heat buildup due to friction. Elastic support structures can reduce the influence of external interference on test results and improve the test accuracy of the testing machine. This is especially important for bearing performance evaluation that requires high-precision measurements, and by ensuring the accuracy and reliability of test results, it can provide more reliable support for bearing research and development work.

[0045] This invention provides a high-speed bearing life and motion state detection tester, thereby completing high-speed bearing life experiments. The invention mainly comprises four parts: a rotational speed control section, a tester structure body, an axial load loading section, and a radial load loading section. The invention allows axial load loading to be applied to the test bearing by an axial load hydraulic cylinder 16, a first bracket 30, and an axial load body 17. The structural design is simple and easy to install. The load loading in this solution is stable and reliable, and maintenance is convenient. Since the axial load body and the axial load hydraulic cylinder 16 are detachably connected by bolts, the axial load body 17 is replaceable, expanding the range of axial load application when loading bearings of different types. By expanding the applicability range of the axial load body 17, the equipment can simultaneously meet axial load requirements under different operating conditions, resulting in greater stability and reliability during use. Expanding the applicability range of the axial load body helps reduce equipment replacement and maintenance costs, improving equipment utilization and economic benefits. Furthermore, expanding the application range of axial load loaders can improve the production efficiency and quality of equipment, allowing the equipment to maintain efficient and stable operation under different operating conditions. Therefore, expanding the application range of axial load loaders can improve the adaptability and flexibility of equipment, enhance production efficiency and quality, reduce maintenance costs, and yield more significant economic benefits.

[0046] In this solution, the bearing testing machine needs to apply a constant load to the test bearing. In the case of a radial load, a force must be applied to the test bearing in a vertically downward direction. In the case of an axial load, the force must be aligned with the direction of the main shaft axis, and the applied pressure must be stabilized. In this invention, both the axial load hydraulic cylinder 16 and the radial load hydraulic cylinder can be pull-rod type hydraulic cylinders.

[0047] This testing machine, through structural optimization, features a simple and rational structural design, facilitates the replacement of test bearings, and simultaneously incorporates vibration sensors and temperature sensors pre-installed on the tools used to assemble the test bearings. This allows for real-time monitoring of bearing vibration and temperature changes during the testing process, resulting in more accurate test data and the collection of data on the bearing condition immediately before bearing failure. Specifically, vibration sensors and temperature sensors are provided inside flange 1 to monitor the operating state of the test auxiliary bearing, and vibration sensors and temperature sensors are further provided inside outer sleeve member 3 to monitor the operating state of the test bearing. The vibration sensors and temperature sensors may use wireless or wired transmission methods, and multiple temperature sensors may be provided along the circumferential direction of flange 1 and / or outer sleeve member 3. For example, mounting holes for the vibration sensors and temperature sensors are provided inside outer sleeve member 3, and the sensors are fixed inside the mounting holes. The vibration sensors are positioned to detect the vibration status of the test bearing, including information such as amplitude, frequency, and phase, to grasp the operating state of the bearing in real time, detect abnormal vibration signals in a timely manner, and prevent equipment failure. Next, the temperature sensor can measure the bearing temperature, which not only helps maintain the bearing within a normal temperature range but can also be used to determine if there are any problems with the bearing, such as overheating. Finally, by using the built-in vibration sensor and temperature sensor together, the motion state of the bearing can be comprehensively monitored, allowing for a more complete and accurate understanding of the bearing's operating condition, enabling timely detection of bearing failures, effective countermeasures to be taken, and facilitating data collection and experimental control.

[0048] The above are merely preferred embodiments of the present invention and do not impose any formal limitations on the present invention. While the present invention is disclosed as described above in preferred embodiments, this does not limit the present invention. Those skilled in the art can make several changes or modifications using the disclosed technical content to create equivalent embodiments of equivalent changes without departing from the scope of the technical solutions of the present invention. Any simple modifications, equivalent changes, and modifications made to the above embodiments based on the technical essence of the present invention without departing from the scope of the technical solutions of the present invention all fall within the scope of the technical solutions of the present invention. [Explanation of Symbols]

[0049] 1. Flange, 1-1. Cavity I, 1-2. Oil inlet, 1-3. Oil outlet I, 1-4. Oil outlet II, 1-5. Mounting cavity, 1-6. Nozzle joint, 2. Flange end cap, 2-1. End cap center hole, 2-2. Flange I, 2-3. Lubrication oil hole, 2-4. Mounting groove, 2-5. Through hole, 3. Outer sleeve member, 3-1. Lubrication oil passage I, 3-2. Connecting oil hole I, 3-3. Cavity II, 4. Inner sleeve member, 4-1. Lubrication oil passage II, 4-2. Connecting oil hole II, 4-3. Cavity III, 5. 5-1, Large diameter section, 5-2, Small diameter section, 5-3, Coupling section, 5-4, Mounting step, 5-5, Keyway, 5-6, Key, 6, Radial load sleeve, 6-1, Cavity IV, 6-2, Threaded hole, 6-3, Threaded through hole, 7, First test bearing, 8, Second test bearing, 9, First test auxiliary bearing, 10, Second test auxiliary bearing, 11, First bush, 12, Second bush, 121, Cavity VI, 122, Stop boss, 123, Threaded blind hole, 13, Through cover I, 15, Support Frame, 16, Axial load hydraulic cylinder, 161, Cylinder body, 162, Cylinder head end cover, 163, Cylinder bottom end cover, 164, Step seal, 165, Piston rod, 166, Piston, 167, Guide sleeve, 168, Seal ring I, 169, Seal ring II, 17, Axial load body, 171, End face cavity, 172, Positioning screw hole, 18, Shaft sleeve I, 19, Shaft sleeve II, 20, Radial load hydraulic cylinder, 21, Through cover II, 22, Shaft end cover, 2 3. Load inner sleeve, 24. Slinger I, 25. Slinger II, 26. Seal ring, 27. Felt ring, 28. Elastic support ring, 30. First bracket, 40. Second bracket, 50. Third bracket, 60. Drive motor, 70. Coupling, 101. Bolt I, 102. Bolt II, 103. Bolt III, 104. Bolt IV, 105. Screw, 106. Positioning screw, 110. Flange I, 120. Flange II, 210. Flange end cover I, 220. Flange end cover II.

Claims

1. A lubrication mechanism for a bearing testing machine, Including flange, flange end cap, outer sleeve member and inner sleeve member, An oil drain port I is provided at the first end face of the flange. The flange end cap includes an end cap and a flange portion I provided in the circumferential direction of the end cap's central hole, and further lubrication oil holes are provided along the axial direction of the flange end cap, with the lubrication oil holes located on one side of the end cap's central hole. The outer sleeve member is provided with a cavity II that penetrates axially, and the two ports of the cavity II of the outer sleeve member are each fitted into the flange I of the flange end cover, and the outer sleeve member is provided with a lubricating oil passage I axially, one end of the lubricating oil hole is connected to the drain port I, and the other end of the lubricating oil hole is connected to the lubricating oil passage I. The lubrication mechanism for a bearing testing machine is characterized in that the inner sleeve member is mounted in the cavity II, the inner sleeve member is provided with a lubricating oil passage II along the axial direction, a connecting oil hole I communicating with the lubricating oil passage I is formed in the inner wall of the outer sleeve member, a connecting oil hole II communicating with the lubricating oil passage II is provided in the outer wall of the inner sleeve member, the connecting oil hole I and the connecting oil hole II are provided facing each other on the inside and outside, enabling communication between the lubricating oil passage I and the lubricating oil passage II, the lubricating oil passage II is arranged to supply oil to a pair of bearings located in the middle of the rotor, and an oil drain port II is provided on the second end face of the flange, the oil drain port II is arranged to supply oil to a pair of bearings located at both ends of the rotor.

2. The lubrication mechanism for a bearing testing machine according to claim 1, characterized in that an oil inlet communicating with the oil outlet I and the oil outlet II is further provided on the circumferential surface of the flange.

3. A bearing detection tester, characterized in that it includes a lubrication mechanism for the bearing tester described in claim 1 or 2.

4. The rotor further includes a test bearing assembly, a test auxiliary bearing assembly, and a radial load sleeve, wherein the rotor includes a large diameter portion and small diameter portions located at both ends of the large diameter portion, the large diameter portion and the small diameter portion are provided coaxially, and a mounting step is formed at the connection point between the large diameter portion and the small diameter portion. The test bearing assembly includes a first test bearing and a second test bearing, the first and second test bearings being mounted on the smaller diameter portions on both sides, one end of the inner rings of the first and second test bearings abutting against the mounting step of the rotor, the inner rings of the first and second test bearings fitted to the rotor, an outer sleeve member fitted to the outside of the outer rings of the first and second test bearings, a radial load sleeve fitted to the outside of the outer sleeve member, and both ends of the radial load sleeve fixed and connected to the flange end caps. The test auxiliary bearing assembly includes a first test auxiliary bearing and a second test auxiliary bearing, the first and second test auxiliary bearings located on the small diameter portion of the rotor, and the first and second test auxiliary bearings located on either side of the test bearing assembly, Or, The rotor includes a large-diameter portion and small-diameter portions located at both ends of the large-diameter portion, the large-diameter portion and the small-diameter portion are provided coaxially, and a mounting step is formed at the connection point between the large-diameter portion and the small-diameter portion. The test auxiliary bearing assembly includes a first test auxiliary bearing and a second test auxiliary bearing, each mounted on the small diameter portions on both sides, one end of the inner ring of the first test auxiliary bearing and the second test auxiliary bearing abuts against the mounting step of the rotor, the inner rings of the first test auxiliary bearing and the second test auxiliary bearing are fitted to the rotor, an outer sleeve member is fitted to the outside of the outer ring of the first test auxiliary bearing and the second test auxiliary bearing, a radial load sleeve is fitted to the outside of the outer sleeve member, and both ends of the radial load sleeve are fixed and connected to the flange end caps. The bearing detection tester according to claim 3, characterized in that the test bearing assembly includes a first test bearing and a second test bearing, the first test bearing and the second test bearing are located in the small diameter portion of the rotor, and the first test bearing and the second test bearing are each located on either side of the test auxiliary bearing assembly.

5. The bearing detection tester according to claim 4, further comprising an axial load mechanism, the axial load mechanism comprising an axial load hydraulic cylinder and an axial load body, wherein the axial load hydraulic cylinder is located on a third bracket, the axial load body is detachably connected to the piston rod of the axial load hydraulic cylinder, and the axial load body is positioned to enter the internal cavity of the load inner sleeve in the second bush and apply an axial load force to the test bearing.

6. A first bushing is fitted to the outside of the first test auxiliary bearing, the first end of the first bushing is fixed in the mounting cavity of the flange, and the other end of the first bushing is connected to the first bearing through cover. The first bush is provided with a cavity V along the axial direction, and the first bearing through cover includes an end plate and a flange portion II provided at the center of the end plate, the flange portion II entering the cavity V and forming an axial stopper for one end of the first test auxiliary bearing or the first test bearing. The bearing detection tester according to claim 5, wherein the second test auxiliary bearing or the second test bearing is provided inside the load inner sleeve, the second bush has a cavity VI along the axial direction, the load inner sleeve is provided inside the cavity VI of the second bush, one end of the second bush and the load inner sleeve is fixed inside the mounting cavity of the flange, and the first bush and the second bush are each connected to the second bracket via a support frame.

7. The bearing detection tester according to claim 4 or 5, further comprising shaft sleeve I and shaft sleeve II, wherein both ends of shaft sleeve I abut against the inner ring of the first test auxiliary bearing and the inner ring of the first test bearing, respectively, both ends of shaft sleeve II abut against the inner ring of the second test bearing and the inner ring of the second test auxiliary bearing, respectively, the other end of the second test auxiliary bearing or the inner ring of the second test bearing abuts against a shaft end cap, and the shaft end cap is fixed to the rotor.

8. The bearing detection tester according to claim 4 or 5, further comprising a radial load hydraulic cylinder, wherein the piston rod of the radial load hydraulic cylinder is fixedly connected to the outer wall of the radial load sleeve via a stud.

9. The bearing detection tester according to claim 5, characterized in that the rotor further includes a coupling portion, the coupling portion is connected to a small diameter portion on one side thereof, and the coupling portion is connected to the rotating shaft of a drive motor via the coupling.

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