Device and method for measuring multidirectional variable load of motor sliding bearing

Abstract

The invention belongs to the technical field of bearing axial load measurement, and particularly relates to a multi-direction variable load measurement device and method for a motor sliding bearing, and the measurement device comprises a housing, a loading assembly and a motor. The loading assembly comprises a loading body, a coil and a permanent magnet, a contact body is formed on the loading body, and the contact body is in contact with the end face of the sliding bearing to be tested; the loading body is an armature made of a ferromagnetic material, the coil is embedded into the loading body, the permanent magnet is arranged above the loading body, the coil is electrified to magnetize the loading body to repel the permanent magnet, the repelling force and the gravity of the loading body are applied to the sliding bearing to be tested, and the sliding bearing to be tested is connected with a pressure sensor. Through the combination of the loading body, the coil and the permanent magnet, the application range of the axial load is remarkably expanded by utilizing the superimposed effect of electromagnetic repulsion and the gravity of the loading body, and meanwhile, the measuring device can be applied to the working condition that the loading body is vertically arranged and can also be applied to the working condition that the loading body is obliquely arranged.

Description

Technical Field

[0001] The present invention belongs to the technical field of bearing axial load measurement, and in particular relates to a device and method for measuring multi-directional variable loads of a motor sliding bearing. Background Art

[0002] As a core component of modern engine fuel supply systems, the fuel motor drives the impeller or rotor within the fuel pump at high speed, generating a pressure differential and enabling efficient fuel delivery from the fuel tank to the combustion chamber. As the power density of internal combustion engines continues to increase, the axial loads and speeds faced by fuel motors are increasing. This is especially true for fuel motors using sliding bearings, where their axial load-bearing capacity under high pressure, high speed, and complex lubrication environments directly determines the reliability and lifespan of the equipment. Fuel motors are categorized as either internal or external fuel motors based on their structural form. Internal fuel motors are typically integrated with the assembly and installed in the fuel tank.

[0003] In the existing technology, there are significant limitations in the test methods for the axial load capacity of sliding bearings. First, traditional testing devices usually use a load-bearing gravity pressure method. However, this method requires a significant increase in the mass of the load-bearing body when testing high-load demand scenarios, resulting in a large test equipment volume and limited operational flexibility, especially low efficiency when conducting comparative tests on bearings of multiple specifications. Secondly, the existing test systems are mostly designed based on the characteristics of rolling bearings, ignoring the dynamic effects of the lubricating film unique to sliding bearings. Since the load-bearing performance of sliding bearings is strongly coupled with the viscosity and speed of the lubricating oil, the existing methods have failed to establish an effective correlation model under different oil environments and speed conditions, resulting in deviations between the test results and the actual working conditions. In addition, the traditional physical load-bearing body relies on the characteristic of gravity pressure, which makes it impossible to accurately control the direction of load application in non-horizontal installation states (such as tilting), resulting in wear measurement errors, and it is difficult to meet the testing requirements of diversified installation scenarios of fuel motors.

[0004] In summary, there is an urgent need to design a multi-directional variable load measuring device for motor sliding bearings to measure the multi-dimensional spatial axial load capacity of sliding bearings. Summary of the Invention

[0005] In order to solve the problems in the above-mentioned background technology, the present invention provides a multi-directional variable load measuring device and method for a motor sliding bearing. By designing the loading component as a combination structure of a slip ring, a coil, a brush, and a loading body, the measuring device of the present application can be applied to working conditions where the loading body is set vertically, and can also be applied to working conditions where the loading body is set at an angle. At the same time, by arranging a contact body on the loading body, the contact area between the loading body and the sliding bearing to be measured is reduced, thereby achieving a larger pressure while maintaining a smaller pressure.

[0006] The first object of the present invention is to provide a multi-directional variable load measuring device for a motor sliding bearing, comprising a housing, a loading assembly disposed within the housing, and a motor disposed outside the housing;

[0007] The loading assembly includes a loading body, a coil, and a permanent magnet. A first connecting shaft is formed at the lower end of the loading body, and a sliding bearing to be tested is mounted on the first connecting shaft. A loading hole is formed on the loading body, and a drive shaft of the motor is connected to the loading hole. A contact body is formed on the end of the loading body opposite to the sliding bearing to be tested, and the contact body contacts the end face of the sliding bearing to be tested. A pressure sensor is connected to the end of the sliding bearing to be tested away from the contact body.

[0008] The loading body is an armature made of ferromagnetic material. The coil is embedded in the loading body. The permanent magnet is set above the loading body. When the coil is energized, the loading body is magnetized. The magnetized loading body and the permanent magnet repel each other. The repulsive force, together with the gravity of the loading body, is applied to the sliding bearing to be tested.

[0009] The loading assembly is arranged in the housing through the first end cover and the second end cover. The housing is filled with oil, and the loading body and the sliding bearing to be tested are immersed in the oil.

[0010] Furthermore, a second connecting shaft extending upward is formed on one end of the loading body away from the sliding bearing to be tested, and a positive slip ring and a negative slip ring which rotate synchronously with the loading body are mounted on the second connecting shaft;

[0011] An insulator is provided on the side of the permanent magnet close to the second connecting shaft. Both the permanent magnet and the insulator are fixed on the shell or the first end cover. A positive brush is provided between the positive slip ring and the insulator, and the positive brush is connected to the positive pole of the power supply; a negative brush is provided between the negative slip ring and the insulator, and the negative brush is connected to the negative pole of the power supply; the positive slip ring and the negative slip ring are both connected to the coil through their respective leads.

[0012] Furthermore, a first spring is fixed between the positive electrode brush and the insulator, the first spring is in a compressed state, and the first spring pushes the positive electrode brush to closely contact the positive electrode slip ring; and / or

[0013] A second spring is fixed between the negative pole brush and the insulator. The second spring is in a compressed state. The second spring pushes the negative pole brush to closely contact the negative pole slip ring.

[0014] Furthermore, the rotation axis of the loading body is arranged vertically, or the rotation axis of the loading body is arranged at an angle to the horizontal plane.

[0015] Furthermore, the contact body is an annular protrusion coaxially arranged with the first connecting shaft, the annular protrusion includes a connecting surface connected to the loading body and a contact surface in contact with the sliding bearing to be tested, and the radial width of the contact surface is smaller than the radial width of the connecting surface.

[0016] Furthermore, the contact body contacts the outer edge of the end face of the sliding bearing to be measured, and the outer edge line of the contact surface coincides with the outer edge line of the end face of the sliding bearing to be measured.

[0017] Furthermore, the radial width of the contact surface is 1mm-3mm, and the contact area between the contact body and the sliding bearing to be tested is 10mm 2 -90mm 2 .

[0018] Furthermore, the cross section of the contact body is an isosceles trapezoidal structure.

[0019] Furthermore, an annular groove is formed at one end of the loading body away from the sliding bearing to be tested, and the coil is wound in the annular groove and rotates synchronously with the loading body.

[0020] A second object of the present invention is to provide a method for measuring a multi-directional variable load on a motor sliding bearing, which is implemented based on any of the above-mentioned devices for measuring a multi-directional variable load on a motor sliding bearing, and comprises the following steps:

[0021] S1: The sliding bearing to be tested is mounted on the first connecting shaft, and a certain oil is filled in the housing. The pressure applied by the loading body to the sliding bearing to be tested is adjusted, and the motor is started to rotate at a certain speed. The motor drives the loading body to rotate, and the contact body on the loading body contacts the sliding bearing to be tested. The pressure applied to the sliding bearing to be tested is fed back through the pressure sensor. After the sliding bearing to be tested has run for a certain period of time, the wear amount of the sliding bearing to be tested is measured. If the wear amount meets the requirements, the process proceeds to step S2.

[0022] S2: increasing the pressure applied by the load to the sliding bearing to be tested, repeating step S1, and continuing to measure the wear of the sliding bearing to be tested after running for a certain period of time. If the wear meets the requirements, then continue to repeat step S2; if the wear does not meet the requirements, then proceed to step S3;

[0023] S3: According to steps S1 and S2, a load-bearing capacity curve of the sliding bearing to be tested in a certain oil and at a certain speed is drawn.

[0024] Compared with the prior art, the present invention has the following beneficial effects:

[0025] (1) This application significantly improves the application range of the axial load by combining a ferromagnetic load body, a coil, and a permanent magnet, utilizing the superposition effect of electromagnetic repulsion and the weight of the load body. Compared with the traditional method of relying on gravity to apply pressure on a physical load body, the electromagnetic force can be dynamically adjusted (by adjusting the coil current intensity), and high load loading can be achieved without increasing the physical mass. This effectively solves the problem of bloated volume caused by excessive loading mass in traditional test equipment, while meeting the testing requirements of high-load sliding bearings. At the same time, because the direction of the electromagnetic repulsion is always perpendicular to the magnetic pole distribution surface of the permanent magnet and the load body, it is independent of the direction of gravity. Even if the measuring device is in an inclined or non-horizontal state, the direction and size of the axial load can still be accurately controlled by the electromagnetic force, which increases the application conditions of the device.

[0026] (2) This application uses the pressure principle to achieve the effect of applying a high load with a small mass load body through the design of the contact body and the end face of the sliding bearing to be tested. Compared with the traditional solution of simply increasing the weight of the load body, the moment of inertia is significantly reduced, and the safety hazard during high-speed rotation is avoided. At the same time, the cavity is filled with oil, which can accurately simulate the actual working conditions of the sliding bearing, further improving the accuracy of the test data.

[0027] (3) The present application does not require an additional rotating shaft. The load body is driven to rotate directly by connecting the motor shaft to the load body, thereby reducing the number of parts. The first connecting shaft and the second connecting shaft are integrally formed on the load body to realize the rotation of the load body and the installation of the sliding bearing, thereby achieving a compact structural design, facilitating disassembly and maintenance, and reducing the operating cost of the equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0029] Figure 1 A schematic cross-sectional view of a measuring device according to an embodiment of the present invention;

[0030] Figure 2 for Figure 1 A magnified view of part A in FIG;

[0031] Figure 3 for Figure 1 An enlarged view of another embodiment of part A in FIG;

[0032] Figure 4 for Figure 1 A magnified view of part B in FIG;

[0033] Figure 5 A schematic cross-sectional view of a loading body provided in one embodiment of the present invention;

[0034] Figure 6 for Figure 5 Enlarged view of part C in FIG;

[0035] Figure 7 A structural diagram of a sliding bearing to be tested provided in one embodiment of the present invention;

[0036] Figure 8 A schematic cross-sectional view of a measuring device in a tilted state provided by another embodiment of the present invention;

[0037] Among them: 1-housing, 2-motor, 3-loading body, 31-first connecting shaft, 32-loading hole, 33-contact body, 331-connecting surface, 332-contact surface, 34-second connecting shaft, 35-annular groove, 4-coil, 5-permanent magnet, 6-sliding bearing to be tested, 61-end face, 7-first end cover, 8-second end cover, 9-sliding bearing, 10-insulator, 11-positive slip ring, 12-negative slip ring, 13-positive brush, 14-negative brush, 15-first spring, 16-second spring. DETAILED DESCRIPTION

[0038] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making any creative efforts are within the scope of protection of the present invention.

[0039] The following is combined with Figure 1 To the attached Figure 8 The present invention is described in detail with reference to specific embodiments.

[0040] See Figures 1 to 8 The present invention provides a multi-directional variable load measuring device for a motor sliding bearing, comprising a housing 1, a loading assembly disposed in the housing 1, and a motor 2 disposed outside the housing 1;

[0041] The loading assembly includes a loading body 3, a coil 4, and a permanent magnet 5. A first connecting shaft 31 is formed at the lower end of the loading body 3, and a sliding bearing 6 to be tested is mounted on the first connecting shaft 31. A loading hole 32 is formed in the loading body 3, and the drive shaft of the motor 2 is connected to the loading hole 32. The motor 2 is used to drive the loading body 3 to rotate. A contact body 33 is formed on the end of the loading body 3 opposite to the sliding bearing 6 to be tested. The contact body 33 contacts the end face 61 of the sliding bearing 6 to be tested to apply pressure to the sliding bearing 6 to be tested. A pressure sensor (not shown in the figure) is connected to the end of the sliding bearing 6 to be tested away from the contact body 33. The pressure sensor can be integrated into the second end cover 8. The pressure sensor is used to measure the load borne by the sliding bearing 6 to be tested in real time.

[0042] The loading body 3 is an armature made of ferromagnetic material, the coil 4 is embedded in the loading body 3, and the coil 4 is an oil-proof coil. The permanent magnet 5 is set above the loading body 3. The coil 4 is energized to magnetize the loading body 3. The magnetized loading body 3 and the permanent magnet 5 repel each other. The repulsive force together with the gravity of the loading body 3 is applied to the sliding bearing 6 to be tested. It can be seen that the pressure applied to the sliding bearing 6 to be tested in this application includes the weight of the loading body 3 and the repulsive force of the permanent magnet 5 on the loading body 3. The structural composition of the loading assembly in this application enables the measuring device to be applied not only to working conditions where the loading body 3 is set vertically (such as Figure 1 ), can also be applied to the case where the load is tilted (as shown in Figure 8 As shown), when applied to the working condition where the load body 3 is tilted, the repulsive force of the permanent magnet 5 on the load body 3 is changed by adjusting the current, thereby changing the force applied by the contact body 33 to the sliding bearing 6 to be tested;

[0043] The loading assembly is disposed within the housing 1 via a first end cap 7 and a second end cap 8. The housing 1 is filled with oil, and the loading element 3 and the sliding bearing 6 to be tested are immersed in the oil to simulate the actual operating environment of the sliding bearing. The present application does not limit the type of oil used; different oils have different viscosities, and the compressive strength of the sliding bearing 6 to be tested under different viscosities also varies. Therefore, during the measurement, the axial load bearing capacity of the sliding bearing 6 to be tested can be recorded in real time under different oil viscosities.

[0044] It should be noted that the loading assembly of the present application is composed of a loading body 3, a coil 4, and a permanent magnet 5, which together occupy the inner cavity of the housing 1. Therefore, the volume and weight of the loading body 3 should not be too large. However, it is preferable to use a material with a high-density solid structure to achieve the purpose of increasing the weight of the loading body 3 within a limited volume. In an optional embodiment, the loading body 3 has a diameter of 90 mm, a height of 30 mm, a weight of 300 g to 400 g, and a gravity of 3N to 4N. When the loading assembly is required to apply a large force to the sliding bearing 6 to be tested, the gravity applied by the loading body 3 to the sliding bearing 6 to be tested can be ignored.

[0045] This application utilizes a combination of a ferromagnetic loading body 3, a coil 4, and a permanent magnet 5, leveraging the combined effect of electromagnetic repulsion and the gravity of the loading body 3 to significantly increase the range of axial load application. Compared to the traditional method of applying pressure by relying on gravity on a physical loading body 3, the electromagnetic force can be dynamically adjusted (by adjusting the coil current intensity), achieving high load loading without increasing physical mass. This effectively solves the problem of bulky conventional testing equipment caused by excessive loading mass, while also meeting the testing requirements of high-load sliding bearings. Furthermore, because the direction of the electromagnetic repulsion is always perpendicular to the magnetic pole distribution plane of the permanent magnet 5 and the loading body 3 and is independent of the direction of gravity, even if the measuring device is tilted or non-horizontal, the direction and magnitude of the axial load can still be precisely controlled by the electromagnetic force, thereby expanding the device's application range.

[0046] It should be noted that the measuring device of the present application is placed in an oil barrel or oil tank when in use. The entire device is immersed in the oil barrel, and the interior of the shell 1 is also filled with the same type of oil. The oil in the shell 1 and the oil in the oil barrel can flow freely, accurately simulating the actual working conditions in the oil environment.

[0047] For further information, see Figure 1 and Figure 5 , an end of the loading body 3 away from the sliding bearing 6 to be tested is formed with a second connecting shaft 34 extending upward, and a sliding bearing 9 for assisting the rotation of the loading body 3 is mounted on the second connecting shaft 34. The sliding bearing 9 and the sliding bearing 6 to be tested are usually the same type of bearings and are arranged in pairs at both ends of the loading body 3. In this embodiment, the sliding bearing 9 and the sliding bearing 6 to be tested are both graphite bearings. Graphite bearings are more suitable for installation in an environment with oil, and in an oil medium, the lubricity of the graphite bearing will be further enhanced. When the loading body 3 rotates in the graphite bearing, an oil film will be formed on the surface of the graphite bearing. When the oil film is broken, the wear of the graphite bearing will be aggravated. Of course, in other embodiments, the sliding bearing 9 and the sliding bearing 6 to be tested may also be selected from other types of bearings, and this application does not make specific limitations.

[0048] See Figure 1 and Figure 2The second connecting shaft 34 is also provided with a positive slip ring 11 and a negative slip ring 12 that rotate synchronously with the loading body 3; an insulator 10 is provided on the side of the permanent magnet 5 close to the second connecting shaft 34, and the permanent magnet 5 and the insulator 10 are both fixed on the shell 1 or the first end cover 7. A positive brush 13 is provided between the positive slip ring 11 and the insulator 10, one end of the positive brush 13 is fixed on the insulator 10, and the other end is in contact with the positive slip ring 11, and the positive brush 13 is connected to the positive pole of the power supply; a negative brush 14 is provided between the negative slip ring 12 and the insulator 10, one end of the negative brush 14 is fixed on the insulator 10, and the other end is in contact with the negative slip ring 12, and the negative brush 14 is connected to the negative pole of the power supply; the positive slip ring 11 and the negative slip ring 12 are both connected to the coil 4 through their respective leads. The current cycle is as follows: positive pole of power supply - positive brush 13 - positive slip ring 11 - coil 4 - negative brush 14 - negative slip ring 12 - negative pole of power supply. When the load body 3 is set vertically, after the coil 4 is energized, the load body 3 is magnetized, repelling the permanent magnet 5, thereby applying an axial force to the sliding bearing 6 to be tested. When the load body 3 is set at an angle, after the coil is energized, the load body 3 is magnetized, repelling the permanent magnet 5, thereby applying an axial force to the sliding bearing 6 to be tested. In addition, the load body 3 also applies a radial force to the sliding bearing 6 to be tested through the contact portion with the sliding bearing 6 to be tested. At this time, the pressure sensor can measure the resultant force of the radial and axial forces, and derive the radial and axial forces through orthogonal decomposition.

[0049] This application uses a contact-type conductive mechanism between slip rings and brushes to avoid the problems of wire breakage or signal interference caused by the rotation and winding of traditional wires, ensuring the continuity and controllability of electromagnetic force loading. Combined with direct access to the positive and negative poles of the power supply, the electromagnetic repulsion force can be dynamically adjusted by adjusting the input current intensity in real time to meet the dynamic load matching requirements under different speeds or transient working conditions. At the same time, an insulator is provided between the permanent magnet and the slip ring to effectively isolate the permanent magnet's magnetic field from interfering with the slip ring's conductive circuit.

[0050] In a preferred embodiment, see Figure 3A first spring 15 is fixed between the positive brush 13 and the insulator 10, one end of the first spring 15 is fixed to the insulator 10, and the other end is fixed to the positive brush 13. The first spring 15 is in a compressed state, and the first spring 15 pushes the positive brush 13 to closely contact the positive slip ring 11; and / or a second spring 16 is fixed between the negative brush 14 and the insulator 10, one end of the second spring 16 is fixed to the insulator 10, and the other end is fixed to the negative brush 14. The second spring 16 is in a compressed state, and the second spring 16 pushes the negative brush 14 to closely contact the negative slip ring 12. The present application applies continuous thrust to the positive brush 13 and the negative brush 14 through the compressed first spring 15 and the second spring 16, ensuring that the positive brush 13 always maintains close contact with the surface of the high-speed rotating positive slip ring 11 and the negative brush 14 always maintains close contact with the surface of the high-speed rotating negative slip ring 12. The elastic deformation of the spring can adaptively compensate for dimensional changes in the slip ring caused by wear or thermal expansion, avoiding current fluctuations or momentary power outages caused by contact gaps, and significantly improving the current transmission stability under rotating conditions, especially in high-speed and high-vibration environments.

[0051] In some embodiments, the rotation axis of the loading body 3 is vertically arranged (see Figure 1 ), or the axis of rotation of the load 3 is set at an angle to the horizontal plane (see Figure 8 By allowing the axis of load body 3 to be set vertically or at an angle to the horizontal, the operating conditions of fuel-powered motors in different spatial orientations can be accurately simulated. This design overcomes the limitation of traditional test equipment that can only test in a vertical setting. It can evaluate the dynamic load-bearing performance of sliding bearings under the combined action of gravity and electromagnetic loading force, ensuring that the test results are highly consistent with actual application scenarios.

[0052] During use, the present application drives the loading body 3 to rotate via the motor 2, and applies the pressure of the loading body 3 to the end face 61 of the sliding bearing 6 to be tested via the contact body 33, thereby achieving a relatively small weight of the loading body 3 to apply a relatively large compressive strength to the bearing. It is worth noting that since the sliding bearing has a strong ability to withstand axial loads, if the loading force applied to the sliding bearing 6 to be tested is increased by increasing the volume of the loading body 3, then if the volume of the loading body 3 is large, its moment of inertia can easily lead to danger when running at high speeds. Therefore, the present application breaks through traditional thinking and creatively designs the contact body 33 on the loading body 3 to achieve the purpose of obtaining a relatively large pressure by reducing the force-bearing area.

[0053] It is worth further emphasizing that, by designing contact body 33 in contact with the end face 61 of the sliding bearing 6 to be tested, this application utilizes the principle of pressure to achieve the effect of applying a high load to the load body 3 with a small mass. Compared to traditional solutions that simply increase the load body's mass, this significantly reduces the moment of inertia and avoids safety hazards during high-speed rotation. Furthermore, by filling the cavity with oil, the actual operating conditions of the sliding bearing can be accurately simulated, further improving the accuracy of the test data. Because the pressure applied to the sliding bearing 6 to be tested by contact body 33 is not solely dependent on the tested sliding bearing 6, pressure can be applied to the tested sliding bearing 6 even if the measuring device is tilted, enabling the measurement of multi-directional variable loads on the tested sliding bearing 6.

[0054] In some embodiments, see Figure 4 and Figure 5 The contact body 33 is an annular protrusion coaxially arranged with the first connecting shaft 31. The annular protrusion includes a connecting surface 331 connected to the load body 3 and a contact surface 332 in contact with the sliding bearing 6 to be tested. The radial width of the contact surface 332 is smaller than the radial width of the connecting surface 331. In other words, the contact body 33 has a structure that is wide at the top and narrow at the bottom, with the end close to the load body 3 being wide and the end close to the sliding bearing 6 to be tested being narrow. This structure not only ensures that the contact area between the load body 3 and the sliding bearing 6 to be tested is small, but also makes the contact body 33 structure that is wide at the top and narrow at the bottom less prone to damage and fracture. The present application significantly improves the bending stiffness by designing the contact body 33 as an annular protrusion structure that is wide at the top and narrow at the bottom, and by increasing the bonding area between the connecting surface 331 and the load body 3, thereby avoiding fracture or plastic deformation caused by local stress concentration and ensuring the reliability of long-term testing. At the same time, by designing the radial width of contact surface 332 to be smaller than the radial width of connection surface 331, the weight of loading element 3 is concentrated on a small annular area on the end face 61 of the sliding bearing 6 to be tested, significantly increasing the local pressure and enabling the precise application of high axial loads without increasing the weight of loading element 3. In this application, the annular protrusion is arranged coaxially with the first connecting shaft 31 to ensure that the contact surface and the end face 61 of the sliding bearing 6 to be tested always maintain concentric contact during high-speed rotation of loading element 3, eliminating eccentric load interference caused by centrifugal force and simulating the axial load state of the sliding bearing under real working conditions.

[0055] In some embodiments, see Figure 4, the contact body 33 contacts the outer edge of the end face 61 of the sliding bearing 6 to be tested, and the outer edge line of the contact surface 332 coincides with the outer edge line of the end face 61 of the sliding bearing 6 to be tested. It should be noted that the greater the distance between the contact body 33 and the rotating shaft of the loading body 3, the greater its linear velocity. The linear velocity is one of the important indicators of the sliding bearing. The reason is: v=w*r, v is the motor axis speed, w is the motor shaft angular velocity, r is the radius. The larger the radius r, the greater the linear velocity v, the thinner the oil film formed between the contact body 33 and the sliding bearing 6 to be tested, the smaller the oil film stiffness, and the more susceptible to wear. The rupture of the oil film will aggravate the wear between the contact body 33 and the sliding bearing 6 to be tested. Therefore, the contact body 33 is set as far away from the rotating shaft of the loading body 3 as possible to test its wear performance at the extreme position. It should be noted that in addition to the influence of linear speed, the viscosity of the oil also has a great influence on the wear of the sliding bearing. The higher the oil viscosity, the greater the oil film stiffness, the less likely the oil film is to be damaged, and the less wear the contact body 33 causes on the sliding bearing. During the test process, it is necessary to comprehensively consider the influence of both on the wear of the sliding bearing.

[0056] In a preferred embodiment, the radial width of the contact surface 332 is 1 mm to 3 mm; the contact area between the contact body 22 and the sliding bearing 5 to be tested is 10 mm. 2 -90mm 2 The contact surface 332 within the above radial width range and contact area range can significantly increase the local pressure, achieve a higher equivalent load under the same load weight, and break through the physical limitations of the traditional large mass load body 3, which is usually 1 mm in radial width and 10 mm in contact area. 2 The contact surface 332 has sufficient structural strength to avoid the formation of edges that accelerate the wear of the oil film due to being too narrow. At the same time, a too narrow contact surface 332 can easily cause the contact body 33 to break.

[0057] In the preferred embodiment, see Figure 6 The cross-section of the contact body 33 is an isosceles trapezoidal structure. This structure evenly distributes pressure along the axis of the contact body 33, avoiding unbalanced loading caused by an asymmetric structure. This effectively reduces stress distribution fluctuations on the end face 61 of the tested sliding bearing 6, improving the repeatability and accuracy of test data. In a more preferred embodiment, a smooth transition is formed between the contact surface 332 of the contact body 33 and the side surface of the contact body 33, preventing the formation of sharp edges that would cause unnecessary wear on the oil film and reduce test accuracy.

[0058] This application achieves the combined extreme working conditions of high speed and high pressure at the same time under limited loading weight by maximizing the linear speed and minimizing the contact area, and accurately tests the axial load-bearing capacity and anti-wear performance of the sliding bearing.

[0059] In a preferred embodiment, the contact body 33 and the loading body 3 are integrally formed, which can reduce the risk of wear or loosening caused by a complex assembly structure.

[0060] By arranging a contact body 33 on the loading body 3, the present application can increase the local pressure by 500%-1000% under the same loading weight. At the same time, compared with the contact body 33 structure in which the radial width of the connecting surface 331 and the contact surface 332 is consistent, the present embodiment designs the contact body 33 with an isosceles trapezoidal cross-section, which can reduce the risk of fracture of the contact body 33 by more than 80%, thereby improving the service life of the device of the present application.

[0061] For details, see Figure 5 An annular groove 35 is formed at the end of the loading body 3 away from the sliding bearing 6 to be tested. The coil 4 is wound in the annular groove 35 and rotates synchronously with the loading body 3. The annular groove 35 provides a standardized winding space for the coil 4, simplifying the installation and positioning process of the coil 4. At the same time, the coil 4 is embedded in the loading body 3 to avoid direct exposure to the high-speed oil environment and prevent damage to the coil 4. Alternatively, the coil 4 can be wound in the annular groove 35 and impregnated with insulating varnish. The insulating varnish can provide insulation protection for the coil and fix the coil 4 in the annular groove 35. In this case, the coil 4 can be directly exposed to the oil environment.

[0062] The present invention further provides a method for measuring a multi-directional variable load of a motor sliding bearing, which is implemented based on any one of the above-mentioned devices for measuring a multi-directional variable load of a motor sliding bearing, and comprises the following steps:

[0063] S1: The sliding bearing 6 to be tested is mounted on the first connecting shaft 31, and the housing 1 is filled with a certain oil. The pressure applied by the loading body 3 to the sliding bearing 6 to be tested is adjusted, and the motor 2 is started to rotate at a certain speed. The motor 2 drives the loading body 3 to rotate, and the contact body 33 on the loading body 3 contacts the sliding bearing 6 to be tested. The pressure applied to the sliding bearing 6 to be tested is fed back through the pressure sensor. After the sliding bearing 6 to be tested has run for a certain period of time, the wear amount of the sliding bearing 6 to be tested is measured. If the wear amount meets the requirements, the process proceeds to step S2.

[0064] S2: increasing the pressure applied by the loading body 3 to the sliding bearing 6 to be tested, repeating step S1, and continuing to measure the wear amount of the sliding bearing 6 to be tested after running for a certain period of time. If the wear amount meets the requirements, then continue to repeat step S2; if the wear amount does not meet the requirements, then proceed to step S3;

[0065] S3: According to steps S1 and S2, a load-bearing capacity curve of the sliding bearing 6 to be tested is drawn in a certain oil and at a certain rotation speed.

[0066] The method of the present application applies all the technical solutions of all the embodiments of the above-mentioned motor sliding bearing multi-directional variable load measuring device, and therefore has at least all the beneficial effects brought by the technical solutions of the embodiments of the above-mentioned motor sliding bearing multi-directional variable load measuring device, which will not be repeated here one by one.

[0067] The present invention is further described above with the aid of specific embodiments. However, it should be understood that the specific description herein should not be construed as limiting the essence and scope of the present invention. Various modifications made to the above embodiments by ordinary technicians in this field after reading this specification are all within the scope of protection of the present invention.

Claims

1. A multi-directional variable load measuring device for a motor sliding bearing, characterized in that: It comprises a housing, a loading assembly arranged in the housing, and a motor arranged outside the housing; The loading assembly includes a loading body, a coil, and a permanent magnet. A first connecting shaft is formed at the lower end of the loading body, and a sliding bearing to be tested is mounted on the first connecting shaft. A loading hole is formed on the loading body, and a drive shaft of the motor is connected to the loading hole. A contact body is formed on the end of the loading body opposite to the sliding bearing to be tested, and the contact body contacts the end face of the sliding bearing to be tested. A pressure sensor is connected to the end of the sliding bearing to be tested away from the contact body. The loading body is an armature made of ferromagnetic material, the coil is embedded in the loading body, and the permanent magnet is arranged above the loading body. When the coil is energized, the loading body is magnetized. The magnetized loading body and the permanent magnet repel each other, and the repulsive force together with the gravity of the loading body is applied to the sliding bearing to be tested; The loading assembly is arranged in the housing through a first end cover and a second end cover. The housing is filled with oil, and the loading body and the sliding bearing to be tested are both immersed in the oil.

2. The motor sliding bearing multi-directional variable load measuring device according to claim 1, characterized in that: A second connecting shaft extending upward is formed on one end of the loading body away from the sliding bearing to be tested, and a positive slip ring and a negative slip ring which rotate synchronously with the loading body are sleeved on the second connecting shaft; An insulator is provided on one side of the permanent magnet close to the second connecting shaft. The permanent magnet and the insulator are both fixed to the shell or the first end cover. A positive brush is provided between the positive slip ring and the insulator, and the positive brush is connected to the positive pole of the power supply; a negative brush is provided between the negative slip ring and the insulator, and the negative brush is connected to the negative pole of the power supply; the positive slip ring and the negative slip ring are both connected to the coil through their respective leads.

3. The motor sliding bearing multi-directional variable load measuring device according to claim 2, characterized in that: A first spring is fixed between the positive brush and the insulator, the first spring is in a compressed state, and the first spring pushes the positive brush to closely contact the positive slip ring; and / or A second spring is fixed between the negative electrode brush and the insulator. The second spring is in a compressed state. The second spring pushes the negative electrode brush to closely contact the negative electrode slip ring.

4. The motor sliding bearing multi-directional variable load measuring device according to claim 1, characterized in that: The rotation axis of the loading body is arranged vertically, or the rotation axis of the loading body is arranged at an angle to the horizontal plane.

5. The motor sliding bearing multi-directional variable load measuring device according to claim 1, characterized in that: The contact body is an annular protrusion coaxially arranged with the first connecting shaft. The annular protrusion includes a connecting surface connected to the loading body and a contact surface in contact with the sliding bearing to be tested. The radial width of the contact surface is smaller than the radial width of the connecting surface.

6. The motor sliding bearing multi-directional variable load measuring device according to claim 5, characterized in that: The contact body contacts the outer edge of the end surface of the sliding bearing to be measured, and the outer edge line of the contact surface coincides with the outer edge line of the end surface of the sliding bearing to be measured.

7. The motor sliding bearing multi-directional variable load measuring device according to claim 5, characterized in that: The radial width of the contact surface is 1mm-3mm; the contact area between the contact body and the sliding bearing to be tested is 10mm 2 -90mm 2 .

8. The motor sliding bearing multi-directional variable load measuring device according to claim 5, characterized in that: The cross section of the contact body is an isosceles trapezoidal structure.

9. The motor sliding bearing multi-directional variable load measuring device according to claim 1, characterized in that: An annular groove is formed on one end of the loading body away from the sliding bearing to be tested. The coil is wound in the annular groove and rotates synchronously with the loading body.

10. A method for measuring a multi-directional variable load on a motor sliding bearing, implemented based on the multi-directional variable load measuring device for a motor sliding bearing according to any one of claims 1 to 9, characterized in that: The following steps are involved: S1: The sliding bearing to be tested is mounted on the first connecting shaft, and a certain oil is filled in the housing. The pressure applied by the loading body to the sliding bearing to be tested is adjusted, and the motor is started to rotate at a certain speed. The motor drives the loading body to rotate, and the contact body on the loading body contacts the sliding bearing to be tested. The pressure applied to the sliding bearing to be tested is fed back through the pressure sensor. After the sliding bearing to be tested has run for a certain period of time, the wear amount of the sliding bearing to be tested is measured. If the wear amount meets the requirements, the process proceeds to step S2. S2: increasing the pressure applied by the load to the sliding bearing to be tested, repeating step S1, and continuing to measure the wear of the sliding bearing to be tested after running for a certain period of time. If the wear meets the requirements, then continue to repeat step S2; if the wear does not meet the requirements, then proceed to step S3; S3: According to steps S1 and S2, a load-bearing capacity curve of the sliding bearing to be tested in a certain oil and at a certain speed is drawn.

Images