Bearing, linear motor, suspension system and vehicle

Abstract

The application discloses a bearing, a linear motor, a suspension system and a vehicle. The bearing comprises a base body and a lubricating part. The base body is in a cylindrical shape. The lubricating part is fixed to the base body. The lubricating part comprises a first lubricating part and a second lubricating part. The first lubricating part is close to a first end of the base body. The second lubricating part is close to a second end of the base body. At least one of the first lubricating part and the second lubricating part protrudes from a first wall surface of the base body. When at least one of the first lubricating part and the second lubricating part is pressed, at least one of the first lubricating part and the second lubricating part does not protrude from the first wall surface of the base body. According to the bearing, the first lubricating part and / or the second lubricating part protruding from the first wall surface of the base body has a buffering performance, can provide buffering when the bearing is knocked, and reduces knocking noise between the bearing and a bearing sliding fitting.

Description

Technical Field

[0001] This application relates to the field of bearing technology, and more specifically, to a bearing, a linear motor having the bearing, a suspension system having the linear motor, and a vehicle having the suspension system. Background Technology

[0002] In related technologies, a linear motor includes a central shaft and a housing. One of the central shaft and the housing is connected to a mover, and the other is connected to a stator. A bearing is provided between the central shaft and the housing, and the bearing is fixed to one of the central shaft and the housing and slides with the other. The coaxiality between the central shaft / housing and the bearing has a significant impact on the bearing's lifespan and the linear motor's NVH performance, especially when the linear motor is used in a vehicle's suspension system. The high-frequency operation of the linear motor requires ensuring the coaxiality between the central shaft / housing and the bearing. Assuming the central shaft and bearing slide with a high degree of coaxiality, when the coaxiality is good, the central shaft will not come into contact with the inner wall of the bearing during relative movement. However, due to the complexity of road conditions in suspension systems, the linear motor often encounters radial forces from the outside, causing the central shaft and bearing to collide and produce occasional abnormal noises, referred to in this application as knocking noises. The presence of such knocking noises greatly reduces the driving and riding experience. Summary of the Invention

[0003] This application aims to at least partially address one of the aforementioned technical problems in the prior art. To this end, this application proposes a bearing that helps reduce knocking noise between the bearing and its sliding mating parts.

[0004] This application also proposes a linear motor having the aforementioned bearing.

[0005] This application also proposes a suspension system having the aforementioned linear motor.

[0006] This application also proposes a vehicle having the above-described suspension system.

[0007] The bearing according to an embodiment of this application includes: a base and a lubricating element. The base is cylindrical, and the lubricating element is fixed to the base. The lubricating element includes: a first lubricating element and a second lubricating element. The first lubricating element is near a first end of the base, and the second lubricating element is near a second end of the base. At least one of the first lubricating element and the second lubricating element protrudes from a first wall surface of the base. When at least one of the first lubricating element and the second lubricating element is pressed, at least one of the first lubricating element and the second lubricating element does not protrude from the first wall surface of the base.

[0008] According to the embodiments of this application, the bearing is provided such that at least one of the first lubricating element and the second lubricating element protrudes from the first wall surface of the base, so that the first lubricating element and / or the second lubricating element protruding from the first wall surface of the base has a buffering performance, which can provide a buffer for the bearing sliding mating parts when they are struck, so that the bearing and the bearing sliding mating parts do not produce a sudden collision knocking sound in the direction perpendicular to the contact surface, thereby reducing the knocking noise between the bearing and the bearing sliding mating parts.

[0009] According to some embodiments of this application, at least one of the first lubricant and the second lubricant has an elastic modulus between 400 MPa and 1200 MPa.

[0010] According to some embodiments of this application, at least one of the first lubricating element and the second lubricating element is configured as a plurality of lubricating monomers distributed circumferentially along the substrate, the lubricating monomers being embedded in the substrate and protruding from a first wall surface of the substrate.

[0011] According to some embodiments of this application, the lubricating monomer is a columnar structure with a constant cross-sectional area A, and the protrusion a of the lubricating monomer protruding from the first wall of the substrate is:

[0012]

[0013] Wherein, F is the impact load on the lubricating monomer along the radial direction of the matrix, L is the dimension of the lubricating monomer in the radial direction of the matrix, E is the elastic modulus of the material of the lubricating monomer, and A is the cross-sectional area of ​​the lubricating monomer in a plane perpendicular to its own length extension direction.

[0014] According to some embodiments of this application, a first mounting groove is provided on the first wall surface of the substrate, which is radially recessed along the substrate. The first mounting groove extends circumferentially along the substrate, and the first lubricant is disposed in the first mounting groove and protrudes from the first wall surface of the substrate.

[0015] According to some embodiments of this application, the first mounting groove is an annular groove extending circumferentially along the substrate, and the first lubricant is an annular structure.

[0016] According to some embodiments of this application, the lubricating element further includes a third lubricating element located between the first lubricating element and the second lubricating element in a first direction, wherein the first direction is the axial direction of the substrate, and the elastic modulus of the third lubricating element is greater than the elastic modulus of the first lubricating element and the second lubricating element.

[0017] According to some embodiments of this application, the substrate includes a first segment and a second segment, the first segment being close to a first end face of the substrate, and the second segment being connected to the end of the first segment away from the first end face of the substrate; in the axial direction away from the second segment, the inner diameter of the first segment gradually increases, and the first lubricant is disposed in the first segment and protrudes from the inner wall surface of the first segment.

[0018] According to some embodiments of this application, the lubricant further includes a third lubricant disposed in the second segment.

[0019] According to some embodiments of this application, the first lubricant does not protrude from the inner wall surface of the second segment.

[0020] According to some embodiments of this application, at least one of the first lubricant and the second lubricant is a combination of polytetrafluoroethylene (PTFE) and additives, wherein the PTFE accounts for more than 50% of the combination material, and the additives are one or more of glass fiber, carbon fiber, graphite, molybdenum disulfide, or bronze powder.

[0021] A linear motor according to a second aspect of this application includes a housing, a central shaft, and a first bearing. The central shaft is at least partially disposed within the housing, and the housing and the central shaft are capable of relative movement along the axial direction of the linear motor. The first bearing is fixed to one of the housing and the central shaft and is slidably engaged with the other of the housing and the central shaft. The first bearing is the aforementioned bearing.

[0022] According to some embodiments of this application, the first bearing is fixed to the housing and slides with the central shaft, and the first wall surface is the inner wall surface of the base.

[0023] According to some embodiments of this application, the first bearing is fixed to the central shaft and slides with the housing, and the first wall surface is the outer wall surface of the base.

[0024] According to the embodiments of the present application, the linear motor, by setting the first lubricating element and / or the second lubricating element of the first bearing to protrude from the first wall surface of the base, enables the first bearing to provide a buffer against impacts to the mating housing or central shaft, so that the first bearing and the mating housing or central shaft do not produce a sudden impact sound in the direction perpendicular to the contact surface, thereby reducing the abnormal impact noise between the first bearing and the mating housing or central shaft.

[0025] The suspension system according to a third aspect of this application includes the linear motor described above.

[0026] According to the suspension system of this application embodiment, by setting the first lubricating element and / or the second lubricating element of the first bearing to protrude from the first wall surface of the base, the first bearing can provide a cushioning effect on the mating housing or central shaft when it is struck, so that the first bearing and the mating housing or central shaft do not produce a sudden collision knocking sound in the direction perpendicular to the contact surface, thereby reducing the knocking noise between the first bearing and the mating housing or central shaft.

[0027] The vehicle according to the fourth aspect of this application includes the suspension system described above.

[0028] According to the embodiments of the present application, the suspension system of the vehicle provides a cushioning effect when the first bearing is impacted by setting the first lubricating element and / or the second lubricating element of the first bearing to protrude from the first wall surface of the base. This prevents the first bearing and the mating housing or central shaft from generating a sudden impact sound in a direction perpendicular to the contact surface, thereby reducing the impact noise between the first bearing and the mating housing or central shaft.

[0029] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0030] Figure 1 This is a perspective view of a bearing according to an embodiment of this application;

[0031] Figure 2 yes Figure 1 A cross-sectional schematic diagram of the bearing shown;

[0032] Figure 3 yes Figure 1 Another cross-sectional view of the bearing shown;

[0033] Figure 4 This is the measured data of motor knocking noise in bearings where all lubricating components are graphite pillars that do not protrude from the first wall of the substrate, which is in the relevant technology.

[0034] Figure 5 The data are measured data of motor knocking noise of bearings in which the first and second lubricating components are both lubricating monomers and are both made of a combination of polytetrafluoroethylene and additives.

[0035] Figure 6 yes Figure 1 The diagram shows a bearing and shaft that do not collide.

[0036] Figure 7 yes Figure 1 A schematic diagram showing the first type of impact between the bearing and the shaft;

[0037] Figure 8 yes Figure 1 A schematic diagram showing the second type of impact between the bearing and the shaft;

[0038] Figure 9 yes Figure 1 A schematic diagram showing the third type of impact between the bearing and the shaft;

[0039] Figure 10 yes Figure 1 A schematic diagram showing the fourth type of impact between the bearing and the shaft;

[0040] Figure 11 This is a perspective view of a bearing according to yet another embodiment of this application;

[0041] Figure 12 yes Figure 11 A cross-sectional schematic diagram of the bearing shown;

[0042] Figure 13 This is a perspective view of a bearing according to another embodiment of this application;

[0043] Figure 14 yes Figure 13 A cross-sectional schematic diagram of the bearing shown;

[0044] Figure 15 yes Figure 13 Another cross-sectional view of the bearing shown;

[0045] Figure 16 This is a schematic diagram of a suspension system according to an embodiment of this application;

[0046] Figure 17 This is yet another schematic diagram of a suspension system according to an embodiment of this application (excluding the top of the strut and the elastic element);

[0047] Figure 18 yes Figure 17 A magnified view of a portion of point A in the middle;

[0048] Figure 19 yes Figure 17 A magnified view of a portion of point B in the middle;

[0049] Figure 20 This is a schematic diagram of a vehicle according to an embodiment of this application.

[0050] Figure label:

[0051] Vehicle 10000, suspension system 1000, linear motor 100, bearing 10, base 1, first wall 11, first mounting groove 12, second mounting groove 13, first section 14, second section 15, third section 16, first end face 17, lubricating component 2, first lubricating component 21, second lubricating component 22, third lubricating component 23, lubricating unit 24, housing 20, central shaft 30, guide cavity 301, first bearing 10a, second bearing 10b, stator 40, iron core 401, winding 402, mover 50, shaft 60, guide column 70, fork arm 200, tower top 300, elastic component 400. Detailed Implementation

[0052] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this application, and should not be construed as limiting this application.

[0053] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0054] The following is combined with Figures 1-20 The present application describes in detail a bearing 10, a linear motor 100 having the bearing 10, a suspension system 1000 having the linear motor 100, and a vehicle 10000 having the suspension system 1000, according to embodiments of the present application.

[0055] Reference Figures 1-3 , Figures 11-15 As shown, the bearing 10 according to the first aspect embodiment of this application includes: a base 1 and a lubricating element 2. The base 1 is cylindrical, and the lubricating element 2 is fixed to the base 1. The lubricating element 2 includes: a first lubricating element 21 and a second lubricating element 22. The first lubricating element 21 is close to a first end of the base 1, and the second lubricating element 22 is close to a second end of the base 1. At least one of the first lubricating element 21 and the second lubricating element 22 protrudes from the first wall surface 11 of the base 1.

[0056] When at least one of the lubricating element 21 and the second lubricating element 22 is pressed, at least one of the first lubricating element 21 and the second lubricating element 22 is in a state where it does not protrude from the first wall surface 11 of the base 1. In this way, when at least one of the first lubricating element 21 and the second lubricating element 22 is pressed, its elastic expansion and contraction play a buffering role, which can reduce the impact force on the bearing sliding fit and reduce the knocking noise between the bearing sliding fit and the bearing.

[0057] In some embodiments, the lubricating element 2 further includes a third lubricating element 23, which is located between the first lubricating element 21 and the second lubricating element 22 in a first direction; wherein, the first direction is the axial direction of the base 1, for example, the axial direction of the base 1 is as follows: Figures 2-3 , Figures 6-10 , Figure 12 , Figures 14-15 The F1-F2 direction is shown in the diagram.

[0058] In some embodiments of this application, reference is made to Figures 1-3 , Figures 11-15 As shown, the substrate 1 is provided with multiple layers of lubricating components 2, wherein the top layer is the first lubricating component 21, the bottom layer is the second lubricating component 22, and the middle layer is the third lubricating component 23. Each layer of lubricating components 2 is arranged along the circumference of the substrate 1.

[0059] In some embodiments, the elastic modulus of at least one of the first lubricant 21 and the second lubricant 22 is less than the elastic modulus of the third lubricant 23.

[0060] In some embodiments, the first lubricant 21, the second lubricant 22, and the third lubricant 23 may also be made of the same material.

[0061] The modulus of elasticity (also known as Young's modulus) is an important indicator for measuring the stiffness of a material. It reflects the material's ability to resist deformation within its elastic range. Materials with a high modulus of elasticity are less likely to deform under external forces, while materials with a low modulus of elasticity are more likely to deform under external forces.

[0062] In some embodiments, the elastic modulus of the first lubricating element 21 is less than that of the third lubricating element 23, thereby making the first lubricating element 21 more prone to deformation than the third lubricating element 23 when subjected to external force.

[0063] The bearing 10 is usually fixedly mounted on a fixed component, and the bearing 10 can slide relative to the bearing sliding fit component. The first wall surface 11 of the bearing 10 refers to the wall surface that rubs against the bearing sliding fit component.

[0064] In some embodiments, for example, the bearing 10 is sleeved on the shaft 60 and the bearing 10 and the shaft 60 move axially relative to each other. In this case, the shaft 60 can be understood as a bearing sliding fit component, the first wall surface 11 refers to the inner wall surface of the base 1, and the first lubricating element 21 protrudes from the inner wall surface of the base 1. (Refer to...) Figures 6-7 When the shaft 60 strikes the bearing 10, the shaft 60 first collides with the first lubricating element 21. The first lubricating element 21 is deformed by compression, which plays a transition buffering role until the first lubricating element 21 is flush with the inner wall surface of the base 1. Then the base 1 continues to bear the pressure of the shaft 60 and rub against the shaft 60. When the shaft 60 leaves the first lubricating element 21, the first lubricating element 21 returns to its state of protruding from the inner wall surface of the base 1.

[0065] In this way, the transition buffering effect of the first lubricating element 21 can greatly reduce the abnormal noise caused by the shaft 60 colliding with the inner wall of the bearing 10.

[0066] In some embodiments, the bearing 10 may also slide relative to other components (e.g., housing, guide post, etc.). For example, the bearing 10 may be fixed to the shaft 60 and slide in fit with the housing 20, which is the bearing sliding fit component. The first wall surface refers to the outer wall surface of the base 1, and the first lubricating element 21 protrudes from the outer wall surface of the base 1. (Not shown in the accompanying drawings)

[0067] For ease of description, this application uses the example of a sliding fit between the shaft 60 and the bearing 10, with the first wall surface 11 serving as the inner wall surface of the base 1, to illustrate the characteristics of the bearing 10.

[0068] In some embodiments, the elastic modulus of the second lubricant 22 is less than that of the third lubricant 23, thereby making the second lubricant 22 more prone to deformation than the third lubricant 23 when subjected to external force.

[0069] In some embodiments, the elastic modulus of the third lubricating element 23 is greater than that of the first lubricating element 21 and the second lubricating element 22, that is, the elastic modulus of the first lubricating element 21 and the second lubricating element 22 is less than that of the third lubricating element 23. As a result, when the first lubricating element 21, the second lubricating element 22 and the third lubricating element 23 are subjected to external forces, the first lubricating element 21 and the second lubricating element 22 are more prone to deformation than the third lubricating element 23.

[0070] In some embodiments, the second lubricating element 22 protrudes from the inner wall surface of the base 1. When the bearing 10 is mounted on the shaft 60 and the bearing 10 and the shaft 60 move axially relative to each other, when the shaft 60 strikes the bearing 10, the shaft 60 may first collide with the second lubricating element 22. The second lubricating element 22 is compressed and deformed, which plays a transition buffering role until the second lubricating element 22 is flush with the inner wall surface of the base 1. Then the base 1 continues to bear the pressure of the shaft 60 and rub against the shaft 60. When the shaft 60 leaves the second lubricating element 22, the second lubricating element 22 returns to its state of protruding from the inner wall surface of the base 1.

[0071] In some embodiments of this application, the elastic modulus of at least one of the first lubricant 21 and the second lubricant 22 is between 400 MPa and 1200 MPa.

[0072] In some embodiments of this application, the elastic modulus of the first lubricating element 21 is between 400 MPa and 1200 MPa. If the elastic modulus of the first lubricating element 21 is too small, under a certain impact force, the first lubricating element 21 will be directly and instantly flattened to be flush with the first wall surface 11 of the substrate 1, thus failing to provide any cushioning effect. Therefore, the elastic modulus of the first lubricating element 21 is selected to be not less than 400 MPa. If the elastic modulus of the first lubricating element 21 is too large, the first lubricating element 21 will not easily deform after being subjected to impact force, and its deformation will be insufficient to make the first lubricating element 21 flush with the first wall surface 11 of the substrate 1. Then, the first lubricating element 21 will be responsible for bearing pressure and friction wear, and will be quickly worn away and unable to recover. After being worn away, the first lubricating element 21 will lose its cushioning ability, that is, the design is an ineffective optimization design. Therefore, the elastic modulus of the first lubricating element 21 is selected to be not greater than 1200 MPa.

[0073] For example, the elastic modulus of the first lubricating component 21 can be 400MPa, 600MPa, 800MPa, 1000MPa, 1200MPa, etc., or other values ​​between 400MPa and 1200MPa, which will not be listed here.

[0074] In some embodiments of this application, the material of the first lubricant 21 includes polytetrafluoroethylene and graphite, or a polymer with a certain degree of elasticity, such as polyetheretherketone (PEEK).

[0075] In some embodiments, the material of the first lubricant 21 includes polytetrafluoroethylene (PTFE) and graphite. The PTFE comprises a mass percentage greater than or equal to 70% and less than or equal to 95%. The graphite comprises a mass percentage greater than or equal to 5% and less than or equal to 30%.

[0076] For example, the mass percentage of polytetrafluoroethylene (PTFE) is 80% and the mass percentage of graphite is 20%. Or, the mass percentage of PTFE is 85% and the mass percentage of graphite is 15%. Or, the mass percentage of PTFE is 90% and the mass percentage of graphite is 10%. Or, the mass percentage of PTFE is 95% and the mass percentage of graphite is 5%, etc.

[0077] In some embodiments, at least one of the first lubricant 21 and the second lubricant 22 is a combination of polytetrafluoroethylene (PTFE) and additives, wherein the proportion of PTFE in the combination (weight of PTFE / weight of the combination) is greater than 50%, and the additives are one or more of glass fiber, carbon fiber, graphite, molybdenum disulfide, or bronze powder.

[0078] In some embodiments, the material of the first lubricant 21 includes polytetrafluoroethylene (PTFE), with PTFE comprising more than 50% of the material. Other materials may be added to adjust its modulus, strength, and other properties. For example, one or more of the following materials may be added: glass fiber, carbon fiber, graphite, molybdenum disulfide, or bronze powder.

[0079] In some embodiments, the first lubricant 21 may be a self-lubricating component such as graphite or molybdenum disulfide added to polytetrafluoroethylene, so that the first lubricant 21 has self-lubricating properties, avoiding the problem that the friction coefficient of the first lubricant 21 is too large, resulting in high resistance and high wear.

[0080] In some embodiments of this application, the elastic modulus of the second lubricating element 22 is between 400 MPa and 1200 MPa. If the elastic modulus of the second lubricating element 22 is too small, under a certain impact force, the second lubricating element 22 will be directly and instantly flattened to be flush with the first wall surface 11 of the substrate 1, thus failing to provide any buffering effect. Therefore, the elastic modulus of the second lubricating element 22 is selected to be not less than 400 MPa. If the elastic modulus of the second lubricating element 22 is too large, the second lubricating element 22 will not easily deform after being subjected to impact force, and its deformation will be insufficient to make the second lubricating element 22 flush with the first wall surface 11 of the substrate 1. Then, the second lubricating element 22 will be responsible for bearing pressure and friction wear, and will be rapidly worn away and unable to recover. After being worn away, the second lubricating element 22 will lose its buffering capacity, that is, the design is an ineffective optimization design. Therefore, the elastic modulus of the second lubricating element 22 is selected to be not greater than 1200 MPa.

[0081] For example, the elastic modulus of the second lubricating component 22 can be 400MPa, 600MPa, 800MPa, 1000MPa, 1200MPa, etc., or other values ​​between 400MPa and 1200MPa, which will not be listed here.

[0082] In some embodiments of this application, the elastic modulus of the first lubricant 21 and the second lubricant 22 are both between 400 MPa and 1200 MPa.

[0083] For the testing methods of the elastic modulus of the first lubricating component 21, the second lubricating component 22, and the third lubricating component 23, different testing methods are suitable for testing different materials. For example, the static tensile method is suitable for metals, plastics, and composite materials; the dynamic mechanical analysis method (DMA) is suitable for polymer materials and composite materials; the ultrasonic method is suitable for metals, ceramics, and crystals; the nanoindentation method is suitable for thin films, coatings, and nanomaterials; and the resonance method is suitable for metals, ceramics, and crystals. Therefore, the corresponding measurement method can be selected to measure the elastic modulus of the first lubricating component 21, the second lubricating component 22, and the third lubricating component 23 according to their types.

[0084] In some embodiments of this application, the material of the second lubricant 22 includes polytetrafluoroethylene and graphite, or a polymer with a certain degree of elasticity, such as polyetheretherketone (PEEK).

[0085] In some embodiments, the material of the second lubricant 22 includes polytetrafluoroethylene (PTFE) and graphite. The PTFE comprises a mass percentage greater than or equal to 70% and less than or equal to 95%. The graphite comprises a mass percentage greater than or equal to 5% and less than or equal to 30%.

[0086] For example, the mass percentage of polytetrafluoroethylene (PTFE) is 80% and the mass percentage of graphite is 20%. Or, the mass percentage of PTFE is 85% and the mass percentage of graphite is 15%. Or, the mass percentage of PTFE is 90% and the mass percentage of graphite is 10%. Or, the mass percentage of PTFE is 95% and the mass percentage of graphite is 5%, etc.

[0087] In some embodiments, the material of the second lubricant 22 includes polytetrafluoroethylene (PTFE), with PTFE comprising more than 50% of the material. Other materials may be added to adjust its modulus, strength, and other properties. For example, one or more of the following materials may be added: glass fiber, carbon fiber, graphite, molybdenum disulfide, or bronze powder.

[0088] In some embodiments, the second lubricant 22 may be a self-lubricating component such as graphite or molybdenum disulfide added to polytetrafluoroethylene, so that the second lubricant 22 has self-lubricating properties, avoiding the problem that the friction coefficient of the second lubricant 22 is too large, resulting in high resistance and high wear.

[0089] In some embodiments of this application, the third lubricant 23 is graphite or molybdenum disulfide, etc.

[0090] In some embodiments of this application, the base 1 of the bearing 10 is made of tin bronze.

[0091] In some embodiments, both the first lubricating element 21 and the second lubricating element 22 protrude from the first wall surface 11 of the base 1. (Refer to...) Figures 6-10 As shown, when the shaft 60 and the bearing 10 come into contact, the shaft 60 first contacts the first wall surface 11 of either the first or second end of the bearing 10 (because the shaft 60 and the bearing 10 will inevitably have a certain relative inclination under normal circumstances). Therefore, the lubricating element near the first end of the base 1 is selected as the first lubricating element 21, and the lubricating element near the second end of the base 1 is selected as the second lubricating element 22. Both the first lubricating element 21 and the second lubricating element 22 protrude from the first wall surface 11 of the base 1. In this way, when the shaft 60 strikes the bearing 10, the shaft 60 first collides with the first lubricating element 21 and / or the second lubricating element 22, which have a buffering effect. For example, Figures 6-10 P in the diagram represents the point of impact. The first lubricant 21 and the second lubricant 22 are deformed by compression, which acts as a transition buffer until they are flush with the first wall surface 11 of the base 1. Then the base 1 continues to bear pressure and friction. When the shaft 60 leaves the surface of the bearing 10, the first lubricant 21 and the second lubricant 22 return to their state of protruding from the first wall surface 11 of the base 1.

[0092] When the coaxiality of shaft 60 and bearing is good, knocking noises are prone to occur. These knocking noises are sporadic and occur because the good coaxiality between shaft 60 and bearing means they are not in constant contact and friction during operation. Therefore, there are moments of sudden contact and knocking noises. The bases of shaft 60 and bearing are generally made of metal, and the knocking noise produced when two metals collide is very crisp and noticeable. For example, if shaft 60 is made of steel with a chrome-plated surface, and the bearing base is made of tin bronze, which is also metal, the knocking noise produced by the collision of shaft 60 and bearing will be very crisp and noticeable. To solve the knocking noise problem, materials with cushioning properties need to be used to provide cushioning during knocking, preventing sudden collisions between shaft 60 and bearing in a direction perpendicular to the contact surface.

[0093] According to the embodiments of this application, the bearing 10, by providing at least one of the first lubricating element 21 and the second lubricating element 22 protruding from the first wall surface 11 of the base 1, enables the first lubricating element 21 and / or the second lubricating element 22 protruding from the first wall surface 11 of the base 1 to have buffering properties, thereby providing cushioning for the bearing sliding mating parts during impact, preventing a sudden collision knocking sound between the bearing sliding mating parts and the bearing 10 in a direction perpendicular to the contact surface, and reducing knocking noise between the bearing sliding mating parts and the bearing 10. For example, the first lubricating element 21 and / or the second lubricating element 22 can provide cushioning for the shaft 60 during impact, preventing a sudden collision knocking sound between the shaft 60 and the bearing 10 in a direction perpendicular to the contact surface, and reducing knocking noise between the shaft 60 and the bearing 10.

[0094] In some embodiments of this application, reference is made to Figures 1-3 As shown, at least one of the first lubricating element 21 and the second lubricating element 22 is configured as a plurality of lubricating monomers 24 distributed circumferentially along the substrate 1, the lubricating monomers 24 being embedded in the substrate 1 and protruding from the first wall surface 11 of the substrate 1.

[0095] In some embodiments, the first wall 11 of the substrate 1 is a cylindrical surface.

[0096] Optionally, the lubricating monomer 24 can be a cylindrical structure, a spherical structure, or other shapes. For example, in Figures 1-3 In the example shown, the lubricating monomer 24 is a cylindrical structure, and the axial direction of the lubricating monomer 24 is consistent with the radial direction of the base 1.

[0097] In some embodiments of this application, reference is made to Figures 1-3 As shown, a first mounting hole is provided on the base 1. The first mounting hole is a through hole. The first lubricating element 21 is installed in the first mounting hole and protrudes from the first wall surface 11 of the base 1.

[0098] In some embodiments of this application, reference is made to Figures 1-3 As shown, a second mounting hole is provided on the base 1. The second mounting hole is a through hole. The second lubricating element 22 is installed in the second mounting hole and protrudes from the first wall surface 11 of the base 1.

[0099] In some embodiments of this application, the lubricating monomer 24 is a columnar structure with a constant cross-sectional area A, and the protrusion a of the lubricating monomer 24 protruding from the first wall 11 of the substrate 1 is:

[0100]

[0101] Where F is the radial impact load on the lubricating monomer 24 along the matrix 1, L is the radial dimension of the lubricating monomer 24 in the matrix 1, E is the elastic modulus of the material of the lubricating monomer 24, and A is the cross-sectional area of ​​the lubricating monomer 24 in a plane perpendicular to its own length extension direction. The units of a are meters (m), F is Newtons (N), L is meters (m), E is Pascals (Pa), and A is square meters (m²). 2 ).

[0102] The lubricating monomer 24 protrudes from the first wall surface 11 of the substrate 1 by an amount 'a', and is designed according to the following steps:

[0103] (1) Calculate the theoretical elastic deformation δ of the lubricating unit 24 that acts as a buffer when the actual bearing 10 is subjected to impact force, taking into account its size and quantity:

[0104]

[0105] δ represents the elastic deformation, measured in meters (m). The calculation of A requires consideration of the number of lubricating units 24 that actually provide cushioning; for example, the cross-sectional area of ​​a single lubricating unit 24 is 7 mm². 2 However, if the bearing 10 is subjected to impact force and it presses down on the two lubrication units 24, then when using this formula to calculate, A should be 7*2=14mm. 2 To calculate, that is, A is the product of the cross-sectional area of ​​a single lubricating unit 24 and the number of extruded lubricating units 24.

[0106] (2) Since the formula above δ calculates the elastic deformation of the lubricating unit 24 under impact in a free state, it does not consider whether the actual lubricating unit 24 is bonded or interference-fitted into the mounting hole of the base 1. Bonding or interference will reduce the elastic deformation of the lubricating unit 24. Therefore, it is necessary to adjust its deformation using a coefficient:

[0107] ε=K·δ

[0108] ε is the theoretical elastic deformation of the lubricating unit 24 with buffering effect after coefficient adjustment, in meters (m).

[0109] Where K is the deformation coefficient, which is dimensionless and has a value of 0.1 ≤ K ≤ 0.38. Therefore, the theoretical range of elastic deformation can be calculated as m ≤ ε ≤ n.

[0110] (3) The protrusion amount 'a' of the lubricating monomer 24 protruding from the first wall surface 11 of the substrate 1 should be within the range of 0.8 × m ≤ a ≤ 0.8 × n. The protrusion amount 'a' needs to be slightly smaller than the theoretical elastic deformation amount ε, because if the protrusion amount 'a' is greater than the theoretical elastic deformation amount ε, the lubricating monomer 24 will not be flush with the first wall surface 11 of the substrate 1 after being impacted, and will be easily worn. In summary, the range of the protrusion amount 'a' is:

[0111]

[0112] For example, the protrusion amount 'a' could be... Wait, it can also be Other values ​​between these ranges will not be listed here.

[0113] In a specific example, such as Figures 1-3 As shown, the first wall 11 of the substrate 1 is a cylindrical surface, the substrate 1 of the bearing 10 is made of tin bronze, the first lubricating element 21 and the second lubricating element 22 are both constructed as multiple lubricating units 24 distributed circumferentially along the substrate 1. The lubricating units 24 are embedded in the substrate 1 and protrude from the first wall 11 of the substrate 1. The first lubricating element 21 and the second lubricating element 22 are both made of a combination of polytetrafluoroethylene and additives. The elasticity of polytetrafluoroethylene is used to buffer the knocking noise between the bearing sliding parts and the bearing 10.

[0114] Taking the bearing sliding fit component, shaft 60, as an example, after shaft 60 and bearing 10 are assembled and arranged vertically or inclinedly, when shaft 60 and bearing 10 come into contact, shaft 60 first contacts the upper or lower end of bearing 10. Therefore, the two layers of lubricating components 2 near the upper end and the lower end of the base 1 are selected as a combination of polytetrafluoroethylene (PTFE) and additives. When shaft 60 strikes bearing 10, it first collides with the lubricating monomer 24 made of the combination of PTFE and additives, which has a buffering effect. The lubricating monomer 24 is deformed by compression, which plays a transition buffering role until it is flush with the first wall surface 11 of the tin bronze base 1. Then, the tin bronze base 1 continues to bear pressure and friction. When shaft 60 leaves the surface of bearing 10, the lubricating monomer 24 returns to its state of protruding from the first wall surface 11 of the tin bronze base 1.

[0115] In some embodiments of this application, reference is made to Figures 11-12As shown, a first mounting groove 12 is provided on the first wall surface 11 of the base 1, which is radially recessed along the base 1. The first mounting groove 12 extends circumferentially along the base 1. A first lubricating element 21 is disposed within the first mounting groove 12 and protrudes from the first wall surface 11 of the base 1. Thus, the first lubricating element 21 is an arc-shaped structure extending circumferentially along the base 1. Compared with point-shaped or columnar lubricating elements 24, when the shaft 60 and the bearing 10 are in contact, the arc-shaped structure provides a larger buffer area for the shaft 60, which is more conducive to reducing knocking noise between the shaft 60 and the bearing 10.

[0116] In the radial direction of the bearing 10, the depth of the first mounting groove 12 is less than the thickness of one side of the base 1. That is to say, the first mounting groove 12 is a blind groove, which will not weaken the strength of the base 1 too much, while ensuring that the base 1 is a complete structure.

[0117] When the first wall surface 11 is the inner wall surface of the base 1, the first mounting groove 12 can be recessed outward along the radial direction of the base 1; when the first wall surface 11 is the outer wall surface of the base 1, the first mounting groove 12 can be recessed inward along the radial direction of the base 1.

[0118] In some embodiments of this application, the protrusion a3 of the first lubricant 21 protruding from the first wall surface 11 of the substrate 1 can be consistent with the protrusion a mentioned above.

[0119] In some embodiments of this application, reference is made to Figures 11-12 As shown, the first mounting groove 12 is an annular groove extending circumferentially along the base 1, and the first lubricating element 21 is an annular structure. Compared with the point-lubricating unit 24, the annular structure has a larger buffer area for the shaft 60. When the shaft 60 and the bearing 10 come into contact, the first lubricating element 21 can be compressed and deformed within a larger range to play a transition buffering role, reducing the knocking noise between the shaft 60 and the bearing 10.

[0120] For example, the first mounting groove 12 is a full-circumferential annular groove extending along the circumference of the base 1, and the first lubricating element 21 is a full-circumferential annular structure. When the shaft 60 and the bearing 10 come into contact, the first lubricating element 21 can be squeezed and deformed within a 360° full-circumference range to play a transition buffering role, reducing the knocking noise between the shaft 60 and the bearing 10.

[0121] In some embodiments of this application, reference is made to Figures 11-12As shown, a second mounting groove 13 is provided on the first wall surface 11 of the base 1, which is radially recessed along the base 1. The second mounting groove 13 extends circumferentially along the base 1. A second lubricating element 22 is disposed within the second mounting groove 13 and protrudes from the first wall surface 11 of the base 1. Thus, the second lubricating element 22 is an arc-shaped structure extending circumferentially along the base 1. Compared to point-shaped or columnar lubricating elements 24, the arc-shaped structure provides a larger buffer area for the shaft 60 when the shaft 60 and bearing 10 are in contact, thereby more effectively reducing knocking noise between the shaft 60 and bearing 10.

[0122] In the radial direction of the bearing 10, the depth of the second mounting groove 13 is less than the thickness of one side of the base 1. That is to say, the second mounting groove 13 is a blind groove, which will not weaken the strength of the base 1 too much, while ensuring that the base 1 is a complete structure.

[0123] When the first wall surface 11 is the inner wall surface of the base 1, the second mounting groove 13 can be recessed outward along the radial direction of the base 1; when the first wall surface 11 is the outer wall surface of the base 1, the second mounting groove 13 can be recessed inward along the radial direction of the base 1.

[0124] In some embodiments of this application, the protrusion a4 of the second lubricant 22 protruding from the first wall surface 11 of the substrate 1 can be consistent with the protrusion a mentioned above.

[0125] In some embodiments of this application, reference is made to Figures 11-12 As shown, the second mounting groove 13 is an annular groove extending circumferentially along the base 1, and the second lubricating element 22 is an annular structure. Compared with the point-lubricating unit 24, the annular structure has a larger buffer area for the shaft 60. When the shaft 60 and the bearing 10 come into contact, the second lubricating element 22 can be compressed and deformed within a larger range to play a transition buffering role, reducing the knocking noise between the shaft 60 and the bearing 10.

[0126] For example, the second mounting groove 13 is a full-circumferential annular groove extending along the circumference of the base 1, and the second lubricating element 22 is a full-circumferential annular structure. When the shaft 60 and the bearing 10 come into contact, the second lubricating element 22 can be compressed and deformed within a 360° full-circumference range to play a transition buffering role, reducing the knocking noise between the shaft 60 and the bearing 10.

[0127] In some embodiments of this application, reference is made to Figures 13-15 As shown, the substrate 1 includes a first segment 14 and a second segment 15. The first segment 14 is close to the first end face 17 of the substrate 1, and the second segment 15 is connected to the end of the first segment 14 away from the first end face 17 of the substrate 1. In the axial direction away from the second segment 15, the inner diameter of the first segment 14 gradually increases. The first lubricating element 21 is provided on the first segment 14 and protrudes from the inner wall surface of the first segment 14.

[0128] It is understandable that "the inner diameter of the first segment 14 gradually increases in the axial direction away from the second segment 15" means that the inner diameter of the first segment 14 gradually increases in the direction from the end of the first segment 14 closer to the second segment 15 to the end away from the second segment 15, that is, in the direction from F2 to F1. There are several ways in which the inner diameter of the first segment 14 gradually increases. For example, one way is that the inner wall surface of the first segment 14 is a conical surface, with the small diameter end of the conical surface close to the second segment 15 and the large diameter end away from the second segment 15. The inner diameter of the conical surface gradually increases from the end of the first segment 14 close to the second segment 15 to the end away from the second segment 15. Another way is that the inner wall surface of the first segment 14 is a stepped surface, with the smaller inner diameter part of the stepped surface close to the second segment 15 and the larger inner diameter part away from the second segment 15. The inner diameter of the stepped surface increases step by step from the end of the first segment 14 close to the second segment 15 to the end away from the second segment 15. Yet another way is that the inner wall surface of the first segment 14 is an arc-shaped surface, which protrudes radially from the base 1 in a direction away from the axis of the base 1. The small diameter end of the arc-shaped surface is close to the second segment 15, and the large diameter end is away from the second segment 15.

[0129] By setting the first segment 14 to a structure with a gradually increasing inner diameter, friction between the inner wall surface of the first segment 14 and the shaft 60 can be avoided. When the shaft 60 and the bearing 10 move relative to each other, the first lubricating element 21 protruding from the inner wall surface of the first segment 14 can contact the shaft 60, playing a transition buffering role and reducing knocking noise between the shaft 60 and the bearing 10.

[0130] In some embodiments of this application, reference is made to Figures 13-15 As shown, the lubricating component 2 also includes a third lubricating component 23, which is disposed in the second segment 15.

[0131] In some embodiments of this application, reference is made to Figures 13-15 As shown, the first lubricating element 21 does not protrude from the inner wall surface of the second segment 15. For example, the inner end face of the first lubricating element 21 may be flush with the inner wall surface of the second segment 15, or it may be slightly recessed relative to the inner wall surface of the second segment 15.

[0132] In some embodiments of this application, reference is made to Figures 13-15 As shown, the base 1 also includes a third segment 16, which is connected to the end of the second segment 15 away from the first segment 14. In the axial direction away from the second segment 15, the inner diameter of the third segment 16 gradually increases. The second lubricating element 22 is provided in the third segment 16 and protrudes from the third segment 16.

[0133] It is understandable that "the inner diameter of the third segment 16 gradually increases in the axial direction away from the second segment 15" means that the inner diameter of the third segment 16 gradually increases in the direction from the end of the third segment 16 closer to the second segment 15 to the end away from the second segment 15, that is, in the direction from F2 to F1. There are several ways to gradually increase the inner diameter of the third segment 16. For example, one way is that the inner wall surface of the third segment 16 is a conical surface, with the small diameter end of the conical surface close to the second segment 15 and the large diameter end away from the second segment 15. The inner diameter of the conical surface gradually increases from the end of the third segment 16 close to the second segment 15 to the end away from the second segment 15. Another way is that the inner wall surface of the third segment 16 is a stepped surface, with the smaller inner diameter part of the stepped surface close to the second segment 15 and the larger inner diameter part away from the second segment 15. The inner diameter of the stepped surface increases step by step from the end of the third segment 16 close to the second segment 15 to the end away from the second segment 15. Yet another way is that the inner wall surface of the third segment 16 is an arc-shaped surface, which protrudes radially from the base 1 in a direction away from the axis of the base 1. The small diameter end of the arc-shaped surface is close to the second segment 15, and the large diameter end is away from the second segment 15.

[0134] In some embodiments of this application, reference is made to Figures 13-15 As shown, the second lubricating element 22 does not protrude from the inner wall surface of the second segment 15. For example, the inner end face of the second lubricating element 22 may be flush with the inner wall surface of the second segment 15, or it may be slightly recessed relative to the inner wall surface of the second segment 15.

[0135] By setting the third segment 16 to a structure with a gradually increasing inner diameter, friction between the inner wall surface of the third segment 16 and the shaft 60 can be avoided. When the shaft 60 and the bearing 10 move relative to each other, the second lubricating element 22 protruding from the inner wall surface of the third segment 16 can contact the shaft 60, playing a transition buffering role and reducing knocking noise between the shaft 60 and the bearing 10.

[0136] In some embodiments of this application, reference is made to Figures 13-15 As shown, the inner end face of the first lubricating element 21 is flush with the inner wall surface of the second segment 15. The first lubricating element 21 is constructed as lubricating units distributed circumferentially along the first segment 14. Each lubricating unit is a columnar structure with a constant cross-sectional area A1. The maximum protrusion a1 of the first lubricating element 21 protruding from the inner wall surface of the first segment 14 is:

[0137]

[0138] Wherein, F1 is the radial impact load on the first lubricating element 21 along the base 1, L1 is the radial dimension of the first lubricating element 21 in the base 1, E1 is the elastic modulus of the first lubricating element 21, and A1 is the cross-sectional area of ​​the first lubricating element 21 in a plane perpendicular to its own length extension direction.

[0139] For example, the protrusion a1 could be Wait, it can also be Other values ​​between these ranges will not be listed here.

[0140] It should be noted that the design steps for the protrusion a1 are similar to those for the protrusion a mentioned above, and will not be repeated here.

[0141] In some embodiments of this application, the inner end face of the second lubricating element 22 is flush with the inner wall surface of the second segment 15. The second lubricating element 22 is constructed as lubricating units distributed circumferentially along the third segment 16. Each lubricating unit is a columnar structure with a constant cross-sectional area A2. The maximum protrusion a2 of the second lubricating element 22 protruding from the inner wall surface of the third segment 16 is:

[0142]

[0143] Wherein, F2 is the radial impact load on the second lubricating element 22 along the base 1, L2 is the radial dimension of the second lubricating element 22 in the base 1, E2 is the elastic modulus of the second lubricating element 22, and A2 is the cross-sectional area of ​​the second lubricating element 22 in a plane perpendicular to its own length extension direction.

[0144] For example, the protrusion a2 could be Wait, it can also be Other values ​​between these ranges will not be listed here.

[0145] It should be noted that the design steps for protrusion a2 are similar to those for protrusion a mentioned above, and will not be repeated here.

[0146] In some embodiments of this application, the first lubricant 21 and the second lubricant 22 are made of the same material. For example, both the first lubricant 21 and the second lubricant 22 are a combination of polytetrafluoroethylene and additives.

[0147] In some embodiments of this application, the first lubricant 21 and the second lubricant 22 are made of different materials. For example, the first lubricant 21 is a combination of polytetrafluoroethylene and additives, and the second lubricant 22 is polyetheretherketone (PEEK).

[0148] In some embodiments of this application, reference is made to Figures 1-3 , Figures 11-15 As shown, a third mounting hole is provided on the first wall surface 11 of the substrate 1, and a third lubricant 23 is filled in the third mounting hole.

[0149] For example, in some embodiments, when the shaft 60 and the bearing 10 have not yet moved relative to each other, the inner end face of the third lubricant 23 can be flush with the first wall surface 11 of the base 1. When the shaft 60 and the bearing 10 move relative to each other, friction will generate heat, and the third lubricant 23 will protrude slightly from the first wall surface 11 of the base 1 due to thermal expansion to lubricate the friction area between the bearing 10 and the shaft 60.

[0150] Of course, in other embodiments, when the shaft 60 and the bearing 10 have not yet moved relative to each other, the inner end face of the third lubricant 23 may protrude slightly from the first wall surface 11 of the base 1 or be slightly recessed relative to the first wall surface 11 of the base 1.

[0151] Reference Figures 16-19 As shown, this application also relates to a linear motor 100, which may further include a housing 20, a central shaft 30, and a first bearing 10a. The central shaft 30 is at least partially disposed within the housing 20, and the housing 20 and the central shaft 30 are capable of relative movement along the axial direction of the linear motor 100. The first bearing 10a is fixed to one of the housing 20 and the central shaft 30, and is in sliding engagement with the other of the housing 20 and the central shaft 30. The first bearing 10a is a bearing 10 as described in any of the above embodiments.

[0152] In some embodiments, the first bearing 10a is fixed to the housing 20 and slidably fitted with the central shaft 30. For example, the housing 20 has a housing bore, the first bearing 10a is fixedly mounted on the bore wall of the housing, and the central shaft 30 passes through the first bearing 10a. The first bearing 10a and the bore wall of the housing bore may be an interference fit, thereby the first bearing 10a can be securely mounted in the housing bore. The first bearing 10a and the central shaft 30 may be a clearance fit, thereby the housing 20 and the first bearing 10a can move relative to the central shaft 30 along the axial direction of the linear motor 100. In this embodiment, the central shaft 30 can be understood as the aforementioned shaft 60, and at least one of the first lubricating element 21 and the second lubricating element 22 protrudes from the first wall surface 11 of the base 1. This means, for example, when the linear motor 100 is not subjected to radial force, or the radial force is small, at least one of the first lubricating element 21 and the second lubricating element 22 protrudes from the inner wall surface of the base 1. In this embodiment, the first wall surface 11 refers to the inner wall surface of the base 1.

[0153] In other embodiments, the first bearing 10a is fixed to the central shaft 30 and slides in fit with the housing 20. Specifically, the housing 20 has a housing bore, and the first bearing 10a is fixedly mounted on the central shaft 30, passing through the housing bore. The first bearing 10a and the central shaft 30 may have an interference fit, thereby ensuring the first bearing 10a is securely mounted on the central shaft 30. Alternatively, the first bearing 10a and the housing bore may have a clearance fit, thereby allowing the housing 20 to move axially relative to the first bearing 10a and the central shaft 30 along the linear motor 100. In this embodiment, at least one of the first lubricating element 21 and the second lubricating element 22 protrudes from the first wall surface 11 of the base 1. This means, for example, when the linear motor 100 is not subjected to radial force, or when the radial force is small, at least one of the first lubricating element 21 and the second lubricating element 22 protrudes from the outer wall surface of the base 1. In this embodiment, the first wall surface 11 refers to the outer wall surface of the base 1.

[0154] In some embodiments of this application, the first bearing 10a is the bearing 10 of the first aspect embodiment described above. Thus, by configuring the first lubricating element 21 and / or the second lubricating element 22 of the first bearing 10a to protrude from the inner or outer wall surface of the base 1, the first bearing 10a can provide cushioning for impacts to the bearing sliding mating member (central shaft 30 or housing 20), preventing sudden impact noise between the first bearing 10a and the bearing sliding mating member from occurring directly in a direction perpendicular to the contact surface, thereby reducing abnormal impact noise between the first bearing 10a and the bearing sliding mating member.

[0155] Reference Figures 16-19 As shown, the linear motor 100 may also include a second bearing 10b and a guide post 70. The guide post 70 is adapted to be fixedly connected to the fork arm 200. The second bearing 10b is fixed to one of the central shaft 30 and the guide post 70, and is slidably engaged with the other of the central shaft 30 and the guide post 70.

[0156] In some embodiments, the second bearing 10b is fixed to the central shaft 30, and the guide post 70 is slidably fitted. Specifically, the central shaft 30 has a guide cavity 301 inside, and the second bearing 10b is mounted on the cavity wall of the guide cavity 301. The second bearing 10b is used for the guide post 70 to pass through, that is, the guide post 70 passes through the second bearing 10b. The second bearing 10b and the cavity wall of the guide cavity 301 may be an interference fit, thereby the second bearing 10b can be firmly installed in the guide cavity 301. The second bearing 10b and the guide post 70 may be a clearance fit, thereby the guide post 70 can move axially along the linear motor 100 relative to the second bearing 10b and the central shaft 30. In this embodiment, the guide post 70 can be understood as the aforementioned shaft 60, where at least one of the first lubricating element 21 and the second lubricating element 22 protrudes from the first wall surface 11 of the base 1. This means, for example, when the linear motor 100 is not subjected to radial force, or when the radial force is small, at least one of the first lubricating element 21 and the second lubricating element 22 protrudes from the inner wall surface of the base 1. In this embodiment, the first wall surface 11 refers to the inner wall surface of the base 1.

[0157] In other embodiments, the second bearing 10b is fixed to the guide post 70, and the central shaft 30 is slidably fitted. Specifically, the central shaft 30 has a guide cavity 301 inside, the second bearing 10b is mounted on the guide post 70, and the second bearing 10b passes through the guide cavity 301. The second bearing 10b and the guide post 70 may have an interference fit, thereby the second bearing 10b can be firmly mounted on the guide post 70. The second bearing 10b and the cavity wall of the guide cavity 301 may have a clearance fit, thereby the guide post 70 and the second bearing 10b can move relative to the central shaft 30 along the axial direction of the linear motor 100. In this embodiment, at least one of the first lubricating element 21 and the second lubricating element 22 protrudes from the first wall surface 11 of the base 1. This means, for example, when the linear motor 100 is not subjected to radial force, or the radial force is small, at least one of the first lubricating element 21 and the second lubricating element 22 protrudes from the outer wall surface of the base 1. In this embodiment, the first wall surface 11 refers to the outer wall surface of the base 1.

[0158] In some embodiments of this application, the second bearing 10b is the bearing 10 of the first aspect embodiment described above. Thus, by configuring the first lubricating element 21 and / or the second lubricating element 22 of the second bearing 10b to protrude from the first wall surface 11 of the base 1, the second bearing 10b can provide cushioning for impacts on the bearing sliding mating parts (guide post 70 or central shaft 30), preventing sudden impact noises between the second bearing 10b and the bearing sliding mating parts in a direction perpendicular to the contact surface, thereby reducing impact noises between the second bearing 10b and its slidingly mating components.

[0159] In some embodiments of this application, the second bearing 10b is the bearing 10 in any of the above embodiments.

[0160] In some embodiments of this application, at least one of the first bearing 10a and the second bearing 10b is the bearing 10 of the first aspect embodiment described above. For example, only the first bearing 10a may be the bearing 10 of the first aspect embodiment, only the second bearing 10b may be the bearing 10 of the first aspect embodiment, or both the first bearing 10a and the second bearing 10b may be the bearing 10 of the first aspect embodiment. According to the linear motor 100 of the embodiments of this application, by setting the first lubricating element 21 and / or the second lubricating element 22 of at least one of the first bearing 10a and the second bearing 10b to protrude from the first wall surface 11 of the base 1, the bearing can provide cushioning for the bearing sliding mating member during impact, so that the bearing and the bearing sliding mating member do not directly generate a sudden collision knocking sound in the direction perpendicular to the contact surface, thereby reducing the knocking noise between the bearing and the bearing sliding mating member.

[0161] Figure 4 This data represents actual measurements of knocking noise from a linear motor bearing in which all lubrication components are graphite pillars that do not protrude from the inner wall of the substrate, a technology in which all lubrication components are graphite pillars. Figure 5 The data represents measured data of knocking noise from a linear motor in a bearing 10, where both the first lubricating element 21 and the second lubricating element 22 are lubricating monomers 24 and are made of a combination of polytetrafluoroethylene and additives. The horizontal axis represents time (in seconds), and the vertical axis represents vibration acceleration (in g, where g is the acceleration due to gravity, g = 9.8 m / s²). 2 The results showed that the bearing 10, which uses the first lubricant 21 and the second lubricant 22 of this application as both being lubricating monomers 24 and both being a combination of polytetrafluoroethylene and additives, can optimize about 90% of the knocking vibration (knocking vibration amplitude from 5g to 0.5g), and can effectively optimize knocking noise.

[0162] In some embodiments of this application, reference is made to Figures 16-17 As shown, the linear motor 100 also includes a stator 40 and a mover 50. The stator 40 is mounted on the central shaft 30, and the mover 50 is mounted on the housing 20. The mover 50 is sleeved on the outer periphery of the stator 40 and is disposed opposite to the stator 40. The stator 40 and the central shaft 30 form a stator assembly, and the mover 50 and the housing 20 form a mover assembly. The mover assembly is movable relative to the stator assembly along the axial direction of the linear motor 100.

[0163] It should be noted that for linear motors, the mover and stator are relative terms. Depending on the operating conditions of the linear motor, the mover can also act as the stator, and vice versa.

[0164] When the linear motor 100 is applied in a vehicle 10000, the linear motor 100 is installed vertically or at an angle. The upper end of the central shaft 30 is adapted to connect to the vehicle body, and the lower end of the housing 20 is adapted to connect to the fork arm 200, which is adapted to connect to the wheel. The first bearing 10a and the housing 20 can move axially along with the follower 50 of the linear motor 100.

[0165] In some other embodiments of this application, the stator 40 may be mounted on the housing 20, and the mover 50 may be mounted on the central shaft 30. In this case, the stator 40 and the housing 20 form a stator assembly, and the mover 50 and the central shaft 30 form a mover assembly, which can move relative to the stator assembly along the axial direction of the linear motor 100.

[0166] In some embodiments of this application, reference is made to Figures 16-17 As shown, the mover 50 is a permanent magnet, and the stator 40 includes an iron core 401 and windings 402. The iron core 401 includes multiple winding slots distributed along the axial direction of the iron core 401, and the windings 402 are wound within the winding slots. The mover 50 is typically composed of multiple permanent magnets arranged in a specific polarity. The iron core 401 is part of the motor's magnetic circuit and can be made of silicon steel sheets or non-crystalline materials stacked together to reduce eddy current losses; the iron core 401 can also be made of a stack of soft magnetic materials.

[0167] The winding 402 is wound around the iron core 401. When energized, it generates a magnetic field that can drive the mover 50 to move along the axial direction of the linear motor 100, thereby driving the components (such as the housing 20) that are fixedly connected to the mover 50 to move synchronously.

[0168] When the bearing 10 is used in the linear motor 100, the linear motor 100 will inevitably be subjected to radial forces of different magnitudes and directions under different application conditions. When the radial force is large, at least one of the first lubricating element 21 and the second lubricating element 22 will not protrude from the first wall surface 11 of the base 1. In this way, at least one of the first lubricating element 21 and the second lubricating element 22 will play a buffering role due to its elastic expansion and contraction, which can reduce the impact force of the bearing sliding fit and reduce the knocking noise between the bearing sliding fit and the bearing.

[0169] Reference Figures 16-19 As shown, the suspension system 1000 according to a third aspect embodiment of this application includes the linear motor 100 of the above embodiment.

[0170] In some embodiments of this application, reference is made to Figures 16-19As shown, the suspension system 1000 also includes a fork arm 200, which is connected to the housing 20. The fork arm 200 is also used to connect to the lower control arm of the frame. The fork arm 200 is fixedly connected to the guide post 70, which is adapted to extend into the guide cavity 301 and can move axially along the central axis 30. The second bearing 10b is disposed at the insertion and mating point between the guide post 70 and the guide cavity 301.

[0171] Taking a case where the first bearing 10a is fixed to the housing 20 and has a sliding fit with the central shaft 30, the second bearing 10b is fixed to the central shaft 30 and has a sliding fit with the guide post 70, the stator 40 is mounted on the central shaft 30, and the mover 50 is mounted on the housing 20, when the winding 402 of the stator 40 is energized, it can drive the mover 50 to move along the axial direction of the linear motor 100, thereby causing the housing 20 and the fork arm 200 to move synchronously. Thus, the housing 20 and the first bearing 10a move relative to the central shaft 30, and the guide post 70 moves relative to the second bearing 10b and the central shaft 30.

[0172] Reference Figure 16 As shown, the suspension system 1000 also includes a strut top 300 and an elastic element 400. The central shaft 30 is fixed to the strut top 300, and the strut top 300 is adapted to be fixed to the vehicle body. The upper end of the elastic element 400 is connected to the strut top 300, and the lower end is connected to the housing 20. When the housing 20 moves along the axial direction of the linear motor 100, the housing 20 moves closer to or further away from the strut top 300 to change the deformation of the elastic element 400. The elastic element 400 can play a role in absorbing vibration and buffering. The elastic element 400 can be a coil spring, an air spring, etc., and its form is not limited.

[0173] According to the suspension system 1000 of this application embodiment, by setting the first lubricating element 21 and / or the second lubricating element 22 of at least one of the first bearing 10a and the second bearing 10b to protrude from the first wall surface 11 of the base 1, the bearing can provide a cushioning effect on the bearing sliding mating part when it is struck, so that the bearing and the bearing sliding mating part do not produce a sudden collision knocking sound in the direction perpendicular to the contact surface, thereby reducing the knocking noise between the bearing and the bearing sliding mating part.

[0174] Reference Figure 20 As shown, the vehicle 10000 according to the fourth aspect of this application includes the suspension system 1000 of the above embodiment.

[0175] According to an embodiment of this application, the vehicle 10000's suspension system 1000, by configuring the first lubricating element 21 and / or the second lubricating element 22 of at least one of the first bearing 10a and the second bearing 10b to protrude from the first wall surface 11 of the base 1, enables the bearing to provide cushioning for the bearing sliding mating parts during impact, so that the bearing and the bearing sliding mating parts do not directly generate a sudden collision knocking sound in the direction perpendicular to the contact surface, reducing the knocking noise between the bearing and the bearing sliding mating parts, thereby improving the driving and riding experience.

[0176] In the description of this application, it should be understood that the terms "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0177] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication between two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0178] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. In addition, those skilled in the art can combine and integrate the different embodiments or examples described in this specification.

[0179] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. A bearing (10), characterized in that, include: The substrate (1) is cylindrical; Lubricating component (2), which is fixed to the base (1), and comprising: A first lubricating element (21) is located near the first end of the substrate (1); The second lubricating element (22) is located near the second end of the base (1); At least one of the first lubricating element (21) and the second lubricating element (22) protrudes from the first wall surface (11) of the substrate (1); When at least one of the first lubricant (21) and the second lubricant (22) is pressed, at least one of the first lubricant (21) and the second lubricant (22) is not protruding from the first wall surface (11) of the substrate (1).

2. The bearing (10) according to claim 1, characterized in that, The elastic modulus of at least one of the first lubricating element (21) and the second lubricating element (22) is between 400 MPa and 1200 MPa.

3. The bearing (10) according to claim 1, characterized in that, At least one of the first lubricating element (21) and the second lubricating element (22) is configured as a plurality of lubricating monomers (24) distributed circumferentially along the substrate (1), the lubricating monomers being embedded in the substrate (1) and protruding from the first wall surface (11) of the substrate (1).

4. The bearing (10) according to claim 3, characterized in that, The lubricating monomer (24) is a columnar structure with a constant cross-sectional area A. The protrusion a of the lubricating monomer (24) from the first wall surface (11) of the substrate (1) is: Wherein, F is the radial impact load on the lubricating monomer (24) along the matrix (1), L is the radial dimension of the lubricating monomer (24) in the matrix (1), E is the elastic modulus of the material of the lubricating monomer (24), and A is the cross-sectional area of ​​the lubricating monomer (24) in a plane perpendicular to its own length extension direction.

5. The bearing (10) according to claim 1, characterized in that, The first wall surface (11) of the substrate (1) is provided with a first mounting groove (12) that is recessed radially along the substrate (1). The first mounting groove (12) extends circumferentially along the substrate (1). The first lubricating element (21) is disposed in the first mounting groove (12) and protrudes from the first wall surface (11) of the substrate (1).

6. The bearing (10) according to claim 5, characterized in that, The first mounting groove (12) is an annular groove extending circumferentially along the substrate (1), and the first lubricating element (21) is an annular structure.

7. The bearing (10) according to any one of claims 1-6, characterized in that, The lubricating element (2) further includes a third lubricating element (23), which is located between the first lubricating element (21) and the second lubricating element (22) in a first direction, wherein the first direction is the axial direction of the base (1); The elastic modulus of the third lubricating element (23) is greater than that of the first lubricating element (21) and the second lubricating element (22).

8. The bearing (10) according to any one of claims 1-4, characterized in that, The substrate (1) includes a first segment (14) and a second segment (15), the first segment (14) being close to a first end face (17) of the substrate (1), and the second segment (15) connecting the end of the first segment (14) away from the first end face (17) of the substrate (1); In the axial direction away from the second segment (15), the inner diameter of the first segment (14) gradually increases, and the first lubricant (21) is provided in the first segment (14) and protrudes from the inner wall surface of the first segment (14).

9. The bearing (10) according to claim 8, characterized in that, The lubricating element (2) further includes a third lubricating element (23), which is disposed in the second segment (15).

10. The bearing (10) according to claim 8, characterized in that, The first lubricating element (21) does not protrude from the inner wall surface of the second segment (15).

11. The bearing (10) according to claim 1, characterized in that, At least one of the first lubricating element (21) and the second lubricating element (22) is a combination of polytetrafluoroethylene and additives, wherein the proportion of polytetrafluoroethylene in the combination is greater than 50%, and the additives are one or more of glass fiber, carbon fiber, graphite, molybdenum disulfide or bronze powder.

12. A linear motor (100), characterized in that, include: Shell (20); A central shaft (30) is at least partially disposed within the housing (20), and the housing (20) and the central shaft (30) are capable of relative movement along the axial direction of the linear motor (100); A first bearing (10a) is fixed to one of the housing (20) and the central shaft (30) and is in sliding engagement with the other of the housing (20) and the central shaft (30); Wherein, the first bearing (10a) is the bearing (10) according to any one of claims 1-11.

13. The linear motor (100) according to claim 12, characterized in that, The first bearing (10a) is fixed to the housing (20) and slides with the central shaft (30), and the first wall surface (11) is the inner wall surface of the base (1).

14. The linear motor (100) according to claim 12, characterized in that, The first bearing (10a) is fixed to the central shaft (30) and slides in fit with the housing (20), and the first wall surface (11) is the outer wall surface of the base (1).

15. A suspension system (1000), characterized in that, include: The linear motor (100) according to any one of claims 12-14.

16. A vehicle (10000), characterized in that, Includes the suspension system (1000) as described in claim 15.

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