Thrust bearing, planetary transmission mechanism and gearbox

Abstract

The invention discloses a thrust bearing, a planetary transmission mechanism and a gearbox, and belongs to the technical field of gears.The thrust bearing comprises a supporting rotating stand, a restraining structure and thrust pads, the multiple thrust pads are arranged on the supporting rotating stand in the circumferential direction of the supporting rotating stand, and bearing faces are formed on the thrust pads; the bearing surface comprises at least two inclined surfaces and a transition surface positioned between the two adjacent inclined surfaces; the lubricating oil can form an oil film on the bearing surface; the restraining structure is used for detachably connecting the thrust pad to the supporting rotating frame. The planetary transmission mechanism is provided with the thrust bearing, and the gearbox comprises the thrust bearing or the planetary transmission mechanism. According to the thrust bearing, the thrust pads are arranged in a split manner, and the bearing surface with the special molded surface and the detachable constraint structure cooperate with each other, so that the maintenance cost of the thrust bearing is reduced, and the lubricating performance is optimized.

Description

Technical Field

[0001] This invention relates to the field of gearbox technology, and more particularly to a thrust bearing, a planetary transmission mechanism, and a gearbox. Background Technology

[0002] In mechanical transmission, the main function of the thrust bearing is to bear axial force, ensure the stable operation of mechanical components in the axial direction, and maintain the normal operation of the entire transmission system.

[0003] In the prior art, the thrust bearings used in conjunction with radial bearings in gearboxes are usually installed at both ends of the planetary gear axis, and are mostly in the form of a single thrust bearing, which is fixed to the rotating frame by bolts and other components.

[0004] However, since the thrust bearings of existing thrust bearings are made of a single piece and are fixedly connected to the rotating frame, once the thrust bearing wears out or fails and requires maintenance, the entire thrust bearing must be replaced, which is costly. Summary of the Invention

[0005] The purpose of this invention is to provide a thrust bearing, a planetary transmission mechanism, and a gearbox to solve the technical problems in the prior art where the thrust bearing is fixedly installed, difficult to disassemble, and thus has high maintenance and replacement costs.

[0006] To achieve this objective, the present invention adopts the following technical solution:

[0007] On one hand, the present invention provides a thrust bearing, comprising:

[0008] Support frame;

[0009] Multiple thrust bearings are arranged circumferentially on the support frame. Each thrust bearing has a bearing surface, which includes at least two inclined surfaces and a transition surface between two adjacent inclined surfaces. Lubricating oil can form an oil film on the bearing surface.

[0010] A constraint structure is provided for detachably connecting the thrust bearing to the support frame.

[0011] Preferably, the transition surface is located in the middle of the bearing surface, and each side of the transition surface is provided with an inclined surface. The inclined surfaces extend from the transition surface to both ends of the thrust bearing, and the height of the two inclined surfaces changes from the middle of the thrust bearing to both ends.

[0012] Preferably, the constraint structure includes a pressure plate and a first fastener; both ends of the thrust pad have stepped surfaces lower than the bearing surface; the pressure plate is disposed between two adjacent thrust pads and presses against two adjacent stepped surfaces; the first fastener fixes the pressure plate to the support frame;

[0013] And / or, the constraint structure includes a second fastener that passes through the transition surface to secure the thrust pad to the support frame.

[0014] Preferably, the height of the upper surface of the pressure plate is lower than the height of the bearing surface, and the pressure plate and the inclined surfaces of the two adjacent thrust bearings form a first oil collection groove. From the middle of the thrust bearings to both ends, the two inclined surfaces extend downwards respectively.

[0015] Preferably, the support frame is provided with an oil passage, and the first fastener is provided with a first connecting channel, which is used to connect the first oil collection tank and the oil passage.

[0016] Preferably, from the middle of the thrust bearing towards both ends, the two inclined surfaces extend downwards, and the inclined surfaces of two adjacent thrust bearings and the supporting frame form a second oil collection groove.

[0017] Preferably, the support frame is provided with an oil passage, and the second fastener is provided with a second connecting passage, which is used to connect the bearing surface and the oil passage; the two inclined surfaces extend upward from the middle of the thrust bearing towards both ends.

[0018] Preferably, a shoulder is formed on the support frame, and the shoulder is arranged around the outer periphery of the thrust bearing to radially limit the thrust bearing.

[0019] On the other hand, the present invention provides a planetary transmission mechanism, including the aforementioned thrust bearing, and further including planetary gears, a pin, and a radial sliding bearing disposed between the two, wherein the pin is disposed on the planet carrier, and the thrust bearing is disposed between the planetary gears and the planet carrier.

[0020] In addition, the present invention also provides a gearbox configured with the aforementioned thrust bearing or planetary transmission mechanism.

[0021] The beneficial effects of this invention are:

[0022] The thrust bearing proposed in this invention employs a segmented structure with multiple independent thrust pads circumferentially arranged on a support frame, detachably connected to the support frame via a constraint structure. This replaces the traditional integral pad structure, allowing for the replacement of the entire thrust bearing only by disassembling and replacing the damaged individual thrust pad when it wears or fails. This simplifies maintenance and saves time and costs. Each thrust pad's bearing surface consists of two inclined surfaces and a transition surface in between. During planetary gear rotation, the inclined surfaces effectively guide lubricating oil into the bearing surface, ensuring a stable oil film formation in both rotational directions. This guarantees the thrust bearing's lubrication performance and load-bearing capacity under various operating conditions (forward and reverse rotation), reducing wear and extending service life. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the first structure of the thrust bearing provided in Embodiment 1 of the present invention;

[0024] Figure 2 This is a schematic diagram of the thrust bearing structure provided in Embodiment 1 of the present invention;

[0025] Figure 3 This is a schematic diagram of the second structure of the thrust bearing provided in Embodiment 1 of the present invention;

[0026] Figure 4 This is an exploded structural diagram of the thrust bearing provided in Embodiment 1 of the present invention;

[0027] Figure 5 This is a cross-sectional view of the thrust bearing provided in Embodiment 1 of the present invention;

[0028] Figure 6 This is a top view of the thrust bearing provided in Embodiment 1 of the present invention;

[0029] Figure 7 This is a front view of the thrust bearing provided in Embodiment 1 of the present invention;

[0030] Figure 8 This is a schematic diagram of the first structure of the thrust bearing provided in Embodiment 2 of the present invention;

[0031] Figure 9 This is a schematic diagram of the second structure of the thrust bearing provided in Embodiment 2 of the present invention;

[0032] Figure 10 This is a cross-sectional view of the thrust bearing provided in Embodiment 2 of the present invention;

[0033] Figure 11 This is a top view of the thrust bearing provided in Embodiment 2 of the present invention;

[0034] Figure 12 This is a front view of the thrust bearing provided in Embodiment 2 of the present invention;

[0035] Figure 13 This is a cross-sectional view of the planetary transmission mechanism provided in Embodiment 3 of the present invention.

[0036] In the picture:

[0037] 100. Planetary gear; 200. Pin; 300. Radial sliding bearing; 400. Planetary carrier;

[0038] 1. Support frame; 11. Oil passage; 12. Shoulder; 13. Threaded hole;

[0039] 2. Thrust pad; 20. Bearing surface; 21. Inclined surface; 22. Transition surface; 23. Stepped surface; 231. Mounting hole; 24. Connecting surface; 25. First oil collection groove; 26. Second oil collection groove; 27. Fixing hole;

[0040] 3. Constraint structure; 31. Pressure plate; 311. Connecting hole; 32. First fastener; 321. First connecting channel; 33. Second fastener; 331. Second connecting channel. Detailed Implementation

[0041] Embodiments of the present invention 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 components or components having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0042] In the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection or a detachable connection; a mechanical connection or an electrical connection; a direct connection or an indirect connection through an intermediate medium; or the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0043] In the description of this invention, unless otherwise expressly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature being directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature being directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0044] The technical solution of the present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0045] Example 1

[0046] See Figures 1 to 7 The thrust bearing provided in this embodiment of the invention includes a support frame 1, thrust bearings 2, and a constraint structure 3. Multiple thrust bearings 2 are arranged circumferentially on the support frame 1. Each thrust bearing 2 has a bearing surface 20, which includes at least two inclined surfaces 21 and a transition surface 22 located between two adjacent inclined surfaces 21. Lubricating oil can form an oil film on the bearing surface 20. The constraint structure 3 is used to detachably connect the thrust bearings 2 to the support frame 1.

[0047] The thrust bearing proposed in this invention employs a segmented structure with multiple independent thrust pads 2 circumferentially arranged on a support frame 1, and detachably connected to the support frame 1 by a constraint structure 3. This replaces the traditional integral pad structure, allowing for the replacement of the entire thrust bearing only by disassembling and replacing the damaged individual thrust pad 2 when a single thrust pad 2 wears or fails. This simplifies maintenance and saves time and costs. The bearing surface 20 of each thrust pad 2 consists of two inclined surfaces 21 and a transition surface 22 in between. The inclined surfaces 21 effectively guide lubricating oil into the bearing surface 20, ensuring a stable oil film on the bearing surface 20 in both rotational directions. This guarantees the lubrication performance and load-bearing capacity of the thrust bearing under various operating conditions, including forward and reverse rotation, reducing wear and increasing service life.

[0048] The working principle and specific structure of this thrust bearing will be explained in detail below.

[0049] Each thrust bearing 2 has a bearing surface 20 formed thereon, which bears axial force. In this embodiment, the bearing surface 20 has a transition surface 22 in the middle, and an inclined surface 21 is provided on both sides of the transition surface 22.

[0050] The inclined surface 21 is the main bearing area of ​​the bearing surface 20, which can guide the lubricating oil to form an effective lubricating oil film during both forward and reverse rotation of the planetary gear 100. The transition surface 22 serves as the connecting part between the inclined surfaces 21. Its specific form can be a plane, an inclined surface, or an arc surface, etc., with the purpose of making the connection between the inclined surfaces 21 smooth and avoiding abrupt transitions. The transition surface 22 can be a single surface or composed of multiple surfaces, which is not limited here.

[0051] In this embodiment, a transition surface 22 is disposed in the middle of the thrust bearing 2, and an inclined surface 21 is provided on each side of the transition surface 22. The two inclined surfaces 21 extend from the transition surface 22 towards both ends of the thrust bearing 2 in the circumferential direction. Furthermore, from the highest point in the middle of the thrust bearing 2 towards both ends, the height of the two inclined surfaces 21 gradually increases, gradually decreases, or one inclined surface 21 gradually increases while the other gradually decreases. This variation in the height of the inclined surfaces 21 allows lubricating oil to be guided into the inclined surfaces 21 and form an oil film on the bearing surface 20 during the operation of the thrust bearing.

[0052] The constraint structure 3 is used to reliably and detachably connect each thrust bearing 2 to the support frame 1. Specifically, the constraint structure 3 includes a pressure plate 31 and a first fastener 32. Each thrust bearing 2 has a stepped surface 23 at both ends along the circumference, the height of which is lower than its bearing surface 20. During assembly, a pressure plate 31 is placed between two adjacent thrust bearings 2, pressing against the stepped surfaces 23 of both adjacent thrust bearings 2. The first fastener 32 passes through the pressure plate 31 and is fixed to the support frame 1, thereby connecting the pressure plate 31 to the support frame 1. By fixing the thrust bearings 2 through the cooperation of the pressure plate 31 and the stepped surfaces 23, the bearing surface 20 of the thrust bearing 2, especially its inclined surface 21, is free of any bolt holes or other connecting structures, thereby increasing the effective working area of ​​the thrust bearing 2 and improving the bearing capacity and service life of the bearing.

[0053] In this embodiment, the first fastener 32 is a bolt, and the following description will also use a bolt as the first fastener 32. In other embodiments, the first fastener 32 may also be a pin, a clip, etc., which will not be elaborated here.

[0054] The number of pressure plates 31 is the same as the number of thrust bearings 2. The specific shape of the pressure plates 31 can be rectangular, triangular, or other irregular shapes, and is not limited here.

[0055] Considering that the first fastener 32 may loosen due to a decrease in preload caused by vibration or thermal cycling during long-term operation of the thrust bearing, and to ensure the safety of the system under extreme conditions, the horizontal cross-sectional shape of the pressure plate 31 is preferably trapezoidal. Specifically, the pressure plate 31 is constructed as a trapezoidal structure with gradually increasing width from the outside to the inside along the radial direction of the supporting frame 1. Correspondingly, wedge-shaped gaps with gradually decreasing width from the outside to the inside are also formed on the step surfaces 23 of two adjacent thrust bearings 2, which are adapted to the pressure plate 31, and the pressure plate 31 can be fitted into the wedge-shaped gaps.

[0056] The interlocking of the pressure plate 31 with the wedge-shaped gap creates an effective radial constraint. Even if the first fastener 32 loosens or fails completely, the pressure plate 31 will not easily detach radially due to the geometric interlock between it and the wedge-shaped gap. This prevents a chain reaction that could lead to the detachment of multiple thrust pads 2 and the failure of the overall bearing ring due to the detachment of a single pressure plate 31. In summary, through this wedge-shaped limiting effect, combined with the locking force of the first fastener 32 and the friction between the pressure plate 31 and the stepped surface 23, the movement of the thrust pads 2 relative to the support frame 1 in the axial and radial directions is effectively restricted, ensuring the stability of the pressure plate 31 connection.

[0057] Furthermore, the constraint structure 3 also includes a shoulder 12 formed on the support frame 1. The shoulder 12 functions to radially limit the thrust bearing 2. Specifically, when the thrust bearing 2 is installed on the support frame 1, the shoulder 12 can prevent the thrust bearing 2 from moving unnecessarily in the radial direction, further ensuring the stability of the thrust bearing 2 installation, so that the thrust bearing 2 can always remain in the correct position during the operation of the thrust bearing and reliably withstand the axial force.

[0058] Regarding the number of thrust bearing pads (2), a minimum of three thrust bearing pads (2) are required on a single thrust bearing. In practical applications, the number of thrust bearing pads (2) can be flexibly determined based on factors such as the specific operating requirements of the gearbox, its load-bearing capacity, and space constraints. No further specific limit is imposed here. For example, for some small gearboxes, due to their relatively small load and limited space, a smaller number, such as three or four thrust bearing pads (2), may suffice to meet the operating requirements. Conversely, for large, heavy-duty gearboxes, to better distribute axial forces and improve load-bearing capacity, the number of thrust bearing pads (2) may be increased, such as to six or eight. By rationally selecting the number of thrust bearing pads (2), the thrust bearing can achieve optimal performance under various operating conditions.

[0059] Regarding the lubrication method for the bearing surface 20, this embodiment provides two optional implementation methods:

[0060] See Figure 1In one embodiment, the support frame 1 has only threaded holes 13 for connecting the first fastener 32, and the first fastener 32 is solid. The upper surface of the pressure plate 31 is designed to be lower in the axial direction than the height of the bearing surface 20. This height difference allows each pressure plate 31 to naturally enclose the inclined surfaces 21 of its two adjacent thrust bearings 2 to form a first oil collection groove 25. At the same time, the two inclined surfaces 21 are configured to extend obliquely downward from the transition surface 22 in the middle of the thrust bearing 2 to both ends. The lubricating oil flowing out from both ends of the radial sliding bearing 300 during operation can be effectively collected and flow into the first oil collection groove 25. When the planetary gear 100 rotates, the axial end face of the planetary gear 100 will drive the lubricating oil in the first oil collection groove 25 into the inclined surface 21 area of ​​the thrust bearing 2, thereby forming an oil film on the inclined surface 21.

[0061] Specifically, see Figure 2 Semi-circular mounting holes 231 are respectively opened on the stepped surfaces 23 of two adjacent thrust bearings 2. When the two adjacent stepped surfaces 23 are joined together, a complete circular mounting hole 231 can be formed. At the same time, the pressure plate 31 is trapezoidal in shape, which matches the shape of the working surface of the thrust bearing 2, and a corresponding connecting hole 311 is opened on the pressure plate 31. The first fastener 32 can pass through the connecting hole 311 on the pressure plate 31 and the mounting hole 231 formed by the joining of adjacent stepped surfaces 23 in sequence, and finally be threadedly connected to the threaded hole 13 on the support frame 1.

[0062] Further, see Figures 3 to 5 In another embodiment, the support frame 1 has an oil passage 11. Simultaneously, the first fastener 32 has a first connecting channel 321 inside, making the bolt a hollow bolt. In the assembled state, one end of the first connecting channel 321 communicates with the oil passage 11 on the support frame 1, and the other end leads to the first oil collection groove 25. Lubricating oil enters from the oil passage 11 of the support frame 1, flows through the first connecting channel 321 inside the first fastener 32, and is directly delivered to the first oil collection groove 25. Therefore, when the planetary gear 100 rotates, the axial end face of the planetary gear 100 will drive the lubricating oil in the first oil collection groove 25 into the inclined surface 21 region of the thrust bearing 2, thereby forming an oil film on the inclined surface 21.

[0063] Regarding the choice of materials, the materials of the pressure plate 31 and the thrust bearing 2 can be the same or different. In a preferred embodiment, the thrust bearing 2 is made of a relatively soft material to facilitate the formation of an oil film and to provide a certain degree of embedding; while the pressure plate 31 is made of a relatively hard material, so that it can withstand a greater preload force of the first fastener 32, thereby ensuring the stability of the connection between the components and preventing loosening, and effectively preventing the loss of preload force due to vibration or temperature changes.

[0064] See Figure 6 and Figure 7 For the geometric parameters of the bearing surface 20, the wrap angles of the two inclined planes 21 can be denoted as... and And the corner of the intermediate transition surface 22 can be denoted as The angles between each inclined plane 21 and the transition surface 22 can be designed to be equal or unequal according to actual working conditions. Similarly, the angle between each inclined plane 21 and the transition surface 22 can be denoted as... and The values ​​can also be designed to be equal or unequal, allowing the thrust bearing to be adaptively optimized for different lubrication conditions and load distributions to achieve the best operating performance.

[0065] Example 2

[0066] Figures 8 to 12 Embodiment 2 is shown, wherein components that are the same as or corresponding to those in Embodiment 1 are referred to using the same reference numerals as those in Embodiment 1. For simplicity, only the differences between Embodiment 2 and Embodiment 1 are described. The difference is that the constraint structure 3 includes a second fastener 33. A fixing hole 27 is provided on the intermediate transition surface 22 of the thrust bearing 2 for the second fastener 33 to pass through. The second fastener 33 passes through the fixing hole 27 and is directly fixed to the support frame 1, thereby fixing the thrust bearing 2 to the support frame 1.

[0067] The direct fixing method using the second fastener 33 eliminates the need for the pressure plate 31 structure in Embodiment 1, making assembly more direct and convenient. Simultaneously, the second fastener 33 fixes the thrust bearing 2 via the transition surface 22, ensuring that no bolt holes or other connecting structures are provided on the inclined surface 21, which plays a major supporting role on the bearing surface 20. This increases the effective working area of ​​the thrust bearing 2, improving the bearing capacity and service life.

[0068] In this embodiment, the second fastener 33 is a bolt, which is used in conjunction with a washer to achieve the fastening effect. The following description will use a bolt as the second fastener 33 as an example. In other embodiments, the second fastener 33 can also be a pin, a snap-fit, etc., which will not be elaborated here.

[0069] Regarding the lubrication method for the bearing surface 20, this embodiment also provides two optional implementation methods:

[0070] See Figure 8In one embodiment, two inclined surfaces 21 are configured to extend downwards from the middle of the thrust bearing 2 towards both ends. In this configuration, the inclined surfaces 21 of adjacent thrust bearings 2 naturally enclose a V-shaped second oil collection groove 26 with the mounting surface of the support frame 1. The second oil collection groove 26 can be used to collect lubricating oil flowing from inside the gearbox, for example, from both ends of the radial sliding bearing 300. When the planetary gear 100 rotates, the lubricating oil is carried from the second oil collection groove 26 into the wedge-shaped gap of the inclined surfaces 21, thereby forming an effective lubricating oil film.

[0071] See Figure 9 and Figure 10 In another embodiment, lubrication employs a central oil supply method. Specifically, an oil passage 11 is provided on the support frame 1. Simultaneously, a second connecting channel 331 is provided inside the second fastener 33, forming a hollow bolt. After assembly, the second connecting channel 331 connects the bearing surface 20 of the thrust bearing 2 with the oil passage 11 on the support frame 1. Lubricating oil can be directly delivered from the frame's oil passage, through the second connecting channel 331 inside the second fastener 33, and sprayed onto the bearing surface 20 for lubrication.

[0072] In this embodiment, in order to better coordinate with the central oil supply and guide the formation of the oil film, the two inclined surfaces 21 of the bearing surface 20 are designed to extend upward from the middle of the thrust bearing 2 to both ends, so that when the planetary gear 100 rotates, the surface of the bearing surface 20 can generate a converging wedge shape, and work together with the lubricating oil from the middle of the bearing surface 20 to form a stable oil film on the bearing surface 20.

[0073] Furthermore, in addition to the intermediate transition surface 22 and the inclined surfaces 21 located on both sides thereon, the bearing surface 20 also has two connecting surfaces 24 extending outward from the outer sides of the two inclined surfaces 21. Thus, when multiple thrust bearings 2 are circumferentially assembled on the support frame 1, a smooth transition can be achieved between the bearing surfaces 20 of adjacent thrust bearings 2, avoiding the formation of sharp steps or corners at the connection. This smooth transition facilitates the continuous delivery of lubricating oil, prevents poor flow from affecting the formation of the oil film, and also reduces abnormal wear on the axial end face of the planetary gear 100 or the thrust bearings 2 themselves caused by localized stress concentration.

[0074] See Figure 11 and Figure 12 For the geometric parameters of the bearing surface 20, the wrap angles of the two inclined planes 21 can be denoted as... and And the corner of the intermediate transition surface 22 can be denoted as The enclosing angle of the two connecting surfaces 24 can be denoted as... and The angles can be designed to be equal or unequal according to actual working conditions. Similarly, the angle between the inclined plane 21 and the transition surface 22 can be denoted as... and And, the angle between the inclined plane 21 and the connecting surface 24 can be denoted as... and The values ​​can also be designed to be equal or unequal, allowing the thrust bearing to be adaptively optimized for different lubrication conditions and load distributions to achieve the best operating performance.

[0075] Since there is no pressure plate 31 structure in this embodiment, two adjacent thrust pads 2 are arranged directly adjacent to each other on their sides. During equipment operation, the thrust pads 2 will undergo thermal expansion due to friction and changes in operating temperature, which may cause slight changes in their dimensions. If adjacent thrust pads 2 are tightly fitted without gaps during assembly, huge internal stress may be generated between the thrust pads 2 due to mutual compression during thermal expansion, leading to deformation, warping, or even damage of the pads. Therefore, a certain circumferential gap needs to be reserved between two adjacent thrust pads 2. However, the size of the circumferential gap needs to be carefully controlled. If the gap is too large, too much lubricating oil will remain in it. This lubricating oil may not be effectively carried into the main load-bearing area, which may weaken the amount of oil entering the inclined surface 21 to form an effective oil film, affecting the overall lubrication efficiency. Therefore, the specific dimensions of the circumferential gap need to be adaptively selected and optimized based on actual working conditions such as the material of the thrust bearing 2, the expected operating temperature range, and the characteristics of the lubricating oil. No uniform limit is set here to ensure that it provides thermal expansion margin without having a significant negative impact on lubrication performance.

[0076] It should be noted that the fixing method and lubrication extraction method of the thrust bearing 2 can be combined in various ways, and all such combinations fall within the protection scope of this invention. For example, all thrust bearings 2 can be fastened with pressure plates and lubricated using the method described in Embodiment 1; all thrust bearings 2 can be directly fastened with fasteners and lubricated using the method described in Embodiment 2; or a combination of the solutions described in Embodiment 1 and Embodiment 2 can be used, for example, using the pressure plate fastening method of Embodiment 1, but using the central oil supply method of Embodiment 2 for lubrication extraction. Furthermore, in the same thrust bearing, some thrust bearings 2 can use the fixing and lubrication extraction method in Embodiment 1, while other thrust bearings 2 can use the method in Embodiment 2. The specific combination method can be selected according to the actual working conditions and design requirements, and is not specifically limited here.

[0077] Example 3

[0078] See Figure 13The present invention also provides a planetary transmission mechanism, which includes a planetary gear 100, a pin 200, a radial sliding bearing 300, a planet carrier 400, and a thrust bearing as in Embodiment 1 or Embodiment 2.

[0079] The pin 200 is fixedly mounted on the planet carrier 400. The planet gear 100 is rotatably mounted on the pin 200 via its internal radial sliding bearing 300. The thrust bearing is located between the axial end face of the planet gear 100 and the planet carrier 400 to bear the axial load generated when the planet gear 100 is in operation.

[0080] In this embodiment, the connection between the thrust bearing support frame 1 and the planetary carrier 400 can be implemented in several ways. In one implementation, the support frame 1 can be an independent annular component, which is fixedly mounted on the planetary carrier 400 by means of fastener connection or interference fit.

[0081] In another embodiment, the support frame 1 can be integrally machined with the planetary carrier 400, that is, the mating surfaces and structures for mounting the thrust bearing 2, pressure plate 31, and related oil passages are directly machined onto the planetary carrier 400. In this integrated design, the corresponding part of the planetary carrier 400 constitutes the support frame 1 of the present invention, thereby enhancing the overall structural rigidity and simplifying the assembly process.

[0082] The working principle of the planetary transmission mechanism is as follows: Power drives the planetary gear 100 to rotate around the pin shaft 200. The radial load is mainly borne by the radial sliding bearing 300, while the axial load is transmitted to the bearing surface 20 of the thrust bearing through the axial end face of the planetary gear 100. Lubricating oil is supplied to the bearing surface 20 of the thrust bearing through the lubrication method of any of the aforementioned embodiments, and a stable hydrodynamic oil film is formed on the two inclined surfaces 21 to achieve efficient lubrication. The segmented design of the thrust bearing makes maintenance more convenient, while its robust constraint structure ensures the operational reliability of the entire planetary transmission mechanism under high-speed and heavy-load conditions.

[0083] Example 4

[0084] This invention also provides a gearbox equipped with the thrust bearing provided in Embodiment 1 or Embodiment 2, or the planetary transmission mechanism provided in Embodiment 3. During actual operation, the gearbox generates axial force. The configured thrust bearing effectively withstands this axial force, ensuring the stable operation of components such as the planetary gears 100 in the axial direction, thereby maintaining the normal operation of the entire gearbox transmission system. In this embodiment, the maintenance and replacement costs are significantly reduced when the thrust bearing 2 wears or fails. Because only a single damaged thrust bearing 2 needs to be disassembled and replaced, instead of replacing the entire thrust bearing 2 assembly, maintenance efficiency is improved, maintenance costs are reduced, and the reliability and stability of the gearbox are enhanced, extending its service life and improving overall performance.

[0085] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the implementation of the present invention. Those skilled in the art can make other variations or modifications based on the above description. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the claims of the present invention.

Claims

1. A thrust bearing, comprising: a support turntable (1); a plurality of thrust pads (2) arranged on the support turntable (1) in a circumferential direction of the support turntable (1), the thrust pads (2) being formed with a load bearing surface (20) including at least two inclined surfaces (21) and a transition surface (22) between two adjacent inclined surfaces (21), and lubricating oil being capable of forming an oil film on the load bearing surface (20); a constraint structure (3) for detachably connecting the thrust pads (2) to the support turntable (1).

2. The thrust bearing of claim 1, wherein, The transition surface (22) is located in a middle portion of the load bearing surface (20), and each of the two inclined surfaces (21) is located on a side of the transition surface (22) and extends from the transition surface (22) to both ends of the thrust pad (2), and the height of the two inclined surfaces (21) changes in a direction from a middle portion of the thrust pad (2) to both ends.

3. The thrust bearing of claim 2, wherein, The constraint structure (3) includes a pressing plate (31) and a first fastener (32); both ends of the thrust pad (2) are formed with a stepped surface (23) lower than the load bearing surface (20); the pressing plate (31) is arranged between two adjacent thrust pads (2) and is pressed onto two adjacent stepped surfaces (23); and the first fastener (32) fixes the pressing plate (31) to the support turntable (1). The constraint structure (3) further includes a second fastener (33) passing through the transition surface (22) to fix the thrust pad (2) to the support turntable (1).

4. The thrust bearing of claim 3, wherein, The height of an upper surface of the pressing plate (31) is lower than the height of the load bearing surface (20), and a first oil collecting groove (25) is formed between the pressing plate (31) and the inclined surfaces (21) of two adjacent thrust pads (2), and the two inclined surfaces (21) respectively extend downward in a direction from a middle portion of the thrust pad (2) to both ends.

5. The thrust bearing of claim 4, wherein, An oil passage (11) is formed in the support turntable (1), and a first connecting passage (321) is formed in the first fastener (32) to connect the first oil collecting groove (25) and the oil passage (11).

6. The thrust bearing of claim 3, wherein, The two inclined surfaces (21) respectively extend downward in a direction from a middle portion of the thrust pad (2) to both ends, and the inclined surfaces (21) of two adjacent thrust pads (2) and the support turntable (1) form a second oil collecting groove (26).

7. The thrust bearing of claim 3, wherein, An oil passage (11) is formed in the support turntable (1), and a second connecting passage (331) is formed in the second fastener (33) to connect the load bearing surface (20) and the oil passage (11); and the two inclined surfaces (21) respectively extend upward in a direction from a middle portion of the thrust pad (2) to both ends.

8. Thrust bearing according to any of claims 1-7, characterized in that A shoulder (12) is formed on the support turntable (1) and arranged around an outer periphery of the thrust pad (2) to limit the thrust pad (2) in a radial direction.

9. A planetary transmission mechanism, characterized by, The thrust bearing according to any one of claims 1 to 8, further comprising a planet wheel (100), a pin shaft (200) arranged on a planet carrier (400), and a radial sliding bearing (300) arranged between the planet wheel (100) and the pin shaft (200), the thrust bearing being arranged between the planet wheel (100) and the planet carrier (400).

10. A gear box characterized in that, The planetary transmission according to claim 9, wherein the thrust bearing according to any one of claims 1 to 8 is provided, or the planetary transmission comprises the thrust bearing according to claim 9.

Images