Planetary gearbox low speed end structure

Abstract

A kind of planetary gearbox low-speed end structure, it is related to gear box field, it includes shell, output gear shaft, radial support unit and two axial support units;Shell is provided with assembly through-hole, output gear shaft is arranged in assembly through-hole and can be rotatably matched with shell, and annular assembly space is formed between output gear shaft and the hole wall of assembly through-hole;Output gear shaft and shell are connected by radial support unit and two axial support units, radial support unit is located between two axial support units, and the radial support roller of radial support unit can roll around first axis, and the axial support roller of axial support unit can roll around second axis. First axis is located in the region surrounded by multiple axial support rollers of the same axial support unit. Product structure is simple, and parts are few, which can not only meet the demand of carrying capacity, but also reduce weight and volume.

Description

Technical Field

[0001] This utility model relates to the field of gearboxes, and more specifically, to a low-speed end structure of a planetary gearbox. Background Technology Common planetary gearbox output terminals are used in wind turbine yaw systems, pitch reducers, and slewing reducers for construction machinery. The gearbox output structure typically includes a housing, output gear shaft, tapered roller bearings, a round nut, seals, and necessary accessories such as cover plates and locking washers for the round nut. Two tapered roller bearings on the output gear shaft are located on the same side of the gear. When the gear is under load, the shaft inevitably experiences overturning moments. Tapered roller bearings are characterized by their ability to withstand both radial and a certain amount of axial load, thus ensuring shaft stability. The selection of bearing type and the arrangement of bearing spacing are related to the load. To meet the need for greater load capacity, the output terminal structure usually requires more space, thus increasing the product weight.

[0002] The inventors discovered during their research that the existing planetary gearbox low-speed end structure has at least the following drawbacks: It is impossible to simultaneously achieve high load-bearing capacity, small product size, and light product weight. Utility Model Content

[0003] The purpose of this utility model includes, for example, providing a low-speed end structure for a planetary gearbox that simplifies the product structure, reduces the product size, and lightens the product weight while meeting the requirements of high load-bearing capacity.

[0004] The embodiments of this utility model can be implemented as follows: In a first aspect, this utility model provides a low-speed end structure for a planetary gearbox, comprising: The housing comprises a housing, an output gear shaft, a radial support unit, and two axial support units; the housing is provided with an assembly through hole, the output gear shaft passes through the assembly through hole and is rotatably engaged with the housing, and an annular assembly space is formed between the output gear shaft and the wall of the assembly through hole; The radial support unit includes a plurality of radial support rollers, all of which are located within the annular assembly space and arranged circumferentially on the output gear shaft. Each radial support roller simultaneously makes rolling contact with the output gear shaft and the housing about its own first axis, which extends in the same direction as the axis of the assembly through hole. The axial support unit includes multiple axial support rollers, all of which are located within the annular assembly space and arranged circumferentially on the output gear shaft. Each axial support roller simultaneously makes rolling contact with both the output gear shaft and the housing around its own second axis. The radial support unit is located between the two axial support units. The first axis is perpendicular to the second axis, and the first axis is located within the area enclosed by the plurality of axial support rollers of the same axial support unit.

[0005] In an optional embodiment, the output gear shaft includes a shaft body, a first bearing housing, and a second bearing housing, both of which are sleeved and fixed to the shaft body; one of the two axial support units is clamped between the first bearing housing and the housing, and the other of the two axial support units is clamped between the second bearing housing and the housing.

[0006] In an optional embodiment, all the radial support rollers are located between the first bearing housing and the second bearing housing, and both ends of each radial support roller in the axial direction are in contact with the first bearing housing and the second bearing housing, respectively.

[0007] In an optional embodiment, the shaft body is provided with a shoulder, which is located outside the housing; the first bearing seat is clamped between the radial support roller and the shoulder, and the second bearing seat is screwed to the shaft body.

[0008] In an optional embodiment, the output gear shaft further includes a lock nut; The shaft body is provided with a shoulder, which is located outside the housing; the first bearing seat is clamped between the radial support roller and the shoulder, and the second bearing seat is sleeved on the shaft body; the locking nut is screwed and fixed outside the shaft body and contacts the side of the second bearing seat away from the first bearing seat.

[0009] In an optional embodiment, the low-speed end structure of the planetary gearbox further includes an oil seal, which is installed between the locking nut and the wall of the mounting through hole, or the oil seal is installed between the second bearing housing and the wall of the mounting through hole.

[0010] In an optional embodiment, the low-speed end structure of the planetary gearbox further includes a support ring, which is simultaneously sleeved and fixed to the shaft body and the locking nut; The low-speed end structure of the planetary gearbox also includes an oil seal, which is installed between the outer peripheral surface of the support ring and the wall of the assembly through hole.

[0011] In an optional embodiment, both the first bearing housing and the second bearing housing have inner and outer annular surfaces that are arranged opposite to each other in their own axial direction, with the inner annular surfaces of the first bearing housing and the second bearing housing facing each other; a limiting ring is protruding from each of the inner annular surfaces, the limiting ring contacting the axial end face of the radial support roller, and the limiting ring being located on the side of the radial support roller closer to the shaft body on the central axis of the radial support roller.

[0012] In an optional embodiment, there are multiple radial support units, which are arranged axially on the output gear shaft.

[0013] In an optional embodiment, the low-speed end structure of the planetary gearbox further includes a spacer ring, which is sleeved on the outside of the output gear shaft. The spacer ring is located between adjacent radial support units, and the end face of each radial support roller is in contact with the spacer ring.

[0014] In an optional embodiment, the low-speed end structure of the planetary gearbox further includes an oil nozzle mounted on the housing, the oil nozzle being used to deliver lubricating medium between adjacent radial support units.

[0015] The beneficial effects of this utility model embodiment include, for example: In summary, the low-speed end structure of the planetary gearbox provided in this embodiment provides radial support through a radial support unit and axial support through two axial support units located at both ends of the radial support unit when the output gear shaft rotates. This results in good support performance, strong load-bearing capacity of the output gear shaft, and high operational stability. Simultaneously, the radial support unit includes multiple radial support rollers, each of which rolls in contact with both the output gear shaft and the housing, relying on the output gear shaft and housing for positioning. This eliminates the need for inner and outer rings, simplifying the structure and reducing the radial dimension. Similarly, the axial support unit includes multiple axial support rollers, each of which rolls in contact with both the output gear shaft and the housing, relying on the output gear shaft and housing for positioning. This also eliminates the need for inner and outer rings, simplifying the structure and reducing the axial dimension. As a result, both the radial and axial dimensions of the output end assembly are reduced, satisfying the requirements for high torque transmission while also reducing the overall size, product weight, and manufacturing costs. Attached Figure Description

[0016] To more clearly illustrate the technical solutions of the embodiments of this utility model, the drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this utility model and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of the low-speed end structure of the planetary gearbox in this embodiment; Figure 2 This is a schematic diagram of a first modified example of the low-speed end structure of the planetary gearbox in this embodiment; Figure 2a This is a schematic diagram of the gear shaft, the first positioning support column, and the second positioning support column from an axial perspective in this embodiment. Figure 2b This is a schematic diagram of a second variation of the low-speed end structure of the planetary gearbox in this embodiment; Figure 2c This is a schematic diagram of a third variation of the low-speed end structure of the planetary gearbox in this embodiment; Figure 3 This is a schematic diagram of the fourth variation of the low-speed end structure of the planetary gearbox in this embodiment; Figure 4 This is a schematic diagram of the fifth variation of the low-speed end structure of the planetary gearbox in this embodiment; Figure 5 This is a schematic diagram of the force analysis of the low-speed end structure of the planetary gearbox in this embodiment; Figure 6 This is a schematic diagram of the stress analysis of the low-speed end structure in the prior art.

[0018] icon: 001-First axis; 002-Second axis; 003-Third axis; 100-Housing; 101-Assembly through hole; 110-Annular positioning boss; 200-Output gear shaft; 210-Shaft body; 211-First shoulder; 212-Second shoulder; 213-Hollow area; 220-First bearing housing; 221-Limiting ring; 230-Second bearing housing; 240-Locking nut; 300-Radial support unit; 310-Radial support roller Column; 400-First axial support unit; 410-First axial support roller; 411-Outer end face; 412-Inner end face; 413-Intersection line; 414-First circumference; 415-Second circumference; 500-Second axial support unit; 510-Second axial support roller; 600-First oil seal; 700-Second oil seal; 800-Support ring; 900-Screw plug; 1000-Oil nozzle; 2000-Magnetic screw plug; 3000-Spacer ring. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. The components of the embodiments of this utility model described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0020] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0021] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0022] In the description of this utility model, it should be noted that if terms such as "upper," "lower," "inner," or "outer" are used to indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship in which the utility model product is usually placed during use, they are only for the convenience of describing this utility model 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 utility model.

[0023] Furthermore, the terms "first" and "second" are used only to distinguish descriptions and should not be interpreted as indicating or implying relative importance.

[0024] It should be noted that, where there is no conflict, the features in the embodiments of this utility model can be combined with each other.

[0025] In existing technologies, the output gear shaft 200 of a planetary output structure is generally supported by two tapered roller bearings. The two tapered roller bearings work together to withstand certain axial and radial loads, ensuring the smooth rotation of the output gear shaft 200. However, due to the large size of tapered roller bearings, the product structure is large, heavy, and has high processing costs.

[0026] In view of this, the designers have provided a low-speed end structure for a planetary gearbox that can meet the torque output requirements, reduce product size and weight, and lower manufacturing costs.

[0027] Please refer to Figures 1-4This embodiment provides a low-speed end structure for a planetary gearbox, including: The housing 100, the output gear shaft 200, the radial support unit 300 and two axial support units are provided; the housing 100 is provided with an assembly through hole 101, the output gear shaft 200 passes through the assembly through hole 101 and is rotatably engaged with the housing 100, and an annular assembly space is formed between the output gear shaft 200 and the hole wall of the assembly through hole 101. The radial support unit 300 includes a plurality of radial support rollers 310, all of which are located in the annular assembly space and arranged in the circumferential direction of the output gear shaft 200. Each radial support roller 310 simultaneously rolls in contact with the output gear shaft 200 and the housing 100 about its own first axis 001, which is consistent with the extension direction of the axis of the assembly through hole 101. The axial support unit includes multiple axial support rollers, which are all located in the annular assembly space and arranged circumferentially on the output gear shaft 200. Each axial support roller simultaneously makes rolling contact with the output gear shaft 200 and the housing 100 around its own second axis 002. The radial support unit 300 is located between the two axial support units. The first axis 001 is perpendicular to the second axis 002, and the first axis 001 is located within the area enclosed by multiple axial support rollers of the same axial support unit.

[0028] As described above, the low-speed end structure of the planetary gearbox provided in this embodiment has at least the following advantages: When the output gear shaft 200 rotates, radial support is provided by the radial support unit 300, and axial support is provided by two axial support units located at both ends of the radial support unit 300. This provides excellent support, resulting in a high load-bearing capacity and high operational stability for the output gear shaft 200. Simultaneously, the radial support unit 300 includes multiple radial support rollers 310, each of which rolls in contact with both the output gear shaft 200 and the housing 100, relying on these components for positioning. This eliminates the need for inner and outer rings, simplifying the structure and reducing the radial dimension. Similarly, the axial support unit includes multiple axial support rollers, each of which rolls in contact with both the output gear shaft 200 and the housing 100, relying on these components for positioning. This eliminates the need for inner and outer rings, simplifying the structure and reducing the axial dimension. As a result, both the radial and axial dimensions of the output assembly are reduced, allowing for high torque transmission while also reducing overall size, product weight, and manufacturing costs.

[0029] The following embodiments illustrate the details of the low-speed end structure of the planetary gearbox of this application by way of example.

[0030] Please refer to Figures 1-4In this embodiment, optionally, the low-speed end structure of the planetary gearbox includes a housing 100, an output gear shaft 200, a radial support unit 300, a first axial support unit 400, a second axial support unit 500, a first oil seal 600, a second oil seal 700, a support ring 800, a screw plug 900, an oil nozzle 1000, and a magnetic screw plug 2000.

[0031] The output gear shaft 200 is rotatably mounted in the housing 100, with its output end extending out of the housing 100. A radial support unit 300, a first axial support unit 400, and a second axial support unit 500 are simultaneously connected to the output gear shaft 200 and the housing 100. The first axial support unit 400 is located on the side of the second axial support unit 500 furthest from the output end. The radial support unit 300 provides radial support to the output gear shaft 200, and the first axial support unit 400 and the second axial support unit 500 cooperate to provide axial support to the output gear shaft 200. A support ring 800 is sleeved on the outside of the output gear shaft 200, located on the side of the first axial support unit 400 furthest from the second axial support unit 500. A first oil seal 600 is disposed between the outer circumferential surface of the support ring 800 and the housing 100. A second oil seal 700 is disposed between the output gear shaft 200 and the housing 100, and is located outside the housing 100. Both the screw plug 900 and the grease nipple 1000 are installed in the housing 100. When the screw plug 900 is opened, lubricating medium can be introduced into the housing 100. The grease nipple 1000 can inject lubricating medium into the area between the first oil seal 600 and the second oil seal 700. The magnetic screw plug 2000 is installed on the output gear shaft 200. When opened, it can discharge lubricating medium from the housing 100 and also adsorb metal powder carried in the lubricating medium, thereby reducing the adverse effects of metal powder on internal components.

[0032] Optionally, the housing 100 has an assembly through hole 101 inside, and a ring-shaped positioning platform protrudes inward on a portion of the hole wall of the assembly through hole 101. The area enclosed by the ring-shaped positioning platform is connected to and coaxial with the assembly through hole 101.

[0033] Please refer to Figure 1 Optionally, the output gear shaft 200 includes a shaft body 210, a first bearing housing 220, a second bearing housing 230, and a locking nut 240. The first bearing housing 220, the second bearing housing 230, and the locking nut 240 are all mounted on the shaft body 210.

[0034] Optionally, the outer peripheral surface of the shaft body 210 is provided with a first shoulder 211 and a second shoulder 212, with the first shoulder 211 located on the side of the second shoulder 212 away from the output end. The shaft body 210 has two hollow regions 213 spaced apart along its axial direction inside, which are not connected. A magnetic plug 2000 is installed on the isolation structure formed between the two hollow regions 213. By providing the hollow regions 213, the weight of the shaft body 210 can be reduced. The inner hollow region 213 can communicate with the internal space of the housing 100. After opening the magnetic plug 2000, the lubricating medium inside the housing 100 can be discharged from the outer middle shell region.

[0035] Please refer to Figure 1 Optionally, both the first bearing housing 220 and the second bearing housing 230 have inner and outer annular surfaces that are opposite to each other in their own axial direction. Both the first bearing housing 220 and the second bearing housing 230 are sleeved on the outside of the shaft body 210. The axes of the first bearing housing 220 and the second bearing housing 230 are collinear and coaxial with the shaft body 210. The first bearing housing 220 is located on the side of the second bearing housing 230 closer to the output end, and the first bearing housing 220 contacts the second shaft shoulder 212. The inner annular surfaces of the first bearing housing 220 and the second bearing housing 230 are opposite to each other, that is, the two inner annular surfaces are located between the two outer annular surfaces. A limiting ring 221 is protruded from each inner annular surface, and the limiting ring 221 of the first bearing housing 220 and the limiting ring 221 of the second bearing housing 230 are coaxially arranged.

[0036] Optionally, the locking nut 240 is screwed and fixed to the outside of the shaft body 210, and the locking nut 240 contacts the side of the second bearing seat 230 away from the first bearing seat 220.

[0037] During assembly, the shaft body 210 passes through the area enclosed by the annular positioning boss 110 and within the assembly through hole 101, forming an annular assembly space with the shaft body 210, the annular positioning boss 110, and the wall of the assembly through hole 101. A radial support unit 300 is located between the annular positioning boss 110 and the shaft body 210; a first axial support unit 400 is located between the second bearing seat 230 and the annular positioning boss 110; and a second axial support unit 500 is located between the second bearing seat 230 and the annular positioning boss 110. Simultaneously, the radial support unit 300 is located between the limiting ring 221 of the first bearing seat 220 and the limiting ring 221 of the second bearing seat 230. The axial position of the radial support unit 300 is limited by the locking nut 240, the first bearing seat 220, the second bearing seat 230, and the second shaft shoulder 212; the radial position of the radial support unit 300 is limited by the annular positioning boss 110 and the shaft body 210. The radial position of the first axial support unit 400 is limited by the wall of the mounting through hole 101 and the first shaft seat, and the axial position of the first axial support unit 400 is limited by the second bearing seat 230 and the annular positioning boss 110. The radial position of the second axial support unit 500 is limited by the wall of the mounting through hole 101 and the second shaft seat, and the axial position of the second axial support unit 500 is limited by the second bearing seat 230 and the annular positioning boss 110. The first oil seal 600 is installed between the support ring 800 and the wall of the mounting through hole 101, and the first oil seal 600 is located on the side of the second bearing seat 230 away from the first bearing seat 220. The second oil seal 700 is installed on the housing 100 and contacts the second bearing seat 230.

[0038] In this embodiment, optionally, the radial support unit 300 includes a plurality of radial support rollers 310. These radial support rollers 310 are all located within the annular assembly space and arranged circumferentially on the shaft body 210. The outer circumferential surface of each radial support roller 310 simultaneously rolls in contact with both the shaft body 210 and the annular positioning boss 110 around its own first axis 001. The first axis 001 extends in the same direction as the axis of the assembly through hole 101. Simultaneously, the two end faces of the radial support roller 310 in the axial direction respectively contact two limiting rings 221.

[0039] It should be understood that the number of radial support rollers 310 is designed as needed, and no specific limit is made in this embodiment.

[0040] Please refer to Figure 1In this embodiment, optionally, the structures of the first axial support unit 400 and the second axial support unit 500 can be set to be the same. The first axial support unit 400 includes a plurality of first axial support rollers 410, which are all located in the annular assembly space and arranged in the circumferential direction of the shaft body 210. The outer peripheral surface of each first axial support roller 410 simultaneously rolls in contact with the second bearing seat 230 and the hole wall of the assembly through hole 101 around its own second axis 002. The two ends of each first axial support roller 410 in its axial direction respectively contact the second bearing seat 230 and the annular positioning boss 110.

[0041] Similarly, the second axial support unit 500 includes multiple second axial support rollers 510, all located within the annular assembly space and arranged circumferentially on the shaft body 210. The outer circumferential surface of each second axial support roller 510 simultaneously rolls in contact with the second bearing housing 230 and the wall of the assembly through hole 101 around its own third axis 003. The two ends of each second axial support roller 510 respectively contact the second bearing housing 230 and the annular positioning boss 110. The first axis 001 is perpendicular to both the second axis 002 and the third axis 003, which are arranged parallel and spaced apart. The extension of the first axis 001 lies within both the area enclosed by the multiple first axial support rollers 410 and the area enclosed by the multiple second axial support rollers 510. That is, the extension line of the first axis 001 is spaced from the first axial support roller 410 and is located on the side of the first axial support roller 410 close to the shaft body 210. At the same time, the extension line of the first axis 001 is spaced from the second axial support roller 510 and is located on the side of the second axial support roller 510 close to the shaft body 210.

[0042] It should be understood that in some embodiments, the first oil seal 600 can be directly installed between the locking nut 240 and the housing 100 bracket, which can eliminate the need for the support ring 800 and simplify the structure.

[0043] Please combine Figure 4 It should be understood that in some embodiments, the second bearing housing 230 can be directly screwed to the shaft body 210 to achieve axial positioning of the second bearing housing 230. This eliminates the need for the locking nut 240, simplifying the structure and reducing weight. In this embodiment, the first oil seal 600 can also be installed on the second bearing housing 230, thereby eliminating the need for the support ring 800.

[0044] Please combine Figure 4 It should be understood that in some embodiments, the first oil seal 600 can be omitted to simplify the structure and reduce weight.

[0045] Please refer to Figure 4In other embodiments, optionally, there may be multiple radial support units 300, which are arranged axially on the output gear shaft 200. For example, two radial support units 300 are used as an example. The two radial support units 300 are arranged axially on the shaft body 210.

[0046] Meanwhile, the low-speed end structure of the planetary gearbox also includes a spacer ring 3000, which is sleeved on the outside of the shaft body 210. The spacer ring 3000 is located between adjacent radial support units 300, and the end face of each radial support roller 310 is in contact with the spacer ring 3000. Furthermore, there is an annular gap between the spacer ring 3000 and the shaft body 210.

[0047] In this embodiment, the grease nipple 1000 can be disposed on the housing 100 at a position between the first bearing seat 220 and the second bearing seat 230. The grease nipple 1000 passes through the annular positioning boss 110 and can deliver the lubricating medium between the two radial support units 300.

[0048] The planetary reducer output structure provided in this embodiment, through the cooperation of radial support unit 300 and two axial support units, can provide stable radial and axial support for the output gear shaft 200, ensuring that the output gear shaft 200 can stably transmit torque under certain radial and axial loads. Simultaneously, the inner and outer raceways of the radial support rollers 310 of the radial support unit 300 are directly integrated onto the shaft body 210 and the annular positioning boss 110. Similarly, the inner and outer raceways of the axial support rollers of the axial support unit are directly integrated onto the first bearing housing 220, the second bearing housing 230, and the housing 100, eliminating the need for inner and outer raceway structures. This simplifies the overall structure and reduces product size and weight while ensuring safe operation.

[0049] It should be understood that the planetary reducer output assembly provided in this embodiment can be applied to the low-speed end of various types of planetary gearboxes, such as the low-speed end of wind power speed increasers.

[0050] Please combine Figure 2 , Figure 2a as well as Figure 5To ensure better load-bearing capacity of the positioning support columns arranged in this embodiment during operation, taking a cross-sectional view perpendicular to the axis of the output gear shaft 200 as a reference, the radial support column 310 is at least located within the area enclosed by the first circumference 414 defined by the pitch circle diameter of the first axial support roller 410. That is, the radial support column 310 is internally tangent to the first circumference 414, or the radial support column 310 is located within the area enclosed by the first circumference 414 and has a non-zero distance from the first circumference 414. This design also ensures that the housing 100 contacts the first axial support roller 410 at least half its axial position, allowing the housing 100 to stably support the first axial support roller 410 without requiring additional support members. Please refer to... Figures 2a-2c Furthermore, the first axial support roller 410 is configured to have an outer end face 411 and an inner end face 412 in its own axial direction (i.e., in the radial direction of the gear shaft). Both the outer end face 411 and the inner end face 412 are circular surfaces. The inner end face 412 is closer to the gear shaft than the outer end face 411. The first axial support roller 410 is cut by a plane perpendicular to the axis of the gear shaft and passing through the axis of the first axial support roller 410. The intersection of this plane with the inner end face 412 of each first axial support roller 410 forms an intersection line 413. All intersection lines 413 have the same length and are chords of the same second circumference 415. The radial support roller is internally tangent to the second circumference 415. Alternatively, the first axial support roller 410 is located in the area enclosed by the second circumference 415 and has a non-zero distance from the second circumference 415.

[0051] The reason for this design is that, through experiments and theoretical calculations, it was found that when the diameters and parameters of the radial support column 310 and the first axial support roller 410 meet the minimum strength requirements, the smaller the difference in pitch circle diameter between the radial support column 310 and the first axial support roller 410, the worse the load-bearing effect of the roller bearing. As the difference in pitch circle diameter between the radial support column 310 and the first axial support roller 410 increases, the load-bearing effect of the roller bearing improves. Moreover, once the difference in pitch circle diameter between the radial support column 310 and the first axial support roller 410 reaches a certain value, the maximum load that the roller bearing can withstand will be greatly increased. From another perspective, when the diameter and parameters of the radial support column 310 are constant, the effective pitch circle diameter of the first axial support roller 410 can be larger, thereby giving the first axial support roller 410 a higher load-bearing capacity, which contributes to a lighter product design.

[0052] Further specific limitations are as follows: Please combine Figure 5 The force analysis diagram of the low-speed end structure of the planetary gearbox in this embodiment is provided, and the following force and torque balance equations are established, where the force values ​​are absolute values.

[0053]

[0054] ≥ +D1+

[0055] In the formula: This is the equivalent load for the axial support roller D. The equivalent load for the axial support roller E. The equivalent load for the radial support roller 310, For gear load lever arm, The pitch circle diameter of the axially supporting roller. D1 is the diameter of the circle containing the cross-section of the cylindrical surface coaxial with the output gear shaft 200 and passing through the first axis 001; D1 is the diameter of the radial support roller 310. This refers to the length of the axial support roller.

[0056] The formula demonstrates that the structural design of this output assembly is theoretically highly feasible. Using radial roller bearings to bear pure radial loads better leverages the advantages of radial roller bearings. By having the thrust roller bearings bear axial loads in different directions, these loads are converted into torques, balancing the torque generated by the output gears. This allows for a more compact shaft system with higher load-bearing capacity.

[0057] Correspondingly, please refer to Figure 6The figure illustrates the output end structure of a yaw and pitch reducer and the structure of a wind power device based on existing patent CN220082083U. In the figure: 01 represents the housing, 02 represents the output shaft, 1 represents the seventh shoulder, 2 represents the first axial positioning bearing, 3 represents the fifth segment, 4 represents the sixth segment, 5 represents the seventh segment, 6 represents the second axial positioning bearing, 7 represents the first fastener, 8 represents the end cover, 9 represents the eighth shoulder, 10 represents the sealing structure, 11 represents the eighth shaft segment, 12 represents the eighth annular groove, 13 represents the ninth shaft segment, 14 represents the cylindrical roller assembly, and 15 represents the gear. In an optional embodiment, the output shaft is equipped with a gear. The output shaft may include an eighth shaft segment and a ninth shaft segment connected sequentially along the axial direction of the output shaft. The ninth shaft segment can be detachably connected to the gear. The diameter of the ninth shaft segment can be smaller than the diameter of the eighth shaft segment and the gear, so that a seventh shoulder is formed at the connection position of the eighth and ninth shaft segments, and an eighth shoulder is formed at the connection position of the ninth shaft segment and the gear. The eighth and ninth shaft segments form an eighth annular groove. The number of axial positioning bearings can be at least two, including a first axial positioning bearing and a second axial positioning bearing, both of which can be fitted onto the ninth shaft segment. A cylindrical roller assembly can also be rolled into the ninth shaft segment. Retaining rings can be provided between the cylindrical roller assembly and the first axial positioning bearing, and between the cylindrical roller assembly and the second axial positioning bearing. The output shaft 02 is supported by the cylindrical roller assembly, the first axial positioning bearing, and the second axial positioning bearing, and the axis of the cylindrical roller assembly passes through both the first and second axial positioning bearings.

[0058] by Figure 5 For reference, a force analysis diagram of a gearbox from an existing patent is provided, and the following force and torque balance equations are established, where the force values ​​are absolute values:

[0059] d1≈d2 in, This is the equivalent load of the axial positioning bearing D. This is the equivalent load of the axial positioning bearing E. Let C be the equivalent load of the cylindrical roller assembly. For gear load lever arm, This refers to the pitch circle diameter of the axial positioning bearing. D1 is the diameter of the circle containing the cross-section of the cylindrical surface coaxial with the output shaft 200 and passing through the axis of the cylindrical roller assembly; D1 is the diameter of the cylindrical roller assembly. This refers to the length of the axial positioning bearing.

[0060] From the two force analysis models in this embodiment and the existing patent, we can obtain: When the external load Fn is the same, Frc is the same in this embodiment and in the prior art. The radial support roller 310 can be designed to the same specifications to just meet the load-bearing requirements. In this case, the pitch circle diameter d1 of the radial support roller 310 is the same in this embodiment and in the prior art, and the diameter D1 and length L1 of a single roller are the same. Comparing the two structures, the prior art has more parts and seals between the cylindrical roller group C and the output gear, and the size of L3 is significantly longer than that of this embodiment. Furthermore, the pitch circle diameter d2 of the axial positioning bearing in the prior art is smaller than that in this embodiment. This leads to a significant increase in the loads FaD and FaE of the axial positioning bearing in the prior art. Therefore, in the prior art's technical solution, since the axis of its radial support roller 310 passes through the first axial positioning bearing 2 and the second axial positioning bearing 6, meaning that the radial support roller 310, the first axial positioning bearing 2, and the second axial positioning bearing 6 all contact the cylindrical surface of the output shaft with the same diameter, it requires axial positioning bearings with greater load-bearing capacity. The size and weight of the first and second axial positioning bearings will be larger, and the cost will also increase significantly.

[0061] Taking the axial support roller D of this embodiment and the axial positioning bearing D of the prior art as the analysis objects, in the technical solution of this embodiment, the axial support roller D is in complete contact with the raceways on both sides, and bears the load within the length L2 of the axial support roller D; while in the technical solution of the prior art, within the length L2 of the axial positioning bearing D, the L'2 range bears the force of the raceway surface on the sixth segment 04, and the L''2 range bears the force of the raceway surface on the eighth shaft segment 11, thus weakening the effective load-bearing capacity of the axial positioning bearing D. The situation is the same for the axial positioning bearing E of the prior art.

[0062] Meanwhile, under the premise that d1 is the same, the pitch circle diameter d2 of the axial support roller in this embodiment is larger than the pitch circle diameter d2 of the axial positioning bearing in the prior art. When the diameters of the axial support roller and the axial positioning bearing are the same, the technical solution of this embodiment can arrange a larger number of axial support rollers around the gear shaft, resulting in a greater load-bearing capacity. Alternatively, under the premise of the same load-bearing capacity, smaller axial support rollers can be selected, thereby reducing the product size.

[0063] The above description is merely a specific embodiment of this utility model, but the protection scope of this utility model is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this utility model should be included within the protection scope of this utility model. Therefore, the protection scope of this utility model should be determined by the protection scope of the claims.

Claims

1. A low-speed end structure for a planetary gearbox, characterized in that, include: The housing (100), output gear shaft (200), radial support unit (300), and two axial support units are provided; the housing (100) is provided with an assembly through hole (101), the output gear shaft (200) passes through the assembly through hole (101) and is rotatably engaged with the housing (100), and an annular assembly space is formed between the output gear shaft (200) and the hole wall of the assembly through hole (101); The radial support unit (300) includes a plurality of radial support rollers (310), all of which are located within the annular assembly space and arranged circumferentially on the output gear shaft (200). Each radial support roller (310) simultaneously rolls in contact with the output gear shaft (200) and the housing (100) about its own first axis (001), the first axis (001) being aligned with the extension direction of the axis of the assembly through hole (101). The axial support unit includes a plurality of axial support rollers, all of which are located within the annular assembly space and arranged circumferentially on the output gear shaft (200). Each axial support roller simultaneously rolls in contact with the output gear shaft (200) and the housing (100) about its own second axis (002). The radial support unit (300) is located between the two axial support units. The first axis (001) is perpendicular to the second axis (002), and the first axis (001) is located within the area enclosed by the plurality of axial support rollers of the same axial support unit.

2. The low-speed end structure of the planetary gearbox according to claim 1, characterized in that: The output gear shaft (200) includes a shaft body (210), a first bearing seat (220), and a second bearing seat (230). The first bearing seat (220) and the second bearing seat (230) are both sleeved and fixed outside the shaft body (210). One of the two axial support units is clamped between the first bearing seat (220) and the housing (100), and the other of the two axial support units is clamped between the second bearing seat (230) and the housing (100).

3. The low-speed end structure of the planetary gearbox according to claim 2, characterized in that: All of the radial support rollers (310) are located between the first bearing housing (220) and the second bearing housing (230), and the two ends of each radial support roller (310) in the axial direction are in contact with the first bearing housing (220) and the second bearing housing (230), respectively.

4. The low-speed end structure of the planetary gearbox according to claim 3, characterized in that: The shaft body (210) is provided with a shoulder, which is located outside the housing (100); the first bearing seat (220) is clamped between the radial support roller (310) and the shoulder, and the second bearing seat (230) is screwed to the shaft body (210).

5. The low-speed end structure of the planetary gearbox according to claim 3, characterized in that: The output gear shaft (200) also includes a locking nut (240); The shaft body (210) is provided with a shoulder, which is located outside the housing (100); the first bearing seat (220) is clamped between the radial support roller (310) and the shoulder, and the second bearing seat (230) is sleeved on the shaft body (210); the locking nut (240) is screwed and fixed to the outside of the shaft body (210) and contacts the side of the second bearing seat (230) away from the first bearing seat (220).

6. The low-speed end structure of the planetary gearbox according to claim 5, characterized in that: The low-speed end structure of the planetary gearbox also includes an oil seal, which is installed between the locking nut (240) and the wall of the assembly through hole (101), or the oil seal is installed between the second bearing seat (230) and the wall of the assembly through hole (101).

7. The low-speed end structure of the planetary gearbox according to claim 5, characterized in that: The low-speed end structure of the planetary gearbox also includes a support ring (800), which is simultaneously sleeved and fixed on the shaft body (210) and the locking nut (240); The low-speed end structure of the planetary gearbox also includes an oil seal, which is installed between the outer peripheral surface of the support ring (800) and the wall of the assembly through hole (101).

8. The low-speed end structure of the planetary gearbox according to any one of claims 2-7, characterized in that: Both the first bearing housing (220) and the second bearing housing (230) have inner and outer ring surfaces that are arranged opposite to each other in their own axial direction. The inner ring surface of the first bearing housing (220) and the inner ring surface of the second bearing housing (230) are opposite to each other. A limiting ring (221) is protruding on each inner ring surface. The limiting ring (221) contacts the end face of the radial support roller (310) in the axial direction, and the limiting ring (221) is located on the side of the radial support roller (310) near the shaft body (210) on the central axis.

9. The low-speed end structure of the planetary gearbox according to any one of claims 1-7, characterized in that: The radial support unit (300) is a plurality of units, and the plurality of radial support units (300) are arranged axially on the output gear shaft (200).

10. The low-speed end structure of the planetary gearbox according to claim 9, characterized in that: The low-speed end structure of the planetary gearbox also includes a spacer ring (3000), which is sleeved on the outside of the output gear shaft (200). The spacer ring (3000) is located between adjacent radial support units (300), and the end face of each radial support roller (310) is in contact with the spacer ring (3000).

11. The low-speed end structure of the planetary gearbox according to claim 9, characterized in that: The low-speed end structure of the planetary gearbox also includes an oil nozzle (1000), which is mounted on the housing (100) and is used to deliver lubricating medium between adjacent radial support units (300).

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