Heavy-load wheel-side planetary reducer

Abstract

The utility model relates to a heavy-load wheel-side planetary reducer which is characterized in that an input flange is connected with a fixed flange, and an input shaft is arranged in the fixed flange; the connecting flange is connected with the fixed flange, and the first double-row full roller bearing is arranged between the fixed flange and the connecting flange; the connecting flange, the flange gear ring and the rotating shell are fixedly connected; a high-speed shaft is arranged on the center shaft in the rotating shell, one end, close to the fixed flange, of the high-speed shaft is in transmission connection with the input shaft, a planetary gear train is arranged on the high-speed shaft, a gear ring is arranged on the inner wall of the flange gear ring and is in meshing transmission with the planetary gear train, and a second double-row full roller bearing is arranged between the planetary gear train and the rotating shell. The planetary gear train is used for supporting the rotary shell under rolling friction; a plurality of deep groove ball bearings are arranged between the planetary gear train and the input shaft and between the planetary gear train and the high-speed shaft and used for supporting the planetary gear train. The utility model has the advantages that the radial load bearing capacity is effectively improved; heating is reduced, and transmission efficiency is improved; and the hub reduction requirement under the heavy-load working condition is met.

Description

Technical Field

[0001] This utility model relates to the field of planetary reducer technology, specifically a heavy-duty wheel-side planetary reducer. Background Technology

[0002] As an important transmission component, wheel-side reducers typically need to withstand large radial loads in practical applications. Currently, the rotary support of wheel-side reducers mostly adopts a double tapered roller bearing cantilever support structure. However, due to the short axial dimensions of the two bearings, their radial load-bearing capacity is limited, making it difficult to meet the requirements of large radial load conditions.

[0003] In addition, the axial fixation of the sun gear in existing wheel-side reducers is usually achieved by end-face fixation, and its circumferential motion relies on sliding friction. This structure is prone to generating more heat and has low transmission efficiency.

[0004] Meanwhile, wheel-side reducers need to be started and stopped frequently in actual use and are often subjected to severe impact loads. The traditional planetary gear arrangement is not reliable enough in dealing with such impacts and there is room for improvement.

[0005] Therefore, there is an urgent need to design a wheel-side reducer that can reduce frictional heat generation, resist impact loads, and change the traditional planetary gear arrangement. Utility Model Content

[0006] The purpose of this invention is to overcome the shortcomings of the prior art and provide a heavy-duty wheel-side planetary reducer to reduce frictional heat generation, resist impact loads, and change the traditional planetary gear arrangement.

[0007] To achieve the above objectives, a heavy-duty wheel-side planetary reducer is designed, comprising: an input flange, a fixed flange, and an input shaft. The fixed flange is coaxially fitted onto the flange neck of the input flange, and the input shaft is positioned on the central axis of the central hole of the fixed flange. The reducer also includes: a connecting flange, a flange gear ring, and a rotating housing. The connecting flange is coaxially fitted onto the flange neck of the fixed flange. The inner and outer rings of the first double-row full roller bearing are respectively positioned on the outer wall of the flange neck of the fixed flange and the inner wall of the connecting flange, so that the fixed flange provides rolling friction support to the connecting flange. The flange gear ring is coaxially fitted onto the flange neck of the connecting flange, and the rotating housing... The housing is coaxially mounted on the end face of the flange gear ring away from the connecting flange. The connecting flange, flange gear ring, and rotating housing are fixedly connected by the first screw. A high-speed shaft is provided on the central shaft inside the rotating housing. The end of the high-speed shaft near the fixed flange is connected to the input shaft for transmission. A planetary gear system is provided on the high-speed shaft. A gear ring is provided on the inner wall of the flange gear ring to mesh with the planetary gear system for transmission. A second double-row full roller bearing is provided between the planetary gear system and the rotating housing to provide rolling friction support for the rotating housing. Several deep groove ball bearings are provided between the planetary gear system and the input shaft and the high-speed shaft to support the planetary gear system.

[0008] Preferably, the present invention further includes: the input shaft and the high-speed shaft are driven by a spline connection; the planetary gear system includes: a high-speed shaft gear ring, disposed on the high-speed shaft at the end away from the input shaft; a second sun gear, slidably sleeved on the high-speed shaft between the high-speed shaft gear ring and the input shaft; a first sun gear, slidably sleeved on the high-speed shaft between the second sun gear and the input shaft; a third planet carrier, sleeved on the second sun gear and meshing with the second sun gear, the third planet carrier having a plurality of third planet shafts arranged along its circumference, the third planet shafts having third planet gears sleeved on the third planet shafts, the third planet gears meshing with the high-speed shaft gear ring; a second planet carrier, sleeved on the first sun gear and meshing with the first sun gear, the second planet carrier having a plurality of second planet shafts arranged along its circumference, the second planet shafts having a plurality of third planet gears sleeved on the second planet shafts. Two planetary gears, the second planetary gear meshing with the second sun gear; a first planetary carrier, disposed between the flange gear ring and the first sun gear, the first planetary carrier having a plurality of first planetary shafts arranged along its circumference, the first planetary shafts having first planetary gears fitted on the first planetary shafts, the first planetary gears meshing with the first sun gear; the first planetary shafts being fixedly connected to the fixed flange by second screws, thus fixing the first planetary carrier to the fixed flange; the end face of the first planetary carrier away from the fixed flange having an extension section; the inner ring of the second double-row full roller bearing being disposed on the outer wall of the extension section of the first planetary carrier or the outer wall of the end of the first planetary shaft; the outer ring of the second double-row full roller bearing being disposed on the inner wall of the rotating housing, so that the first planetary carrier forms rolling friction support on the rotating housing through the second double-row full roller bearing.

[0009] Preferably, the present invention further includes: a fourth deep groove ball bearing, disposed in the gap between the high-speed shaft gear ring and the second sun gear, the inner ring of the fourth deep groove ball bearing being sleeved on the high-speed shaft, the two end faces of the inner ring abutting against the high-speed shaft gear ring and the second sun gear respectively, and the outer ring of the fourth deep groove ball bearing being disposed on the inner wall of the third planetary carrier, so that the high-speed shaft forms rolling friction support on the third planetary carrier through the fourth deep groove ball bearing; a third deep groove ball bearing, disposed in the gap between the second sun gear and the first sun gear, the second sun gear having a stepped structure at the end near the first sun gear, the inner ring of the third deep groove ball bearing being fitted into the stepped structure of the second sun gear, the two end faces of the inner ring of the third deep groove ball bearing abutting against the second sun gear and the first sun gear respectively, and the third... The outer ring of the three deep groove ball bearing is disposed on the inner wall of the second planetary carrier to provide rolling friction support for the second sun gear against the second planetary carrier; the second deep groove ball bearing is disposed between the fixed flange and the first sun gear, and the inner wall of the flange neck of the fixed flange and the end of the first sun gear near the fixed flange are provided with opposing stepped mechanisms, and the inner and outer rings of the second deep groove ball bearing are respectively disposed within the stepped structure of the first sun gear and the stepped structure of the fixed flange to provide rolling friction support for the fixed flange against the first sun gear; the first deep groove ball bearing is disposed between the input shaft and the fixed flange, and the inner and outer rings of the first deep groove ball bearing are respectively disposed on the outer wall of the input shaft and the inner wall of the fixed flange to provide rolling friction support for the fixed flange against the input shaft.

[0010] Preferably, the present invention further includes: a first rotary lip seal, disposed at the end face of the first double-row full roller bearing near the fixed flange and between the connecting flange and the fixed flange, wherein the inner sealing ring of the first rotary lip seal is disposed on the outer wall of the flange neck of the fixed flange and the outer sealing ring of the first rotary lip seal is disposed on the inner wall of the connecting flange; and a second rotary lip seal, disposed at the end face of the input shaft near the input flange and between the input flange and the fixed flange, wherein the inner sealing ring of the second rotary lip seal is disposed on the outer wall of the input shaft and the outer sealing ring of the second rotary lip seal is disposed on the inner wall of the flange neck of the input flange.

[0011] Preferably, the present invention further includes: an annular protrusion structure on the inner wall of the end face of the rotating housing near the high-speed shaft, the inner diameter of the annular protrusion structure being larger than the diameter of the high-speed shaft, and a stepped structure at the end of the high-speed shaft near the rotating housing; a fifth deep groove ball bearing is disposed between the end face of the rotating housing and the high-speed shaft, the inner ring of the fifth deep groove ball bearing being disposed on the stepped structure of the high-speed shaft near the rotating housing, and the outer ring of the fifth deep groove ball bearing being disposed on the inner ring wall of the annular protrusion structure on the end face of the rotating housing, so that the end face of the rotating housing forms a rolling friction support for the high-speed shaft.

[0012] Preferably, the present invention further includes: the rotating housing is a detachable structure, including a rotating housing body and an end cover, the end face of the rotating housing away from the fixed flange is an open structure, the end face of the rotating housing near the high-speed shaft is an end cover, and the end cover is fixedly installed at the open structure by screws to achieve a compression seal.

[0013] Preferably, the present invention further includes: the inner wall of the rotating housing is provided with a plurality of toothed rings, and the toothed rings of the rotating housing mesh with the toothed rings of the second planetary gear and the third planetary gear.

[0014] Preferably, the present invention further includes: a piston is provided between the fixed flange and the input flange, and a disc spring abutting against the input flange and a friction plate abutting against the fixed flange are respectively provided at both ends of the piston; a piston oil chamber is provided between the piston and the fixed flange; a pressure oil passage is provided on the input flange and the fixed flange; the pressure oil passage is connected to the piston oil chamber of the piston for injecting pressure oil to drive the piston to move; the friction plate includes a stationary friction plate provided on the fixed flange and a moving friction plate fixedly provided on the input shaft.

[0015] Compared with the prior art, the advantages of this utility model are:

[0016] To enhance radial load bearing capacity, a simple-support design for the rotating housing bearing is adopted. The flange gear ring and the fixed flange and the first planetary carrier are fixed by the first double-row full roller bearing and the second double-row full roller bearing respectively, forming a stable simple-support structure. This effectively extends the axial layout dimension of the bearing and significantly improves the reducer's ability to withstand large radial loads.

[0017] To reduce frictional losses and improve transmission efficiency, deep groove ball bearings are used in key transmission parts such as the high-speed shaft and the third planetary carrier, the second sun gear and the second planetary carrier, and the first sun gear and the fixed flange to achieve rolling friction contact, replacing the traditional sliding friction structure. This effectively reduces frictional heat generation and improves transmission efficiency.

[0018] Enhanced sealing and dustproof performance, extended service life: By using a rotary lip seal in conjunction with an oil nozzle to inject lubricating oil into a labyrinth structure, external dust is effectively prevented from entering the reducer, reducing dust wear on the seals and improving the reducer's sealing reliability and overall service life.

[0019] To improve operational reliability under impact loads, the planetary gears adopt a full roller arrangement, which optimizes the load-bearing capacity of the planetary gears under frequent start-stop and severe impact load conditions, reduces the risk of failure due to impact, and significantly improves the operational reliability of the reducer.

[0020] The arrangement of planetary gears in the heavy-duty wheel-side planetary reducer is different from that in the traditional heavy-duty wheel-side planetary reducer. This shortens the required transmission shaft length and reduces the lateral width of the heavy-duty wheel-side planetary reducer, thus improving its compactness and reducing its encroachment on working space to accommodate more load-bearing equipment. Attached Figure Description

[0021] Figure 1 This is a sectional view of the present invention;

[0022] In the diagram: 1 First screw plug, 2 Input flange, 3 Fixed flange, 4 Connecting flange, 5 Oil nozzle, 6 First end face gasket, 7 Roller, 8 First planetary gear, 9 Flange gear ring, 10 First elastic retaining ring, 11 First screw, 12 First sun gear, 13 First planetary shaft, 14 Gear ring, 15 Second planetary carrier, 16 Second sun gear, 17 Second end face gasket, 18 Second planetary shaft, 19 Second planetary gear, 20 Third planetary carrier, 21 Third end face gasket, 22 Third planetary gear, 23 Third planetary shaft, 24 End cap, 25 Fifth deep groove ball bearing, 26 First needle roller, 27 Third elastic retaining ring, 28 Fourth deep groove ball bearing. 29. Deep groove ball bearing; 30. Second needle roller; 31. Second elastic retaining ring; 32. Third deep groove ball bearing; 33. High-speed shaft; 34. Second double-row full roll bearing; 35. First planetary carrier; 36. Second screw; 37. Second elastic cylindrical pin; 38. Second deep groove ball bearing; 39. First double-row full roll bearing; 40. First deep groove ball bearing; 41. First rotary lip seal; 42. Static friction plate; 43. Moving friction plate; 44. Piston; 45. Input shaft; 46. Disc spring; 47. Second screw plug; 48. Hydraulic motor; 49. Piston oil chamber; 50. Rotary housing; 51. High-speed shaft gear ring; 52. Second rotary lip seal. Detailed Implementation

[0023] To make the purpose, principle and structure of this utility model clearer, the following description is provided in conjunction with the accompanying drawings and specific embodiments.

[0024] This utility model provides a heavy-duty wheel-side planetary reducer, the specific structure of which is as follows.

[0025] The main components include an input flange 2, a fixed flange 3, an input shaft 45, a connecting flange 4, a flange gear ring 9, a rotating housing 50, a high-speed shaft 32, and a planetary gear system. The fixed flange 3 is coaxially fitted onto the flange neck of the input flange 2. The input shaft 45 is positioned on the central axis of the central hole of the fixed flange 3 and is connected to the hydraulic motor 48. The fixed flange 3 is fixedly connected to the vehicle equipment. A cavity exists between the input flange 2 and the fixed flange 3, within which a piston 44 and a disc spring 46 are installed. Both ends of the piston 44 abut against the disc spring 46 and friction plates, respectively. The friction plates include a stationary friction plate 42 fixedly connected to the fixed flange 3 via a spline and a moving friction plate 43 fixedly connected to the input shaft 45 via a spline, forming a braking structure.

[0026] The braking structure includes two working states: automatic braking and brake release.

[0027] When the braking structure is in automatic braking mode: the disc spring 46 abuts against and expands the piston 44 and the input flange 2 on both sides respectively. Under the supporting force generated by the elastic deformation of the disc spring 46, the piston 44 moves towards the friction plate. The end of the piston 44 away from the disc spring 46 abuts against the friction plate. Several stationary friction plates 42 and moving friction plates 43 are spaced apart in the friction plate. Under the thrust of the piston 44, the gap between the stationary friction plates 42 and the moving friction plates 43 gradually disappears and they gradually come into close contact, generating a large friction braking force. At this time, the rotational motion between the fixed flange 3 and the input shaft 45, which are respectively connected to the stationary friction plates 42 and the moving friction plates 43, is stopped under the action of the friction braking force. Furthermore, since the friction braking force is a large static friction, the fixed flange 3 and the input shaft 45 also form a relative stationary state.

[0028] When the braking structure is in the released state: pressurized oil is injected into the piston oil chamber 49 between the piston 44 and the fixed flange 3, near the friction plate end of the piston 44. The oil pushes the piston 44 away from the friction plate and towards the disc spring 46. At this time, the friction plates lose their thrust and move away from each other, forming a non-contact gap. The disc spring 46 undergoes compression deformation under the thrust of the oil, and this compression force is converted into the elastic deformation potential energy of the disc spring 46, which is released again when the oil is withdrawn from the piston oil chamber 49. Sealing rings are provided at the mating points of the fixed flange 3 and the piston 44 at both ends of the piston oil chamber 49.

[0029] Preferably, the piston oil chamber 49 is disposed between the piston 44 and the fixed flange 3, and is connected to an external pressure oil system with a pressure pump through an oil passage disposed in the fixed flange 3 and the input flange 2. An opening for the pressure oil passage is provided on the end face of the input flange 2 away from the fixed flange 3, and a first screw plug 1 and a second screw plug 47 are respectively provided at the opening to control the opening and closing of the pressure oil passage.

[0030] Input flange 2, fixed flange 3, and connecting flange 4 are all necked flanges. Necked flange is a common technical term in the mechanical field. A necked flange includes a flange plate and a flange neck located on the end face of the flange plate. The flange plate is a cylindrical structure with a circular cross-section. Several bolt holes parallel to the central axis of the flange plate are distributed along its circumference. These bolt holes are used to connect the flange to other equipment with bolts. The central part of the necked flange has a central through hole coaxial with the flange plate. On the end face of the flange plate, there is a circumferential extension surrounding the central through hole, extending away from the end face of the flange plate. This extension is collectively referred to in the art as the flange neck or flange neck. The flange neck can be cylindrical or conical. The aforementioned necked flange and flange neck are knowledge that should be known to those skilled in the art.

[0031] The connecting flange 4 is coaxially fitted onto the flange neck of the fixed flange 3, and the two are rolled together by a first double-row full roll bearing 39. The inner ring of the first double-row full roll bearing 39 is fitted onto the outer wall of the flange neck of the fixed flange 3, and the outer ring is fixed to the inner wall of the connecting flange 4. The flange gear ring 9 is coaxially fitted onto the flange neck of the connecting flange 4, and the rotating housing 50 is coaxially disposed on the end face of the flange gear ring 9 away from the connecting flange 4. The connecting flange 4, the flange gear ring 9, and the rotating housing 50 are fixedly connected by a first screw 11 and further reinforced by a first elastic cylindrical pin 34 and a second elastic cylindrical pin 37.

[0032] A high-speed shaft 32 is mounted on the central axis within the rotating housing 50. Its end near the fixed flange 3 is connected to the input shaft 45 via a spline connection. The high-speed shaft 32 is equipped with a planetary gear system, specifically including a high-speed shaft gear ring 51, a second sun gear 16, a first sun gear 12, a third planet carrier 20, a second planet carrier 15, and a first planet carrier 35. The high-speed shaft gear ring 51 is fixed at the end of the high-speed shaft 32 furthest from the input shaft 45. The second sun gear 16 and the first sun gear 12 are sequentially slidably mounted on the high-speed shaft 32, located between the high-speed shaft gear ring and the input shaft. It is worth noting that the first sun gear 12 is positioned on the high-speed shaft 32, close to the fixed flange 3 and away from the high-speed shaft gear ring 51. The second sun gear 16 is positioned on the high-speed shaft 32, away from the fixed flange 3 and close to the high-speed shaft gear ring 51. The high-speed shaft gear ring 51 is positioned at the end of the high-speed shaft 32 furthest from the fixed flange 3. Both the first sun gear 12 and the second sun gear 16 have a sliding fit with the high-speed shaft 32, while the high-speed shaft gear ring 51 is fixedly mounted on the high-speed shaft 32 for direct transmission. The high-speed shaft gear ring 51 is an external gear ring.

[0033] Preferably, the spline transmission between the input shaft 45 and the high-speed shaft 32 can be achieved by opening a through hole with a splined inner wall in the input shaft 45, setting a spline on the outer wall of the end of the high-speed shaft 32, inserting the end of the high-speed shaft 32 into the through hole of the input shaft, forming a fit between the inner and outer splines of the two components, which can realize the transmission of rotational motion.

[0034] The third planetary carrier 20 is mounted on the second sun gear 16 and meshes with the second sun gear 16. Several third planetary shafts 23 are evenly distributed around the third planetary carrier 20 and extend away from the fixed flange 3. The third planetary shafts 23 are mounted on the third planetary shafts 23 and the third planetary shafts 22 surround the high-speed shaft gear ring 51 and mesh with the high-speed shaft gear ring 51.

[0035] The second planetary carrier 15 is mounted on the first sun gear 12 and meshes with the first sun gear. Several second planetary shafts 18 are evenly distributed around its circumference and extend away from the fixed flange 3. Second planetary gears 19 are mounted on the second planetary shafts 18 and surround the second sun gear 16 and mesh with the second sun gear 16.

[0036] The first planetary carrier 35 is arranged around the flange gear ring 9 and the first sun gear 12, forming a clearance between the first planetary carrier 35 and the first sun gear 35 to prevent contact and collision. A plurality of first planetary shafts 13 extending away from the fixed flange 3 are evenly distributed around the circumference of the first planetary carrier 35. First planetary gears 8 are fitted onto the first planetary shafts 13, and a plurality of rollers 7 filling the gap between the first planetary gears 8 and the first planetary shafts 13 are arranged around the gap. The first planetary gears 8 mesh with the first sun gear 12. The first planetary gears 6 mesh with the inner wall gear ring of the flange gear ring 9 to achieve transmission.

[0037] The first planetary shaft 13 is fixed to the fixed flange 3 by second screws 36 passing through its two end faces. Since the first planetary shaft 13 is fixedly mounted on the first planetary carrier 35, the first planetary carrier 35 can also be fixedly connected to the fixed flange 3 through the first planetary shaft 13. The end face of the first planetary carrier 35 away from the fixed flange 3 is provided with an extension section. A second double-row full roller bearing 33 is provided between the outer wall of the extension section and the inner wall of the rotating housing 50. The inner ring of the second double-row full roller bearing 33 is located on the outer wall of the extension section of the first planetary carrier 35 or the outer wall of the end of the first planetary shaft 13. The outer ring of the second double-row full roller bearing 33 is located on the inner wall of the rotating housing 50, so as to realize the rolling support of the first planetary carrier on the rotating housing 50.

[0038] Preferably, a plurality of gear rings 14 are provided on the inner wall of the rotating housing 50 at the positions corresponding to the planetary gears, and the gear rings 14 mesh with the planetary gears to achieve transmission.

[0039] Preferably, a first needle roller 26 filling the gap is arranged around the gap between the third planetary shaft 23 and the third planetary gear 22, and a second needle roller 29 filling the gap is arranged around the gap between the second planetary shaft 18 and the second planetary gear 19.

[0040] Preferably, the roller 7 can be a double-row roller, and a first elastic retaining ring 10 is provided at the gap between the double-row rollers for separation. The first needle roller 26 and the second needle roller 29 can be double-row needle rollers. A second elastic retaining ring 30 is provided between the double-row needle rollers of the first needle roller 26, and a third elastic retaining ring 27 is provided between the double-row needle rollers of the second needle roller 29 for separating the needle rollers.

[0041] To reduce friction and improve transmission efficiency, deep groove ball bearings are installed between the main rotating parts.

[0042] A fourth deep groove ball bearing 28 is installed in the gap between the high-speed shaft gear ring 51 and the second sun gear 16. The inner ring of the fourth deep groove ball bearing 28 is fitted on the high-speed shaft 32, and the two end faces abut against the high-speed shaft gear ring 51 and the second sun gear 16 respectively. The outer ring is fixed to the inner wall of the third planetary carrier 20.

[0043] A third deep groove ball bearing 31 is installed in the gap between the second sun gear 16 and the first sun gear 12. The second sun gear 16 has a stepped structure at one end near the first sun gear 12. The inner ring of the third deep groove ball bearing 31 is fitted in the step, and the two end faces abut against the second sun gear 16 and the first sun gear 12 respectively. The outer ring is fixed to the inner wall of the second planetary carrier 15.

[0044] A second deep groove ball bearing 38 is provided between the fixed flange 3 and the first sun gear 12. The inner wall of the flange neck of the fixed flange 3 and the end of the first sun gear 12 near the fixed flange 3 are provided with opposing steps. The inner ring and outer ring of the second deep groove ball bearing 28 are respectively locked in the steps of the first sun gear 38 and the fixed flange 3.

[0045] A first deep groove ball bearing 40 is provided between the input shaft 45 and the fixed flange 3. The inner ring and outer ring of the first deep groove ball bearing 40 are respectively sleeved on the outer wall of the input shaft 45 and the inner wall of the fixed flange 3.

[0046] The end face of the rotating housing 50 away from the fixed flange 3 can be configured as a detachable end cover 24. The end cover 24 is fixed and tightened onto the end face of the rotating housing 50 by screws to form a seal. A fifth deep groove ball bearing 25 is provided between the end cover 24 of the rotating housing 50 and the high-speed shaft 32. The end cover 24 has an annular protrusion on the side near the high-speed shaft 32, and its inner diameter is larger than the diameter of the high-speed shaft 32. The end of the high-speed shaft 32 near the end cover 24 has a stepped structure. The inner ring of the fifth deep groove ball bearing 25 is fitted on the stepped structure of the high-speed shaft 32, and the outer ring is fixed to the inner ring wall of the annular protrusion of the end cover 24, so as to realize the rolling support of the end of the high-speed shaft 32 by the end cover 24.

[0047] For sealing and dust prevention, a first rotary lip seal 41 is provided between the fixed flange 3 and the connecting flange 4. The inner sealing ring of the first rotary lip seal 41 is fitted onto the outer wall of the flange neck of the fixed flange 3, and the outer sealing ring is fixed to the inner wall of the connecting flange 4, used to seal the lubricating oil inside the reducer. A second rotary lip seal 52 is provided between the input shaft 45 and the input flange 2. The inner sealing ring of the second rotary lip seal 52 is fitted onto the outer wall of the input shaft 45, and the outer sealing ring is fixed to the inner wall of the flange neck of the input flange 2. Lubricating oil is injected into the oil passage and cavity between the fixed flange 3 and the connecting flange 4 through the grease nipple 5 provided on the fixed flange 3, which can effectively prevent dust from entering and wearing the seals.

[0048] Preferably, a first end face gasket 6 is provided between the first planetary gear 8 and the fixed flange 3, a second end face gasket 17 is provided between the second planetary carrier and the second planetary gear 19, and a third end face gasket 21 is provided between the third planetary carrier 20 and the third planetary gear 22, in order to reduce friction and impact between the planetary gears and the planetary carrier and the fixed flange, and increase the load impact resistance.

[0049] The power transmission and braking process of this reducer is as follows: When power needs to be transmitted, pressurized oil is injected into the piston oil chamber 49 through the first screw plug 1, pushing the piston 44 to move to the left, compressing the disc spring 46 and releasing the friction stationary plate 42 and the friction moving plate 43, and the input shaft 45 is released from braking. The hydraulic motor 48, located within the input flange 2, drives the input shaft 45 to rotate via internal and external splines. The input shaft 45, through splines, drives the high-speed shaft 32 to rotate. The high-speed shaft gear ring 51 rotates accordingly, causing the third planetary gear 22 to revolve. The third planetary gear 22 drives the third planetary carrier 20 to rotate via the third planetary shaft 23, forming the first stage of reduction. The third planetary carrier 20 meshes with the second sun gear 16 via internal gears, driving the second sun gear 16 to rotate. The second sun gear 16, through meshing, drives the second planetary gear 19 to revolve. The second planetary gear 19, through the second planetary shaft 18, drives the second planetary carrier 15 to rotate, forming the second stage of reduction. The second planetary carrier 15, through gear meshing or splines, drives the first sun gear 12 to rotate. Since the first planetary carrier 13 is fixed to the fixed flange 3 via the first planetary shaft 13 and the second screw 36, the meshing of the first sun gear 12 can only drive the first planetary gear 8 to rotate. The first planetary gear 8, through meshing, drives the flange gear ring 9 to rotate, forming the third stage of reduction. Finally, power is output through the rotating housing 50, which is fixedly connected to the flange gear ring 9.

[0050] In addition, the rotating housing 50 adopts a detachable structure, including the housing body and the end cover 24. The end cover 24 is fixed to the open end of the housing body by screws, which facilitates the installation and maintenance of internal components.

[0051] This reducer effectively improves radial load capacity through a combination design of double-row full roller bearings and deep groove ball bearings; it reduces heat generation and improves transmission efficiency by replacing sliding friction with rolling friction; it achieves high speed ratio reduction through a multi-stage planetary gear system, while also having a reliable sealing and dustproof structure, making it suitable for wheel-side reduction requirements under heavy load conditions.

[0052] 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 equivalent substitutions or modifications made by those skilled in the art within the technical scope disclosed in this utility model, based on the technical solution and novel concept of this utility model, should be included within the protection scope of this utility model.

Claims

1. A heavy-duty wheel-side planetary reducer, comprising: The system comprises an input flange, a fixed flange, and an input shaft. The fixed flange is coaxially fitted onto the flange neck of the input flange, and the input shaft is positioned on the central axis of the central hole of the fixed flange. The system further includes a connecting flange, a flange gear ring, and a rotating housing. The connecting flange is coaxially fitted onto the flange neck of the fixed flange. The inner and outer rings of a first double-row full roller bearing are respectively positioned on the outer wall of the flange neck of the fixed flange and the inner wall of the connecting flange, so that the fixed flange provides rolling friction support to the connecting flange. The flange gear ring is coaxially fitted onto the flange neck of the connecting flange, and the rotating housing is coaxially positioned on the end face of the flange gear ring away from the connecting flange. The connecting flange, the flange gear ring, and the rotating housing are fixedly connected by a first screw. A high-speed shaft is mounted on the central shaft inside the rotating housing. The high-speed shaft is connected to the input shaft at its end near the fixed flange. A planetary gear system is mounted on the high-speed shaft. A gear ring on the inner wall of the flange gear ring meshes with the planetary gear system. A second double-row full roller bearing is positioned between the planetary gear system and the rotating housing, so that the planetary gear system provides rolling friction support to the rotating housing. Several deep groove ball bearings are provided between the planetary gear train and the input shaft and high-speed shaft to support the planetary gear train.

2. The heavy-duty wheel-side planetary reducer as described in claim 1, characterized in that, The input shaft and high-speed shaft are driven by a spline connection. The planetary gear system includes: a high-speed shaft gear ring, disposed on the high-speed shaft at the end away from the input shaft; a second sun gear, slidably sleeved on the high-speed shaft between the high-speed shaft gear ring and the input shaft; a first sun gear, slidably sleeved on the high-speed shaft between the second sun gear and the input shaft; a third planet carrier, sleeved on the second sun gear and meshing with it, with a plurality of third planet shafts arranged along the circumference of the third planet carrier, each third planet shaft having a third planet gear meshing with the high-speed shaft gear ring; a second planet carrier, sleeved on the first sun gear and meshing with it, with a plurality of second planet shafts arranged along the circumference of the second planet carrier, each second planet shaft having a second planet gear meshing with the second sun gear; and a first planet carrier, disposed between a flange gear ring and the first sun gear, with a plurality of first planet shafts arranged along the circumference of the first planet carrier, each first planet shaft having a first planet gear meshing with the first sun gear. The first planetary shaft is fixedly connected to the fixed flange by the second screw, so that the first planetary carrier is fixedly connected to the fixed flange. The end face of the first planetary carrier away from the fixed flange is provided with an extension section. The inner ring of the second double-row full roller bearing is disposed on the outer wall of the extension section of the first planetary carrier or on the outer wall of the end of the first planetary shaft. The outer ring of the second double-row full roller bearing is disposed on the inner wall of the rotating housing, so that the first planetary carrier forms a rolling friction support on the rotating housing through the second double-row full roller bearing.

3. A heavy-duty wheel-side planetary reducer as described in claim 2, characterized in that, Also includes: The fourth deep groove ball bearing is disposed in the gap between the high-speed shaft gear ring and the second sun gear. The inner ring of the fourth deep groove ball bearing is sleeved on the high-speed shaft, and the two end faces of the inner ring abut against the high-speed shaft gear ring and the second sun gear, respectively. The outer ring of the fourth deep groove ball bearing is disposed on the inner wall of the third planetary carrier, so that the high-speed shaft forms a rolling friction support on the third planetary carrier through the fourth deep groove ball bearing. The third deep groove ball bearing is disposed in the gap between the second sun gear and the first sun gear. The end of the second sun gear near the first sun gear has a stepped structure. The inner ring of the third deep groove ball bearing is fitted into the stepped structure of the second sun gear. The two end faces of the inner ring of the third deep groove ball bearing abut against the second sun gear and the first sun gear, respectively. The outer ring of the third deep groove ball bearing is disposed on the inner wall of the second planetary carrier, so that the second sun gear forms a rolling friction support on the second planetary carrier. A second deep groove ball bearing is disposed between a fixed flange and a first sun gear. The inner wall of the flange neck of the fixed flange and the end of the first sun gear near the fixed flange are provided with opposing stepped mechanisms. The inner ring and outer ring of the second deep groove ball bearing are respectively disposed within the stepped structure of the first sun gear and the stepped structure of the fixed flange, so that the fixed flange provides rolling friction support to the first sun gear. A first deep groove ball bearing is disposed between an input shaft and a fixed flange. The inner ring and outer ring of the first deep groove ball bearing are respectively disposed on the outer wall of the input shaft and the inner wall of the fixed flange, so that the fixed flange provides rolling friction support to the input shaft.

4. A heavy-duty wheel-side planetary reducer as described in claim 1, characterized in that, Also includes: The first rotary lip seal is located at the end face of the first double-row full roller bearing near the fixed flange and is positioned between the connecting flange and the fixed flange. The inner sealing ring of the first rotary lip seal is located on the outer wall of the fixed flange neck, and the outer sealing ring of the first rotary lip seal is located on the inner wall of the connecting flange. The second rotary lip seal is located at the end face of the input shaft near the input flange and is positioned between the input flange and the fixed flange. The inner sealing ring of the second rotary lip seal is located on the outer wall of the input shaft, and the outer sealing ring of the second rotary lip seal is located on the inner wall of the input flange neck.

5. A heavy-duty wheel-side planetary reducer as described in claim 1, characterized in that, The inner wall of the rotating housing near the high-speed shaft has an annular protrusion structure. The inner diameter of the annular protrusion structure is larger than the diameter of the high-speed shaft. The end of the high-speed shaft near the rotating housing has a stepped structure. A fifth deep groove ball bearing is disposed between the end face of the rotating housing and the high-speed shaft. The inner ring of the fifth deep groove ball bearing is disposed on the stepped structure of the high-speed shaft near the rotating housing, and the outer ring of the fifth deep groove ball bearing is disposed on the inner ring wall of the annular protrusion structure on the end face of the rotating housing, so that the end face of the rotating housing forms a rolling friction support for the high-speed shaft.

6. A heavy-duty wheel-side planetary reducer as described in claim 1 or 5, characterized in that, The rotating housing is a detachable structure, including the rotating housing body and end caps. The end face of the rotating housing away from the fixed flange is an open structure, and the end face of the rotating housing near the high-speed shaft is the end cap. The end cap is fixed to the open structure with screws to achieve a compression seal.

7. A heavy-duty wheel-side planetary reducer as described in claim 2, characterized in that, The inner wall of the rotating housing is provided with several gear rings, which mesh with the gear rings of the second planetary gear and the third planetary gear.

8. A heavy-duty wheel-side planetary reducer as described in claim 1, characterized in that, A piston is provided between the fixed flange and the input flange. At both ends of the piston are a butterfly spring that abuts against the input flange and a friction plate that abuts against the fixed flange, respectively. A piston oil chamber is provided between the piston and the fixed flange. Pressure oil passages are provided on the input flange and the fixed flange. The pressure oil passages are connected to the piston oil chamber of the piston to inject pressure oil to drive the piston movement. The friction plate includes a stationary friction plate provided on the fixed flange and a moving friction plate fixedly provided on the input shaft.

Images