Gear assembly for reduction gearbox

Abstract

The utility model provides a gear assembly for a reduction gearbox, which comprises a gear shaft with a gear, the interior of the gear shaft is of a hollow structure, and a first end of the gear shaft, into which lubricating oil is injected, is provided with a flange structure. The flange structure protrudes from the periphery of the first end of the gear shaft to the interior of the hollow structure along the periphery of the first end of the gear shaft. According to the gear assembly for the reduction gearbox, the flange structure is arranged at the end, where the lubricating oil is jetted into, of the gear shaft, so that the lubricating oil can be blocked when the gear is lubricated by the lubricating oil, the gear cannot be rapidly thrown out of the gear under the action of centrifugal force, and it is guaranteed that the gear is sufficiently lubricated.

Description

Technical Field

[0001] The present application relates to the field of reduction gearbox systems, and more particularly, to a gear assembly for a reduction gearbox. Background Art

[0002] For the reducer with a planetary structure, the sun gear in the planetary stage is connected to the internal teeth at the center of the output gear shaft through the drum teeth. When the reducer on the market lubricates this part of the connection, the lubricating oil is easily thrown to both sides under the action of centrifugal force.

[0003] In addition, when the planetary gear is running, force is applied to the bearing installed in the inner hole of the planetary gear, and the load is very high. Therefore, as a heavy-load area, the amount of lubricating oil required here is very large, and the current planetary gear structure cannot ensure the smooth discharge of the lubricating oil.

[0004] In addition, the traditional lubricating oil sealing component is only a skeleton oil seal installed on the oil seal position of the input gear shaft. The parallel stage input gear shaft has a high rotation speed and large vibration. The bearings in this part bear a large load and generate a lot of heat during operation. Therefore, a large amount of lubricating oil is allocated. A skeleton oil seal is placed to prevent lubricating oil leakage. However, as the running time increases, the skeleton oil seal ages and wears more due to the erosion of the lubricating oil, loses its sealing effect, and the oil seal life is relatively short. Utility Model Content

[0005] In order to solve one of the above problems, the utility model provides a gear assembly for a reduction box, which can block lubricating oil when lubricating the gear, so that the gear will not be quickly thrown out of the gear due to the centrifugal force, thereby ensuring that the gear is sufficiently lubricated.

[0006] In order to achieve the above-mentioned purpose, a gear assembly for a reduction box is provided, wherein the gear assembly includes a gear shaft with a gear, and the interior of the gear shaft is a hollow structure, and the first end of the gear shaft into which the lubricating oil is injected is provided with a guard structure, and the guard structure is along the outer periphery of the first end of the gear shaft and protrudes from the outer periphery to the interior of the hollow structure.

[0007] Furthermore, the retaining edge structure protrudes toward the interior of the hollow structure along the radial direction of the end surface where the first end of the gear shaft is located.

[0008] Furthermore, the lengths of the sidewall structures protruding into the interior of the hollow structure are the same.

[0009] Furthermore, the gear assembly is also provided with a bearing for supporting the gear shaft, and the inner diameter of the retaining edge structure is 0.6 to 0.8 times the diameter of the position where the bearing is located.

[0010] Furthermore, the gear structure also includes a planetary-stage reduction structure having a plurality of planetary gears, and an oil drain hole penetrating the gear body is formed on the gears of the planetary gears.

[0011] Furthermore, the gears of the planetary gears include herringbone gears.

[0012] Furthermore, the herringbone gear is provided with a cutter recess.

[0013] Furthermore, the oil drain hole includes a straight hole and a stepped hole.

[0014] Furthermore, the planetary gear further comprises a reserved boss protruding toward the center of the circumference on the inner surface of the gear body along the circumference of the inner surface of the gear body, and the oil drain hole is formed on the reserved boss.

[0015] Furthermore, the oil drain holes are evenly distributed along the reserved boss.

[0016] Furthermore, the distance between the edge of the oil drain hole and the tooth root of the adjacent herringbone gear ranges from 2 mm to 5 mm.

[0017] Furthermore, the gear assembly is also provided with a labyrinth sealing structure and a skeleton oil seal cooperating with the labyrinth sealing structure.

[0018] According to the present application, the gear assembly for the reduction box is provided with a retaining edge structure at one end of the gear shaft where the lubricating oil is sprayed in, which can block the lubricating oil when lubricating the gear, so that the lubricating oil will not be quickly thrown out of the gear due to the centrifugal force, thereby ensuring that the gear is sufficiently lubricated.

[0019] Furthermore, by providing an oil drain hole in the gear assembly, excess lubricating oil can be discharged without causing oil blockage, thereby ensuring smooth discharge of the lubricating oil.

[0020] In addition, a combined sealing structure having a labyrinth sealing structure and a skeleton oil seal is provided in the gear assembly, which can not only increase the sealing effect but also increase the service life of the oil seal. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The drawings constituting part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation on the present invention. In the drawings:

[0022] Figure 1 A partial structural cross-sectional view of a reduction gearbox system according to an embodiment of the present application is shown;

[0023] Figure 2 Shows Figure 1A partial cross-sectional view of a perspective view of a partial structure of the reduction gearbox system shown;

[0024] Figure 3 A cross-sectional view of a gear assembly with a retaining edge structure according to an embodiment of the present application is shown;

[0025] Figure 4 A cross-sectional view of a gear assembly with an oil drain hole according to another embodiment of the present application is shown;

[0026] Figure 5 Shows Figure 4 A cross-sectional view of the gear structure shown with some components removed;

[0027] Figure 6 Shows Figure 5 An enlarged view of section E is shown;

[0028] Figure 7 A cross-sectional view of a combined sealing structure provided with a labyrinth seal and a skeleton oil seal according to yet another embodiment of the present application is shown;

[0029] Fig. 8A and Figure 8B They are shown respectively Figure 7 A perspective view and a cross-sectional view of an end cap included in the labyrinth seal shown in FIG. 1 ; and

[0030] Fig. 9 Shows Figure 7 The shown diagram shows the arrangement of the labyrinth seal inner ring and the labyrinth seal inner ring when assembling the combined seal structure. DETAILED DESCRIPTION

[0031] In order to make the purpose, technical solution and advantages of the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0032] According to the present application, a gear assembly for a reduction gear box is provided, wherein the gear assembly includes a gear shaft with a gear, and the interior of the gear shaft is a hollow structure, and the first end of the gear shaft into which the lubricating oil is injected is provided with a guard structure, and the guard structure is along the outer periphery of the first end of the gear shaft and protrudes from the outer periphery to the interior of the hollow structure.

[0033] According to the present application, the gear assembly for the reduction box is provided with a retaining edge structure at one end of the gear shaft where the lubricating oil is sprayed in, which can block the lubricating oil when lubricating the gear, so that the lubricating oil will not be quickly thrown out of the gear due to the centrifugal force, thereby ensuring that the gear is sufficiently lubricated.

[0034] The structure according to the present application is described below by taking a gear assembly for a reduction box including a parallel-stage reduction structure and a planetary-stage reduction structure connected to the parallel-stage reduction structure as an example, wherein the parallel-stage reduction structure may include a parallel-stage pinion shaft, a first gear disposed on the parallel-stage pinion shaft, a parallel-stage large gear shaft, and a second gear disposed on the parallel-stage large gear shaft and meshing with the first gear, and the planetary-stage reduction structure may include a sun gear and a plurality of planetary gears meshing with the sun gear, and the parallel-stage large gear shaft meshes with the wheel axle of the sun gear. In addition, the gear assembly for the reduction box also includes a double-linked drum-shaped tooth that connects the gear assembly to a component such as a crankshaft. However, the structure according to the present application is not limited thereto.

[0035] Figure 1 A partial structural cross-sectional view of a reduction gearbox system according to an embodiment of the present application is shown.

[0036] like Figure 1 As shown, according to a preferred embodiment of the present application, the gear assembly structure includes: a driving flange 1003 providing power, a parallel stage reduction structure, a planetary stage reduction structure, a labyrinth seal and a skeleton oil seal double seal structure (such as Figure 1 D in the figure) and duplex crown teeth 1013 that connect the gear assembly to a component such as a crankshaft.

[0037] The parallel stage reduction structure includes a parallel stage pinion shaft 1004, a spherical roller bearing 1005, a first gear 1006 arranged on the parallel stage pinion shaft, a parallel stage large gear shaft (or output gear shaft) 1008, a second gear 1007 integrally arranged with the parallel stage large gear shaft, and a cylindrical roller bearing 1009 supporting the parallel stage large gear shaft 1008.

[0038] The planetary stage reduction structure includes planetary gears 1001 , cylindrical roller bearings 1010 without outer rings for the planetary gears 1001 , planetary gear shafts 1012 on which the planetary gears 1001 are mounted, sun gears 1014 meshing with the planetary gears 1001 , planet carriers 1015 , and inner gear rings 1002 .

[0039] The parallel stage reduction structure and the planetary stage reduction structure are supported by the housing assembly and the bearing assembly. The torque transmission between the parallel stage reduction structure and the planetary stage reduction structure is realized by connecting the internal teeth formed inside the parallel stage gear shaft and the external teeth formed at one end of the sun gear shaft.

[0040] The driving flange 1003 is connected to the parallel-stage pinion shaft (or input gear shaft) in the parallel-stage reduction structure, and the engine inputs torque and speed by connecting to the driving flange 1003 .

[0041] The first gear 1006 on the parallel-stage pinion shaft is meshed with the second gear 1007 on the parallel-stage large gear shaft. Figure 1 As shown in part B, the parallel-stage large gear shaft 1008 is internally machined with internal teeth, and one end of the sun gear shaft is provided with external teeth of drum-shaped teeth, and the internal teeth of the parallel-stage large gear shaft 1008 are meshed with the external teeth of the sun gear shaft.

[0042] The sun gear 1014 meshes with N (N≥2) planetary gears 1001. The planetary gears 1001 mesh with a fixed inner gear ring 1002. The planetary gears 1001 mounted on the planetary carrier 1015 via the planetary gear shaft 1012 revolve around the sun gear 1014, thereby driving the planetary carrier 1015 to rotate.

[0043] Figure 1 and Figure 2 Part A shows a rib structure provided on a gear assembly according to an embodiment of the present application, part C shows a structure provided with an oil drain hole according to an embodiment of the present application, and part D shows a double sealing structure provided with a labyrinth seal and a skeleton oil seal according to an embodiment of the present application.

[0044] The rib structure, the oil drain hole structure, and the double sealing structure of the labyrinth seal and the skeleton oil seal according to each embodiment of the present application will be described in detail below with reference to the accompanying drawings.

[0045] like Figure 3 As shown, it shows a gear assembly provided with a rib structure 102. The interior of the parallel-stage large gear shaft is a hollow structure, and the internal teeth 101 are arranged inside the parallel-stage large gear shaft. As shown in the figure, the first end (label 103 shows the direction of lubricating oil entering) of the parallel-stage large gear shaft into which the lubricating oil is injected is provided with a rib structure. The rib structure 102 protrudes from the outer periphery to the interior of the hollow structure along the outer periphery of the first end of the parallel-stage large gear shaft. The rib structure 102 is arranged above the internal teeth 101.

[0046] According to a preferred embodiment of the present application, the rib structure protrudes toward the interior of the hollow structure along the radial direction of the end surface where the first end of the parallel-stage gear shaft is located.

[0047] Furthermore, according to another preferred embodiment of the present application, the lengths of the sidewall structures protruding into the interior of the hollow structure are the same.

[0048] In addition, according to another preferred embodiment of the present application, the gear assembly is further provided with a bearing (for example, Figure 1 For cylindrical roller bearings 1009), the inner diameter of the rib structure is 0.6 to 0.8 times the diameter of the bearing.

[0049] By providing a flange structure at the end of the parallel gear shaft where the lubricating oil is injected, the lubricating oil lubricating the drum-shaped teeth of the sun gear can be blocked, so that it will not be thrown out quickly due to the centrifugal force (such as Figure 3 The reference numeral 104 shows the direction in which the lubricating oil is thrown out), thereby ensuring that the drum teeth of the sun gear are sufficiently lubricated.

[0050] Although the rib structure is provided at the first end of the parallel-stage large gear shaft into which the lubricating oil is injected in the above-mentioned embodiment, the rib structure can be formed on any desired gear shaft as required.

[0051] The following description will be made by taking an example where an oil drain hole is formed on the gear of the planetary gear, but the present application is not limited thereto.

[0052] like Figures 4 to 6 , which shows a gear assembly with an oil drain hole.

[0053] As shown in the figure, the planetary gear 203 is arranged on the planetary gear shaft 201, and the planetary gear 203 is formed with an oil drain hole 206 penetrating the gear body of the planetary gear. The planetary gear 203 is meshed with the inner ring gear 204. The lubricating oil is Figure 4 The direction of 205 shown enters the gear assembly. A cylindrical roller bearing 202 without an outer ring is arranged on the planetary gear shaft 201.

[0054] According to the bearing selection, the current wheel rim thickness is less than 4 times the modulus, and the wall thickness is very thin, which makes it easy to run circles when installing the bearing. In addition, the bearing used is very large. The larger the bearing, the higher the price. As mentioned above, a cylindrical roller bearing 202 without an outer ring is provided on the planetary gear shaft 201, that is, the inner hole of the planetary gear is used as the outer ring of the bearing. The use of a bearing without an outer ring here can not only greatly reduce the price of the bearing, but also make it more convenient to assemble the bearing, and can increase the wall thickness of the planetary gear and increase the service life of the planetary gear.

[0055] The inner hole serves as the inner raceway of the bearing, and the surface roughness is controlled at Ra0.3~Ra0.6. In order to ensure a certain hardness, the surface is hardened by carburizing, nitriding or carbonitriding. The depth of the carburizing layer is 1~2mm, and the depth of the nitriding layer is 0.3~1mm.

[0056] According to a preferred embodiment of the present application, the gears of the planetary gears include herringbone gears. Figure 5 As shown, the planetary wheel rim 208 is provided with a herringbone gear 209. According to one embodiment of the present application, the herringbone gear 209 is provided with a backing groove 207.

[0057] Furthermore, according to the present application, the planetary gear further includes a reserved boss protruding toward the center of the circumference on the inner surface of the gear body along the circumference of the inner surface of the gear body, for example Figure 5 The reserved boss 210 is shown in FIG.

[0058] Furthermore, according to another preferred embodiment of the present application, an oil drain hole 206 (for example, Figure 5 shown).

[0059] During rotation, the pressure inside and outside the planetary gear is different. The pressure inside the planetary gear is high, and the excess lubricating oil can be discharged through the oil discharge hole 206 without causing oil retention, thereby ensuring smooth discharge of the lubricating oil.

[0060] The diameter of the oil drain hole 206 is 2-8 mm, and the oil drain hole can be a straight hole or a stepped hole, and the form is not limited. In addition, the distribution of the oil drain holes on the reserved boss can be uniform or uneven, and the number of distribution on the reserved boss is N, and N≥1.

[0061] According to a preferred embodiment of the present application, Figure 6 As shown, the distance d between the right or left edge of the oil drain hole 206 and the tooth root 212 of the adjacent herringbone gear is between 2 and 5 mm. With this structure, stress concentration can be reduced and the fatigue life of the tooth root can be reduced.

[0062] Although the oil leakage hole is formed on the gear of the planetary gear in the above embodiment, the oil leakage hole may be formed on any desired gear as required.

[0063] The following will be based on the attached Figures 7 to 9 The invention discloses a combined sealing structure provided with a labyrinth sealing structure and a skeleton oil seal.

[0064] like Figure 1 As shown, a labyrinth seal and skeleton oil seal combination as shown in part D is used on the side of the reducer input shaft bearing close to the driving flange 1003.

[0065] Figure 7 A cross-sectional view of a combined sealing structure provided with a labyrinth sealing structure and a skeleton oil seal according to yet another embodiment of the present application is shown; Fig. 8A and Figure 8B They are shown respectively Figure 7 A perspective view and a cross-sectional view of an end cap included in the labyrinth seal structure shown in FIG. Fig. 9 Shows Figure 7 The shown diagram shows the arrangement of the labyrinth seal inner ring and the labyrinth seal inner ring when assembling the combined seal structure.

[0066] As shown in the figure, the combined sealing structure includes a labyrinth sealing structure, a skeleton oil seal, an oil seal gasket 313 and a wear-resistant bushing 306 arranged on the input gear shaft 305. The combined sealing structure is arranged on the input gear shaft 305, and the input gear shaft 305 is provided with a bearing including a bearing inner ring 308, a bearing rolling element 309 and a bearing outer ring 310, and the bearing is supported on a bearing seat 311. A driving flange 304 is also arranged on the input gear shaft 305.

[0067] The labyrinth seal structure is provided with an end cover 301 and a labyrinth seal inner ring 307. A cavity for installing the skeleton oil seal 303 is integrally designed on the end cover 301, and the width of the cavity is wider than the width of the skeleton oil seal 303, preferably, 5-10 mm wide. A grease injection port 315 is also provided on the end cover 301 for injecting grease. The grease injection port 315 is located between the labyrinth seal inner ring 307 on the end cover 301 and the cavity for installing the skeleton oil seal 303. The labyrinth seal inner ring 307 is installed on the input gear shaft 305 in a transition or small interference fit manner. An outer ring that cooperates with the labyrinth seal inner ring 307 can be integrated on the end cover 301.

[0068] Fig. 8A and Figure 8B The end cap 301 is shown with an integrated outer ring 316. Lubricating oil enters the end cap from a lubricating oil inlet direction 317 and flows out from a lubricating oil outlet direction 318.

[0069] Of course, the outer ring can also be made into a separate split structure as needed. If the outer ring is made into a split structure, considering that the inner ring of the labyrinth seal must remain stationary during the operation of the reduction gearbox, an anti-rotation pin or a large interference fit design can be added to the outer ring to fix the outer ring to the end cover.

[0070] Whether the outer ring is integrated on the end cover or the outer ring is a separate component and connected to the end cover through an interference fit or an anti-rotation pin, the outer ring is directly sleeved on the inner ring of the labyrinth seal. In addition, the single-side side clearance between the inner ring and the outer ring of the labyrinth seal is 0.5-2.5mm, preferably 0.9-1mm, so as to ensure that the inner ring of the labyrinth seal will not interfere with the outer ring when rotating. When the inner ring of the labyrinth seal rotates, a cyclone will be generated in the gap, thereby preventing the lubricating oil from entering the cavity where the skeleton oil seal is located.

[0071] The depth and width of the grooves of the inner and outer rings of the labyrinth seal are preferably 0.5 to 4 mm, and the distance between each groove is preferably 2 to 8 mm. The number of grooves on the inner and outer rings of the labyrinth seal is not limited and is greater than 1.

[0072] During assembly, the grooves on the inner and outer rings of the labyrinth seal can be facing each other (such as Figure 7 312 in FIG. 3), there may also be a certain misalignment (such as Fig. 9 320 in FIG. 1 ), which is not limited here.

[0073] The inner ring of the labyrinth seal can be on the same shaft section as the bearing (such as Fig. 9 As shown), it can also be on a different shaft segment than the bearing (as shown Figure 7 shown).

[0074] Preferably, the outer diameter of the inner ring of the labyrinth seal is 1.05 to 1.2 times the inner diameter of the bearing on the input gear shaft on which the inner ring of the labyrinth seal is mounted.

[0075] According to an embodiment of the present application, Figure 7 As shown, the oil seal gasket 313 and the skeleton oil seal 303 are installed in the cavity of the skeleton oil seal reserved in the end cover 301, wherein the oil seal gasket 313 and the cavity are clearance-matched, and the skeleton oil seal 303 and the cavity are interference-fitted. The labyrinth seal inner ring 307 is arranged on the right side of the bearing inner ring 308 and is aligned therewith. One side of the wear-resistant bushing 306 is installed on the right side of the labyrinth seal inner ring 307 and is close to the labyrinth seal inner ring 307, and the other side of the wear-resistant bushing 306 is in contact with the driving flange 304. One side of the end cover 301 provided with the oil seal gasket 313 and the skeleton oil seal 303 is fitted on the bearing seat 311 and the bearing outer ring 310, and the other side of the end cover 301 and one side of the skeleton oil seal 303 are provided with an oil seal baffle 302.

[0076] Preferably, the ratio of the distance between the labyrinth seal inner ring 307 and the bearing end face to the inner diameter of the bearing is 0.01-0.2.

[0077] The shapes of the grooves on the inner ring 307 and the outer ring of the labyrinth seal can be semicircular or other shapes, such as rectangular grooves and irregular shapes.

[0078] After the lubricating oil has completed the function of lubrication and cooling, it will return from both sides of the bearing. The left side will directly return to the box body, and most of the lubricating oil from the right side will flow back to the box body through the oil return hole from the groove 314 on the end cover. When the labyrinth seal inner ring 307 assembled on the input gear shaft 305 rotates at high speed, a cyclone is generated in the labyrinth seal groove, so that the lubricating oil flowing through the bearing cannot or only a small amount of lubricating oil can enter the cavity where the skeleton oil seal is installed on the right side.

[0079] The skeleton oil seal and the wear-resistant bushing are assembled together to seal a small amount of lubricating oil from the bearing lubrication. A small amount of lubricating oil can play the role of a lubricating oil seal and also block impurities such as dust from the outside.

[0080] When assembling the combined sealing structure, a certain amount of grease is injected through the grease injection port 315. When less lubricating oil passes through the labyrinth sealing structure, the grease can act as a lubricant to ensure sufficient lubrication at the skeleton oil seal and reduce the friction between the oil seal and the wear-resistant sleeve.

[0081] The grease injection port 315 is located between the labyrinth seal inner ring 307 and the cavity of the skeleton oil seal 303 on the end cover 301, and together with the double-lip skeleton oil seal, it can prevent external dust, fine sand, etc. from entering the interior of the gear assembly.

[0082] The width of the cavity on the end cover where the skeleton oil seal is installed is greater than the width of the skeleton oil seal, so the position of the skeleton oil seal on the wear-resistant bushing can be easily adjusted. When the surface of the wear-resistant bushing is worn, the position of the skeleton oil seal can be adjusted so that the lip and the undamaged surface are assembled together to continue to play a sealing role.

[0083] The inner ring of the labyrinth seal can limit the outer ring of the bearing, while the wear-resistant bushing limits the inner ring of the labyrinth seal in the axial direction. The wear-resistant bushing is axially limited by the drive flange connected to the external spline on the input gear shaft. The design of the wear-resistant bushing can facilitate the replacement of the wear-resistant bushing after the oil seal position is damaged in the later stage, and the replacement cost is low.

[0084] According to the present application, a combined sealing structure having a labyrinth sealing structure and a skeleton oil seal is provided in the gear assembly, which can not only increase the sealing effect but also increase the service life of the oil seal.

[0085] The above description is only the preferred embodiment of the utility model, and is not intended to limit the utility model. For those skilled in the art, the utility model can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the utility model shall be included in the protection scope of the utility model.

[0086] List of reference numerals:

[0087] 1001 planetary gear 1002 inner ring gear

[0088] 1003 driving flange 1004 parallel level pinion shaft

[0089] 1005 spherical roller bearing 1006 first gear

[0090] 1007 second gear 1008 parallel level large gear shaft

[0091] 1009 cylindrical roller bearing 1010 cylindrical roller bearing without outer ring

[0092] 1012 planetary gear shaft 1013 double drum gear

[0093] 1014 sun gear 1015 planet carrier

[0094] 101 internal teeth 102 rib structure

[0095] 103 Lubricating oil inlet direction 104 Lubricating oil ejection direction

[0096] 201 planetary gear shaft 202 cylindrical roller bearing without outer ring

[0097] 203 planetary gear 204 internal ring gear

[0098] 205 Direction of lubricating oil entering the gear assembly 206 Oil drain hole

[0099] 207 backing groove 208 planetary wheel rim

[0100] 209 herringbone gear 210 reserved boss

[0101] 212 herringbone gear tooth root 301 end cover

[0102] 302 oil seal baffle 303 skeleton oil seal

[0103] 304 driving flange 305 input gear shaft

[0104] 306 wear-resistant bushing 307 seal inner ring

[0105] 308 bearing inner ring 309 bearing rolling element

[0106] 310 bearing outer ring 311 bearing seat

[0107] 314 groove 315 grease injection port

[0108] 316 outer ring 317 lubricating oil entry direction

[0109] 318 Lubricating oil outflow direction.

Claims

1. A gear assembly for a reduction gear box, characterized in that: The gear assembly comprises a gear shaft (1008) with a gear, and the interior of the gear shaft (1008) is a hollow structure. The first end of the gear shaft (1008) into which the lubricating oil is injected is provided with a retaining edge structure (102), and the retaining edge structure (102) is along the outer periphery of the first end of the gear shaft (1008) and protrudes from the outer periphery to the interior of the hollow structure.

2. The gear assembly for a reduction gearbox according to claim 1, characterized in that: The retaining edge structure (102) protrudes toward the interior of the hollow structure along the radial direction of the end surface where the first end of the gear shaft (1008) is located.

3. The gear assembly for a reduction gearbox according to claim 1 or 2, characterized in that: The lengths of the sidewall structures (102) protruding into the interior of the hollow structure are the same.

4. The gear assembly for a reduction gearbox according to claim 3, characterized in that: The gear assembly is also provided with a bearing (1009) for supporting the gear shaft (1008), and the inner diameter of the retaining edge structure (102) is 0.6 to 0.8 times the diameter of the position where the bearing (1009) is located.

5. The gear assembly for a reduction gearbox according to claim 1, characterized in that: The gear assembly also includes a planetary stage reduction structure having a plurality of planetary gears (1001), and an oil drain hole (206) penetrating the gear body is formed on the planetary gear (203) of the planetary gear (1001).

6. The gear assembly for a reduction gearbox according to claim 5, characterized in that: The planetary gear (203) includes a herringbone gear (209).

7. The gear assembly for a reduction gearbox according to claim 6, characterized in that: The herringbone gear (209) is provided with a cutter recess (207).

8. The gear assembly for a reduction box according to any one of claims 5 to 7, characterized in that: The oil drain hole (206) includes a straight hole and a stepped hole.

9. The gear assembly for a reduction box according to any one of claims 5 to 7, characterized in that: The planetary gear (203) further comprises a reserved boss (210) protruding toward the center of the circumference on the inner surface of the gear body along the circumference of the inner surface of the gear body, and the oil drain hole (206) is formed on the reserved boss (210).

10. The gear assembly for a reduction gearbox according to claim 9, characterized in that: The oil drain holes (206) are evenly distributed along the reserved boss (210).

11. The gear assembly for a reduction gearbox according to claim 7, characterized in that: The distance between the edge of the oil drain hole (206) and the tooth root of the adjacent herringbone gear (209) ranges from 2 mm to 5 mm.

12. The gear assembly for a reduction gearbox according to claim 1 or 5, characterized in that: The gear assembly is also provided with a labyrinth seal structure and a skeleton oil seal matched with the labyrinth seal structure.

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