Differential cover and differential

Abstract

The differential cover comprises a gear ring, a sealing plate is arranged on the first side of the gear ring, a shaft hole for a first half shaft to penetrate through is formed in the sealing plate, and an opening is formed in the second side of the gear ring. The opening is used for installing a first half shaft gear connected with the first half shaft, a planetary gear shaft and two planetary gears arranged on the planetary gear shaft in a sleeving mode in the gear ring. The differential mechanism cover solves the problems that a ball cage type differential mechanism cover is complex in structure, high in manufacturing cost and not beneficial to assembly and disassembly of internal structural parts of a differential mechanism.

Description

Technical Field

[0001] This application relates to the field of differential technology, and in particular to a differential cover and a differential. Background Technology

[0002] Currently, ride-on lawnmowers require a differential in their gearbox to enable turning. However, the differentials currently used in the market often employ a ball-cage type differential cover. This type of differential cover has a complex structure, high manufacturing cost, and is not conducive to the assembly and disassembly of the internal components of the differential. Utility Model Content

[0003] The purpose of this application is to provide a differential cover and a differential, which solves the problems of complex structure, high manufacturing cost, and difficulty in assembling and disassembling internal structural components of the differential.

[0004] To achieve the above objectives, this application provides a differential cover, including a gear ring. A sealing plate is provided on a first side of the gear ring, and the sealing plate has a shaft hole for a first half-shaft to pass through. An opening is provided on a second side of the gear ring, and the opening is used to accommodate a first half-shaft gear connected to the first half-shaft, a planetary gear shaft, and two planetary gears sleeved on the planetary gear shaft in the gear ring.

[0005] In some embodiments, the gear ring has two opposing limiting surfaces inside, which are used to limit the distance between the two planetary gears.

[0006] In some embodiments, a countersunk platform is provided on both of the limiting surfaces. The two countersunk platforms are respectively used for the two ends of the planetary gear shaft to be installed, and also for the planetary gear shaft and the two planetary gears to move along the axial direction of the first half-shaft.

[0007] In some embodiments, the dimension of the countersink along the axis of the gear ring is set to be greater than the radius of the planetary gear shaft and less than the diameter of the planetary gear shaft.

[0008] In some embodiments, the two limiting surfaces are two parallel planes.

[0009] In some embodiments, the sealing plate has an annular protrusion, which is coaxially arranged with the shaft hole, and the annular protrusion has an oil hole.

[0010] In some embodiments, the sealing plate has at least two pairs of process holes arranged around the shaft hole.

[0011] In some embodiments, the gear ring and the sealing plate are integrally cast structures.

[0012] This application also provides a differential, including the differential cover described in any of the above claims.

[0013] In some embodiments, it also includes:

[0014] Planetary gear shaft, installed in the gear ring of the differential cover;

[0015] Two planetary gears are fitted onto the planetary gear shaft;

[0016] A first half-shaft and a first half-shaft gear, the first half-shaft passing through the sealing plate of the differential cover, the first half-shaft gear being located inside the gear ring and connected to the first half-shaft, the first half-shaft gear meshing with two planetary gears;

[0017] The second half-shaft and the second half-shaft gear are coaxially arranged with the first half-shaft. The second half-shaft gear is located outside the gear ring and connected to the second half-shaft. The second half-shaft gear meshes with the two planetary gears.

[0018] Compared with the above background technology, the differential cover provided in the embodiments of this application includes a gear ring. A sealing plate is provided on the first side of the gear ring, and the sealing plate has a shaft hole for the first half shaft to pass through. An opening is provided on the second side of the gear ring for the first half shaft gear connected to the first half shaft, the planetary gear shaft, and two planetary gears sleeved on the planetary gear shaft to be installed in the gear ring.

[0019] This differential cover features a semi-open structure, with one side of the gear ring sealed by a plate and the other side having an opening to facilitate the assembly and disassembly of the first half-shaft gear, the planetary gear shaft, and the two planetary gears mounted on the planetary gear shaft. Compared to the traditional closed ball cage type differential cover structure, this design is relatively simple, has a lower manufacturing cost, and facilitates the assembly and disassembly of the first half-shaft gear, the planetary gear shaft, and the planetary gears. This solves the problems of the complex structure, high manufacturing cost, and difficulty in assembling and disassembling internal differential components associated with the ball cage type differential cover. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of this application or related technologies, the drawings used in the description of the embodiments or related technologies will be briefly introduced below. Obviously, the drawings described below are only embodiments of this application. For those skilled in the art, other drawings can be obtained based on the provided drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the differential cover structure in an embodiment of this application;

[0022] Figure 2 for Figure 1 The diagram shows the assembly of the differential cover, planetary gear shaft, and planetary gears.

[0023] Figure 3 for Figure 2 Another perspective illustration;

[0024] Figure 4 This is a schematic diagram of the assembly of the differential and the intermediate gear in an embodiment of this application;

[0025] Figure 5 for Figure 4 A sectional view;

[0026] Figure 6 for Figure 4 A partial structural diagram.

[0027] in:

[0028] 10-Differential cover, 11-Ring gear, 111-Limiting surface, 112-Sunk, 12-Sealing plate, 121-Shaft hole, 122-Annular protrusion, 123-Oil hole, 124-Process hole, 13-Opening;

[0029] 20 - Planetary gear shaft;

[0030] 30-Planetary Gear;

[0031] 40 - First half-shaft;

[0032] 50 - First half-shaft gear;

[0033] 60 - Second half-shaft;

[0034] 70 - Second half-shaft gear;

[0035] 80 - Intermediate gear. Detailed Implementation

[0036] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0037] To enable those skilled in the art to better understand the present application, the present application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0038] It should be noted that the directional terms such as "upper end," "lower end," "left side," and "right side" mentioned below are defined based on the accompanying drawings in the instruction manual.

[0039] Please refer to Figures 1 to 6 , Figure 1This is a schematic diagram of the differential cover structure in an embodiment of this application; Figure 2 for Figure 1 The diagram shows the assembly of the differential cover, planetary gear shaft, and planetary gears. Figure 3 for Figure 2 Another perspective illustration; Figure 4 This is a schematic diagram of the assembly of the differential and the intermediate gear in an embodiment of this application; Figure 5 for Figure 4 A sectional view; Figure 6 for Figure 4 A partial structural diagram.

[0040] The differential cover 10 provided in this application embodiment is applied to a differential. The principle structure of the differential includes a differential cover 10, two half shafts, two half shaft gears, a planetary gear shaft 20, and two planetary gears 30. When the torque output by the engine is transmitted to the differential cover 10 through the intermediate gear 80, the differential cover 10 drives the two planetary gears 30 to rotate, and the two planetary gears 30 drive the two half shaft gears to rotate, thereby enabling the two half shafts to drive the wheels and drive the whole vehicle to move.

[0041] The differential cover 10 currently on the market mainly adopts a ball cage structure. The ball cage structure is complex, has a high manufacturing cost, and is not conducive to the assembly and disassembly of internal differential components.

[0042] Therefore, the differential cover 10 provided in this application embodiment includes a gear ring 11. A sealing plate 12 is provided on the first side of the gear ring 11. The sealing plate 12 is provided with a shaft hole 121 for the first half shaft 40 to pass through. An opening 13 is provided on the second side of the gear ring 11. The opening 13 is used to allow the first half shaft gear 50 connected to the first half shaft 40, the planetary gear shaft 20, and the two planetary gears 30 sleeved on the planetary gear shaft 20 to be installed in the gear ring 11.

[0043] The differential cover 10 with this design adopts a semi-open structure. Specifically, one side of the gear ring 11 is closed by a sealing plate 12, and the other side has an opening 13 to facilitate the disassembly and assembly of the first half-shaft gear 50, the planetary gear shaft 20, and the two planetary gears 30 sleeved on the planetary gear shaft 20. Compared with the traditional closed ball cage type differential cover 10 structure, its structure is relatively simple, the manufacturing cost is lower, and it is convenient for the disassembly and assembly of the first half-shaft gear 50, the planetary gear shaft 20, and the planetary gears 30. This solves the problem that the ball cage type differential cover 10 has a complex structure, high manufacturing cost, and is not conducive to the disassembly and assembly of internal differential components.

[0044] To facilitate the positioning of the two planetary gears 30, the gear ring 11 has two opposing positioning surfaces 111 inside, which are used to limit the distance between the two planetary gears 30.

[0045] Understandably, since the two planetary gears 30 are loosely fitted onto the planetary gear shaft 20, if the distance between the two planetary gears 30 on the planetary gear shaft 20 is too large, it can easily lead to excessive meshing clearance between the two planetary gears 30 and the first half-shaft gear 50 and the second half-shaft gear 70. This would affect the tight fit between the two planetary gears 30 and the first half-shaft gear 50 and the second half-shaft gear 70, thus affecting the transmission accuracy of the differential. Therefore, two opposing limiting surfaces 111 are provided inside the gear ring 11. These two limiting surfaces 111 contact and abut against the outer end faces of the two planetary gears 30, respectively, keeping the distance between the two planetary gears 30 on the planetary gear shaft 20 within a preset range. This prevents excessive meshing clearance between the two planetary gears 30 and the first half-shaft gear 50 and the second half-shaft gear 70, ensuring meshing accuracy.

[0046] In some embodiments, considering that the outer end faces of the two planetary gears 30 are both planes, the two limiting surfaces 111 are two parallel planes, which can increase the contact area between the limiting surface 111 and the corresponding outer end face of the planetary gear 30, thereby maximizing the limiting effect.

[0047] Furthermore, both limiting surfaces 111 are provided with recesses 112 or grooves. The two recesses 112 are used to accommodate the two ends of the planetary gear shaft 20, and also to allow the planetary gear shaft 20 and the two planetary gears 30 to move along the axial direction of the first half-shaft 40.

[0048] Of course, the depth of the two recessed platforms 112 can be designed according to the axial dimension of the planetary gear shaft 20, and the dimension of the two recessed platforms 112 along the axis of the first half-shaft 40 can be designed according to the radial dimension of the planetary gear shaft 20, so as to ensure that the two ends of the planetary gear shaft 20 can be fitted with the two recessed platforms 112, and that the planetary gear shaft 20 can move along the axis of the first half-shaft 40.

[0049] In this way, by moving the planetary gear shaft 20 and the two planetary gears 30 along the axial direction of the first half-shaft 40, the clearance between the two planetary gears 30 and the first half-shaft gear 50 and the second half-shaft gear 70 can be adjusted, thereby preventing jamming and other situations during differential operation, which helps to improve the flexibility and stability of differential operation.

[0050] In some embodiments, the dimension of the countersunk platform 112 along the axial direction of the gear ring 11 is set to be greater than the radius of the planetary gear shaft 20 and less than the diameter of the planetary gear shaft 20.

[0051] In other words, the dimension of the countersunk plate 112 along the axis of the gear ring 11 is between the radius and diameter of the planetary gear. This design allows the edge of the countersunk plate 112 to provide initial guidance and positioning when the planetary gear shaft 20 is inserted, guiding the planetary gear shaft 20 to be accurately installed in the predetermined position, reducing misalignment or skew during installation, and improving assembly efficiency and accuracy. Simultaneously, this dimensional design allows for a more rational contact area and force distribution between the planetary gear shaft 20 and components such as the countersunk plate 112 and the gear ring 11. When the planetary gear 30 rotates, the force acting on the planetary gear shaft 20 can be more evenly transmitted to adjacent components through the contact area with the countersunk plate 112, reducing localized stress concentration and the possibility of deformation or damage due to excessive stress, thus extending the service life of the components.

[0052] Furthermore, the use of the above-mentioned appropriate size of the countersunk plate 112 helps to ensure a good meshing relationship between the planetary gear 30 and the half-shaft gear. If the size of the countersunk plate 112 is too large or too small, it may cause the position deviation of the planetary gear shaft 20, thereby affecting the meshing accuracy between the planetary gear 30 and the half-shaft gear, and generating noise, vibration and other problems. The above-mentioned size design can effectively avoid these problems and ensure the smoothness and reliability of power transmission.

[0053] In some embodiments, the sealing plate 12 is provided with an annular protrusion 122, which protrudes from the sealing plate 12 toward the side away from the opening 13. The annular protrusion 122 is coaxially arranged with the shaft hole 121 and is provided with an oil hole 123.

[0054] The axial direction of the oil hole 123 is perpendicular to the axial direction of the shaft hole 121. Of course, multiple oil holes 123 can be distributed along the circumference of the annular protrusion 122 to facilitate lubrication of the first half-shaft 40.

[0055] In some embodiments, the sealing plate 12 is provided with at least two pairs of process holes 124 arranged around the shaft hole 121.

[0056] For example, two pairs of four process holes 124 can be provided, with the four process holes 124 evenly distributed on the outer periphery of the shaft hole 121. This can not only release the stress on the sealing plate 12, but also reduce the overall weight of the differential cover 10.

[0057] In some embodiments, the gear ring 11 and the end plate 12 are integrally cast. For example, the differential cover 10 can be integrally cast from cast iron.

[0058] The differential provided in this application includes the differential cover 10 described in the above specific embodiments.

[0059] Meanwhile, the differential also includes a planetary gear shaft 20, two planetary gears 30, a first half-shaft 40, a first half-shaft gear 50, a second half-shaft 60, and a second half-shaft gear 70.

[0060] This differential is used in fuel-powered ride-on lawnmowers. When the lawnmower uses a mechanical gearbox, this differential is required within the gearbox to enable the vehicle to turn.

[0061] Specifically, the planetary gear shaft 20 is installed in the gear ring 11 of the differential cover 10, two planetary gears 30 are sleeved on the planetary gear shaft 20, the first half-shaft 40 passes through the sealing plate 12 of the differential cover 10, the first half-shaft gear 50 is located inside the gear ring 11 and connected to the first half-shaft 40, the first half-shaft gear 50 meshes with the two planetary gears 30, the second half-shaft 60 is coaxially arranged with the first half-shaft 40, the second half-shaft gear 70 is located outside the gear ring 11 and connected to the second half-shaft 60, the second half-shaft gear 70 meshes with the two planetary gears 30.

[0062] More specifically, a shaft hole 121 is provided on the bottom of the differential cover 10. The first half-shaft 40 passes through this hole, and the first half-shaft gear 50 is connected to the first half-shaft 40 through a spline and then positioned by a shaft retaining ring. The first half-shaft gear 50 is placed at the bottom of the inner cavity of the differential cover 10. The planetary gear 30 is loosely fitted onto the planetary gear shaft 20 and then placed together on the recess 112 of the differential cover 10. The planetary gear 30 and the planetary gear shaft 20 can move between the two recesses 112 to adjust the clearance between the two planetary gears 30 and the first half-shaft gear 50 and the second half-shaft gear 70, thereby ensuring the meshing accuracy of the two planetary gears 30 with the first half-shaft gear 50 and the second half-shaft gear 70, and ensuring the smoothness and reliability of power transmission.

[0063] With this configuration, the torque transmitted from the engine is transmitted to the differential cover via the intermediate gear 80. The planetary gear shaft 20 is installed in the differential cover 10, which drives the planetary gear shaft 20 to rotate around its own axis. The planetary gear shaft 20, in turn, drives the planetary gear 30 on the shaft to rotate (the planetary gear 30 revolves around the sun). The planetary gear 30, in turn, drives the two half-shaft gears to rotate, and the two half-shaft gears, in turn, drive the corresponding half-shafts to rotate. The half-shafts then drive the tires to rotate, thus propelling the vehicle forward or backward. When the vehicle turns, the inner and outer wheels require different speeds. The rotation of the planetary gear 30 changes its meshing relationship with the half-shaft gears on both sides, causing one half-shaft gear to accelerate and the other half-shaft gear to decelerate, thereby achieving a speed difference between the two wheels. This meets the requirement of different speeds for the inner and outer wheels when the vehicle turns, allowing the vehicle to turn smoothly.

[0064] In other words, as the planetary gear 30 revolves, it continues to transmit the power from the engine to the half-shaft gears and half-shafts on both sides, thereby driving the wheels to rotate. This ensures that the vehicle continues to receive power output during cornering, maintaining its driving status. The rotation of the planetary gear 30 changes the direction and magnitude of power transmission, allowing power to be more rationally distributed to the wheels on both sides. This improves the vehicle's power utilization efficiency and driving stability during cornering, preventing slippage and loss of control caused by uneven power distribution.

[0065] It should be noted that in this specification, relational terms such as first and second are used only to distinguish one entity from several other entities, and do not necessarily require or imply any such actual relationship or order between these entities.

[0066] The differential cover and differential provided in this application have been described in detail above. Specific examples have been used to illustrate the principles and implementation methods of this application. The descriptions of the embodiments above are only for the purpose of helping to understand the solution and core ideas of this application. It should be noted that those skilled in the art can make several improvements and modifications to this application without departing from the principles of this application, and these improvements and modifications also fall within the protection scope of this application.

Claims

1. A differential cover (10) characterized by, The device includes a gear ring (11), a sealing plate (12) on the first side of the gear ring (11), a shaft hole (121) for the first half shaft (40) to pass through, and an opening (13) on the second side of the gear ring (11), the opening (13) for the first half shaft gear (50) connected to the first half shaft (40), the planetary gear shaft (20), and the two planetary gears (30) sleeved on the planetary gear shaft (20) to be installed in the gear ring (11).

2. The differential cover (10) of claim 1, wherein, The gear ring (11) has two opposing limiting surfaces (111) inside, which are used to limit the distance between the two planetary gears (30).

3. The differential cover (10) of claim 2, wherein, Each of the two limiting surfaces (111) is provided with a recess (112). The two recesses (112) are used to accommodate the two ends of the planetary gear shaft (20) and to allow the planetary gear shaft (20) and the two planetary gears (30) to move along the axial direction of the first half shaft (40).

4. The differential cover (10) of claim 3, wherein The dimension of the countersink (112) along the axis of the gear ring (11) is set to be greater than the radius of the planetary gear shaft (20) and less than the diameter of the planetary gear shaft (20).

5. The differential cover (10) of claim 2, wherein, The two limiting surfaces (111) are two parallel planes.

6. The differential cover (10) according to any one of claims 1 to 5, characterized in that The sealing plate (12) is provided with an annular protrusion (122), which is coaxially arranged with the shaft hole (121), and the annular protrusion (122) is provided with an oil hole (123).

7. The differential cover (10) according to any one of claims 1 to 5, characterized in that The sealing plate (12) is provided with at least two pairs of process holes (124) arranged around the shaft hole (121).

8. The differential cover (10) of any of claims 1-5, wherein, The gear ring (11) and the sealing plate (12) are integrally cast structures.

9. A differential, characterized in that, Includes the differential cover (10) as described in any one of claims 1-8.

10. The differential of claim 9 wherein, Also includes: Planetary gear shaft (20) is installed in the gear ring (11) of the differential cover (10); Two planetary gears (30) are fitted onto the planetary gear shaft (20); The first half-shaft (40) and the first half-shaft gear (50) are located inside the gear ring (11) and connected to the first half-shaft (40). The first half-shaft gear (50) meshes with the two planetary gears (30). The second half-shaft (60) and the second half-shaft gear (70) are arranged coaxially with the first half-shaft (40). The second half-shaft gear (70) is located outside the gear ring (11) and connected to the second half-shaft (60). The second half-shaft gear (70) meshes with the two planetary gears (30).

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