Gear differential and vehicle with same

Abstract

The gear differential mechanism comprises a shaft transmission gear, shaft transmission outer teeth are arranged on the periphery of the shaft transmission gear in the radial direction, the shaft transmission outer teeth are in transmission connection with a power input end, and the gear differential mechanism further comprises a planetary gear carrier, a planetary gear, a sun gear and a gear ring which are in transmission connection. The planetary gear carrier is arranged on the inner side of the shaft transmission gear, the planetary gear is connected to the inner side of the planetary gear carrier through a planetary pin shaft and eccentrically positioned on the radial outer side of the planetary gear carrier, outer meshing teeth are arranged on the radial periphery of the planetary gear, and the outer meshing teeth of the planetary gear are matched and meshed with the outer teeth of the sun gear and the inner teeth of the gear ring at the same time; the middle of the axis of the sun gear and the middle of the axis of the gear ring are fixedly connected with the left half shaft and the right half shaft. The gear differential mechanism has the advantages of being compact in structure, short in axial size and convenient to produce and machine.

Description

Technical Field

[0001] The utility model relates to the technical field related to differentials, in particular to a gear differential. Background Art

[0002] A differential is a mechanism that enables the left and right drive wheels or the front and rear drive wheels to rotate at different speeds. Most common differentials are bevel gear differentials, which include two planetary bevel gears and two or more axle gears connected to the drive shaft. These gears are arranged in an internal housing of the differential and mesh with each other. The planetary gears are connected to the differential housing through planetary shafts, which are perpendicular to the left and right axle shafts.

[0003] For example, a Chinese patent with application number CN201820825923.4 discloses an integrated structure of a driven bevel gear and a left differential housing. In the disclosed scheme, a first tapered roller bearing, a left differential housing, a driven bevel gear, a first half-shaft gear, a long planetary gear shaft, etc. are provided to cooperate to realize a differential transmission scheme, and a bevel gear is used for differential transmission. However, when this bevel gear is used for transmission, the axial dimension of the differential is large due to the perpendicular arrangement of the planetary shaft and the left and right half-shafts, and the production and processing of the bevel gear is also relatively complicated.

[0004] Therefore, when the differential in the prior art adopts the bevel gear solution, there are problems such as large axial size of the differential and complex production and processing of the bevel gear. Utility Model Content

[0005] The utility model aims to solve the problems of large axial dimension and complicated production and processing of bevel gears in the prior art bevel gear differential.

[0006] In order to solve the above technical problems, an embodiment of the utility model discloses a gear differential, including a shaft transmission gear, the shaft transmission gear is provided with shaft transmission external teeth along the outer periphery in the radial direction, the shaft transmission external teeth are transmission-connected to the power input end, and also includes a planetary gear carrier, planetary gears, and a sun gear and a ring gear that are transmission-connected.

[0007] The planetary gear carrier is arranged on the inner side of the shaft transmission gear, the planetary gears are connected to the inner side of the planetary gear carrier through planetary pins and are eccentrically positioned on the radial outer side of the planetary gear carrier, and the radial outer peripheries of the planetary gears are provided with external meshing teeth, and the external meshing teeth of the planetary gears are adapted to mesh with the external teeth of the sun gear and the internal teeth of the ring gear at the same time, and the sun gear and the ring gear are fixedly connected to the left half shaft and the right half shaft respectively at the center of the axis.

[0008] In the cross-sectional view taken along the axial direction of the gear differential, the sun gear, the ring gear, the planetary gear carrier and the shaft transmission gear are coaxially arranged, the planetary pin and the planetary gear are coaxially arranged, and the axis of the planetary pin is arranged parallel to the axis of the sun gear. In addition, the power input end is connected to the shaft transmission gear, the shaft transmission gear rotates synchronously with the planetary gear carrier, the planetary gear carrier is connected to the planetary gears, and the planetary gears are connected to the sun gear and the ring gear respectively.

[0009] By adopting the above technical solution, the utility model discloses a gear differential, specifically a cylindrical gear differential, in which no bevel gear is used, so the axial dimension of the differential is relatively short, and common cylindrical gears are used for meshing transmission, so the production and processing are relatively simple and convenient. By setting a planetary gear carrier, planetary gears, sun gear and ring gear connected in transmission, the structure is relatively compact, which helps to save space and makes it more flexible in the layout of the vehicle chassis.

[0010] Furthermore, the outer meshing teeth of the planetary gears are adapted to mesh with the outer teeth of the sun gear and the inner teeth of the ring gear. Due to the large contact area of ​​the tooth surface, it can withstand greater torque and load, so that the differential can maintain stable performance under harsh working conditions. The friction force is small during transmission, so the transmission efficiency is high, which can reduce energy consumption. The teeth are closely matched, so the vibration and noise are small during operation, which improves ride comfort and is also easy to disassemble and repair.

[0011] The embodiment of the utility model also discloses a gear differential, wherein the planetary gear includes two rows of gears arranged side by side in the axial direction thereof and forming an integral body, wherein the outer teeth of one row of gears mesh with the outer teeth of the sun gear, and the outer teeth of the other row of gears mesh with the inner teeth of the gear ring. The outer diameter of the row of gears meshing with the sun gear is smaller than the outer diameter of the other row of gears meshing with the gear ring; and the sun gear and the gear ring are both provided with splines in the middle of the axis center respectively adapted to connect with the left half shaft and the right half shaft.

[0012] By adopting the above technical solution, the planetary gear is provided with two rows of gears which can simultaneously mesh with the outer teeth of the sun gear and the inner teeth of the ring gear, thereby improving the transmission ratio, sharing the load, reducing the size and weight, and improving the transmission efficiency.

[0013] The embodiment of the utility model further discloses a gear differential, in which in a cross-sectional view taken along the axial direction of the gear differential, the planetary gear carrier includes a first connecting frame and a second connecting frame arranged on both sides of the planetary gear along the axial direction. Support members are also respectively arranged between the first connecting frame and the second connecting frame and the axial end surface of the planetary gear, and the support members include support washers or support bearings.

[0014] By adopting the above technical solution, providing a support gasket or a support bearing can ensure that the planetary gear will not interfere with the first connecting frame or the second connecting frame when rotating.

[0015] The embodiment of the utility model further discloses a gear differential, wherein the first connecting frame and the second connecting frame are fixedly connected together by welding or bolts, or the first connecting frame and the second connecting frame are integrally cast.

[0016] The embodiment of the utility model also discloses a gear differential, in which the planetary pin is fixedly connected to the planetary gear frame, the planetary gear and the planetary pin are supported by a clearance fit or by a needle bearing, and a lubricating oil channel hole is provided on the planetary pin.

[0017] By adopting the above technical solution, the planetary gears and the planetary pins are supported by clearance fit or by needle bearing fit, which makes assembly easier and more flexible, reduces friction and wear, and extends the service life of parts. It also has the advantages of compact structure and strong load capacity. The lubricating oil channel holes are provided to lubricate the planetary pins and planetary gears.

[0018] The embodiment of the utility model further discloses a gear differential. When looking toward the gear differential along the axial direction of the gear differential, at least three groups of planetary pins and planetary gears are arranged at intervals in the circumferential direction of the planetary gear carrier.

[0019] The embodiment of the utility model also discloses a gear differential, in which, in a cross-sectional view taken along the axial direction of the gear differential, a side of the planetary gear carrier away from the planetary gear in the radial direction is fixedly connected to the shaft transmission gear through a fastening member, and both the planetary gear carrier and the shaft transmission gear are provided with a positioning step portion on a side close to the fastening member, and the positioning step portions of the planetary gear carrier and the shaft transmission gear are adapted to abut against each other. Providing the positioning step portions to abut against each other can improve assembly accuracy and ensure that the planetary gear carrier and the shaft transmission gear are coaxially arranged.

[0020] The embodiment of the utility model also discloses a gear differential, in which in a cross-sectional view taken along the axial direction of the gear differential, the planetary gear carrier is axially limited by the shaft transmission gear and the ring gear. In addition, the side of the planetary gear carrier close to the ring gear is supported on the inner shaft shoulder of the ring gear through a bearing.

[0021] The embodiment of the utility model further discloses a gear differential, wherein a bushing or a bearing is arranged between the sun gear and the planetary gear carrier.

[0022] The embodiment of the utility model also discloses a vehicle, comprising any of the above-mentioned gear differentials, wherein the outer shoulder of one end of the planetary gear carrier of the gear differential is connected to the gearbox housing through a bearing, and the outer shoulder of the other end of the ring gear is connected to the gearbox housing through a bearing. In addition, the shaft transmission outer teeth of the shaft transmission gear are drivingly connected to the intermediate shaft of the gearbox, and the left half shaft and the right half shaft are respectively connected to the left wheel and the right wheel of the vehicle.

[0023] In summary, the utility model discloses a gear differential, in which bevel gears are not used, but cylindrical gears are used for meshing transmission, so the axial dimension of the differential is shorter, and the production and processing are simpler and more convenient. Furthermore, the outer meshing teeth of the planetary gears are adapted to mesh with the outer teeth of the sun gear and the inner teeth of the ring gear at the same time. Since the contact area of ​​the tooth surface is large, it can withstand greater torque and load, so that the differential can maintain stable performance under harsh working conditions. The friction force is small during transmission, so the transmission efficiency is high, which can reduce energy consumption, and the teeth are closely matched, so the vibration and noise are small during operation, which improves ride comfort, and is also easy to disassemble and repair. The structure is relatively compact, which helps to save space and makes it more flexible in the vehicle chassis layout. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 A cross-sectional view of the gear differential provided by an embodiment of the utility model taken along the axial direction;

[0025] Figure 2 A cross-sectional view taken along the axial direction of another embodiment of the gear differential provided by an embodiment of the utility model.

[0026] Description of reference numerals:

[0027] 1. Gear differential; 2. Shaft drive gear; 3. Shaft drive external gear; 4. Planetary gear carrier; 5. Planetary gear; 6. Sun gear; 7. Ring gear; 8. Planetary pin; 9. External meshing teeth; 10. External teeth; 11. Internal teeth; 12. Spline; 13. First connecting frame; 14. Second connecting frame; 15. Support member; 16. Lubricating oil channel hole; 17. Fastening member; 18. Positioning step; 19. Bearing; 20. Inner shoulder of ring gear; 21. Axis centerline of sun gear; 22. Axis centerline of planetary pin. DETAILED DESCRIPTION

[0028] Bevel gear differential is a transmission device widely used in engineering machinery, ships, generator sets and other fields. Its structure is mainly composed of differential housing, planet carrier, sun gear, planetary gear, mandrel, bevel gear and so on. The working principle of bevel gear differential is mainly to use the meshing relationship between planetary gear and sun gear, inner ring gear and outer ring gear to realize the differential transmission of different shafts. However, due to the constraints of design transmission, bevel gear differential adopts bevel gear transmission. Affected by the radial size of bevel gear, bevel gear differential has the problem of large axial size; bevel gear manufacturing process requirements are high, processing cost is high, and bevel gear differential also has the problem of high installation difficulty. Therefore, bevel gear differential has the problem of large axial size and complex production and processing of bevel gear.

[0029] Therefore, the present application provides a gear differential that no longer uses bevel gears for transmission design, but uses cylindrical gears, so that the axial size of the gear differential is shortened, the structure is more compact, and the cost is lower.

[0030] In order to solve the above technical problems, the implementation method of this embodiment discloses a gear differential. First, see Figure 1 The gear differential 1 disclosed in this embodiment includes a shaft transmission gear 2 arranged at the outermost side, and the shaft transmission gear 2 is provided with shaft transmission external teeth 3 along the outer periphery in the radial direction, and the shaft transmission external teeth 3 are transmission-connected with the power input end (not shown in the figure), and also includes a planetary gear carrier 4, planetary gears 5, and a sun gear 6 and a ring gear 7 which are transmission-connected in the shaft transmission gear 2. It should be noted that the input end of the gear differential 1 disclosed in this embodiment is the shaft transmission gear 2, that is, the shaft transmission external teeth 3 of the shaft transmission gear 2 of the gear differential 1 disclosed in this embodiment are transmission-connected with the power input end. For example, in one of the specific use scenarios, when the gear differential 1 is installed in a transmission for use, the power input end is the intermediate shaft of the gearbox, and the intermediate shaft of the gearbox and the shaft transmission gear 2 are transmission-engaged to transmit power to the gear differential 1 disclosed in this embodiment, and the power and differential distribution are performed through the gear differential 1.

[0031] Next, continue to see Figure 1 , the planetary gear carrier 4, the planetary gear 5, the sun gear 6, the ring gear 7 and other structures in the gear differential 1 disclosed in this embodiment are described:

[0032] Figure 1It is a cross-sectional view of the gear differential 1 disclosed in this embodiment taken along the axial direction, wherein the planetary gear carrier 4 is arranged on the inner side of the shaft transmission gear 2, the planetary gear 5 is connected to the inner side of the planetary gear carrier 4 through the planetary pin 8 and is eccentrically positioned on the radial outer side of the planetary gear carrier 4, and the radial outer periphery of the planetary gear 5 is provided with external meshing teeth 9, and the external meshing teeth 9 of the planetary gear 5 are simultaneously adapted to mesh with the external teeth 10 of the sun gear 6 and the internal teeth 11 of the ring gear 7, and the sun gear 6 and the ring gear 7 are fixedly connected to the left half shaft (not shown in the figure) and the right half shaft (not shown in the figure) at the center of the axis respectively. It should be noted that the eccentric positioning of the planetary gear 5 on the radially outer side of the planetary gear carrier 4 through the planetary pin 8 means that the planetary gear 5 is located on the outer side relative to the axis (rotation center) of the planetary gear carrier 4, and because the external meshing teeth 9 of the planetary gear 5 are respectively adapted to mesh with the external teeth 10 of the sun gear 6 and the internal teeth 11 of the ring gear 7, the external teeth 10 of the sun gear 6 and the internal teeth 11 of the ring gear 7 have different diameters and different numbers of teeth, so the meshing speed ratios of the planetary gear 5 and the sun gear 6, and the meshing speed ratios of the planetary gear 5 and the ring gear 7 are also different, thereby realizing differential power distribution.

[0033] See also Figure 1 , in the cross-sectional view taken along the axial direction of the gear differential 1, the sun gear 6, the ring gear 7, the planetary gear carrier 4 and the shaft transmission gear 2 are coaxially arranged, that is, the axis centers of the sun gear 6, the ring gear 7, the planetary gear carrier 4 and the shaft transmission gear 2 coincide with each other, the planetary pin 8 and the planetary gear 5 are coaxially arranged, the axis centers of the planetary pin 8 and the planetary gear 5 coincide with each other, the axis center line 22 of the planetary pin 8 is arranged parallel to the axis center line 21 of the sun gear 6, and the axis center line 22 of the planetary pin 8 and the axis center line 21 of the sun gear 6 are as shown in FIG. Figure 1 In addition, the power input end is connected to the shaft transmission gear 2, the shaft transmission gear 2 rotates synchronously with the planetary gear carrier 4, the planetary gear carrier 4 is pivotally connected to the planetary gear 5, and the planetary gear 5 is connected to the sun gear 6 and the ring gear 7 respectively.

[0034] With the above structural design, the present embodiment discloses a gear differential, specifically a cylindrical gear differential, in which no bevel gear is used, so the axial dimension of the differential is short, and common cylindrical gears are used for meshing transmission, so the production and processing are relatively simple and convenient. By providing a planetary gear carrier 4, planetary gears 5, sun gear 6 and ring gear 7 connected in transmission, the structure is relatively compact, which helps to save space and makes it more flexible in the vehicle chassis layout.

[0035] Furthermore, the outer meshing teeth 9 of the planetary gear 5 are adapted to mesh with the outer teeth 10 of the sun gear 6 and the inner teeth 11 of the ring gear 7. Since the contact area of ​​the tooth surface is large, it can withstand greater torque and load, so that the differential can maintain stable performance under harsh working conditions. The friction force is small during transmission, so the transmission efficiency is high, which can reduce energy consumption. The teeth are closely matched, so the vibration and noise are small during operation, which improves the ride comfort and is also easy to disassemble and repair.

[0036] Next, the power transmission path of the gear differential 1 disclosed in this embodiment is briefly described:

[0037] See also Figure 1 , the shaft transmission outer teeth 3 are transmission connected with the power input end, the external power input end transmits the power to the shaft transmission gear 2, the shaft transmission gear 2 transmits the power to the planetary gear carrier 4, the planetary gear carrier 4 will drive the planetary gears 5 arranged thereon to rotate and transmit the power to the planetary gears 5, the planetary gears 5 transmit the power to the sun gear 6 and the ring gear 7 respectively, and because the gear ratios of the planetary gears 5, the sun gear 6 and the ring gear 7 are different, the power and speed ratios transmitted by the planetary gear 5 to the sun gear 6 and the ring gear 7 are not the same, thereby realizing power differential distribution, the sun gear 6 and the ring gear 7 are respectively connected to the left half shaft and the right half shaft, and finally the power is output to the wheels.

[0038] It should be noted that the specific structure of the planetary gear 5 can be designed and selected according to actual needs. For example, this application discloses two different structures of the planetary gear 5. Figure 1 and Figure 2 Only different arrangements and implementations of the planetary gear 5 in two different embodiments are shown. Figure 1 In the implementation mode, two rows of gears are arranged on the planetary gear 5. Figure 2 In the implementation of the embodiment, a whole row of gears is arranged on the planetary gear 5, but the diameters of the outer teeth 10 of the sun gear 6 and the inner teeth 11 of the ring gear 7 (in this embodiment, the outer teeth 10 and the inner teeth 11 are Figure 2 The dashed box in the middle is different. Next, Figure 1 The following examples are used to illustrate:

[0039] See also Figure 1In the gear differential 1 disclosed in this embodiment, the planetary gear 5 includes two rows of gears arranged side by side in the axial direction thereof and formed into one body, wherein the outer teeth 10 of one row of gears mesh with the outer teeth 10 of the sun gear 6, and the outer teeth 10 of the other row of gears mesh with the inner teeth 11 of the ring gear 7. The outer diameter of the row of gears meshing with the sun gear 6 is smaller than the outer diameter of the other row of gears meshing with the ring gear 7; and the sun gear 6 and the ring gear 7 are provided at the central part of the axis with splines 12 respectively adapted to connect with the left half shaft and the right half shaft. It should be noted that the parts of the left half shaft and the right half shaft connected with the sun gear 6 and the ring gear 7 are also provided with splines 12. For example, in one implementation, the sun gear 6 is fixedly connected to the left half shaft through the splines 12, and the ring gear 7 is fixedly connected to the right half shaft through the splines 12 structure. With this structural design, the planetary gear 5 is provided with two rows of gears which can simultaneously mesh with the outer teeth 10 of the sun gear 6 and the inner teeth 11 of the ring gear 7, thereby improving the transmission ratio, sharing the load, reducing the size and weight, and improving the transmission efficiency.

[0040] Next, Figure 2 The embodiments in the following are explained, and it should be understood that Figure 2 The embodiments shown and Figure 1 The only difference is the structure of planetary gear 5:

[0041] See also Figure 2 ,exist Figure 2 In the embodiment shown, the outer wall portion (external meshing teeth) of the planetary gear 5 is an integral body, and the outer diameters of the planetary gears 5 are the same, but the outer teeth 10 ( Figure 2 The outer side of the sun gear 6 is shown by the dotted line) close to the planetary gear 5 and meshes with the planetary gear 5. The inner teeth 11 ( Figure 2 The outer teeth 10 of the planetary gears 5 (as shown by the dotted line on the inner side of the middle gear ring 7) are close to and mesh with each other, which also ensures that the gear ratio and speed ratio of the planetary gears 5 are different from those of the sun gear 6 and the gear ring 7, thereby achieving differential speed distribution.

[0042] Furthermore, in the gear differential 1 disclosed in the present embodiment, in a cross-sectional view taken along the axial direction of the gear differential 1, the planetary gear carrier 4 includes a first connecting frame 13 and a second connecting frame 14 arranged along the axial direction on both sides of the planetary gear 5. Support members 15 are also respectively arranged between the first connecting frame 13 and the second connecting frame 14 and the axial end faces of the planetary gear 5, and the support member 15 includes a support gasket or a support bearing.

[0043] With the above-mentioned structure, the support gasket or the support bearing can ensure that the planetary gear 5 does not interfere with the first connecting frame 13 or the second connecting frame 14 when rotating. It is not difficult for those skilled in the art to understand that the first connecting frame 13 and the second connecting frame 14 can be integrally formed by casting, or can be fixedly connected by welding, screwing, etc., and the support member 15 can also be set as other members, such as washers, etc., which are not specifically limited in this embodiment.

[0044] In one preferred implementation manner of the present embodiment, the first connecting frame 13 and the second connecting frame 14 are fixedly connected together by welding or bolts, or the first connecting frame 13 and the second connecting frame 14 are integrally cast.

[0045] In another preferred implementation manner disclosed in this embodiment, the planetary pin 8 is fixedly connected to the planetary gear carrier 4, the planetary gear 5 and the planetary pin 8 are supported by a clearance fit or by a needle bearing fit, and a lubricating oil channel hole 16 is provided on the planetary pin 8.

[0046] With this structural design, the planetary gear 5 and the planetary pin 8 are supported by clearance fit or by needle bearing fit, making assembly easier and more flexible, reducing friction and wear, and extending the service life of parts. It also has the advantages of compact structure and strong load capacity. The lubricating oil channel hole 16 is provided to lubricate the planetary pin 8 and the planetary gear 5. The design of the planetary pin 8 enables the planetary gear 5 to revolve relative to the planetary gear carrier 4 and also rotate around the planetary pin 8.

[0047] The implementation manner of the present embodiment also discloses a gear differential. When looking toward the gear differential 1 along the axial direction of the gear differential 1, at least three groups of planetary pins 8 and planetary gears 5 are arranged at intervals in the circumferential direction of the planetary gear carrier 4. For example, three, four or even more groups of planetary pins 8 and planetary gears 5 can be arranged in the axial direction of the planetary gear carrier 4. However, in one of the preferred embodiments, three groups of planetary pins 8 and planetary gears 5 are arranged and are evenly and spaced apart around the circumferential direction of the planetary gear carrier 4.

[0048] In one of the preferred implementations disclosed in this embodiment, please refer to Figure 1 or Figure 2In the cross-sectional view taken along the axial direction of the gear differential 1, the planetary gear carrier 4 is fixedly connected to the shaft transmission gear 2 by a fastening member 17 on the side away from the planetary gear 5 in the radial direction, and the planetary gear carrier 4 and the shaft transmission gear 2 are both provided with a positioning step 18 on the side close to the fastening member 17, and the positioning step 18 of the planetary gear carrier 4 and the shaft transmission gear 2 are mutually adapted and abutted. Providing the positioning step 18 to abut against each other can improve the assembly accuracy and ensure that the planetary gear carrier 4 and the shaft transmission gear 2 are coaxially arranged, and the fastening member 17 can be a common bolt, screw, nut or other member.

[0049] See also Figure 1 In the cross-sectional view taken along the axial direction of the gear differential 1, the planetary gear carrier 4 is axially limited by the shaft transmission gear 2 and the ring gear 7. In addition, the side of the planetary gear carrier 4 close to the ring gear 7 is supported on the inner shoulder 20 of the ring gear 7 through the bearing 19.

[0050] In another preferred implementation manner disclosed in this embodiment, axial and radial bushings or bearings (not shown in the figure) are arranged between the sun gear 6 and the planetary gear carrier 4. The axial and radial bushings or bearings are arranged between the sun gear 6 and the planetary gear carrier 4 to avoid interference between the sun gear 6 and the planetary gear carrier 4 during rotation.

[0051] The implementation of this embodiment also discloses a vehicle, comprising any of the above-mentioned gear differentials 1, wherein the outer shoulder of one end of the planetary gear carrier 4 of the gear differential 1 is connected to the gearbox housing through a bearing 19, and the outer shoulder of the other end of the ring gear 7 is connected to the gearbox housing through a bearing 19. In addition, the shaft transmission outer teeth 3 of the shaft transmission gear 2 are drivingly connected to the intermediate shaft of the gearbox, and the left half shaft and the right half shaft are respectively connected to the left wheel and the right wheel of the vehicle.

[0052] In summary, the utility model discloses a gear differential, in which cylindrical gear meshing transmission is used instead of bevel gears, so the axial dimension of the differential is shorter, and the production and processing is simpler and more convenient. Furthermore, the outer meshing teeth 9 of the planetary gear 5 are adapted to mesh with the outer teeth 10 of the sun gear 6 and the inner teeth 11 of the ring gear 7 at the same time. Since the contact area of ​​the tooth surface is large, it can withstand greater torque and load, so that the differential can maintain stable performance under harsh working conditions. The friction force is small during transmission, so the transmission efficiency is high, which can reduce energy consumption. The teeth are closely matched, so the vibration and noise are small during operation, which improves the ride comfort, and is also easy to disassemble and repair. The structure is relatively compact, which helps to save space and makes it more flexible in the vehicle chassis layout.

[0053] Next, the use and installation method of the gear differential 1 disclosed in this embodiment installed in the gearbox and the power transmission path are briefly described:

[0054] First, the gear differential 1 disclosed in this embodiment is installed in a gearbox housing for use. The outer shoulder of one end of the planetary gear carrier 4 is connected to the gearbox housing through a bearing 19, and the outer shoulder of the other end of the ring gear 7 is connected to the gearbox housing through a bearing 19. Figure 2 As shown, that is to say, the shoulders on both sides of the axial direction of the gear differential 1 are supported in the gearbox housing through bearings 19, and the ring gear 7 is fixedly connected to the right half shaft (or left half shaft) through the spline 12, and the sun gear 6 is fixedly connected to the left half shaft (or right half shaft) through the spline 12, and the intermediate shaft of the gearbox is in transmission meshing with the shaft transmission gear 2.

[0055] Furthermore, the intermediate shaft transmits power to the shaft transmission gear 2, the shaft transmission gear 2 transmits power to the planetary gear carrier 4, the planetary gear carrier 4 drives the planetary gears 5 arranged thereon to rotate and transmit power to the planetary gears 5, the planetary gears 5 transmit power to the sun gear 6 and the ring gear 7 respectively, and because the gear ratios of the planetary gears 5, the sun gear 6 and the ring gear 7 are different, the power and speed ratios transmitted by the planetary gear 5 to the sun gear 6 and the ring gear 7 are not the same, thereby realizing power differential distribution, and the sun gear 6 and the ring gear 7 are respectively connected to the left half shaft and the right half shaft, and finally the power is output to the wheels.

[0056] It should be noted that, in addition to the implementation methods of the utility model described in the above-mentioned specific specific embodiments, those skilled in the art can easily understand other advantages and functions of the utility model from the contents disclosed in this specification. Although the description of the utility model will be introduced in conjunction with the preferred embodiment, this does not mean that the features of this utility model are limited to this implementation method. On the contrary, the purpose of introducing the utility model in conjunction with the implementation method is to cover other options or modifications that may be extended based on the claims of the utility model. In order to provide an in-depth understanding of the utility model, the above description contains many specific details, and the utility model can also be implemented without using these details. In addition, in order to avoid confusion or blurring the focus of the utility model, some specific details will be omitted in the description. It should be noted that, in the absence of conflict, the embodiments in the utility model and the features in the embodiments can be combined with each other.

[0057] It should be noted that in this specification, similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, it does not need to be further defined and explained in the subsequent drawings.

[0058] In the description of this embodiment, it should be noted that the terms "upper", "lower", "inner", "bottom", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, or are the orientations or positional relationships in which the utility model product is usually placed when in use. They are only for the convenience of describing the utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the utility model.

[0059] The terms “first”, “second”, etc. are only used for distinguishing descriptions and should not be understood as indicating or implying relative importance.

[0060] In the description of this embodiment, it is also necessary to explain that, unless otherwise clearly specified and limited, the terms "set", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in this embodiment can be understood according to specific circumstances.

[0061] Although the present invention has been illustrated and described with reference to certain preferred embodiments of the present invention, it should be understood by those skilled in the art that the above contents are further detailed descriptions of the present invention in combination with specific embodiments, and it cannot be determined that the specific implementation of the present invention is limited to these descriptions. Those skilled in the art may make various changes in form and details, including making several simple deductions or substitutions, without departing from the spirit and scope of the present invention.

Claims

1. A gear differential, comprising a shaft transmission gear, wherein the shaft transmission gear is provided with shaft transmission external teeth along the outer periphery in the radial direction, and the shaft transmission external teeth are transmission-connected to the power input end, characterized in that: Also includes: The planetary gear carrier, planetary gears, sun gear and ring gear connected in driving manner; in The planetary gear carrier is arranged on the inner side of the shaft transmission gear, the planetary gears are connected to the inner side of the planetary gear carrier through planetary pins and are eccentrically positioned on the radial outer side of the planetary gear carrier, the radial outer periphery of the planetary gears is provided with external meshing teeth, the external meshing teeth of the planetary gears are adapted to mesh with the external teeth of the sun gear and the internal teeth of the gear ring at the same time, and the sun gear and the gear ring are fixedly connected to the left half shaft and the right half shaft respectively at the center of the axis; and In a cross-sectional view taken along the axial direction of the gear differential, the sun gear, the ring gear, the planetary gear carrier and the shaft transmission gear are coaxially arranged, the planetary pins and the planetary gears are coaxially arranged, and the axis of the planetary pins is arranged parallel to the axis of the sun gear; and The power input end is transmission-connected with the shaft transmission gear, the shaft transmission gear rotates synchronously with the planetary gear carrier, the planetary gear carrier is transmission-connected with the planetary gears, and the planetary gears are transmission-connected with the sun gear and the ring gear respectively.

2. The gear differential according to claim 1, characterized in that: The planetary gear comprises two rows of gears arranged side by side in the axial direction thereof and forming an integral body, wherein the external teeth of one row of gears mesh with the external teeth of the sun gear, and the external teeth of the other row of gears mesh with the internal teeth of the ring gear; wherein the outer diameter of the one row of gears meshing with the sun gear is smaller than the outer diameter of the other row of gears meshing with the ring gear; and The central parts of the axes of the sun gear and the ring gear are provided with splines which are respectively adapted to be connected with the left half shaft and the right half shaft.

3. The gear differential according to claim 1, characterized in that: In a cross-sectional view taken along the axial direction of the gear differential, the planetary gear carrier includes a first connecting frame and a second connecting frame arranged on both sides of the planetary gear along the axial direction; wherein Support components are respectively provided between the first connecting frame, the second connecting frame and the axial end surface of the planetary gear, and the support components include support washers or support bearings.

4. The gear differential according to claim 3, characterized in that: in The first connecting frame and the second connecting frame are fixedly connected together by welding or bolts; or The first connecting frame and the second connecting frame are integrally cast.

5. The gear differential according to claim 1, characterized in that: The planetary pin is fixedly connected to the planetary gear carrier, and the planetary gear and the planetary pin are supported by clearance fit / or by needle bearing fit; and The planetary pin shaft is provided with a lubricating oil channel hole.

6. The gear differential according to claim 1, characterized in that: When looking toward the gear differential along the axial direction of the gear differential, at least three groups of planetary pins and planetary gears are arranged at intervals in the circumferential direction of the planetary gear carrier.

7. The gear differential according to claim 1, characterized in that: In a cross-sectional view taken along the axial direction of the gear differential, a side of the planetary gear carrier away from the planetary gears in the radial direction is fixedly connected to the shaft transmission gear via a fastening member; and The planetary gear carrier and the shaft transmission gear are both provided with positioning step portions on one side close to the fastening member, and the positioning step portions of the planetary gear carrier and the shaft transmission gear are adapted to abut against each other.

8. The gear differential according to claim 1, characterized in that: In a cross-sectional view taken along the axial direction of the gear differential, the planetary gear carrier is axially limited by the shaft transmission gear and the ring gear; and The side of the planetary gear carrier close to the gear ring is supported on the inner shoulder of the gear ring through a bearing.

9. The gear differential according to claim 1, characterized in that: A bushing or a bearing is arranged between the sun gear and the planetary gear carrier.

10. A vehicle, characterized in that: A gear differential comprising the gear differential according to any one of claims 1 to 9, wherein the outer shoulder of one end of the planetary gear carrier of the gear differential is connected to the gearbox housing through a bearing, and the outer shoulder of the other end of the ring gear is connected to the gearbox housing through a bearing; and The shaft transmission outer teeth of the shaft transmission gear are drivingly connected to the intermediate shaft of the gearbox, and the left half shaft and the right half shaft are respectively connected to the left wheel and the right wheel of the vehicle.

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