Planet wheel type differential mechanism assembly for double-motor assembly

Abstract

The planet wheel type differential mechanism assembly comprises an output gear, a differential mechanism right shell and a differential mechanism left shell are arranged on the two sides of the output gear respectively, bolts are arranged between the differential mechanism right shell and the output gear and between the differential mechanism left shell and the output gear, and the differential mechanism right shell and the differential mechanism left shell are fixed through the bolts. And a mounting cavity is formed after fixed connection. Due to the fact that the planet row adopts the mode that a plurality of gear pairs of cylindrical gears are meshed at the same time, the occupation of the planet wheel type differential mechanism on the inner axial space of the shell is only limited to the length of a long planet wheel, and due to the fact that the gear pairs are meshed at the same time, under the same input torque, the load borne by each gear pair is greatly reduced, and the service life of the planet wheel type differential mechanism is prolonged. The axial size of the planet wheel type differential mechanism assembly is greatly reduced compared with a traditional cone type differential mechanism assembly, the structure of the planet wheel type differential mechanism is more compact, and light weight of the structure is facilitated.

Description

Technical Field

[0001] The utility model relates to the technical field of star-wheel differential assemblies, and more specifically to a planetary-wheel differential assembly for a dual-motor assembly. Background Art

[0002] The differential assembly is an important component in the vehicle drive system. Its function is to enable the wheels to rotate independently, thereby ensuring the stability and smoothness of the vehicle during driving. Whether in fuel vehicles or new energy electric vehicles, it is the differential assembly that transmits power to the wheel half shafts to drive the vehicle. With the development of the new energy vehicle industry, under the trend of increasing sales of electric vehicles, the lightweight of electric vehicles has become more and more emphasized;

[0003] The traditional bevel gear differential has a large axial dimension, resulting in a relatively large overall volume and mass of the corresponding drive assembly, which is not conducive to the layout of the vehicle power system and meeting the lightweight trend. Therefore, a new technical solution is needed to solve this problem. Summary of the Utility Model

[0004] The purpose of the utility model is to provide a planetary-wheel differential assembly for a dual-motor assembly, which solves the problem that the traditional bevel gear differential has a large axial dimension, resulting in a relatively large overall volume and mass of the corresponding drive assembly, which is not conducive to the layout of the vehicle power system and meeting the lightweight trend.

[0005] To achieve the above purpose, the utility model provides the following technical solution: A planetary-wheel differential assembly for a dual-motor assembly, comprising: an output gear, with a differential right housing and a differential left housing respectively arranged on both sides of the output gear. Bolts are arranged between the differential right housing and the differential left housing and the output gear and fixed by the bolts. After the fixed connection, an installation cavity is formed. Installation holes are arranged at the centers and inside of the differential right housing and the differential left housing. A large sun gear and a small sun gear are arranged in the installation holes at the centers. A short planetary gear is arranged outside the small sun gear and a long planetary gear is arranged outside the large sun gear. The short planetary gear meshes with the long planetary gear, and the long planetary gear also meshes with the large sun gear. The large sun gear and the small sun gear are axially and radially positioned by the differential right housing and the differential left housing respectively. A planetary pin is arranged inside the long planetary gear and the short planetary gear. The long planetary gear and the short planetary gear are installed on the differential right housing and the differential left housing through the planetary pin. Clamping plates are arranged on both sides of the differential right housing and the differential left housing. The planetary pin is axially and circumferentially limited by the clamping plates.

[0006] As a preferred embodiment of the present utility model, a plurality of groups of rivets are provided inside the clamping plate and are respectively riveted to the right differential housing and the left differential housing through the plurality of groups of rivets.

[0007] As a preferred embodiment of the present utility model, an annular step and a counterbore are designed on the clamping plate.

[0008] As a preferred embodiment of the present utility model, a plurality of groups of first radially penetrating oil grooves are provided at the edge of the central hole of the large sun gear.

[0009] As a preferred embodiment of the present utility model, a plurality of groups of second radially penetrating oil grooves are provided at the edge of the central hole of the small sun gear.

[0010] As a preferred embodiment of the present utility model, a plurality of groups of third radially penetrating oil grooves are provided at the edge of the central hole of the right differential housing, and a plurality of groups of first relief holes are provided inside the right differential housing.

[0011] As a preferred embodiment of the present utility model, a plurality of groups of fourth radially penetrating oil grooves are provided at the edge of the central hole of the left differential housing, and a plurality of groups of second relief holes are provided inside the left differential housing.

[0012] As a preferred embodiment of the present utility model, an axially penetrating oil hole and radially penetrating oil holes distributed along the axis are provided at the center of the planet pin, and the center of the radially penetrating oil hole is along the meshing center line direction of the planet gear and the sun gear.

[0013] As a preferred embodiment of the present utility model, an arc-shaped step is provided on the end face of the planet pin and a contact mating surface is provided on the surface.

[0014] As a preferred embodiment of the present utility model, an oil storage cavity is formed among the output gear, the right differential housing, the left differential housing and the clamping plate.

[0015] Compared with the prior art, the beneficial effects of the present utility model are as follows:

[0016] The utility model uses the output gear as the power driving source, and then adopts the form of meshing transmission between the short planet gear and the long planet gear to drive and connect the large and small sun gears on the left and right sides. When there is no rotational speed difference between the left and right wheels of the vehicle, the long and short sun gears do not rotate around their respective planet pin shafts, and the planet mounting seat drives the left and right half shafts to rotate synchronously; when there is a rotational speed difference between the left and right wheels of the vehicle, the large and small sun gears on the left and right sides mean having different rotational speeds. Through the self-rotation of the long and short planet gears around their respective planet pins, the differential rotation between the left and right half shafts is realized; at the same time, since the planetary gear set adopts the form of multiple pairs of gear pairs of cylindrical gears meshing simultaneously, the occupation of the axial space inside the housing by the planetary gear differential is only limited to the length of the long planet gear. And because there are multiple pairs of gear pairs meshing simultaneously, under the same input torque, the load borne by each pair of gear pairs is greatly reduced, which makes the axial dimension of the planetary gear differential assembly much smaller than that of the traditional conical differential assembly, making the structure of the planetary gear differential more compact and conducive to the lightweight of the structure. Brief Description of the Drawings

[0017] Figure 1 is a schematic exploded view of the planetary gear differential assembly of the utility model;

[0018] Figure 2 is a schematic front view structure diagram of the planetary gear differential assembly of the utility model;

[0019] Figure 3 of the utility model Figure 2 is a schematic sectional view of structure A-A;

[0020] Figure 4 is a schematic diagram of the large sun gear and lubrication characteristics structure of the utility model;

[0021] Figure 5 is a schematic diagram of the small sun gear and lubrication characteristics structure of the utility model;

[0022] Figure 6 is a schematic diagram of the right housing of the differential of the utility model and related lubrication characteristics and lightening hole structure;

[0023] Figure 7 is a schematic diagram of the left housing of the differential of the utility model and related lubrication characteristics and lightening hole structure;

[0024] Figure 8 is a schematic diagram of the planet pin and lubrication characteristics structure of the utility model;

[0025] Figure 9 is a schematic diagram of the clamping plate and step structure of the utility model;

[0026] Figure 10 is a schematic diagram of the clamping plate and sunk groove structure of the utility model;

[0027] Figure 11 This is a schematic diagram of the semi-closed oil storage tank structure of the planetary gear differential assembly of the present utility model.

[0028] In the figure: 1. Output gear; 2. Right housing of the differential; 3. Left housing of the differential; 4. Planet pin; 5. Short planet gear; 6. Large sun gear; 7. Small sun gear; 8. Long planet gear; 9. Clamping plate; 10. Bolt; 11. Rivet; 12. Oil storage cavity; 13. First radially penetrating oil groove; 14. Second radially penetrating oil groove; 15. Third radially penetrating oil groove; 16. First relief hole; 17. Second relief hole; 18. Fourth radially penetrating oil groove; 19. Axially penetrating oil hole; 20. Radially penetrating oil hole; 21. Arc-shaped step; 22. Contact mating surface; 23. Ring-shaped step; 24. Sunk groove. Specific embodiments

[0029] Next, the technical solutions in the embodiments of the present utility model will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are only a part of the embodiments of the present utility model, rather than all of the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present utility model without creative efforts shall fall within the protection scope of the present utility model.

[0030] Please refer to Figure 1-11, the present utility model provides a technical solution: a planetary differential assembly for a dual-motor assembly, comprising: an output gear 1, with a differential right housing 2 and a differential left housing 3 respectively arranged on both sides of the output gear 1. Bolts 10 are arranged between the differential right housing 2 and the differential left housing 3 and are fixed through the bolts 10 to form an installation cavity after being fixedly connected. Installation holes are provided at the center and inside of the differential right housing 2 and the differential left housing 3. A large sun gear 6 and a small sun gear 7 are arranged in the installation hole at the center. A short planet gear 5 is arranged outside the small sun gear 7 and a long planet gear 8 is arranged outside the large sun gear 6. The short planet gear 5 meshes with the long planet gear 8, and the long planet gear 8 meshes with the large sun gear 6 at the same time. The large sun gear 6 and the small sun gear 7 are axially and radially positioned through the differential right housing 2 and the differential left housing 3 respectively. A planet pin 4 is arranged inside the long planet gear 8 and the short planet gear 5. The long planet gear 8 and the short planet gear 5 are installed on the differential right housing 2 and the differential left housing 3 through the planet pin 4. Clamping plates 9 are arranged on both sides of the differential right housing 2 and the differential left housing 3. The planet pin 4 is axially and circumferentially limited through the clamping plates 9. Taking the output gear 1 as a power driving source, and then adopting the form of meshing transmission between the short planet gear 5 and the long planet gear 8 to drive and connect the large and small sun gears 7 on the left and right sides. When there is no rotational speed difference between the left and right wheels of the vehicle, the long and short sun gears do not rotate around their respective planet pin 4 axes, and the planet mounting seat drives the left and right half shafts to rotate synchronously; when there is a rotational speed difference between the left and right wheels of the vehicle, the large and small sun gears 7 on the left and right sides mean having different rotational speeds. Through the self-rotation of the long and short planet gears 5 around their respective planet pins 4 themselves, the differential rotation between the left and right half shafts is realized; at the same time, since the planetary gear set adopts the form of multiple pairs of gear pairs of cylindrical gears meshing at the same time, the occupation of the axial space inside the housing by the planetary differential is only limited to the length of the long planet gear 8. And because there are multiple pairs of gear pairs meshing at the same time, under the same input torque, the load borne by each pair of gear pairs is greatly reduced, which makes the axial dimension of the planetary differential assembly much smaller than that of the traditional conical differential assembly, making the structure of the planetary differential more compact and conducive to the lightweight of the structure.

[0031] Further improved, as Figure 1 shown: A number of groups of rivets 11 are arranged inside the clamping plates 9 and are respectively riveted to the differential right housing 2 and the differential left housing 3 through the number of groups of rivets 11. The use of the rivet 11 structure for fixation ensures the stability of the installation.

[0032] Further improved, as Figure 9 , 10As shown: An annular step 23 and a counterbore 24 are designed on the clamping plate 9. The annular step 23 cooperates with the end shoulder of the planetary pin 4 to limit the circumferential rotation of the planetary pin 4, and the counterbore 24 is used to hide the head of the rivet 11.

[0033] Further improved, as Figure 4 As shown: A number of groups of first radially penetrating oil grooves 13 are provided at the edge of the central hole of the large sun gear 6. The radially penetrating oil grooves can ensure that lubricating oil or coolant is evenly and quickly distributed to the key friction surfaces of the gear, reducing wear caused by insufficient local lubrication.

[0034] Further improved, as Figure 5 As shown: A number of groups of second radially penetrating oil grooves 14 are provided at the edge of the central hole of the small sun gear 7. The radially penetrating oil grooves can ensure that lubricating oil or coolant is evenly and quickly distributed to the key friction surfaces of the gear, reducing wear caused by insufficient local lubrication.

[0035] Further improved, as Figure 6 As shown: A number of groups of third radially penetrating oil grooves 15 are provided at the edge of the central hole of the right differential housing 2. A number of groups of first lightening holes 16 are provided inside the right differential housing 2. The radially penetrating oil grooves can ensure that lubricating oil or coolant is evenly and quickly distributed to the key friction surfaces of the gear, reducing wear caused by insufficient local lubrication. The setting of the lightening holes realizes weight reduction.

[0036] Further improved, as Figure 7 As shown: A number of groups of fourth radially penetrating oil grooves 18 are provided at the edge of the central hole of the left differential housing 3. A number of groups of second lightening holes 17 are provided inside the left differential housing 3. The radially penetrating oil grooves can ensure that lubricating oil or coolant is evenly and quickly distributed to the key friction surfaces of the gear, reducing wear caused by insufficient local lubrication. The setting of the lightening holes realizes weight reduction.

[0037] Further improved, as Figure 8 As shown: An axially penetrating oil hole 19 and radially penetrating oil holes 20 distributed along the axis are provided in the center of the planetary pin 4. The centers of the radially penetrating oil holes 20 are along the meshing center line direction of the planet gear and the sun gear. The lubricating oil in the oil storage cavity 12 can flow to the radially penetrating oil holes 20 through the axially penetrating oil hole 19. When the short planet gear 5 and the long planet gear 8 rotate relative to the planetary pin 4, the contact mating surface 22 can be lubricated and cooled.

[0038] Further improved, as Figure 8 As shown: An arc-shaped step 21 is provided on the end face of the planetary pin 4 and a contact mating surface 22 is provided on the surface. The arc-shaped step 21 cooperates with the annular step 23 to limit the circumferential rotation of the planetary pin 4.

[0039] Further improved, such as Figure 11 As shown: An oil storage cavity 12 is formed between the output gear 1, the right differential housing 2, the left differential housing 3 and the clamping plate 9. During the rotation of the differential assembly, all gear meshing points can be cooled and lubricated.

[0040] Working principle: The overall of the output gear 1 and the left differential housing 3 and the right differential housing 2 fixedly connected thereto by bolts 10 is used as the power input. Then, the form of meshing transmission of the short planet gear 5 and the long planet gear 8 is adopted to drive and connect the small sun gear 7 and the large sun gear 6. When there is no rotational speed difference between the left and right half shafts of the vehicle, the left half shaft and the right half shaft rotate synchronously; when there is a rotational speed difference between the left and right half shafts of the vehicle, there is a resistance difference between the left half shaft and the right half shaft. The relative rotation of the short planet gear 5 and the long planet gear 8 around their respective planet pins 4 inside realizes the resistance balance, thereby realizing the differential rotation between the left half shaft and the right half shaft. After the lubricating oil passes through the relief holes on the left differential housing 3 and the relief holes on the right differential housing 2, oil is stored in the oil storage cavity 12 formed between the output gear 1, the left differential housing 3, the right differential housing 2 and the clamping plate 9. During the rotation of the differential assembly, all gear meshing points can be cooled and lubricated; Axial through oil holes 19 and radial through oil holes 20 are respectively designed on the planet pin 4. The lubricating oil in the oil storage cavity 12 can flow to the radial through oil holes 20 through the axial through oil holes 19. When the short planet gear 5 and the long planet gear 8 rotate relative to the planet pin 4, the contact mating surface 22 can be lubricated and cooled. The clamping plate 9 is designed with an annular step 23, which is used to limit the circumferential rotation of the planet pin 4 by cooperating with the arc-shaped step 21 on the planet pin 4. Based on the purpose of reducing the axial dimension of the differential, the clamping plate 9 is connected to the left differential housing 3 and the right differential housing 2 by rivets 11. At the same time, the clamping plate 9 is designed with a counterbore 24 for hiding the head of the rivet 11. The small sun gear 7 and the large sun gear 6 need to maintain a relatively rotating state. In order to prevent wear and overheating between the two, based on the purpose of reducing the axial dimension of the differential, in this embodiment, radial through oil grooves are respectively provided between the small sun gear 7 and the large sun gear 6. There is relative rotation between the small sun gear 7 and the left differential housing 3 and between the large sun gear 6 and the right differential housing 2. In order to prevent wear and overheating between the two, based on the purpose of reducing the axial dimension of the differential, in this embodiment, radial through oil grooves are respectively provided between the left differential housing 3 and the right differential housing 2.

[0041] The foregoing has shown and described the basic principles, main features and advantages of the present utility model. For those skilled in the art, it is obvious that the present utility model is not limited to the details of the above-mentioned exemplary embodiments, and without departing from the spirit or basic features of the present utility model, the present utility model can be implemented in other specific forms. Therefore, from any point of view, the embodiments should be regarded as exemplary and non-limiting. The scope of the present utility model is defined by the appended claims rather than the above description. Therefore, all changes falling within the meaning and scope of the equivalent elements of the claims are intended to be embraced within the present utility model. Any reference signs in the claims should not be construed as limiting the claims involved.

[0042] Finally, several points should be noted: First, in the description of the present application, it should be noted that unless otherwise specified and defined, the terms "installation", "connection", and "coupling" should be understood in a broad sense, which can be a mechanical connection or an electrical connection, or the internal communication of two components, and can be directly connected. "Upper", "lower", "left", "right", etc. are only used to indicate the relative position relationship. When the absolute position of the object being described changes, the relative position relationship may change.

[0043] Finally, it should be noted that the above are only the preferred embodiments of the present utility model and are not intended to limit the present utility model. Although the present utility model has been described in detail with reference to the foregoing embodiments, for those skilled in the art, they can still modify the technical solutions described in the foregoing embodiments, or perform equivalent replacements for some of the technical features. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present utility model shall be included within the protection scope of the present utility model.

Claims

1. A planetary differential assembly for a dual-motor assembly, characterized in that: Including: An output gear (1), with a differential right housing (2) and a differential left housing (3) respectively arranged on both sides of the output gear (1). Bolts (10) are arranged between the differential right housing (2) and the differential left housing (3) and the output gear (1) and fixed by the bolts (10). After being fixedly connected, an installation cavity is formed. Installation holes are arranged at the center and inside of the differential right housing (2) and the differential left housing (3). A large sun gear (6) and a small sun gear (7) are arranged in the installation hole at the center. A short planet gear (5) is arranged outside the small sun gear (7) and a long planet gear (8) is arranged outside the large sun gear (6). The short planet gear (5) meshes with the long planet gear (8), and the long planet gear (8) meshes with the large sun gear (6) at the same time. The large sun gear (6) and the small sun gear (7) are axially and radially positioned by the differential right housing (2) and the differential left housing (3) respectively. A planet pin (4) is arranged inside the long planet gear (8) and the short planet gear (5). The long planet gear (8) and the short planet gear (5) are installed on the differential right housing (2) and the differential left housing (3) through the planet pin (4). Clamping plates (9) are arranged on both sides of the differential right housing (2) and the differential left housing (3). The planet pin (4) is axially and circumferentially limited by the clamping plates (9).

2. The planetary differential assembly for a dual-motor assembly according to claim 1, wherein: A number of groups of rivets (11) are arranged inside the clamping plates (9) and are respectively riveted to the differential right housing (2) and the differential left housing (3) through the number of groups of rivets (11).

3. A planetary gear differential assembly for a dual-motor assembly according to claim 1, characterized in that: Annular steps (23) and sunk grooves (24) are designed on the clamping plates (9).

4. A planetary gear differential assembly for a dual-motor assembly, characterized in that: A number of groups of first radially penetrating oil grooves (13) are arranged at the edge of the central hole of the large sun gear (6).

5. A planetary gear differential assembly for a dual motor assembly according to claim 1, characterized in that: A number of groups of second radially penetrating oil grooves (14) are arranged at the edge of the central hole of the small sun gear (7).

6. A planetary gear differential assembly for a dual-motor assembly, characterized in that: A number of groups of third radially penetrating oil grooves (15) are arranged at the edge of the central hole of the differential right housing (2), and a number of groups of first lightening holes (16) are arranged inside the differential right housing (2).

7. A planetary gear differential assembly for a dual-motor assembly according to claim 1, characterized in that: A number of groups of fourth radially penetrating oil grooves (18) are arranged at the edge of the central hole of the differential left housing (3), and a number of groups of second lightening holes (17) are arranged inside the differential left housing (3).

8. A planetary gear differential assembly for a dual-motor assembly according to claim 1, characterized in that: An axially penetrating oil hole (19) and radially penetrating oil holes (20) distributed along the axis are arranged at the center of the planet pin (4). The center of the radially penetrating oil holes (20) is along the meshing center connection line direction of the planet gear and the sun gear.

9. A planetary gear differential assembly for a dual-motor assembly according to claim 1, characterized in that: An arc-shaped step (21) is arranged at the end face of the planet pin (4) and a contact mating surface (22) is arranged on the surface.

10. A planetary gear differential assembly for a dual-motor assembly according to claim 1, characterized in that: An oil storage cavity (12) is formed among the output gear (1), the differential right housing (2), the differential left housing (3) and the clamping plates (9).

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