Differential mechanism and vehicle

Abstract

The invention discloses a differential mechanism and a vehicle, and relates to the field of new energy automobiles, the differential mechanism comprises a main reduction gear and a straight-line-shaped shaft, an inner hole of the main reduction gear is provided with two opposite seam allowances, each end of the straight-line-shaped shaft is provided with a transmission assembly, and each transmission assembly comprises a planetary gear and a cushion block which are sequentially connected to the end of the straight-line-shaped shaft in a sleeving mode; a through hole is formed in the center of the cushion block, the end of the linear shaft extends out of the cushion block through the through hole, the part, extending out of the cushion block, of one end of the linear shaft is clamped and pressed on one seam allowance, the other end of the linear shaft is clamped and pressed on the other seam allowance, and the face, away from the planetary gear, of the cushion block is fixedly connected with the seam allowances. Wherein the middle of the straight shaft is sleeved with a supporting seat, the two ends of the supporting seat are sleeved with half-axle gears, the half-axle gears are meshed with the planetary gears, and bearings are arranged outside the half-axle gears in a sleeving mode. Through close fit of the cushion blocks and the spigots, it is ensured that the planetary gears cannot generate too large radial displacement when transmitting torque, and the shell-free differential mechanism is achieved.

Description

Technical Field

[0001] The present invention relates to the field of new energy vehicles, and in particular to a differential and a vehicle. Background Art

[0002] The differential plays a crucial role in a vehicle's drivetrain, enabling the left and right wheels to rotate at different speeds when the vehicle turns, ensuring smooth and maneuverable driving. However, existing differentials are generally heavy, with the differential housing, a key component, comprising a significant portion of the total differential weight. A heavier differential not only increases the vehicle's overall weight but also negatively impacts its power and economy. As the vehicle's weight increases, the engine must output more energy to propel it, resulting in increased fuel consumption and reduced power performance. Furthermore, a heavier differential means higher costs associated with raw material procurement, processing, and manufacturing. Reducing the weight of the differential, particularly the differential housing, is crucial for improving vehicle power, reducing energy consumption, and improving fuel economy. It also effectively reduces production costs and enhances product competitiveness in the market. Therefore, there is an urgent need to develop a lightweight differential.

[0003] Common approaches to reducing the weight of differential housings currently focus on removing weight from the housing itself. However, this does not alter the differential's torque transmission path, resulting in limited weight reduction. Furthermore, relying on machining methods like turning and drilling to reduce the housing's shape poses strength and durability risks, and increases machining costs. Alternatively, welding the transmission assembly to the housing eliminates the need for bolted connections. Ultimately, the weight reduction comes from a process change, without altering the differential's torque transmission path. This results in limited weight reduction, high welding costs, and unpredictable cracks in the welding process, posing quality risks. Furthermore, the housing cannot be disassembled after welding, making it impossible to clean the internal components. Summary of the Invention

[0004] The present application provides a differential and a vehicle, which can solve the technical problem of excessive weight of the differential in the prior art.

[0005] The transmission gears are connected to the gears of the transmission gears of the present invention in a manner that the transmission gears of the transmission gears of the transmission gears are connected to the gears of the transmission gears of the transmission gears of the transmission gears.

[0006] In combination with the first aspect, in one embodiment, at least two steps are provided around the circumference of the through hole on a side of the block away from the planetary gear, and the sides of the steps facing the through hole are all smooth arc surfaces, and the arc surfaces of the multiple steps all match the curvature of the through hole.

[0007] In combination with the first aspect, in one embodiment, the stop is in the shape of a boss with a hollow interior, and a concave stop groove is provided on the end face of the stop facing the center of the main reduction gear, and a convex stop platform is provided at the end of the straight shaft, and the convex stop platform and the concave stop groove are interference fit so that the straight shaft can be clamped on the stop.

[0008] In combination with the first aspect, in one embodiment, the top surface of the step is welded to the end surface of the stop facing the center of the main reduction gear.

[0009] In combination with the first aspect, in one embodiment, a guide chamfer is provided at the entrance of the concave stop groove.

[0010] In combination with the first aspect, in one embodiment, the height of the step is less than the length of the end of the straight shaft extending from the spacer.

[0011] In combination with the first aspect, in one embodiment, a guide bevel is provided around the through hole on a side of the spacer block facing the planetary gear, the guide bevel extends from the edge of the through hole to the outer edge of the spacer block, and the guide bevel is inclined in a conical shape.

[0012] In combination with the first aspect, in one embodiment, the differential further includes: a washer, and the washer is arranged on the end surface of the support seat facing the side gear.

[0013] In combination with the first aspect, in one embodiment, the bearing is a ball bearing or a tapered bearing.

[0014] In a second aspect, an embodiment of the present application provides a vehicle, comprising a differential as described in any of the above embodiments, wherein the internal splines of the half-shaft gears are engaged with the vehicle half-shafts.

[0015] The beneficial effects of the technical solutions provided in the embodiments of the present application include: In the embodiment of the present application, the spacer is installed at the stopper of the main reducer gear, providing stable radial support for the planetary gears. The tight fit between the spacer and the stopper ensures that the planetary gears do not experience excessive radial displacement during torque transmission, thereby ensuring proper meshing between the planetary gears and the straight and side gears, replacing the supporting function of the housing for the planetary gears. Furthermore, the spacer provides precise support for the main reducer gear and planetary gears, ensuring their positional accuracy, reducing unnecessary displacement between the gears, and ensuring proper meshing. The spacer also effectively reduces the gap between components, preventing shaking and impact during gear rotation, making power transmission smoother and more efficient. The embodiment of the present application eliminates the differential case in traditional differentials, effectively reducing the weight of the differential. In a vehicle transmission system, this not only reduces the overall vehicle mass but also reduces the burden on the engine, making vehicle acceleration easier and improving power performance. Furthermore, the lighter weight helps reduce vehicle inertia and improves handling flexibility, especially during acceleration, deceleration, and cornering, resulting in a more responsive vehicle and a better driving experience. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0017] Figure 1 A front view of a differential provided in an embodiment of the present application; Figure 2 A side view of a differential provided in an embodiment of the present application; Figure 3 A schematic diagram of the exploded structure of a differential provided in an embodiment of the present application; Figure 4 Schematic diagram of the installation of the differential provided in an embodiment of the present application in a vehicle.

[0018] In the figure: 1. Main reduction gear; 11. Stopper; 111. First stopper; 112. Second stopper; 2. Straight shaft; 3. Spacer; 301. Step; 31. First spacer; 32. Second spacer; 4. Planetary gear; 41. First planetary gear; 42. Second planetary gear; 5. Axle gear; 51. First axle gear; 52. Second axle gear; 6. Bearing; 7. Gasket; 8. Support seat. DETAILED DESCRIPTION

[0019] In order to enable those skilled in the art to better understand the present invention, the following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0020] The present application provides a differential and a vehicle, which can solve the technical problem of excessive weight of the differential in the prior art.

[0021] Figure 1 This is a front view of a differential provided in an embodiment of the present application. Figure 3 This is a schematic diagram of the exploded structure of the differential provided in the embodiment of the present application. Figure 1 and Figure 3 The transmission unit 2 includes a first gear 4 and a second gear 5. The first gear 4 is connected to the transmission unit 2 by a toothed connection cam 6. The toothed connection cam 6 is connected to the first gear 4 and the second gear 5 is connected to the transmission unit 2 by a toothed connection cam 6. The toothed connection cam 6 is connected to the first gear 4 and the second gear 5 is connected to the transmission unit 2 by a toothed connection cam 6.

[0022] In this embodiment, the torque transmission path is from main reducer gear 1 to slotted shaft 2, planetary gears 4, side gears 5, and finally the vehicle's side shafts. Specifically, main reducer gear 1 receives torque from the vehicle's drivetrain. Slotted shaft 2 is pressed into the inner bore of main reducer gear 1 through stopper 11. This allows main reducer gear 1 to directly drive slotted shaft 2. Torque is then transmitted via slotted shaft 2 to planetary gears 4, which then mesh with side gears 5 and output torque to the vehicle's side shafts.

[0023] Furthermore, a relative first stop 111 and a second stop 211 are provided at the inner hole of the main reduction gear 1, a first transmission assembly is provided at one end of the straight shaft 2, and a second transmission assembly is provided at the other end of the straight shaft 2. The first transmission assembly includes a first planetary gear 41 and a first pad 31 which are sequentially sleeved on one end of the straight shaft 2, and the second transmission assembly includes a first planetary gear 42 and a first pad 32 which are sequentially sleeved on the other end of the straight shaft 2. The part of one end of the straight shaft 2 extending outward from the first pad 31 is pressed on the first stop 111, and the part of the other end extending outward from the first pad 32 is pressed on the second stop 112, and the side of the first pad 31 away from the first planetary gear 41 is fixedly connected to the first stop 111, and the side of the first pad 32 away from the first planetary gear 42 is fixedly connected to the second stop 112. The first half-shaft gear 51 and the second half-shaft gear 52 are respectively sleeved on both ends of the support seat 8.

[0024] When the car is traveling in a straight line, the wheels on both sides rotate at the same speed, and the first stop 111 and the second stop 112 of the inner hole of the main reduction gear 1 synchronously drive the two ends of the straight shaft 2. Through the fixed connection between the first cushion block 31 and the first stop 111 and the fixed connection between the first cushion block 32 and the second stop 112, the first planetary gear 41 and the first planetary gear 42 only revolve with the straight shaft 2 without rotating on their own, and the torque is equally distributed to the first half-shaft gear 51 and the second half-shaft gear 52. When the vehicle turns, the inner resistance increases, and the torque formed by the inner resistance causes the differential to play a differential role. The thrust of the first planetary gear 41 is transmitted to the first stop 111 through the first pad 31. The first stop 111 serves as a fixed fulcrum to drive the first planetary gear 41 to rotate. At the same time, the first planetary gear 42 rotates in the opposite direction, and the two ends of the straight shaft 2 are respectively clamped on the first stop 111 and the second stop 112, coupling the rotation movements on both sides, so that the first half-shaft gear 51 obtains incremental torque and the torque of the second half-shaft gear 52 is reduced, thereby achieving the requirement of different speeds of the wheels on both sides to prevent the wheels on both sides from slipping and spinning on the ground.

[0025] During the assembly of the differential provided in the embodiment of the present application, the support base 8 is fixed to the middle portion of the straight shaft 2. The first planetary gears 41 and 42 are then assembled to the ends of the straight shaft 2. The first spacers 31 and 32 are then assembled to the ends of the straight shaft 2. The portion of the straight shaft 2 extending outward from the first spacer 31 is pressed against the first stop 111, and the portion of the other end extending outward from the first spacer 32 is pressed against the second stop 112. The first spacer 31 is then fixed to the first stop by laser welding, and the first spacer 32 is then fixed to the second stop. Subsequently, the first and second side gears 51, 52 at both ends of the support base 8, as well as the bearings 6 on the outer circumferences of the first and second side gears 51, 52, are assembled in sequence.

[0026] In an embodiment of the present application, at least two steps 301 are provided around the circumference of the through hole on the side of the gasket 3 away from the planetary gear 4, and the sides of the steps 301 facing the through hole are all smooth arc surfaces, and the arc surfaces of the multiple steps 301 all match the curvature of the through hole.

[0027] Specifically, the two steps 301 are arranged at opposite ends, and the two arc surfaces of the two steps 301 facing the through hole can form a smooth arc surface, that is, the curvature radius of the two arc surfaces of the two steps 301 facing the through hole is adapted to the curvature of the through hole, so that the arc surface can naturally transition and connect with the inner wall of the through hole, thereby making it easier for components such as the planetary gear 4 to be aligned and matched with the gasket 3. At the same time, the smooth transition of the arc surface reduces the friction with the surface of the straight shaft 2 during the assembly process, making it easier for the straight shaft 2 to pass through the through hole, reducing the resistance during the assembly process, and improving the assembly efficiency.

[0028] In some other embodiments of the present application, more steps 301 may be arranged around the circumference of the through hole. It is only necessary to ensure that the side of the multiple steps 301 facing the through hole can form a smooth arc surface. The number of steps 301 is not limited here.

[0029] Figure 2 A side view of a differential provided in an embodiment of the present application. Figure 2 and Figure 3 In the embodiment of the present application, the stop 11 is in the shape of a hollow boss, and the end face of the stop 11 facing the center of the main reduction gear 1 is provided with a concave stop groove, and the end of the straight shaft 2 is provided with a convex stop platform, and the convex stop platform and the concave stop groove are interference fit so that the straight shaft 2 can be clamped on the stop 11.

[0030] Specifically, the interior of the spigot 11 is hollow, which reduces the weight of the spigot 11 by reducing the use of materials, thereby further reducing the weight of the entire differential. At least two flat surfaces are cut out at both ends of the straight shaft 2 by cutting or other methods to form convex spigot steps on the ends of the straight shaft 2. These two flat surfaces cooperate with the side walls of the concave spigot groove to ensure a tight connection between the straight shaft 2 and the main reducer gear 1, ensuring efficient power transmission from the main reducer gear 1 to the straight shaft 2 and reducing energy loss.

[0031] In the embodiment of the present application, the top surface of the step 301 is welded to the end surface of the stop 11 facing the center of the main reducer gear 1. Specifically, during assembly of the differential, the portion of one end of the straight shaft 2 extending outward from the first spacer 31 is clamped onto the first stop 111, and the portion of the other end extending outward from the first spacer 32 is clamped onto the second stop 112. Thereafter, the top surface of the step 301 of the first spacer 31 is welded to the end surface of the first stop facing the center of the main reducer gear 1 by laser welding, and the top surface of the step 301 of the first spacer 32 is welded to the end surface of the second stop facing the center of the main reducer gear 1.

[0032] In the embodiment of the present application, a guiding chamfer is provided at the entrance of the concave stop groove to prevent damage during the clamping.

[0033] The guide chamfer is specifically a slope with a small inclination, which gradually slopes from the outside to the inside of the concave stop groove, providing a smooth transition surface, so that the convex stop platform can enter more easily when it is clamped into the concave stop groove, reducing the resistance during the clamping process, while avoiding damage to the edges at the entrance of the concave stop groove, thereby extending the service life of the differential. In another embodiment of the present application, an elastic sealing ring can also be provided at the entrance of the concave stop groove, and the outer diameter of the sealing ring is slightly larger than the entrance diameter of the concave stop groove, so that during the clamping process, the convex stop platform can push the elastic sealing ring into the concave stop groove. The elastic deformation of the sealing ring can play a guiding and protective role.

[0034] In the embodiment of the present application, the height of the step 301 is less than the length of the end of the straight shaft 2 extending out of the spacer block 3. This ensures that after the end of the straight shaft 2 passes through the through hole of the spacer block 3, its protruding portion is long enough to be clamped and connected to the stopper 11 of the main reduction gear 1.

[0035] In another embodiment of the present application, a guide bevel is provided around the through hole on the side of the spacer 3 facing the planetary gear 4. The guide bevel extends from the edge of the through hole to the outer edge of the spacer 3 and is inclined in a conical shape. Therefore, the step 301 is not required, and the effect of the step 301 is the same.

[0036] Specifically, the conical guide bevel can disperse stress. The setting of the guide bevel allows the pad 3 to form a gradually expanding guide surface on the side facing the planetary gear 4 during the assembly process of the differential, which helps the pad 3 to be more easily aligned and matched with the planetary gear 4 during the assembly process, thereby improving the assembly efficiency.

[0037] In the embodiment of the present application, the differential further includes: a gasket 7 , which is arranged on the end surface of the support seat 8 facing the side gear 5 .

[0038] Specifically, before assembling the first half-shaft gear 51 and the second half-shaft gear 52 at both ends of the support seat 8, and the bearings 6 on the outer peripheral sides of the first half-shaft gear 51 and the second half-shaft gear 52 in sequence, it is necessary to select the thickness of the gasket 7. Specifically, by measuring the depth A from the left housing assembly surface to the support seat 8, the depth B from the right housing assembly surface to the support seat 8, and the total axial thickness C of the differential assembly in the assembly housing of the differential in the whole vehicle, and then calculating the clearance value, the calculation formula is: |C-(A + B)|, and selecting the gasket 7 of corresponding thickness according to the clearance value, thereby accurately adjusting the axial assembly clearance of the half-shaft gear 5 and eliminating axial shaking.

[0039] In the embodiment of the present application, the bearing 6 is a ball bearing or a tapered bearing.

[0040] Specifically, the bearing 6 is used to support the side gear 5 to ensure that they can rotate steadily and smoothly. In some other embodiments of the present application, different types of bearings such as needle bearings can also be used, which is not limited here.

[0041] In a second aspect, an embodiment of the present application provides a vehicle, comprising a differential according to any of the above embodiments, wherein the internal spline of the half-shaft gear 5 is engaged with the vehicle half-shaft.

[0042] Figure 4 This is a schematic diagram of the installation of the differential provided in the embodiment of the present application in a vehicle. Figure 4 The differential assembly connects to the half-shafts via the internal splines of the half-shaft gears 5 to achieve power output, transmitting torque to the drive wheels on both sides. The differential provided in the above embodiment of the present application is preferably used in a parallel-axis arrangement of an electric drive reducer. The differential provided in the above embodiment of the present application is also applicable to traditional fuel vehicles or coaxial arrangements, without limitation here.

[0043] The spacer 3 in the embodiment of the present application is installed at the stop 11 of the main reducer gear 1, providing stable radial support for the planetary gears 4. The close fit between the spacer 3 and the stop 11 ensures that the planetary gears 4 do not experience excessive radial displacement when transmitting torque, thereby ensuring proper engagement between the planetary gears 4 and the straight shaft 2 and the side gears 5, replacing the supporting function of the housing for the planetary gears 4. Furthermore, the spacer 3 provides precise support for the main reducer gear 1 and the planetary gears 4, ensuring their positional accuracy, reducing unnecessary displacement between the gears, and ensuring proper engagement. The provision of the spacer 3 also effectively reduces the gap between components, preventing shaking and impact during gear rotation, making power transmission smoother and more stable, thereby improving power transmission efficiency. The embodiment of the present application eliminates the differential case in traditional differentials, effectively reducing the weight of the differential. In a vehicle transmission system, this not only reduces the overall vehicle mass but also reduces the burden on the engine, making vehicle acceleration easier and improving power performance. At the same time, lighter weight helps reduce vehicle inertia and improve handling flexibility, especially when accelerating, decelerating and turning, the vehicle's response is more agile and the driving experience is better.

[0044] In the description of this application, it should be noted that the terms "upper" and "lower" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing this application 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 this application. Unless otherwise clearly specified and limited, the terms "installed", "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 an indirect connection through an intermediate medium, or it can be internal communication between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

[0045] It should be noted that, in this application, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device comprising a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the sentence "comprising a ..." does not exclude the presence of other identical elements in the process, method, article or device comprising the element.

[0046] The foregoing is merely a list of specific embodiments of the present application, intended to enable those skilled in the art to understand or implement the present application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application is not limited to the embodiments shown herein, but is intended to conform to the broadest scope consistent with the principles and novel features of the present application.

Claims

1. A differential, characterized in that: The differential comprises: A main reduction gear (1), wherein the inner hole of the main reduction gear (1) is provided with two opposite stoppers (11); A straight shaft (2), each end of the straight shaft (2) is provided with a transmission assembly, the transmission assembly comprising a planetary gear (4) and a pad (3) which are sequentially sleeved on the ends of the straight shaft (2), a through hole being provided at the center of the pad (3), the end of the straight shaft (2) extending outward from the pad (3) through the through hole, a portion of one end of the straight shaft (2) extending outward from the pad (3) being clamped on one of the stoppers (11), and a portion of the other end extending outward from the pad (3) being clamped on the other stopper (11), and a side of the pad (3) away from the planetary gear (4) being fixedly connected to the stopper (11); A support seat (8) is sleeved on the middle of the straight shaft (2), the axis of the support seat (8) is perpendicular to the axis of the straight shaft (2), and half-shaft gears (5) are sleeved on both ends of the support seat (8), the half-shaft gears (5) are meshed with the planetary gears (4), and the outer peripheral side of the half-shaft gears (5) is sleeved with bearings (6).

2. A differential according to claim 1, characterized in that: At least two steps (301) are provided on a side of the pad (3) away from the planetary gear (4) around the circumference of the through hole, and the sides of the steps (301) facing the through hole are all smooth arc surfaces, and the arc surfaces of the multiple steps (301) all match the curvature of the through hole.

3. A differential according to claim 2, characterized in that: The stop (11) is in the shape of a boss with a hollow interior, and a concave stop (11) groove is provided on the end surface of the stop (11) facing the center of the main reduction gear (1), and a convex stop (11) platform is provided at the end of the straight shaft (2), and the convex stop (11) platform and the concave stop (11) groove are interference-fitted so that the straight shaft (2) is clamped on the stop (11).

4. A differential according to claim 3, characterized in that: The top surface of the step (301) is welded to the end surface of the stop (11) facing the center of the main reduction gear (1).

5. A differential according to claim 3, characterized in that: A guiding chamfer is provided at the entrance of the recessed stop (11) groove.

6. A differential according to claim 2, characterized in that: The height of the step (301) is less than the length of the end of the straight shaft (2) extending out of the cushion block (3).

7. The differential according to claim 1, characterized in that: A guide bevel is provided around the through hole on one side of the pad (3) facing the planetary gear (4), the guide bevel extending from the edge of the through hole to the outer edge of the pad (3), and the guide bevel is inclined in a conical shape.

8. The differential according to claim 1, characterized in that: The differential further comprises: A gasket (7), the gasket (7) being arranged on the end surface of the support seat (8) facing the half-shaft gear (5).

9. The differential according to claim 1, characterized in that: The bearing (6) is a ball bearing or a tapered bearing.

10. A vehicle, characterized in that: A differential comprising any one of claims 1 to 9, wherein the internal spline of the half-shaft gear (5) is engaged with the vehicle half-shaft.

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