Free wheel type antiskid differential mechanism

Abstract

According to the free wheel type antiskid differential mechanism, a half axle gear 3 is meshed with a first planetary gear 4, the first planetary gear 4 is meshed with a second planetary gear 5, and therefore when the first planetary gear 4 and the second planetary gear 5 do not revolve, the half axle gear 3 rotates, the rotating direction of the second planetary gear 5 is the same as that of the half axle gear 3, and the second planetary gear 5 is meshed with an inner gear ring 6; the inner gear ring 6 is fixedly connected with the outer gear ring 7, so that the rotation direction of the outer gear ring 7 is the same as that of the half axle gear 3, and the outer gear ring 7 and the half axle gear 3 are jointly meshed with a free gear, so that a structure with a zero arm of force is formed; if the half shaft on one side is not stressed due to slipping or suspension of the vehicle, the planetary gears 4 and 5 of the half shaft on the stressed side revolve to enable the outer gear ring 7 to rotate, the outer gear ring 7 and the half shaft gear 3 are in a locking state due to the fact that the force arm is zero, then escaping is achieved, instant response in the whole process is not delayed, and the service life of the vehicle is prolonged. Due to the fact that the force arm is zero in locking, friction loss is not generated, the pure mechanical structure supports large torque, and the device can be applied to various scenes such as off-road vehicles and heavy trucks.

Description

Technical Field

[0001] The invention belongs to the field of differentials and relates to a free-wheel anti-slip differential. Background Art

[0002] There are two main types of automotive differentials commonly used at present, one is an open differential, and the other is a limited slip differential. Limited slip differentials are mostly high friction or forced locking types. The forced locking type requires the vehicle to stop operating, while the high friction type will cause energy loss and cannot achieve torque distribution from 0 to 100. Summary of the invention

[0003] The main purpose of the present invention is to provide a free-wheel limited slip differential to solve one or more of the above problems.

[0004] In order to achieve the above object, according to one aspect of the present invention, a free-wheel type anti-slip differential is provided; Two coaxially arranged gears mesh with a freely arranged planetary gear. One of the coaxially arranged gears is stationary while the other is used as a drive. Since the force arm acting on the planetary gear is zero, the planetary gear cannot be moved. The present invention is designed based on this principle. On the basis of the open differential, a half-shaft gear is constructed, both ends of the half-shaft gear are rotatably arranged on the differential housing, and the half-shaft gear is connected to the half-shaft through a spline; Constructing a first planetary gear, the first planetary gear meshing with the side gear, the first planetary gear rotatably disposed on the differential housing; constructing a second planetary gear, the second planetary gear meshing with the first planetary gear, the second planetary gear being rotatably disposed on the differential housing; Constructing an inner gear ring, the inner gear ring meshing with the second planetary gear, the inner gear ring being rotatably disposed on the differential housing, and the axis center line of the inner gear ring coincides with the axis center line of the side gear; Constructing an outer gear ring, wherein the outer gear ring is fixedly connected to the inner gear ring, and the radius of the outer gear ring is smaller than the radius of the inner gear ring, and the outer gear ring is rotatably disposed on the half-shaft gear; Construct a free gear, wherein the free gear is composed of two gears of different sizes fixedly connected, the axis lines of the two gears of different sizes in the free gear coincide, wherein the large gear is meshed with the half-shaft gear, wherein the small gear is meshed with the outer gear ring, the half-shaft gear or the outer gear ring is stationary, and the outer gear ring or the half-shaft gear cannot drive the free gear to move due to the zero force arm; constructing a first rotating frame, wherein the first rotating frame is rotatably disposed on the outer gear ring; Constructing a second rotating frame, wherein the second rotating frame is rotatably disposed on the half-shaft gear, and two ends of the free gear are rotatably disposed on the first rotating frame and the second rotating frame respectively; The transmission ratio between the inner gear ring, the outer gear ring, the half-shaft gear and the free gear must follow the principle that when the first planetary gear and the second planetary gear are not revolving, the half-shaft gear can rotate freely.

[0005] As a further technical solution, a plurality of combinations of the first planetary gear and the second planetary gear may be provided on the side gear and evenly distributed on the side gear.

[0006] As a further technical solution, a plurality of the free gears may be arranged on the half-shaft gear, and the plurality of the free gears are evenly distributed on the half-shaft gear.

[0007] As a further technical solution, the first planetary gears or the second planetary gears on the two half shafts can mesh with each other, thereby eliminating the need for an additional open differential structure.

[0008] With this structure, the side gear meshes with the first planetary gear, and the first planetary gear meshes with the second planetary gear. Therefore, when the first planetary gear and the second planetary gear do not revolve, the side gear rotates and the direction of rotation of the second planetary gear is the same as that of the side gear. The second planetary gear meshes with the inner ring gear, and the inner ring gear is fixedly connected to the outer ring gear. Therefore, the rotation direction of the outer ring gear is the same as that of the side gear, and the outer ring gear and the side gear mesh with the free gear together, thereby forming a structure with a zero force arm. Then, when the differential case rotates to cause the first planetary gear and the second planetary gear to revolve, if one side of the side shaft is not subjected to force due to vehicle slippage or suspension, the planetary gear of the side shaft subjected to force revolves to cause the outer ring gear to rotate, and since the force arm is zero, a locking state is formed between the outer ring gear and the side shaft gear, thereby achieving escape. The entire process responds instantly without delay, and since no friction loss is generated due to the locking with a zero force arm, the pure mechanical structure supports large torque and can be applied to various scenarios, such as off-road vehicles, heavy trucks, etc. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Figure 1 It is a schematic diagram of a free-wheel limited-slip differential assembly, wherein: 1. differential housing; 2. open differential structure; and since there are many types of open differential structures, they are left blank and not illustrated; 3. half-shaft gears; 4. first planetary gears; 5. second planetary gears; 6. inner ring gear; 7. outer ring gear; 8. small gear in the free gear; 9. large gear in the free gear; 10. first rotating frame; 11. second rotating frame; 12. input ring gear on the differential housing. Specific embodiments The following will be combined with the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. 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 the present invention.

[0011] like Figure 1 As shown, a differential case 1 and a half-shaft gear 3, both ends of the half-shaft gear 3 are rotatably arranged on the differential case 1, and the half-shaft gear 3 is connected to the half-shaft through a spline; A first planetary gear 4, wherein the first planetary gear 4 is meshed with the side gear 3, and the first planetary gear 4 is rotatably disposed on the differential housing 1; A second planetary gear 5, the second planetary gear 5 is meshed with the first planetary gear 4, and the second planetary gear 5 is rotatably arranged on the differential housing 1; An inner gear ring 6, the inner gear ring 6 is meshed with the second planetary gear 5, the inner gear ring 6 is rotatably arranged on the differential case 1, and the axis center line of the inner gear ring 6 coincides with the axis center line of the side gear 3; An outer gear ring 7, wherein the outer gear ring 7 is fixedly connected to the inner gear ring 6, and the radius of the outer gear ring 7 is smaller than the radius of the inner gear ring 6, and the outer gear ring 7 is rotatably disposed on the side gear 3; A free gear, wherein the free gear is composed of two gears 9 and 8 of different sizes fixedly connected, wherein the axis lines of the two gears 9 and 8 of different sizes in the free gear coincide with each other, wherein the large gear 9 is meshed with the side gear 3, wherein the small gear 8 is meshed with the outer gear ring 7, and if the side gear 3 or the outer gear ring 7 is stationary, then the outer gear ring 7 or the side gear 3 cannot drive the free gear to move due to the zero force arm; A first rotating frame 10, wherein the first rotating frame 10 is rotatably disposed on the outer gear ring 7; A second rotating frame 11, wherein the second rotating frame 11 is rotatably disposed on the half-shaft gear 3, and both ends of the free gear are rotatably disposed on the first rotating frame 10 and the second rotating frame 11 respectively; The transmission ratio between the inner gear ring 6, the outer gear ring 7, the half-shaft gear 3 and the free gear must follow the principle that when the first planetary gear 4 and the second planetary gear 5 are not revolving, the half-shaft gear 3 can rotate freely.

[0012] According to this structure, the side gear 3 meshes with the first planetary gear 4, and the first planetary gear 4 meshes with the second planetary gear 5. Therefore, when the first planetary gear 4 and the second planetary gear 5 do not revolve, the side gear 3 rotates and the second planetary gear 5 rotates in the same direction as the side gear 3. The second planetary gear 5 meshes with the inner ring gear 6, and the inner ring gear 6 is fixedly connected to the outer ring gear 7. Therefore, the rotation direction of the outer ring gear 7 is the same as that of the side gear 3, and the outer ring gear 7 and the side gear 3 mesh with the free gear together, thereby forming a structure with a zero force arm. Then, when the differential case 1 rotates to make the first planetary gear 4 and the second planetary gear 5 revolve, if one half shaft is not subjected to force due to vehicle slippage or suspension, the planetary gears 4 and 5 of the half shaft on the side subjected to force revolve to make the outer ring gear 7 rotate, and because the lever arm is zero, a locking state is formed between the outer ring gear 7 and the half shaft gear 3, thereby achieving escape. The whole process responds instantaneously without delay, and because the locking due to the zero lever arm does not generate friction loss, the pure mechanical structure supports large torque and can be applied to various scenarios, such as off-road vehicles, heavy trucks, etc.

[0013] The above are only preferred embodiments of the present invention and are not intended to limit the invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A free-wheel anti-slip differential, characterized in that ； Two coaxially arranged gears mesh with a freely arranged planetary gear. One of the coaxially arranged gears is stationary while the other is used as a drive. Since the force arm acting on the planetary gear is zero, the planetary gear cannot be moved. The present invention is designed based on this principle. On the basis of the open differential, a half-shaft gear is constructed, both ends of the half-shaft gear are rotatably arranged on the differential housing, and the half-shaft gear is connected to the half-shaft through a spline; Constructing a first planetary gear, the first planetary gear meshing with the side gear, the first planetary gear rotatably disposed on the differential housing; constructing a second planetary gear, the second planetary gear meshing with the first planetary gear, the second planetary gear being rotatably disposed on the differential housing; Constructing an inner gear ring, the inner gear ring meshing with the second planetary gear, the inner gear ring being rotatably disposed on the differential housing, and the axis center line of the inner gear ring coincides with the axis center line of the side gear; Constructing an outer gear ring, wherein the outer gear ring is fixedly connected to the inner gear ring, and the radius of the outer gear ring is smaller than the radius of the inner gear ring, and the outer gear ring is rotatably disposed on the half-shaft gear; Construct a free gear, wherein the free gear is composed of two gears of different sizes fixedly connected, the axis lines of the two gears of different sizes in the free gear coincide, wherein the large gear is meshed with the half-shaft gear, wherein the small gear is meshed with the outer gear ring, the half-shaft gear or the outer gear ring is stationary, and the outer gear ring or the half-shaft gear cannot drive the free gear to move due to the zero force arm; constructing a first rotating frame, wherein the first rotating frame is rotatably disposed on the outer gear ring; A second rotating frame is constructed, wherein the second rotating frame is rotatably disposed on the half-shaft gear, and both ends of the free gear are rotatably disposed on the first rotating frame and the second rotating frame respectively.

2. According to claim 1, a free-wheel type anti-slip differential, characterized in that: The transmission ratio between the inner gear ring, the outer gear ring, the half-shaft gear and the free gear must follow the principle that when the first planetary gear and the second planetary gear are not revolving, the half-shaft gear can rotate freely.

3. According to claim 1, a free-wheel type anti-slip differential, characterized in that: The combination of the first planetary gear and the second planetary gear may be arranged in multiple groups on the side gear and evenly distributed on the side gear.

4. According to claim 1, a free-wheel type anti-slip differential, characterized in that: A plurality of the free gears may be arranged on the side gear, and the plurality of the free gears are evenly distributed on the side gear.

5. According to claim 1, a free-wheel type anti-slip differential, characterized in that: The first planetary gears or the second planetary gears on the two half shafts can mesh with each other, thereby eliminating the need for an additional open differential structure.

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