Transmission method and device for free wheel of differential mechanism

Abstract

When a differential half shaft 11 on one side is not stressed due to slipping or suspension, and rotation of a differential shell 1 serves as input to drive a first planetary gear 12 and a second planetary gear 3 to revolve, the first planetary gear 12 and the second planetary gear 3 drive an inner gear ring 5 on a half shaft on the other side to rotate in the same direction. Due to the fact that the first planet bevel gear 8 and the second planet bevel gear 7 are fixedly connected and coaxially arranged, and the diameter of the inner gear ring 5 is far larger than that of the half shaft bevel gear 13, the differential mechanism shell 1 rotates to enable the inner gear ring 5, the first planet bevel gear 8 and the second planet bevel gear 7 on the other side to rotate, and the first planet bevel gear 8 and the second planet bevel gear 7 are driven to rotate. The first planet bevel gear 8 and the second planet bevel gear 7 are evenly distributed, force generated by locking of the inner gear ring 5 only pushes the second planet bevel gear 7 to rotate, and the direction of the force at the meshing position of the first planet bevel gear 8 and the second planet bevel gear 7 is the same as the rotating direction of the differential shell 1, so that the first planet bevel gear 8 and the second planet bevel gear 7 are in a locked state, and then the differential shell 1 is released. Therefore, the defect of a single cantilever of a free wheel in a free wheel type antiskid differential mechanism is overcome, and the whole structure is more durable.

Description

TECHNICAL FIELD

[0001] The application belongs to the field of differential, and relates to a transmission method and device of a freewheel in a freewheel type anti-slip differential. BACKGROUND

[0002] The freewheel type anti-slip differential is a kind of anti-slip differential without friction, and the patent application number is 202510307280.9. The cylindrical gear design scheme of the freewheel forms a single cantilever effect, so that the stress of the freewheel is uneven, and then the service life is affected.

[0003] The freewheel type anti-slip differential is a kind of anti-slip differential without friction, and the patent application number is 202510307280.9. According to the structure shown in claim 5, the working principle of the anti-slip differential is as follows: according to the principle of the open cylindrical gear differential, the sun gears on both sides are extended, the planet gears meshing with the sun gears on both sides are called first planet gears, a second planet gear is constructed, the second planet gear and the first planet gear are both rotationally arranged on the differential housing, the second planet gear meshes with the first planet gear, and there is no meshing relationship between the second planet gear and the sun gear, an inner ring gear is constructed, the inner ring gear meshes with the second planet gear, and there is no meshing relationship between the inner ring gear and the first planet gear, an outer ring gear is constructed, the two outer ring gears are both fixedly arranged on one side of the two inner ring gears located on the outer side of the open cylindrical gear differential, a freewheel is constructed, the freewheel is fixedly connected by two cylindrical gears of different sizes, the axis lines of the two cylindrical gears of different sizes in the freewheel coincide, the large gear in the freewheel meshes with the extended part of the sun gear, the small gear in the freewheel meshes with the outer ring gear, a plurality of freewheels are rotationally arranged on the retainer on both sides, the retainer is rotationally arranged on the differential housing on the outer side, and the retainer is rotationally arranged on the sun gear and the outer ring gear on the inner side. Thus, when the input drives the differential housing to rotate to drive the first planet gear and the second planet gear to revolve, and one side half shaft is suspended or slips, the freewheel and the outer ring gear and the sun gear form a locking effect due to the transmission ratio between the sun gear, the inner ring gear, the outer ring gear and the freewheel, and the freewheel forms a single cantilever effect due to the retainer on both sides, so that the torsion is generated between the retainers on both sides. SUMMARY

[0004] The main purpose of the present application is to provide a new transmission method of the differential freewheel to solve the above problems.

[0005] In order to achieve the above purpose, according to one aspect of the present application, a transmission method of a differential freewheel is provided. Based on the principle of open cylindrical gear differentials, and building upon the structure of "A Freewheel Type Anti-Slip Differential," the sun gears (half-shaft gears) on both sides are no longer extended. Half-shaft bevel gears are constructed on the sides of the sun gears away from the center of the differential. These half-shaft bevel gears are fixedly connected to the sun gears on the same side. The half-shaft bevel gears and the sun gears are connected to the differential half-shaft via splines. A rotating block is positioned in the middle between the two sun gears, with its two sides rotatably connected to the two sun gears to stabilize their relative positions. Sun gear cages can be individually provided between the two sun gears and the first and second planetary gears to maintain stable relative positions. The first planetary gear, second planetary gear, and sun gear are all rotatably connected to the sun gear cages. Two or four sun gear cages can be provided. The outer gear ring is removed, and the two inner gear rings are rotatably connected to the differential housing via tapered pressure bearings on their sides near the middle of the differential, so that the inner gear rings can withstand the displacement pressure from the sides. The outer rings of the two inner gear rings are rotatably connected to the differential housing via bearings. Construct an annular bevel gear, with two annular bevel gears respectively fixedly disposed on the sides of the two internal gear rings away from the middle position of the differential; Remove the free wheel and the cage structure connected to it in "A Free Wheel Type Anti-Slip Differential" and construct an annular cage. The outer rings of the two annular cages are rotatably mounted on the differential housing. The sides of the two annular cages away from the middle position of the differential are rotatably mounted on the differential housing through tapered pressure bearings so that the annular cages can withstand the displacement pressure from the sides. Construct a bevel gear shaft, one end of which is fixedly mounted on the inner ring of the annular cage. Two or more bevel gear shafts are evenly distributed on the inner ring of the annular cage. The other ends of the two or more bevel gear shafts are fixedly connected by an annular structure. The middle of the annular structure allows the differential half-shaft to pass through, but it is not connected to the half-shaft. A first planetary bevel gear is constructed, which meshes with the half-shaft bevel gear. There can be two or more first planetary bevel gears, which are evenly distributed on the half-shaft bevel gear. A second planetary bevel gear is constructed, which meshes with the ring bevel gear. There can be two or more second planetary bevel gears, which are evenly distributed on the ring bevel gear. The number of first planetary bevel gears and second planetary bevel gears is the same. Each first planetary bevel gear is fixedly connected to one second planetary bevel gear and rotatably mounted on the same bevel gear shaft.

[0006] As a further technical solution, the first planetary gear and the second planetary gear are rotatably mounted on the differential housing, and the rotation of the differential housing is used as an input to drive the first planetary gear and the second planetary gear to revolve. Alternatively, the sun gear cage can be fixedly connected to the differential housing, and the rotation of the differential housing is used as an input to drive the rotation of the sun gear cage, thereby causing the first planetary gear and the second planetary gear to revolve.

[0007] As a further technical solution, the transmission ratio between the sun gear and the internal gear ring, the half-shaft bevel gear, the first planetary bevel gear, the ring bevel gear, and the second planetary bevel gear must follow the principle that when the first planetary gear and the second planetary gear do not revolve, the two sun gears and the two half-shaft bevel gears can produce rotations with the same speed but opposite directions.

[0008] With this structure, when one half-shaft is not under force due to slippage or suspension, when the rotation of the differential housing is used as input to drive the first planetary gear and the second planetary gear to revolve, the first planetary gear and the second planetary gear drive the internal gear ring on the other half-shaft to rotate in the same direction. Since the first planetary bevel gear and the second planetary bevel gear are fixedly connected and coaxially arranged, and the diameter of the internal gear ring is much larger than the diameter of the half-shaft bevel gear, the rotation of the differential housing causes the internal gear ring, the first planetary bevel gear, the second planetary bevel gear, and the half-shaft bevel gear on the other side to form a locking state, thereby freeing them from the predicament. Since the first planetary bevel gear and the second planetary bevel gear are evenly distributed, and the force generated by the locking of the internal gear ring only pushes the second planetary bevel gear to rotate, the direction of the force at the meshing point is the same as the rotation direction of the differential housing. Therefore, the shortcomings of the free wheel single cantilever in "A Free Wheel Type Anti-slip Differential" are solved, making the overall structure more durable. Attached Figure Description

[0009] Due to the symmetry of the two sides of the differential structure, the accompanying drawings only describe one side of the differential structure.

[0010] Figure 1 This is a schematic diagram of a freewheel type anti-slip differential according to claim 5, with the freewheel structure removed and replaced by a bevel gear structure. In the diagram, 1 is the differential housing, 2 is the input bevel gear, 3 is the second planetary gear, 4 is the sun gear, 5 is the internal gear ring, 6 is the annular external gear ring, 7 is the second planetary bevel gear, 8 is the first planetary bevel gear, 9 is the annular cage, 10 is the bevel gear shaft, 11 is the differential half-shaft, 12 is the first planetary gear, and 13 is the half-shaft bevel gear. Figure 2This is a schematic diagram of a bevel gear shaft, where 10 is the bevel gear shaft and 15 is the ring structure. Specific Implementation

[0011] The technical solutions of the present invention will be clearly and completely described below with reference to the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0012] As shown in the figure, there is a differential housing 1 and an input bevel gear 2. The input bevel gear 2 is fixedly mounted on the differential housing 1. The specific shape of the input bevel gear 2 varies depending on the application scenario. When applied to an inter-wheel differential, a ring bevel gear is used, and when applied to a central differential, an external gear ring structure is used. The two internal gear rings 5 ​​are rotatably connected to the differential housing 1 via tapered pressure bearings on their sides near the middle position of the differential, so that the internal gear rings 5 ​​can withstand the displacement pressure from the side. The outer rings of the two internal gear rings 5 ​​are rotatably connected to the differential housing 1 via bearings. The second planetary gear 3 meshes with the internal gear ring 5, and a plurality of the second planetary gears 3 are evenly distributed within the internal gear ring 5; A first planetary gear 12 meshes with a second planetary gear 3, and each first planetary gear 12 corresponds to one second planetary gear 3; A sun gear 4 meshes with a first planetary gear 12. Multiple first planetary gears 12 are evenly distributed on the sun gear 4. A rotating block is positioned at the midpoint between two sun gears 4. The two sides of the rotating block are rotatably connected to the two sun gears 4 respectively to stabilize their relative positions. A sun gear cage can be individually provided between each of the two sun gears 4 and the first planetary gear 12 and second planetary gear 3 to maintain a stable relative position. The first planetary gear 12, second planetary gear 3, and sun gear 4 are all rotatably connected to the sun gear cage. Two or four sun gear cages can be provided. Half-shaft bevel gears 13 are constructed on the sides of the sun gears 4 on both sides of the differential, away from the middle position of the differential. The half-shaft bevel gears 13 are fixedly connected to the sun gears 4 on the same side. The half-shaft bevel gears and the sun gears are connected to the differential half-shaft 11 through splines. A differential half-shaft 11 is provided, wherein the differential half-shaft 11 is connected to the half-shaft bevel gear 13 and the sun gear 4 via a spline; The two ring bevel gears 6 are respectively fixedly disposed on the sides of the two internal gear rings 5 ​​away from the middle position of the differential; The outer rings of the two ring cages 9 are rotatably mounted on the differential housing 1, and the sides of the two ring cages 9 away from the middle position of the differential are rotatably mounted on the differential housing 1 through tapered pressure bearings, so that the ring cages 9 can withstand the displacement pressure from the sides. A bevel gear shaft 10, one end of which is fixedly disposed on the inner ring of the annular cage 9, two or more bevel gear shafts 10 are evenly distributed on the inner ring of the annular cage 9, and the other ends of the two or more bevel gear shafts 10 are fixedly connected by an annular structure 15. The middle of the annular structure 15 allows the differential half shaft 11 to pass through, but it is not connected to the differential half shaft 11. The first planetary bevel gear 8 meshes with the half-shaft bevel gear 13. There may be two or more first planetary bevel gears 8, which are evenly distributed on the half-shaft bevel gear 13. The second planetary bevel gear 7 meshes with the ring bevel gear 6. There can be two or more second planetary bevel gears 7, which are evenly distributed on the ring bevel gear 6. The number of first planetary bevel gears 8 is the same as that of second planetary bevel gears 7. Each first planetary bevel gear 8 is fixedly connected to one second planetary bevel gear 7 and rotatably mounted on the same bevel gear shaft 10.

[0013] As a further technical solution, the first planetary gear 12 and the second planetary gear 3 are rotatably mounted on the differential housing 1. The rotation of the differential housing 1 is used as an input to drive the first planetary gear 12 and the second planetary gear 3 to revolve. Alternatively, the sun gear cage can be fixedly connected to the differential housing 1, and the rotation of the differential housing 1 is used as an input to drive the sun gear cage to rotate, thereby causing the first planetary gear 12 and the second planetary gear 3 to revolve.

[0014] As a further technical solution, the transmission ratio between the sun gear 4 and the internal gear ring 5, the half-shaft bevel gear 13, the first planetary bevel gear 8, the ring bevel gear 6, and the second planetary bevel gear 7 must follow the principle that when the first planetary gear 12 and the second planetary gear 3 do not revolve, the two sun gears 4 and the two half-shaft bevel gears 13 can produce rotations with the same speed but opposite directions.

[0015] With this structure, when one side of the differential half-shaft 11 is not under force due to slippage or suspension, when the rotation of the differential housing 1 is used as input to drive the first planetary gear 12 and the second planetary gear 3 to revolve, the first planetary gear 12 and the second planetary gear 3 drive the internal gear ring 5 on the other side of the half-shaft to rotate in the same direction. Since the first planetary bevel gear 8 and the second planetary bevel gear 7 are fixedly connected and coaxially arranged, and the diameter of the internal gear ring 5 is much larger than the diameter of the half-shaft bevel gear 13, the rotation of the differential housing 1 causes the internal gear ring 5, the first planetary bevel gear 8, the second planetary bevel gear 7, and the half-shaft bevel gear 13 on the other side to form a locking state, thereby freeing them from the predicament. Since the first planetary bevel gear 8 and the second planetary bevel gear 7 are evenly distributed, and the force generated by the locking of the internal gear ring 5 only pushes the second planetary bevel gear 7 to rotate, the direction of the force at the meshing point is the same as the rotation direction of the differential housing 1. Therefore, the shortcomings of the free wheel single cantilever in "A Free Wheel Type Anti-slip Differential" are solved, making the overall structure more durable.

[0016] The above are merely 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 within the protection scope of the present invention.

Claims

1. A transmission method and device for a differential freewheel, characterized in that, Based on the principle of open cylindrical gear differentials, and building upon the structure of "A Freewheel Type Anti-Slip Differential," the sun gears (half-shaft gears) on both sides are no longer extended. Half-shaft bevel gears are constructed on the sides of the sun gears away from the center of the differential. These half-shaft bevel gears are fixedly connected to the sun gears on the same side. The half-shaft bevel gears and the sun gears are connected to the differential half-shaft via splines. A rotating block is positioned in the middle between the two sun gears, with its two sides rotatably connected to the two sun gears to stabilize their relative positions. Sun gear cages can be individually provided between the two sun gears and the first and second planetary gears to maintain stable relative positions. The first planetary gear, second planetary gear, and sun gear are all rotatably connected to the sun gear cages. Two or four sun gear cages can be provided. The outer gear ring is removed, and the two inner gear rings are rotatably connected to the differential housing via tapered pressure bearings on their sides near the middle of the differential, so that the inner gear rings can withstand the displacement pressure from the sides. The outer rings of the two inner gear rings are rotatably connected to the differential housing via bearings. Construct an annular bevel gear, with two annular bevel gears respectively fixedly disposed on the sides of the two internal gear rings away from the middle position of the differential; Remove the free wheel and the cage structure connected to it in "A Free Wheel Type Anti-Slip Differential" and construct an annular cage. The outer rings of the two annular cages are rotatably mounted on the differential housing. The sides of the two annular cages away from the middle position of the differential are rotatably mounted on the differential housing through tapered pressure bearings so that the annular cages can withstand the displacement pressure from the sides. Construct a bevel gear shaft, one end of which is fixedly mounted on the inner ring of the annular cage. Two or more bevel gear shafts are evenly distributed on the inner ring of the annular cage. The other ends of the two or more bevel gear shafts are fixedly connected by an annular structure. The middle of the annular structure allows the differential half-shaft to pass through, but it is not connected to the half-shaft. A first planetary bevel gear is constructed, which meshes with the half-shaft bevel gear. There can be two or more first planetary bevel gears, which are evenly distributed on the half-shaft bevel gear. A second planetary bevel gear is constructed, which meshes with the ring bevel gear. There can be two or more second planetary bevel gears, which are evenly distributed on the ring bevel gear. The number of first planetary bevel gears and second planetary bevel gears is the same. Each first planetary bevel gear is fixedly connected to one second planetary bevel gear and rotatably mounted on the same bevel gear shaft.

2. According to claim 1, a transmission method and device for a differential freewheel is characterized in that, The first planetary gear and the second planetary gear are rotatably mounted on the differential housing. The rotation of the differential housing is used as an input to drive the first planetary gear and the second planetary gear to revolve. Alternatively, the sun gear cage can be fixedly connected to the differential housing, and the rotation of the differential housing is used as an input to drive the sun gear cage to rotate, thereby causing the first planetary gear and the second planetary gear to revolve.

3. According to claim 1, a transmission method and device for a differential freewheel is characterized in that, The transmission ratio between the sun gear and the internal gear ring, the half-shaft bevel gear, the first planetary bevel gear, the ring bevel gear, and the second planetary bevel gear must follow the principle that when the first planetary gear and the second planetary gear do not revolve, the two sun gears and the two half-shaft bevel gears can produce rotations with the same speed but opposite directions.

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