CN118009015A - Dynamic differential mechanism - Google Patents

Abstract

The present invention discloses a dynamic differential, which specifically belongs to the field of automobile transmission, and aims to solve the problem that the existing differential adopts an equal proportion distribution method (i.e., 50% of the power is distributed on both sides), and the wheels are prone to slipping when encountering a slippery road, causing the car to be unable to drive. The inventor has made a new design for the structure of the differential. The improved differential can achieve that when driving on a curve, not only the outer power is greater than the inner power, but also the turning trajectory and body posture can be effectively adjusted, and the wheels will not slip, so as to better improve the off-road and road handling performance of the car, and has a high degree of originality.

Description

Dynamic differential

Technical Field

The invention relates to the field of machinery, in particular to the field of automobile transmission, and specifically to a dynamic differential.

Background technique

At present, differentials have been widely used in the automotive field and play an important role in the operation of automobiles. Practice has found that when a car turns, the friction between the outer wheels and the ground is greater due to the centrifugal force, so the outer wheels need greater power and higher speed. The existing differential uses an equal proportion distribution method (i.e., 50% of the power is distributed to one side), which cannot achieve dynamic distribution.

The function of the differential is fixed, and the main difference lies in the different transmission structures; the transmission structure determines the overall performance of the differential, which is its core and fundamental. The applicant has been conducting research on the expansion of differential functions since 2022, and proposed a differential structure with new functions. To this end, the present application provides a dynamic differential.

Summary of the invention

The invention aims to provide a differential to solve the problem that the existing differential adopts an equal proportion distribution method (i.e., 50% of the power is distributed on one side) and the wheels are prone to slipping when encountering a slippery road, causing the car to be unable to drive. The inventor has made a new design for the structure of the differential. The improved differential can achieve that when driving on a curve, the power on the outside is greater than that on the inside, which effectively adjusts the turning trajectory and the body posture, better improves the handling performance of the car, and the wheels will not slip, which has a high degree of originality.

As mentioned above, the power distribution of existing differentials is mostly in the form of equal distribution of power on both sides, that is, 50% of the power is evenly distributed on both sides. With this method, it is impossible to achieve a good power match when turning. At the same time, with the existing differential, when the wheels pass through a slippery road, the wheels are prone to slipping, which is not conducive to the operation of the vehicle.

The basic idea of the present invention is to use different combinations of differential mechanisms in the prior art, such as bevel gear differential mechanisms, parallel axis cylindrical gear differential mechanisms, and planetary gear differential mechanisms, to form a meshing closed-loop differential unit, and then combine the present invention's use of the axial thrust of the helical gears and the alternating switching of power by the power switching gears to achieve a dynamic distribution in which the power on the outside is greater than that on the inside when the vehicle turns, and the speed difference of the outer wheels is about 10% greater than that of the existing differential, which is more conducive to the adjustment of the vehicle body posture and turning trajectory and has better controllability.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will be described in detail with reference to four embodiments and the accompanying drawings to illustrate different structures and principles thereof.

FIG. 1 is a view showing the internal structure of Example 1.

FIG. 2 is a component view of the internal structure of Example 1. FIG.

FIG3 is a view of the one-piece sun gear of Embodiment 1.

FIG. 4 is a view showing the internal structure of the second embodiment.

FIG. 5 is a component view of the internal structure of Embodiment 2.

FIG. 6 is a component view of the internal structure of Example 3. FIG.

FIG. 7 is a view showing the internal structure of Example 4.

FIG. 8 is a component view of the internal structure of Example 4.

Markings in the figure: 1. housing, 2. end cover, 3. end cover baffle, 4. power switching gear, 5. axial thrust gear, 6. thrust spring, 7. spline spur gear, 8. bevel gear, 9. alternating switching gear one, 10. alternating switching gear two, 11. alternating switching gear three, 12. alternating switching gear four, 13. ring gear end plate, 14. conjoined sun gear, 15. sun gear, 16. ring gear, 17. double-layer differential gear, 18. inner output gear, 19. outer output gear, 20. integrated end cover, 21. planetary gear, 22. planetary carrier, 23. reversing gear, 24. reversing gear shaft, 25. double-layer differential gear carrier, 26. planetary gear set mounting hole, 27. planetary gear set, 28. integrally arranged annular disc, 29. separately arranged annular disc.

Detailed ways

All features disclosed in this specification, or steps in all methods or processes disclosed, except mutually exclusive features and/or steps, can be combined in any manner.

Any feature disclosed in this specification, unless otherwise stated, can be replaced by other equivalent or alternative features with similar purposes. That is, unless otherwise stated, each feature is only an example of a series of equivalent or similar features.

Example 1

The dynamic differential, as shown in Figures 1 and 2, comprises: a housing, an end cover, a meshing closed-loop differential unit, an alternating switching gear, an axial thrust gear and a thrust spring, wherein the housing is in the shape of a circular tube, at least two differential gear shaft holes are radially arranged in the middle of the housing, the axial section of the end cover is in the shape of a step and is provided with a half-shaft hole, an inwardly facing annular end cover baffle is integrally arranged at the outlet end of the half-shaft hole, the housing and the end cover are screw-connected to form a supporting body of the dynamic differential, the meshing closed-loop differential unit is a bevel gear differential mechanism arranged between two planetary gear mechanisms, at least two differential gears are axially meshed at 90 degrees between two circular tubular output gears of the bevel gear differential mechanism, and the differential gear is installed in the differential gear shaft hole in the middle of the housing; a protruding planetary gear shaft or hole is integrally arranged on the conical back surface of the two output gears as a planetary carrier of the planetary gear differential mechanism; the planetary gear (21) is a cylindrical gear, and at least three planetary gears are respectively installed in the protruding planetary gear shaft or mounting hole on the output gear equivalent to the planetary carrier.

As shown in FIG3 , the conjoined sun gear (14) is in the shape of a circular tube, and the outer wall of the circular tube is respectively provided with teeth meshing with the two sets of planetary gears and meshing with them respectively. The two ends of the conjoined sun gear are smooth surfaces and are provided with power switching gears (4), and the power switching gears (4) are radially distributed plane equal height teeth with a pressure angle; the ring gear (16) is in the shape of a circular tube, and the outer wall of the circular tube is in contact with the inner wall of the shell body and provided with rotation support therefrom, and the inner walls of the two circular tubes are provided with internal teeth and meshing with the two sets of planetary gears (21) respectively, and the inner walls of the end faces of the two circular tubes facing away (that is, the back faces of the opposite faces) are integrally provided with an annular ring gear end plate (13) having the same inner diameter as the conjoined sun gear circular tube, and spline straight teeth (7) are provided on the annular inner wall of the ring gear end plate (13), and the opposite end faces of the ring gear end plate (13) are provided with teeth meshing with the power switching gears (4) at the two ends of the conjoined sun gear (14) and semi-meshing,

The alternating switching gear (9) is in the shape of a circular tube, and the outer wall of the circular tube is provided with teeth that mesh with the spline spur teeth (7) on the inner wall of the gear ring end plate (13), and the inner wall of the circular tube is provided with a helical gear (8), and the rotation directions of the helical gears (8) on the left and right sides are opposite, and the opposite end faces of the two alternating switching gears (9) are in contact with the smooth surfaces at both ends of the connected sun gear to transmit mutual axial force to achieve power switching; the axial thrust gear (5) is a circular tube with an outer end plate, and the outer wall of the outer end plate of the axial thrust gear is smaller than the inner wall of the gear ring end plate (13), and the outer wall of the circular tube is provided with teeth that mesh with the helical gear (8) of the alternating switching gear (9), and the inner wall of the circular tube is provided with spline spur teeth (7) as an external half shaft of the power output end, and a thrust spring (6) is provided between the axial thrust gear (5) and the end cover baffle (3);

In this embodiment, only the conjoined sun gear (14), the alternating switching gear 1 (9) and the axial thrust gear (5) are capable of axial movement;

In this embodiment, the two planetary gear differential mechanisms form an engaging closed loop through the meshing of the differential gear output gears of the connected sun gear and the bevel gear differential mechanism. This meshing closed loop is equivalent to a synchronous gear, which can realize the separation and engagement of the power switching gear at any time. In addition, after the turn is completed, the wheels on both sides rotate synchronously, the power is evenly distributed, and the axial force is balanced, so the power switching gear can smoothly return to the semi-engaged state and then go straight or turn continuously.

The above are the structural features, component shape features, meshing relationship and positional relationship features of this embodiment. The following describes the power transmission and working principle of the vehicle of this embodiment in different states:

Straight-ahead state: power is transmitted from the housing to the differential gear and output gear of the meshing closed-loop differential unit bevel gear differential mechanism. Since the output gear is also the planet carrier of the planetary gear differential mechanism, the two output gears transmit 50% of the power to the planetary gear mechanism respectively. The two planetary gear differential mechanisms have two power output end connected sun gears and ring gears respectively. In this embodiment, the power output end of the ring gear is connected to the power output half shaft through the alternating switching gear 1 and the axial thrust gear. If there is no power switching gear on the end face of the connected sun wheel and the power switching gear on the end plate of the ring gear, the power cannot be output. When moving straight ahead, due to the two alternating switching gears, the power output end of the ring gear is connected to the power output half shaft through the alternating switching gear 1 and the axial thrust gear. If there is no power switching gear on the end face of the connected sun wheel and the power switching gear on the end plate of the ring gear, the power cannot be output. The rotation direction of the gear-changing gear 1 is opposite, and it fits with the smooth surfaces of the end faces of the connected sun gear at both ends. Its axial force can keep the power switching gear in a semi-meshing state at all times. At this time, the end face of the axial thrust gear fits with the inner side of the end cover as a fulcrum of force. When reversing, the direction of the force changes, and the two axial thrust gears in turn push the alternating switching gear 1 and repeatedly push the end faces of the connected sun gear to fit together, keeping the power switching gear in a semi-meshing state. The two alternating switching gears 1 and the helical gears of the axial thrust gear both generate an axial thrust toward the middle when moving forward and reversing to achieve thrust balance. It is the connected sun gear that enables power to be output and the vehicle to move straight forward.

Turning state: When the vehicle enters the turning state, due to the differential speed difference, the thrust balance of the two alternating switching gears is broken, and the axial thrust on the outside is smaller than that on the inside. Therefore, under the action of the axial thrust of the bevel gear, the power switching gear on the connected sun gear is fully engaged with the power switching gear on the outer ring gear end plate, and the inner side is completely separated to realize the state of going straight to turning. After entering the curve, the axial thrust on the inner side always makes the inner side completely separated and the outer side completely engaged.

In this embodiment, the data of the planetary gear mechanism is as follows: cylindrical bevel gear, module 1.5, helix angle 45 degrees, ring gear teeth number 50, sun gear teeth number 40, planetary gear teeth number 5, the power distributed to the ring gears on both sides is 28%, and the power distributed to the sun gear is 22%. Since the power switching gear on the outer ring gear end plate is fully engaged and the inner side is completely disengaged, 22% of the power of the inner sun gear is also transmitted to the outer side, so the outer side gets 72% and the inner side only has 28%. In this way, the vehicle's body posture and trajectory in the curve are corrected, and the vehicle can turn at a higher speed.

Regarding the speed difference, the speed difference of the differential in the prior art is 2, that is, when turning, the less rotation of the inner side is added to the outer side, and this minus one plus one is exactly 2. In the turning state of this embodiment, the outer planetary gear mechanism has been locked by the connected sun gear, and it is the inner planetary gear mechanism that realizes the turn, which is equivalent to the ring gear not moving and the planetary carrier input and the sun gear output. According to the planetary gear calculation formula, the number of teeth of the planetary carrier is the number of teeth of the ring gear plus the number of teeth of the sun gear, which is 90. The number of teeth of the planetary carrier as the input, 90, divided by the number of teeth of the sun gear as the output, 40, is equal to 2.25. The speed difference of 2.25 in this embodiment divided by the speed difference of 2 of the existing differential is 12.5% greater than that of the existing differential.

Regarding anti-skid, due to the structural features of this embodiment, in order to slip, the vehicle must first enter a turning state, that is, the power switching gear on the connected sun gear must be pushed to one side to fully engage and the other side to fully disengage. Because the vehicle is not in a turning state, the thrust balance and output power balance will not be broken and the wheels will not slip; if one side of the wheel is completely suspended, under the action of the bevel gear differential mechanism, the power switching gear on the ring gear end plate on the suspended side will in turn push the power switching gear on the end face of the sun gear, and transmit the power to the non-suspended wheel through the connected sun gear, and at the same time can offset the axial thrust of the bevel gear on the alternating switching gear. However, if the vehicle has entered a turning state, there is no automatic anti-skid function. If slipping occurs, the power needs to be cut off (either by stepping on the clutch or releasing the accelerator). At this time, the thrust spring will push the connected sun gear back to a semi-engaged state on both sides (straight-ahead state). At this time, the wheel will not slip if power is applied again.

In this embodiment, the bevel gear differential mechanism of the meshing closed-loop differential unit can be equivalently replaced by a parallel-axis cylindrical gear differential mechanism.

As an alternative, this embodiment can also be as follows: internal teeth are arranged on the inner walls of the circular tubes of the two output gears of the bevel gear differential mechanism as the internal teeth of the gear ring of the planetary gear differential mechanism, and planet carriers are separately arranged as power output ends, the planet carriers are in the form of annular discs, and raised planet gear shafts or holes are arranged on the opposite surfaces of the two planet carriers, and teeth meshing with the power switching gear on the connected sun gear and semi-meshing are arranged on the opposite surfaces of the two planet carriers, spline spur teeth are arranged on the annular inner wall of the planet carrier, the planetary gear set is composed of two mutually meshing cylindrical gears, and the two cylindrical gears of the planetary gear set are respectively meshed with the connected sun gear and the gear ring, and at least three sets of planetary gear sets are installed on the planet carrier. On the planetary gear shaft, the alternating switching gear 1 is in the shape of a circular tube, and the outer wall of the circular tube is provided with teeth meshing with the spline spur teeth on the annular inner wall of the planet carrier, and the inner wall of the circular tube is provided with helical gears, and the rotation directions of the helical gears on the left and right sides are opposite. The opposite end faces of the two alternating switching gears 1 fit with the smooth surfaces at both ends of the connected sun gear to transmit mutual axial force to realize power switching; the axial thrust gear is a circular tube with an outer end plate, and the outer wall diameter of the outer end plate of the axial thrust gear is smaller than the annular inner wall of the planet carrier, and the outer wall of the circular tube is provided with teeth meshing with the helical gear of the alternating switching gear 1, and the inner wall of the circular tube is provided with spline spur teeth as the external half shaft of the power output end, and a thrust spring is provided between the axial thrust gear and the end cover baffle;

In this method, the power on the inside is greater than that on the outside when turning. Its advantage is that when used as a central differential, the power on the rear axle is greater than that on the front axle when turning.

Example 2

The dynamic differential, as shown in FIGS. 4 and 5, comprises: a housing (1), an end cover (2), a meshing closed-loop differential unit, an axial thrust gear (5) and an alternating switching gear 2 (10); the housing (1) is in the shape of a circular tube, the axial section of the end cover (2) is in the shape of a step and is provided with a half-shaft hole, an inwardly facing annular end cover baffle (3) is integrally provided at the outlet end of the half-shaft hole, and the housing and the end cover are screw-connected to form a supporting body of the dynamic differential; the meshing closed-loop differential unit is a two parallel planetary gear differential mechanism: comprising a planet carrier (22), a planetary gear (21) connected to a sun gear (14) and a ring gear (16); the planet carrier (22 ) is an annular disk, and protruding planetary gear shafts or mounting holes are arranged on the two end surfaces of the disk. The outer wall of the disk is relatively connected and fixed to the inner wall of the housing (1) or is arranged integrally; the planetary gears (21) are cylindrical gears, and at least three planetary gears (21) are respectively installed in the protruding planetary gear shafts or mounting holes at the two ends of the planetary carrier (22). The planetary gears (21) at the two ends of the planetary carrier (22) can be connected planetary gears; the connected sun gear (14) is in the shape of a circular tube, and the outer wall of the circular tube is respectively provided with teeth meshing with the planetary gears (21) and meshing respectively; the gear ring (16) is in the shape of a circular tube, and the outer wall of the circular tube is relatively connected to the housing (1) ) inner wall is attached to and provided with rotation support by it, inner wall of the circular tube is provided with internal teeth and meshes with the planetary gears (21) on both sides of the planetary carrier respectively, inner wall of the end face opposite to the circular tube is provided with an annular gear ring end plate (13) having the same diameter as the circular tube inner diameter of the integrated sun gear (14), end faces between the gear ring end plate (13) and the integrated sun gear (14) are provided with power switching gears (4), the power switching gears are radially distributed flat equal-height teeth with pressure angles, the alternating switching gear 2 is a circular tube with an outer end plate, both sides of the outer end plate are provided with teeth meshing with the gear ring end plate and the power switching gear of the integrated sun gear and semi-meshing, the inner wall of the circular tube is provided with an inner ring gear end plate (13) and meshing with the power switching gear of the integrated sun gear (14), ... The wall is provided with helical gears, and the rotation directions of the helical gears on the left and right sides are opposite. The opposite end faces of the two alternating switching gears are fitted together to transmit mutual axial force to realize power switching. The axial thrust gear (5) is a circular tube with an outer end plate. The outer wall of the circular tube is provided with teeth that mesh with the helical gear (8) of the alternating switching gear 2 (10). The outer walls of the outer end plates of the two axial thrust gears (5) are respectively fitted with the inner walls of the two gear ring end plates and provided with rotation support by them. The inner wall of the circular tube is provided with spline straight teeth (7) as an external half shaft of the power output end. A thrust spring (6) is provided between the axial thrust gear (5) and the end cover baffle (3).

In this embodiment, only the alternating switching gear 2 (10) and the axial thrust gear (5) are capable of axial movement.

In this embodiment, the meshing of the planetary gears, the connected sun gear and the ring gear of the two parallel planetary gear differential mechanisms of the meshing closed-loop differential unit forms a meshing closed-loop circuit. This meshing closed-loop circuit is equivalent to a synchronous gear, so the separation and engagement of the power switching gear can be achieved at any time. In addition, after the turn is completed, the wheels on both sides rotate synchronously, the power is evenly distributed, and the axial force is balanced, so the power switching gear can smoothly return to the semi-meshed state and then go straight or turn continuously.

The above are the structural features, component shape features, meshing relationship and positional relationship features between the components of this embodiment. Compared with Example 1, Example 2 omits a bevel gear differential mechanism, and the structure is simple and easy to implement. The following describes the power transmission and working principle of the vehicle of this embodiment in different states.

Straight state: the power goes from the housing to the planetary gears and then to the ring gears and the integrated sun gears on both sides. Since the ring gears and the integrated sun gears are half-engaged with the power switching gear of the alternating switching gear 2, the power goes to the alternating switching gear 2 to the axial thrust gear external half-shaft output.

Turning state: Due to the speed difference and power distribution difference (the power on the outside is less than that on the inside), the axial force balance of the alternating switching gear 2 on both sides is broken, and the inner ring gear end plate and the power switching gear of the alternating switching gear 2 change from semi-engagement to complete separation and fully engage with the power switching gear of the integrated sun gear, while the outer side is fully engaged with the power switching gear of the ring gear end plate to achieve turning.

This embodiment has no anti-skid locking function but only a strong limited slip function, but the power on the outside is greater than that on the inside, so the vehicle's body posture and trajectory in the curve are corrected, and the vehicle can turn at a higher speed.

2. As an alternative, this embodiment can also be as follows: the two end covers serve as planet carriers respectively, the raised planet gear shaft or hole is integrally arranged on the inner side of the end cover, the gear ring is arranged as a conjoined gear ring, the outer wall of the conjoined gear ring is in contact with the inner wall of the shell and provided with rotation support thereby, a circular ring gear ring end plate is integrally arranged in the middle of the inner wall of the conjoined gear ring, and a circular ring sun gear end plate is integrally arranged on the inner wall of the end faces of the two sun gears facing away from each other (that is, the back sides of the opposite faces), the two ends of the two sun gears are respectively in contact with the gear ring end plate and the planet carrier to limit their axial movement, and the opposite faces of the sun gear end plates and the two faces of the gear ring end plates are respectively provided with power switching Gears, the power switching gear of the alternating switching gear 2 is semi-engaged with the power switching gear on the sun gear end plate and the ring gear end plate respectively, the opposite end faces of the two alternating switching gear 2 round tubes are fitted to transmit mutual axial force to realize power switching, the helical gears on the outer wall of the two axial thrust gear round tubes are respectively meshed with the two helical gears of the alternating switching gear 2, the outer walls of the outer end plates of the two axial thrust gears are respectively fitted with the annular inner walls of the two sun gear end plates and provided with rotation support; the spline spur teeth of the two axial thrust gears are used as the external half shaft of the power output end, and a thrust spring is arranged between the axial thrust gear and the end cover baffle;

In this method, the power on the inside is greater than that on the outside when turning, and the speed of the outer wheel is 10% greater than that of the inside compared to the existing technology. Its advantage is that when used as a central differential, the power of the rear axle is greater than that of the front axle when turning, so that the vehicle's body posture and trajectory in the curve are corrected, or when used as a rear axle, it can easily drift through corners and can turn at a higher speed.

Example 3

The dynamic differential as shown in FIG6 comprises: a housing (1), an end cover (2), a meshing closed-loop differential unit, an alternating switching gear three (11) and an axial thrust gear (5), wherein the housing (1) is in the shape of a circular tube, the axial section of the end cover (2) is in the shape of a step and is provided with a semi-axle hole, an inwardly facing annular end cover baffle (3) is integrally provided at the outlet end of the semi-axle hole, and the housing and the end cover are screw-connected to form a supporting body of the dynamic differential; the meshing closed-loop differential unit is composed of two planetary gear differential mechanisms and a reversing gear (23): including a planetary gear set (27), a reversing gear (23), a planet carrier (22), a sun gear (15) and a ring gear (16); the planetary gear set (27) is composed of two cylindrical gears of equal length and partially meshed with each other; the reversing gear The wheel (23) is a cylindrical gear with an axial through hole; the planet carrier (22) is an annular disc, at least three sets of planetary gear set mounting holes (26) and a protruding reversing gear shaft (24) are evenly arranged on both sides of the disc, and the planetary gear set (27) and the reversing gear (23) are installed, and the reversing gear is meshed with the planetary gear of the unmeshed part on this side, the outer wall of the disc is relatively connected and fixed with the inner wall of the housing (1) or is integrally arranged, the sun gear (15) is in the shape of a circular tube, and the outer wall of the circular tube is provided with teeth meshing with the reversing gear (23) and meshing respectively; the gear ring (16) is in the shape of a circular tube, the outer wall of the circular tube is in contact with the inner wall of the housing (1) and is provided with rotation support, the inner wall of the circular tube is provided with internal teeth and meshes respectively with the planetary gears at both ends of the planet carrier (22), and the two circular tubes are opposite to each other (that is, opposite to each other). An annular gear ring end plate (13) is integrally provided on the inner wall of the end face (the back side of the opposite face) and is respectively fitted with the end face of the sun gear (15). The end faces of the two gear ring end plates (13) facing away from each other (that is, the back side of the opposite face) are provided with a power switching gear (4). The end faces of the two sun gears (15) facing each other are provided with a power switching gear (4). The power switching gear (4) is a radially distributed plane with equal height teeth having a pressure angle. The alternating switching gear three (11) is in the shape of a circular tube. A helical gear (8) is provided on the inner wall of the circular tube, and the rotation directions of the helical gears (8) on the left and right sides are opposite. The gear ring end plate (13) and the sun gear (15) are rotatably mounted on the outer wall of the circular tube. Two annular discs are provided at both ends of the circular tube. One annular disc is separately provided with the circular tube and fixed by spline connection. Another annular disc is integrally arranged with the circular tube, the integrally arranged annular disc is provided with teeth meshing with and semi-meshing the power switching gear (4) on the gear ring end plate (13), the separately arranged annular disc is provided with teeth meshing with and semi-meshing the power switching gear (4) on the sun gear (15), and the two opposite end faces of the alternating switching gears (three) (separately arranged annular discs) fit together to transmit mutual axial force to realize power switching; the axial thrust gear (5) is a circular tube with an outer end plate, the outer wall of the circular tube is provided with teeth meshing with the helical gear (8) of the alternating switching gear three (10), the inner wall of the circular tube is provided with spline straight teeth (7) as an external half shaft of the power output end, and a thrust spring (6) is provided between the axial thrust gear (5) and the end cover baffle (3);

In this embodiment, only the alternating switching gear three (11) and the axial thrust gear (5) can move axially;

In this embodiment, the meshing of the planetary gears, reversing gears, sun gears and ring gears of the two parallel planetary gear differential mechanisms of the meshing closed-loop differential unit forms a meshing closed-loop circuit. This meshing closed-loop circuit is equivalent to a synchronous gear, so the separation and engagement of the power switching gear can be achieved at any time. In addition, after the turn is completed, the wheels on both sides rotate synchronously, the power is evenly distributed, and the axial force is balanced, so the power switching gear can smoothly return to a semi-meshed state and then go straight or turn continuously.

The above are the structural features, component shape features, meshing relationship and positional relationship features of this embodiment. The following describes the power transmission and working principle of the vehicle of this embodiment in different states:

Straight-ahead state: the power is transmitted from the housing to the planetary gears, the reversing gears to the sun gears and ring gears on both sides, and then to the alternating switching gear three and the axial thrust gear to output the power to the external half-shaft.

Turning state: Due to the speed difference and power distribution difference (the power on the outside is less than that on the inside), the axial force balance of the alternating switching gears 3 on both sides is broken. The inner alternating switching gear 3 is fully meshed with the power switching gear on the ring gear end plate and completely separated from the power switching gear on the sun gear. The outer alternating switching gear 3 is completely separated from the power switching gear on the gear end plate and fully meshed with the power switching gear on the sun gear to achieve turning.

This embodiment has an anti-skid locking function, which is that the power on the inside is greater than that on the outside when turning. The power on the inside is greater than that on the outside and the rotation speed of the outside wheel is 10% greater than that of the inside compared to the prior art. Its advantage is that when used as a central differential, the power on the rear axle is greater than that on the front axle when turning, so that the vehicle's body posture and trajectory in the curve are corrected. Or when used as a rear axle, it can easily perform drifting and turning movements, and can turn at a higher speed.

As an alternative, this embodiment can also be as follows: power switching gears are respectively arranged on the surfaces between the ring gear end plate and the sun gear, the alternating switching gear three is a circular tube with an outer end plate, and the two end faces of the outer end plate are provided with teeth meshing with the power switching gears on the ring gear end plate and the sun gear and semi-meshing, and the two opposite end faces of the two alternating switching gears three fit together to transmit mutual axial force to realize power switching; the axial thrust gear is a circular tube with an outer end plate, and the outer wall of the circular tube is provided with teeth meshing with the helical gear of the alternating switching gear three, and the inner wall of the circular tube is provided with spline spur teeth as an external half-shaft of the power output end, the outer walls of the outer end plates of the two axial thrust gears are respectively fitted with the annular inner walls of the two ring gear end plates and provided with rotation support thereby, and a thrust spring is arranged between the axial thrust gear and the end cover baffle.

In this way, if the number of teeth on the reversing gear is made twice that of the differential gear, the power on the outside will be greater than that on the inside, and the speed of the outside wheel will be 10% greater than that on the inside compared to the existing technology. In this way, the vehicle's body posture and trajectory in the curve are corrected, and the vehicle can turn at a higher speed.

Example 4

The dynamic differential comprises, as shown in Fig. 7 and Fig. 8, two integral end covers (20), a meshing closed-loop differential unit, an alternating switching gear four (12) and an axial thrust gear (5), and is characterized in that: one end of the integral end cover (20) is open, the axial section of the integral end cover (20) is stepped and provided with a half-shaft hole, an inwardly facing annular end cover baffle (3) is integrally provided at the outlet end of the half-shaft hole, the end surfaces opposite to the openings of the two integral end covers are radially provided with mounting holes for a double-layer differential gear frame (25), and the two integral end cover screws (20) are connected and fixed together to form a supporting body of the dynamic differential; the meshing closed-loop differential unit is composed of a double-layer bevel gear differential mechanism, including a double-layer differential gear (17), a double-layer differential gear The double-layer differential gear (17) is composed of two bevel gears with the same number of teeth and modulus, which are axially integrated with the inner and outer differential gears, and the axial center of the double-layer differential gear (17) is provided with a through hole; the two outer layer output gears (19) are respectively meshed with the outer layer differential gears axially at 90 degrees, and the two inner layer output gears (18) are respectively meshed with the inner layer differential gears axially at 90 degrees; the double-layer differential gear frame (25) is in the shape of a circular tube, and the outer wall of the circular tube is integrally provided with double-layer differential gear shafts equal in number to the double-layer differential gears (17), and the double-layer differential gears (17) are installed on the double-layer differential gear shafts on the double-layer differential gear frame (25). The double-layer differential gear frame (25) is installed in the mounting holes of the double-layer differential gear frame radially arranged on the end faces opposite to the openings of the two end covers; the outer layer output gear (19) and the inner layer output gear are axially provided with through holes, the outer layer output gear cone back is integrally provided with an inward annular end plate, the surface between the outer layer output gear annular end plate and the inner layer output gear is respectively provided with power switching gears, the power switching gear (4) is a radially distributed plane with equal height teeth with a pressure angle, the alternating switching gear four (12) is a circular tube with an outer end plate, the inner wall of the circular tube is provided with a helical gear (8) and the rotation directions of the helical gears on the left and right sides are opposite, and the two outer end plates are respectively provided with the outer layer output gear (19) and the inner layer output gear (18) on both sides. The teeth of the power switching gears are meshed and semi-meshed, the round tube is rotatably mounted on the inner wall of the inner layer output gear through hole, and the opposite end faces of the round tubes of the two alternating switching gears (12) are fitted to transmit mutual axial force to achieve power switching; the axial thrust gear (5) is a round tube with an outer end plate, the outer wall of the round tube is provided with teeth meshed with the helical gear (8) of the alternating switching gear (12), and the inner wall is provided with spline straight teeth (7) as the external half shaft of the power output end; a thrust spring (6) is arranged between the axial thrust gear (5) and the end cover baffle (3), and the outer walls of the outer end plates of the two axial thrust gears are respectively fitted with the annular inner walls of the annular end plates of the two outer layer output gears and provided with rotation support therefrom.

In this embodiment, only the alternating switching gear four (12) and the axial thrust gear (5) are capable of axial movement;

In this embodiment, the meshing of the outer output gear (19) of the double-layer bevel gear differential mechanism of the meshing closed-loop differential unit and the inner output gear with the double-layer differential gear forms a meshing closed-loop circuit, which is equivalent to a synchronous gear, so the separation and meshing of the power switching gear can be achieved at any time. In addition, after the turn is completed, the wheels on both sides rotate synchronously, the power is evenly distributed and the axial force is balanced, so the power switching gear can smoothly return to the semi-meshing state and then go straight or turn continuously.

The above are the structural features, component shape features, meshing relationship and positional relationship features between components of this embodiment. The following describes the power transmission and working principle of the vehicle of this embodiment in different states.

In straight-ahead state, the power is transmitted from the integrated end cover to the double-layer differential gear carrier, to the double-layer differential gear, to the inner output gear and the outer output gear, and then to the alternating switching gear four and the axial thrust gear to the external half-shaft output power.

Turning state: Since the number of teeth and module of the double-layer differential gears are equal, the number of teeth of the inner output gear is smaller than that of the outer output gear. Due to the difference in the number of teeth, two gears with the same number of teeth drive two gears with different numbers of teeth at the same time, so the speeds of the two driven gears must be different. At the moment of turning, the inner output gear on the inside is actually faster than the outer output gear and turns backward to disengage the power switching gear of the alternating switching gear four, while the outer output gear on the outside is disengaged from the power switching gear of the alternating switching gear four. Under the action of the speed difference and axial force, the power switching gear of the inner alternating switching gear four and the outer output gear changes from semi-engagement to complete separation and complete engagement with the inner output gear, and the power switching gear of the outer alternating switching gear four and the outer output gear changes from semi-engagement to complete engagement and complete separation from the inner output gear to achieve turning, and the power on the outside is greater than that on the inside.

Regarding anti-skid, if one side of the wheel is suspended in the air, since the number of teeth and module of the double-layer differential gears are equal, the number of teeth of the inner output gear is smaller than that of the outer output gear. Due to the difference in the number of teeth, two gears with the same number of teeth drive two gears with different numbers of teeth at the same time, so the speeds of the two driven gears must be different. The inner output gear on the inside is actually faster than the outer output gear and after it turns backward and disengages from the power switching gear of the alternating switching gear four, it will contact and lock with the other side of the tooth gap of the semi-meshing power switching gear. On the outside, after the outer output gear disengages from the power switching gear of the alternating switching gear four, it will contact and lock with the other side of the tooth gap of the semi-meshing power switching gear and transmit power to the inside while balancing the axial thrust of the inner alternating switching gear four. Therefore, even if one side of the wheel is suspended in the air, it will not slip.

As an alternative, the present embodiment may also be as follows: the meshing closed-loop differential unit is a bevel gear differential mechanism, the differential gear rack is in the shape of a circular tube, the outer wall of the circular tube is integrally provided with differential gear shafts equal to the number of differential gears, the differential gears are mounted on the differential gear shafts on the differential gear rack, and the differential gear rack is mounted in the mounting holes of the differential gear rack on the two integral end covers; at least two differential gears are axially meshed at 90 degrees between the two output gears, through holes are axially provided on the two output gears and spline spur teeth are provided on the inner walls of the through holes, a power switching gear is provided on the end face between the two output gears, a thrust circular tube is provided between the two output gears, and the end faces of both ends of the thrust circular tube are provided with power switching gears on the end faces of the output gears The teeth of the meshing gears are semi-meshed, the outer wall of the thrust circular tube is in contact with the inner wall of the differential gear frame and is supported for rotation therefrom, the alternating switching gear four is in the shape of a circular tube, the outer wall of the circular tube is provided with teeth meshing with the spline spur teeth on the inner wall of the output gear through hole, a helical gear is provided on the inner wall of the circular tube, and the rotation directions of the helical gears on the left and right sides are opposite, the opposite end faces of the two alternating switching gears four are in contact with the smooth surfaces at both ends of the thrust circular tube to transmit mutual axial force to realize power switching; the helical gears on the outer walls of the two axial thrust gear circular tubes are respectively meshed with the helical gears of the two alternating switching gears four, the spline spur teeth of the axial thrust gear serve as the external half-shaft of the power output end, and a thrust spring is provided between the axial thrust gear and the end cover baffle.

The result of this method is that it can only prevent slipping, but the power is evenly distributed on both sides.

Claims (5)

1. A dynamic differential, comprising: a housing, an end cover, a meshing closed-loop differential unit, an alternating switching gear 1, an axial thrust gear and a thrust spring, wherein: the housing is in a cylindrical shape, at least two differential gear shaft holes are radially arranged in the middle of the housing, the axial section of the end cover is in a stepped shape and is provided with a half-shaft hole, an inwardly annular end cover baffle is integrally arranged at the outlet end of the half-shaft hole, and the housing and the end cover are screw-connected to form a supporting body of the dynamic differential; The meshing closed-loop differential unit is a bevel gear differential mechanism arranged between two planetary gear mechanisms, the cone backs of the two output gears of the bevel gear differential mechanism are integrally provided with planetary gear shafts or holes as the planet carriers of the two planetary gear differential mechanisms, the sun gears of the two planetary gear mechanisms are tubular connected sun gears, the two ends of the connected sun gears are smooth surfaces and are provided with power switching gears, and the power switching gears are radially distributed plane equal height teeth with pressure angles; spline spur teeth are arranged on the annular inner wall of the ring gear end plate, and the opposite end faces of the ring gear end plate are provided with teeth meshing with the power switching gears at both ends of the connected sun gear and semi-meshing; or the inner walls of the two output gears of the bevel gear differential mechanism are provided with internal teeth as the inner teeth of the gear rings of the two planetary gear differential mechanisms, and two planet carriers are separately provided as the power output ends, the planet carriers are annular discs, the opposite faces of the two planet carriers are provided with protruding planetary gear shafts or holes, the opposite faces of the two planet carriers are provided with teeth meshing with the power switching gears on the connected sun gear and semi-meshing, and the annular inner walls of the two planet carriers are provided with spline spur teeth; The alternating switching gear 1 is in the shape of a circular tube, and the outer wall of the circular tube is provided with teeth meshing with the spline spur teeth on the inner wall of the gear ring end plate or the inner wall of the planetary carrier ring, and the inner wall of the circular tube is provided with helical gears, and the rotation directions of the helical gears on the left and right sides are opposite, and the opposite end faces of the two alternating switching gears 1 are fitted with the smooth surfaces at both ends of the connected sun gear to transmit mutual axial force to realize power switching; The axial thrust gear is a circular tube with an outer end plate. The outer wall diameter of the outer end plate of the axial thrust gear is smaller than the inner wall of the ring gear end plate or the annular inner wall of the planetary carrier. The outer wall of the circular tube is provided with teeth that mesh with the helical gear of the alternating switching gear one. The inner wall of the circular tube is provided with spline spur teeth as an external half-shaft at the power output end. A thrust spring is provided between the axial thrust gear and the end cover baffle. 2. The dynamic differential according to claim 1: the meshing closed-loop differential unit is a two parallel planetary gear differential mechanism, the planet carrier is integrally arranged in the middle of the inner wall of the shell, the planetary gears are connected or split cylindrical gears, and the surfaces between the connected sun gear and the ring gear end plate are respectively provided with power switching gears; the alternating switching gear 2 is a circular tube with an outer end plate, and the two surfaces of the outer end plate are provided with teeth that mesh with the power switching gears on the ring gear end plate and the connected sun gear and are semi-meshed, and the inner wall of the circular tube is provided with helical gears, and the rotation directions of the helical gears on the left and right sides are opposite, and the opposite end faces of the two alternating switching gear 2 circular tubes are fitted to transmit mutual axial force to realize power switching; the helical gears on the outer walls of the circular tubes of the two axial thrust gears are respectively meshed with the helical gears of the two alternating switching gears 2, and the outer walls of the outer end plates of the two axial thrust gears are respectively fitted with the annular inner walls of the two ring gear end plates and provided with rotation support therefrom; or the two end covers are respectively used as planet carriers, and the raised planetary gear shafts or holes are integrally arranged at the end On the inside of the cover, the gear ring is arranged as a connected gear ring and the outer wall of the connected gear ring is in contact with the inner wall of the shell and provided with rotation support thereby. A circular ring gear end plate is integrally arranged in the middle of the inner wall of the connected gear ring. The two sun gears are circular tubular. The inner walls of the end faces of the two sun gears facing away from each other (that is, the backs of the opposite faces) are integrally provided with a circular ring gear end plate. The two ends of the two sun gears are respectively in contact with the gear ring end plates and the planetary carriers to limit their axial movement. Power switching gears are respectively arranged on the opposite faces of the sun gear end plates and the two faces of the gear ring end plates. The power switching gears of the alternating switching gear 2 are respectively semi-meshed with the power switching gears on the sun gear end plates and the ring gear end plates. The opposite end faces of the two alternating switching gear 2 circular tubes are in contact with each other to transmit mutual axial force to realize power switching. The helical gears on the outer walls of the two axial thrust gear circular tubes are respectively meshed with the helical gears of the two alternating switching gears 2. The outer walls of the outer end plates of the two axial thrust gears are respectively in contact with the annular inner walls of the two sun gear end plates and provided with rotation support thereby. 3. The dynamic differential according to claim 1: the meshing closed-loop differential unit is composed of two planetary gear differential mechanisms plus a reversing gear, the planetary gear set is composed of two cylindrical gears of equal length and partially meshed with each other, the planet carrier is integrally arranged in the middle of the inner wall of the shell, at least three sets of planetary gear set mounting holes and three reversing gear shafts are evenly arranged on both sides of the planet carrier, and the planetary gear set and the reversing gear are installed, and the reversing gear is meshed with the unmeshed part of the planetary gear on this side, the power switching gear is arranged on the opposite faces (that is, the back faces of the opposite faces) of the two ring gear end plates, and the power switching gear is arranged on the opposite end faces of the two sun gears; the alternating switching gear three is in the shape of a circular tube, the inner wall of the circular tube is arranged with a helical gear, and the rotation directions of the helical gears on the left and right sides are opposite, the ring gear end plate and the sun gear are rotatably mounted on the outer wall of the circular tube, two annular discs are arranged at both ends of the circular tube, one annular disc is separately arranged with the circular tube and fixed by spline connection, and the other annular disc is integrally arranged with the circular tube, and the integrally arranged annular disc is arranged with the power switching gear on the ring gear end plate The teeth of the meshing wheels are semi-meshed, the separately arranged annular disk is provided with teeth meshing with the power switching gear on the sun gear and semi-meshed, the opposite end faces of the two alternating switching gears three (separately arranged annular disks) fit together to transmit mutual axial force to realize power switching, and the helical gears of the two axial thrust gears are respectively meshed with the helical gears of the two alternating switching gears three; or the surfaces between the ring gear end plate and the sun gear are respectively provided with power switching gears, the alternating switching gear three is a circular tube with an outer end plate, and the two surfaces of the outer end plate are provided with teeth meshing with the power switching gear on the ring gear end plate and the sun gear and semi-meshed, the inner wall of the circular tube is provided with helical gears, and the rotation directions of the helical gears on the left and right sides are opposite, the opposite end faces of the circular tubes of the two alternating switching gears three fit together to transmit mutual axial force to realize power switching, the helical gears on the outer walls of the circular tubes of the two axial thrust gears are respectively meshed with the helical gears of the two alternating switching gears three, and the outer walls of the outer end plates of the two axial thrust gears are respectively fitted with the annular inner walls of the two ring gear end plates and provided with rotation support thereby. 4. The dynamic differential according to claim 1: the meshing closed-loop differential unit is a double-layer bevel gear differential mechanism, the double-layer differential gear is composed of two bevel gears with equal modulus axially forming an inner and outer differential gears, and a through hole is set in the axial center of the double-layer differential gear; the two outer output gears are respectively meshed with the outer differential gears axially at 90 degrees, and the two inner output gears are respectively meshed with the inner differential gears axially at 90 degrees, the double-layer differential gear frame is in the shape of a circular tube, and the outer wall of the circular tube is integrally provided with double-layer differential gear shafts equal to the number of double-layer differential gears, the double-layer differential gears are installed on the double-layer differential gear shafts on the double-layer differential gear frame, and the double-layer differential gear frame is installed on the installation of the double-layer differential gear frame on the two integral end covers. The outer output gear and the inner output gear are axially provided with through holes, the outer output gear cone back is integrally provided with an inward annular end plate, and the surfaces between the annular end plate of the outer output gear and the inner output gear are respectively provided with power switching gears; the alternating switching gear four is a circular tube with an outer end plate, and the two surfaces of the outer end plate are provided with teeth meshing with the annular end plate of the outer output gear and the power switching gear on the inner output gear and semi-meshing, a helical gear is provided on the inner wall of the circular tube, and the rotation directions of the helical gears on the left and right sides are opposite, and the opposite end faces of the two alternating switching gear four circular tubes are fitted to transmit mutual axial force to realize power switching, and the helical gears on the outer walls of the two axial thrust gear circular tubes are respectively meshed with the helical gears of the two alternating switching gear fours The outer walls of the outer end plates of the two axial thrust gears are respectively attached to the annular inner walls of the two outer layer output gear annular end plates and provided with rotation support therefrom; or the meshing closed-loop differential unit is a bevel gear differential mechanism, the differential gear frame is in the shape of a circular tube, and the outer wall of the circular tube is integrally provided with differential gear shafts equal to the number of differential gears, the differential gears are mounted on the differential gear shafts on the differential gear frame, and the differential gear frame is mounted in the mounting holes of the differential gear frame on the two integral end covers; at least two differential gears are meshed axially at 90 degrees between the two output gears, through holes are axially provided on the two output gears and spline spur teeth are provided on the inner walls of the through holes, a power switching gear is provided on the end face between the two output gears, and a thrust circular gear is provided between the two output gears. Tube, the end faces of both ends of the thrust circular tube are provided with teeth meshing with the power switching gear on the end face of the output gear and semi-meshing, the outer wall of the thrust circular tube is in contact with the inner wall of the differential gear frame and provided with rotation support therefrom, the alternating switching gear four is in the shape of a circular tube, the outer wall of the circular tube is provided with teeth meshing with the spline spur teeth on the inner wall of the output gear through hole and meshing, the inner wall of the circular tube is provided with helical gears and the rotation directions of the helical gears on the left and right sides are opposite, the opposite end faces of the two alternating switching gears four are in contact with the smooth surfaces at both ends of the thrust circular tube to transmit mutual axial force to realize power switching; the helical gears on the outer walls of the two axial thrust gear circular tubes are respectively meshed with the helical gears of the two alternating switching gears four, and the spline spur teeth of the axial thrust gears serve as the external half-axles of the power output end. 5. The dynamic differential according to claim 1: the outer wall of the housing can also be integrally provided with a main reduction gear for external power input of the dynamic differential.