CN118009015A

CN118009015A - Dynamic differential mechanism

Info

Publication number: CN118009015A
Application number: CN202410315731.9A
Authority: CN
Inventors: 魏家斌; 魏子媛
Original assignee: Individual
Current assignee: Individual
Priority date: 2023-11-01
Filing date: 2024-03-14
Publication date: 2024-05-10
Also published as: CN117345833A

Abstract

The invention discloses a dynamic differential mechanism, in particular to the field of automobile transmission, and aims to solve the problems that an existing differential mechanism adopts an equal proportion distribution mode (namely 50% of power is distributed on two sides), and when the differential mechanism encounters a wet road surface, wheels are easy to slip, so that an automobile cannot run. The inventor carries out brand-new design to the structure of differential mechanism, and the differential mechanism after the improvement can realize that in the bend driving, not only outside power is greater than inboard power can also realize effectively adjusting turn track and automobile body gesture to the wheel can not skid, promotes the cross country of car and highway control performance better, has higher originality.

Description

Dynamic differential mechanism

Technical Field

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

Background

At present, the differential mechanism is widely applied to the field of automobiles, and has an important function for the operation of automobiles. The practice shows that when the automobile turns, the friction force between the outer wheels and the ground is larger due to the action of centrifugal force, so that the outer wheels need larger power and higher rotating speed, and the existing differential mechanism adopts an equal-proportion distribution mode (namely, 50% of power is distributed on one side) and cannot realize dynamic distribution.

The function of the differential is determined, the main differences being that: the transmission structure is different; the transmission structure determines the overall performance of the differential, and is the core and the root of the differential. The applicant has studied about the expansion of the differential function since 2022 and has proposed a differential structure with a new function, for which purpose the present application provides a dynamic differential.

Disclosure of Invention

The invention aims to provide a differential mechanism, which aims at solving the problems that the existing differential mechanism adopts an equal-proportion distribution mode (namely, one side distributes 50% of power), and wheels are easy to slip when the differential mechanism encounters a wet road surface, so that an automobile cannot run. The inventor carries out brand-new design to the structure of differential mechanism, and the differential mechanism after the improvement can realize in the bend driving, and outside power is greater than the inboard and carries out effective adjustment to turn track and automobile body gesture, promotes the steering performance of car better, and the wheel can not skid, has higher originality.

As described above, most of the power distribution of the existing differential adopts a mode of equally distributing power on both sides, that is, equally distributing power on both sides by 50%. In this way, a good match of the power is not achieved when turning. Meanwhile, when the existing differential mechanism is adopted and wheels pass through a wet road surface, the wheels are easy to slip, and the running of the vehicle is not facilitated.

The basic idea of the invention is as follows: with prior art differential mechanisms such as: the bevel gear differential mechanism, the parallel shaft cylindrical gear differential mechanism and the planetary gear differential mechanism are combined to form the meshed closed-loop differential unit, and the axial thrust of the bevel gear and the power switching gear are used for alternately switching power to ensure that the power on the outer side is greater than the dynamic distribution on the inner side when the vehicle turns, and the rotating speed difference of the wheels on the outer side is about 10 percent greater than that of the existing differential mechanism, so that the automobile body posture and turning track can be adjusted more conveniently, and better operability is realized.

Drawings

The invention will be described with respect to 4 embodiments and with reference to the accompanying drawings to illustrate various constructions and principles thereof.

Fig. 1 is an internal structure view of embodiment 1.

Fig. 2 is a component view of the internal structure of embodiment 1.

Fig. 3 is a conjoined sun gear view of embodiment 1.

Fig. 4 is an internal structure view of embodiment 2.

Fig. 5 is a component view of the internal structure of embodiment 2.

Fig. 6 is a component view of the internal structure of embodiment 3.

Fig. 7 is an internal structure view of embodiment 4.

Fig. 8 is a component view of the internal structure of embodiment 4.

The marks in the figure: 1. the gear comprises a shell, 2, an end cover, 3, an end cover baffle, 4, a power switching gear, 5, an axial thrust gear, 6, a thrust spring, 7, spline straight teeth, 8, a bevel gear, 9, a first alternate switching gear, 10, a second alternate switching gear, 11, a third alternate switching gear, 12, a fourth alternate switching gear, 13, a gear ring end plate, 14, a conjoined sun gear, 15, a sun gear, 16, a gear ring, 17, a double-layer differential gear, 18, an inner-layer output gear, 19, an outer-layer output gear, 20, an integral end cover, 21, a planetary gear, 22, a planetary carrier, 23, a reversing gear, 24, a reversing gear shaft, 25, a double-layer differential gear carrier, 26, a planetary gear set mounting hole, 27, a planetary gear set, 28, an integrally arranged annular disc, 29 and a separately arranged annular disc.

Detailed Description

All of the features disclosed in this specification, or all of the steps in a method or process disclosed, may be combined in any combination, except for mutually exclusive features and/or steps.

Any feature disclosed in this specification may be replaced by alternative features serving the same or equivalent purpose, unless expressly stated otherwise. That is, each feature is one example only of a generic series of equivalent or similar features, unless expressly stated otherwise.

Example 1

Dynamic differentials, as in fig. 1,2, include: casing, end cover, meshing closed loop differential unit, alternate switching gear one, axial thrust gear and thrust spring, characterized by: the shell is in a circular tube shape, at least two differential gear shaft holes are radially formed in the middle of the shell, the axial section of the end cover is in a step shape and is provided with a half shaft hole, an inward circular end cover baffle is integrally arranged at the outlet end of the half shaft hole, the shell and an end cover screw are connected together to form a supporting main body of the dynamic differential mechanism, a bevel gear differential mechanism is arranged between two planetary gear mechanisms in a meshing closed-loop differential unit, at least two differential gears are meshed between two circular tube-shaped output gears of the bevel gear differential mechanism in an axial direction by 90 degrees, and the differential gears are arranged in the differential gear shaft holes in the middle of the shell; convex planetary gear shafts or holes are integrally arranged on the back surfaces of the cones of the two output gears and used as planetary carriers of a planetary gear differential mechanism; the planetary gears (21) are cylindrical gears, and at least three planetary gears are respectively installed in a convex planetary gear shaft or an installation hole corresponding to an output gear of the planet carrier.

As shown in fig. 3, the conjoined sun gear (14) is in a circular tube shape, the outer wall of the circular tube is respectively provided with teeth meshed with two groups of planetary gears and respectively meshed with the two groups of planetary gears, 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 plane constant-height teeth with pressure angles and distributed radially; the gear ring (16) is in a circular tube shape, the outer wall of the circular tube is adhered to the inner wall of the shell and is provided with rotary support by the inner wall, the inner walls of the two circular tubes are provided with inner teeth and are respectively meshed with two groups of planetary gears (21), the inner walls of the end faces of the two opposite circular tubes (namely the back faces of opposite faces) are integrally provided with a circular ring gear end plate (13) which is equal to the inner diameter of the circular tube of the conjoined sun gear, the annular inner wall of the gear ring end plate (13) is provided with spline straight teeth (7), the opposite end faces of the gear ring end plate (13) are provided with teeth meshed with the power switching gears (4) at two ends of the conjoined sun gear (14) and are semi-meshed,

The first alternate switching gears (9) are in a circular tube shape, teeth meshed with spline straight teeth (7) on the inner wall of the gear ring end plate (13) are arranged on the outer wall of the circular tube and meshed, the bevel gears (8) are arranged on the inner wall of the circular tube, the rotation directions of the bevel gears (8) on the left side and the right side are opposite, and the opposite end surfaces of the first alternate switching gears (9) are attached to smooth surfaces on the two ends of the conjoined sun gear to transfer mutual axial force so as to realize power switching; the axial thrust gear (5) is a circular tube outer end plate, 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), teeth meshed with the bevel gears (8) of the alternate switching gears (9) are arranged on the outer wall of the circular tube and meshed with the bevel gears, spline straight teeth (7) serving as power output ends are arranged on the inner wall of the circular tube and are externally connected with a half shaft, and a thrust spring (6) is arranged between the axial thrust gear (5) and the end cover baffle (3);

In the embodiment, only the conjoined sun gear (14), the alternate switching gear I (9) and the axial thrust gear (5) can axially move;

In this embodiment, the two planetary gear differential mechanisms form a closed-loop meshing circuit by meshing the differential gear output gears of the conjoined sun gear and the bevel gear differential mechanism, the closed-loop meshing circuit is equivalent to a synchronous gear, separation and meshing of the power switching gears can be realized at any time, and after turning is completed, wheels on two sides synchronously rotate, and power is evenly distributed to the axial force and balanced, so that the power switching gears can smoothly return to a semi-meshing state and then directly or continuously turn.

The structural features, the component shape features, the engagement relationship between the components, and the positional relationship features of the present embodiment are described above, and the power transmission and the operation principle of the vehicle of the present embodiment in different states are described below:

Straight running state: in the embodiment, the power output end of the gear ring is connected with the power output half shaft through alternately switching the first axial thrust gear and the second axial thrust gear, if the power switching gear on the end face of the connected sun wheel is not in half engagement with the power switching gear on the end plate of the gear ring, the power cannot be output, and the axial force of the two alternately switching gears is applied to the smooth surfaces of the end faces of the two connected sun gears to enable the power switching gears to always maintain a half engagement state, and the end faces of the axial thrust gears are applied to the inner sides of end covers as force fulcra.

Turning state: when the vehicle enters a turning state, the thrust balance of the two alternate switching gears I is broken due to the slip speed difference, the axial thrust on the outer side is smaller than that on the inner side, so that under the action of the axial thrust of the bevel gears, the power switching gear on the conjoined sun gear is completely meshed with the power switching gear on the outer side gear ring end plate, the inner side is completely separated to realize a state of going straight to the turning, and the axial thrust on the inner side after entering the turning always enables the inner side to be completely separated and the outer side to be completely meshed.

In this embodiment, the data of the planetary gear mechanism is as follows: the cylindrical helical gear has the modulus of 1.5, the helical angle of 45 degrees, the tooth number of the gear ring of 50, the tooth number of the sun gear of 40 and the tooth number of the planetary gear of 5, the power distributed to the gears on two sides of the helical gear is 28 percent, the power distributed to the sun gear is 22 percent, and the power on the 22 percent of the sun gear on the inner side is transmitted to the outer side because the power switching gear on the end plate of the outer side is completely meshed with the inner side and completely separated, so that the inner side is only 28 percent of the outer side, the posture and the track of the vehicle in a curve are corrected, and the vehicle can be overturned with higher speed.

The rotational speed difference is as follows: the rotational speed difference of the differential in the prior art is 2, that is, the inner side is less turned and added to the outer side, the reduction is just 2, while in the turning state of the embodiment, the outer side planetary gear mechanism is locked by the conjoined sun gear to realize turning, which is equivalent to the input of the planet carrier with the fixed gear to the sun gear output, the number of teeth of the planet carrier is the number of teeth of the gear and the number of teeth of the sun gear is 90 according to the calculation formula of the planet gear, the number of teeth of the planet carrier is 90 which is taken as input divided by the number of teeth of the sun gear which is taken as output is 40 which is equal to 2.25, and the rotational speed difference 2.25 of the embodiment divided by the rotational speed difference 2 of the existing differential is 12.5% larger than the existing differential.

The slip resistance is as follows: because the structural characteristics of the embodiment determine that the skid must first enter a turning state, that is, the power switching gear on the conjoined sun gear is pushed to one side to be completely engaged with one side to be completely separated, because the vehicle does not break the thrust balance and the output power balance wheels in the turning state and does not skid; if one side of the wheel is completely suspended, under the action of the bevel gear differential mechanism, the power switching gear on the end plate of the gear ring on one side of the suspended gear ring can reversely push the power switching gear on the end surface of the sun gear, power is transmitted to the wheel without suspension through the conjoined sun gear, and meanwhile, the axial thrust of the bevel gear on the alternative switching gear can be counteracted, but when the vehicle enters a turning state, the automatic anti-skid function is not available, if slipping occurs, power is required to be cut off (the clutch is stepped on or the throttle is released), at the moment, the thrust spring can push the conjoined sun gear back to a semi-meshing state (straight state) at both sides, and at the moment, the wheel with the power cannot slip.

The bevel gear differential mechanism of the meshing closed-loop differential unit of the embodiment can be equivalently replaced by a parallel-shaft cylindrical gear differential mechanism.

Alternatively the present embodiment may also be such that: the inner walls of circular tubes of two output gears of the bevel gear differential mechanism are provided with inner teeth serving as inner teeth of a gear ring of the planetary gear differential mechanism, planetary carriers are respectively and independently arranged to serve as power output ends, the planetary carriers are circular discs, opposite surfaces of the two planetary carriers are provided with convex planetary gear shafts or holes, opposite surfaces of the two planetary carriers are provided with teeth meshed with power switching gears on the conjoined sun gears and are semi-meshed, the annular inner walls of the planetary carriers are provided with spline straight teeth, the planetary gear sets are composed of two meshed cylindrical gears, the two cylindrical gears of the planetary gear sets are meshed with the conjoined sun gears and the gear rings respectively, at least three groups of planetary gear sets are arranged on planetary gear shafts on the planetary carriers, the first alternate switching gears are in a circular tube shape, the outer walls of the circular tubes are provided with teeth meshed with the spline straight teeth of the annular inner walls of the planetary carriers and are meshed with the spiral gears of the opposite directions of the bevel gears of the left side and the right side bevel gears, and the opposite directions of rotation of the bevel gears of the two alternate switching gears are jointed with the smooth surfaces at the two ends of the conjoined sun gears to transmit mutual axial force to realize power switching; the axial thrust gear is a circular tube outer end plate, the diameter of the outer end plate outer wall of the axial thrust gear is smaller than that of the annular inner wall of the planet carrier, teeth meshed with the helical gears of the alternate switching gears I are arranged on the outer wall of the circular tube and meshed with the helical gears, spline straight teeth are arranged on the inner wall of the circular tube and serve as power output ends to be externally connected with a half shaft, and a thrust spring is arranged between the axial thrust gear and the end cover baffle;

The mode is that the power of the inner side is larger than that of the outer side when the vehicle turns, and the mode has the advantage that the power of the rear axle is larger than that of the front axle when the vehicle turns as a central differential mechanism.

Example 2

The dynamic differential, as shown in fig. 4 and 5, includes: the device comprises a shell (1), an end cover (2), a meshing closed-loop differential unit, an axial thrust gear (5) and an alternate switching gear II (10); the shell (1) is in a circular tube shape, the axial section of the end cover (2) is in a step shape and is provided with a half shaft hole, the outlet end of the half shaft hole is integrally provided with an inward annular end cover baffle (3), and the shell and an end cover screw are connected together to form a supporting main body of the dynamic differential mechanism; the meshing closed-loop differential unit is composed of two parallel planetary gear differential mechanisms: comprises a planet carrier (22), a planet gear (21), a conjoined sun gear (14) and a gear ring (16); the planet carrier (22) is an annular disc, two end faces of the disc are provided with convex planet gear shafts or mounting holes, and the outer wall of the disc is fixedly connected with the inner wall of the shell (1) relatively or integrally arranged; the planetary gears (21) are cylindrical gears, at least three planetary gears (21) are respectively arranged in convex planetary gear shafts or mounting holes at two ends of the planetary carrier (22), and the planetary gears (21) at two ends of the planetary carrier (22) can be connected planetary gears; the integrated sun gear (14) is in a circular tube shape, teeth meshed with the planetary gears (21) are respectively arranged on the outer wall of the circular tube and meshed with the planetary gears (21), the gear ring (16) is in a circular tube shape, the outer wall of the circular tube is meshed with the inner wall of the shell (1) and is provided with rotary support by the inner wall of the circular tube, the inner wall of the circular tube is provided with internal teeth and meshed with the planetary gears (21) on two sides of the planet carrier respectively, the inner wall of the end face of the circular tube opposite to the inner wall of the circular tube is integrally provided with a circular ring gear end plate (13) with the same inner diameter as the circular tube of the integrated sun gear (14), the end face between the end plate (13) of the circular ring gear and the integrated sun gear (14) is respectively provided with a power switching gear (4), the power switching gear is a plane contour tooth with radially distributed pressure angles, the two alternately switching gears are respectively provided with a circular tube outer end plate, two surfaces of the outer end plate are provided with teeth meshed with the power switching gear (8) of the circular ring gear and the two alternately switching gears, the opposite end faces of the circular tube are oppositely arranged on the left and right, the two alternately switching gears are oppositely opposite end faces of the circular tube are meshed with each other, and the two axially opposite end faces of the bevel gears are meshed with the two axially opposite end plates (8) respectively; spline straight teeth (7) are arranged on the inner wall of the circular tube and serve as an external half shaft of a power output end, and a thrust spring (6) is arranged between the axial thrust gear (5) and the end cover baffle plate (3).

In this embodiment, only the alternate switching gear two (10) and the axial thrust gear (5) can move axially.

In this embodiment, the meshing of the planetary gears, the conjoined 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, which is equivalent to a synchronous gear, so that the separation and meshing of the power switching gears can be realized at any time, and the wheels on both sides synchronously rotate after the completion of turning, and the power is evenly distributed with the axial force and balanced, so that the power switching gears can smoothly return to a half-meshing state and then go straight or turn continuously.

The structural features, the shape features of the parts, the engagement relationship between the parts and the positional relationship features of the present embodiment are described above, and compared with embodiment 1, embodiment 2 omits a bevel gear differential mechanism, has a simple structure and is easy to implement, and the power transmission and the operation principle of the vehicle of the present embodiment in different states are described below.

Straight running state: the power is output from the shell to the planetary gears and then to the gear rings and the conjoined sun gears on two sides respectively, because the gear rings and the conjoined sun gears are semi-meshed with the power switching gears of the alternative switching gears II, the power is output from the alternative switching gears II to the external half shaft of the axial thrust gears,

Turning state: because of the occurrence of the rotation speed difference and the power distribution difference (the power at the outer side is smaller than that at the inner side), the axial force balance of the alternate switching gear II at the two sides is broken, the power switching gear of the inner side gear ring end plate and the alternate switching gear II is changed from half meshing to complete separation and is completely meshed with the power switching gear of the conjoined sun gear, the outer side is completely meshed with the power switching gear of the gear ring end plate to realize turning,

The embodiment has no anti-skid locking function and only has a strong limited skid function, but the outside power is larger than the inside power, so that the vehicle body posture and track of the vehicle in a curve are corrected, and the vehicle can be overturned by using a higher vehicle speed.

2, As an alternative the present embodiment may also be such: the two end covers are respectively used as planetary carriers, the raised planetary gear shafts or holes are integrally arranged on the inner sides of the end covers, the gear rings are arranged as connected gear rings, the outer wall of each connected gear ring is jointed with the inner wall of the shell and is provided with rotary support by the corresponding connected gear rings, the middle part of the inner wall of each connected gear ring is integrally provided with a circular gear ring end plate, the inner walls of the end faces of the two sun gears, which are opposite (are the back faces of opposite faces), are integrally provided with circular sun gear end plates, the two ends of each sun gear are respectively jointed with the gear ring end plates and the planetary carriers to limit the axial movement of the ring gear end plates, the opposite faces of the sun gear end plates and the two sides of the gear ring end plates are respectively provided with power switching gears, the power switching gears of the second alternate switching gears are respectively semi-meshed with the power switching gears on the sun gear end plates and the gear ring end plates, the opposite end faces of the two alternate switching gears are jointed between the opposite ends of the circular gears to transmit mutual axial force to realize power switching, the helical gears of the outer walls of the two circular gears of the two axial thrust gears are respectively meshed with the helical gears of the second alternate switching gears of the two axial thrust gears, and the outer end plates of the two axial thrust gears are respectively jointed with the annular inner walls of the two sun gear end plates of the two end plates and are provided with rotary support; spline straight teeth of the two axial thrust gears are used as power output ends to be externally connected with a half shaft, and a thrust spring is arranged between the axial thrust gears and the end cover baffle;

The mode is that the power of the inner side is larger than that of the outer side in the turning state, the power of the inner side is larger than that of the outer side, and the rotating speed of the outer wheels is larger than that of the inner side by 10% compared with the prior art, and the mode has the advantages that the mode is used as a central differential mechanism, the power of the rear axle is larger than that of the front axle in the turning driving process, so that the posture and the track of the vehicle body in the curve are corrected, or the mode is used as a rear axle, the drifting and bending action can be easily carried out, and the higher vehicle speed can be used for the over-bending.

Example 3

The dynamic differential as in fig. 6 includes: casing (1), end cover (2), meshing closed-loop differential unit, alternate switching gear three (11) and axial thrust gear (5), characterized by: the shell (1) is in a circular tube shape, the axial section of the end cover (2) is in a step shape and is provided with a half shaft hole, the outlet end of the half shaft hole is integrally provided with an inward annular end cover baffle (3), and the shell and an end cover screw are connected together to form a supporting main body of the dynamic differential mechanism; the meshing closed-loop differential unit consists of two planetary gear differential mechanisms and a reversing gear (23): comprises a planetary gear set (27), a reversing gear (23), a planet carrier (22), a sun gear (15) and a gear ring (16); the planetary gear set (27) consists of two cylindrical gears which are equal in length and are partially meshed with each other; the reversing gear (23) is a cylindrical gear with an axial through hole; the planet carrier (22) is a circular disc, at least three groups of planet gear set mounting holes (26) and raised reversing gear shafts (24) are uniformly arranged on two sides of the disc, a planet gear set (27) and a reversing gear (23) are mounted on the planet carrier, the reversing gear is meshed with a planet gear of an un-meshed part of the side, the outer wall of the disc is fixedly connected with the inner wall of the shell (1) relatively or integrally arranged, the sun gear (15) is in a circular tube shape, and teeth meshed with the reversing gear (23) are arranged on the outer wall of the circular tube and are meshed with the reversing gear respectively; the gear ring (16) is in a circular tube shape, the outer wall of the circular tube is jointed with the inner wall of the shell (1) and is provided with rotary support by the inner wall of the circular tube, the inner wall of the circular tube is provided with inner teeth and is respectively meshed with planetary gears at two ends of the planetary carrier (22), the inner walls of the end faces of the two circular tubes which are opposite (are opposite surfaces) are integrally provided with circular ring gear end plates (13) and are respectively jointed with the end faces of the sun gears (15), the end faces of the two circular ring end plates (13) which are opposite (are opposite surfaces) are provided with power switching gears (4), the opposite end faces of the two sun gears (15) are provided with power switching gears (4), the power switching gears (4) are radially distributed and are provided with plane contour teeth with pressure angles, the alternate switching gears (11) are in a circular tube shape, the inner walls of the circular tube are provided with bevel gears (8) and the rotary directions of the bevel gears at the left side and the right side and the bevel gears (8) are opposite, the two ends of the circular tube are provided with two circular ring disks, one circular disk is separately arranged with the circular ring gear and is fixedly connected with a spline, the other circular disk is meshed with the power switching gears (4) which are integrally arranged on the circular ring gear end plates (13) and meshed with the power switching gears (4) which are meshed with the power switching gears (4), the opposite end surfaces of the two alternate switching gears III (annular discs which are arranged in a split manner) are attached to each other to transmit axial force to realize power switching; the axial thrust gear (5) is a circular tube outer end plate, teeth meshed with helical gears (8) of the alternate switching gears (10) are arranged on the outer wall of the circular tube and meshed with the helical gears, spline straight teeth (7) are arranged on the inner wall of the circular tube and serve as power output ends to be externally connected with a half shaft, and a thrust spring (6) is arranged between the axial thrust gear (5) and the end cover baffle plate (3);

in the embodiment, only the alternate switching gear III (11) and the axial thrust gear (5) can axially move;

In this embodiment, the meshing of the planetary gears, the reversing gear, the 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, and the meshing closed-loop circuit is equivalent to a synchronous gear, so that the separation and meshing of the power switching gears can be realized at any time, and the wheels on both sides synchronously rotate after the completion of turning, and the power is evenly distributed and the axial force is balanced, so that the power switching gears can smoothly return to a half-meshing state and then go straight or turn continuously.

straight running state: the power is output from the shell to the planetary gears, the reversing gears to the sun gears on two sides and the gear rings, and then to the external half shaft of the alternate switching gear III and the axial thrust gear.

Turning state: because of the occurrence of the rotation speed difference and the power distribution difference (the power on the outer side is smaller than that on the inner side), the axial force balance of the alternate switching gear three on the two sides is broken, the alternate switching gear three on the inner side is completely meshed with the power switching gear of the gear ring end plate and completely separated from the power switching gear of the sun gear, the alternate switching gear three on the outer side is completely separated from the power switching gear on the gear end plate and completely meshed with the power switching gear of the sun gear to realize turning,

The embodiment has the anti-skid locking function, the mode is that the inner side power is larger than the outer side during turning, the inner side power is larger than the outer side in the turning state, and the rotating speed of the outer wheels is larger than 10% of that of the inner side compared with the prior art, and the anti-skid locking device has the advantages that the anti-skid locking device is used as a central differential mechanism, the rear axle power is larger than the front axle during turning, so that the posture and the track of a vehicle body in a curve can be corrected, or the anti-skid locking device can be used as a rear axle to easily make drifting and bending actions, and can be used for higher vehicle speed to overstretch.

Alternatively the present embodiment may also be such that: the power switching gears are respectively arranged on the surfaces between the gear ring end plate and the sun gear, the alternate switching gears are round pipe outer end plates, teeth meshed with the power switching gears on the gear ring end plate and the sun gear are arranged on two end surfaces of the outer end plate and are semi-meshed, and the opposite end surfaces of the two alternate switching gears are attached to each other to transmit mutual axial force to realize power switching; the axial thrust gear is a circular tube outer end plate, the outer wall of the circular tube is provided with teeth meshed with helical gears of the alternate switching gear III and meshed with the helical gears, the inner wall of the circular tube is provided with spline straight teeth serving as an external half shaft of a power output end, the outer wall of the outer end plate of the two axial thrust gears is respectively bonded with the annular inner walls of the two gear ring end plates and is provided with rotary support by the annular inner walls of the two gear ring end plates, and a thrust spring is arranged between the axial thrust gear and the end cover baffle plate.

In this way, if the number of teeth of the reversing gear is twice that of the differential gear, the outside power is greater than the inside power, and the rotation speed of the outside wheels is greater than 10% of that of the prior art, so that the posture and track of the vehicle body in a curve can be corrected, and the vehicle can be overturned at a higher speed.

Example 4

The dynamic differential as in fig. 7 and 8 includes: two integral end covers (20), meshing closed-loop differential unit, alternate switching gear four (12) and axial thrust gear (5), characterized by: one end of the integrated end cover (20) is opened, the axial section of the integrated end cover (20) is in a step shape and is provided with a half shaft hole, the outlet end of the half shaft hole is integrally provided with an inward annular end cover baffle (3), the opposite end surfaces of the two integrated end cover openings are radially provided with mounting holes of a double-layer differential gear frame (25), and the two integrated end cover screws (20) are connected and fixed together to form a supporting main body of the dynamic differential mechanism; the meshing closed-loop differential unit consists of a double-layer bevel gear differential mechanism and comprises a double-layer differential gear (17), a double-layer differential gear rack (25), an inner-layer output gear (18) and an outer-layer output gear (19); the double-layer differential gear (17) is an inner differential gear and an outer differential gear which are integrated by two bevel gears with the same tooth number and modulus in the axial direction, and a through hole is arranged in the axial center of the double-layer differential gear (17); the two outer layer output gears (19) are respectively meshed with the outer layer differential gears in the axial direction by 90 degrees, and the two inner layer output gears (18) are respectively meshed with the inner layer differential gears in the axial direction by 90 degrees; the double-layer differential gear frame (25) is in a circular tube shape, double-layer differential gear shafts with the same number as the double-layer differential gears (17) are integrally arranged on the outer wall of the circular tube, the double-layer differential gears (17) are arranged on the double-layer differential gear shafts on the double-layer differential gear frame (25), and the double-layer differential gear frame (25) is arranged in mounting holes of the double-layer differential gear frame which are 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 cone back of the outer layer output gear is integrally provided with an inward annular end plate, the surfaces between the annular end plate of the outer layer output gear and the inner layer output gear are respectively provided with a power switching gear, the power switching gears (4) are radially distributed plane constant-height teeth with pressure angles, the fourth alternate switching gear (12) is a circular tube outer end plate, the inner walls of the circular tubes are provided with helical gears (8) with opposite rotation directions of left and right helical gears, the two surfaces of the two outer end plates are respectively provided with teeth meshed with the power switching gears on the outer layer output gear (19) and the inner layer output gear (18) and are semi-meshed, the circular tubes are rotatably arranged on the inner wall of the inner layer output gear through holes, and the opposite end surfaces of the circular tubes of the fourth alternate switching gears (12) are jointed to transmit axial force mutually to realize power switching; the axial thrust gear (5) is a circular tube outer end plate, the outer wall of the circular tube is provided with teeth meshed with the helical gears (8) of the alternate switching gears (12) and meshed with the helical gears, and the inner wall of the circular tube is provided with spline straight teeth (7) serving as a power output end externally connected with a half shaft; a thrust spring (6) is arranged between the axial thrust gear (5) and the end cover baffle plate (3), and the outer walls of the outer end plates of the two axial thrust gears are respectively attached to the annular inner walls of the annular end plates of the two outer output gears and are provided with rotary support by the annular inner walls.

In the embodiment, only the alternate switching gear IV (12) and the axial thrust gear (5) can axially move;

In the embodiment, the outer layer output gear (19) and the inner layer output gear of the double-layer bevel gear differential mechanism of the meshed closed-loop differential unit are meshed with the double-layer differential gear to form a meshed closed loop, and the meshed closed loop is equivalent to a synchronous gear, so that the separation and the meshing of the power switching gears can be realized at any time, and after the turning is completed, the wheels on two sides synchronously rotate, and the power is evenly distributed and the axial force is balanced, so that the power switching gears can smoothly return to a half-meshed state and then directly move or continuously turn.

The structural features, the component shape features, the engagement relationship between the components, and the positional relationship features of the present embodiment are described above, and the power transmission and the operation principle of the vehicle of the present embodiment in different states are described below.

Straight running state: the power is output from an integrated end cover to a double-layer differential gear frame, a double-layer differential gear, an inner-layer output gear and an outer-layer output gear, and then to an external half shaft of an alternate switching gear IV and an axial thrust gear.

Turning state: the number of teeth of the inner layer output gear is smaller than that of the outer layer output gear, two gears with the same number of teeth simultaneously drive gears with different numbers of teeth due to the existence of the difference of the number of teeth, the rotation speeds of the two gears driven are definitely different, the inner layer output gear is actually faster than the outer layer output gear and rotates backwards to be separated from contact with the power switching gear of the alternate switching gear IV in the moment of turning, the outer layer output gear is separated from contact with the power switching gear of the alternate switching gear IV in the outer side, the power switching gear of the alternate switching gear IV in the inner side is completely separated from the power switching gear of the outer layer output gear from half engagement to complete engagement with the inner layer output gear under the action of the difference of rotation speed and axial force, the power switching gear of the alternate switching gear IV in the outer side is completely separated from the outer layer output gear from half engagement to complete engagement with the inner layer output gear to realize turning, and the power of the outer side is larger than the inner side.

The slip resistance is as follows: if one side wheel is suspended, the number of teeth of the inner layer output gear is smaller than that of the outer layer output gear because of the number of teeth of the double-layer differential gear and the equal modulus, and two gears with the same number of teeth simultaneously drive gears with two different numbers of teeth because of the number of teeth difference, the rotation speeds of the two driven gears are definitely different, the inner layer output gear on the inner side is faster than the outer layer output gear and is in contact with the other side of the tooth gap of the half-meshing power switching gear to lock after the inner layer output gear is in backward rotation and is out of contact with the power switching gear of the fourth alternate switching gear, and the outer layer output gear is in contact with the other side of the tooth gap of the fourth alternate switching gear to lock after the outer layer output gear is out of contact with the other side of the tooth gap of the fourth alternate switching gear and balance the axial thrust of the fourth alternate switching gear when power is transmitted to the inner side, so that one side wheel is suspended and cannot slip.

Alternatively the present embodiment may also be such that: the meshing closed-loop differential unit is a bevel gear differential mechanism, a differential gear frame is in a circular tube shape, differential gear shafts with the same number as the differential gears are integrally arranged on the outer wall of the circular tube, the differential gears are arranged on the differential gear shafts on the differential gear frame, and the differential gear frame is arranged in the mounting holes of the differential gear frames on the two integrated end covers; at least two differential gears are axially meshed with each other by 90 degrees, through holes are axially formed in the two output gears, spline straight teeth are formed in the inner walls of the through holes, power switching gears are arranged on the end faces between the two output gears, a thrust circular tube is arranged between the two output gears, teeth meshed with the power switching gears on the end faces of the output gears are arranged on the end faces of the two ends of the thrust circular tube and are meshed with each other in a half mode, the outer wall of the thrust circular tube is meshed with the inner walls of differential gear frames and is provided with rotary support, the four alternative switching gears are in a circular tube shape, teeth meshed with the spline straight teeth of the inner walls of the through holes of the output gears are arranged on the outer walls of the circular tube and meshed with the spline straight teeth of the inner walls of the through holes of the output gears, helical gears on the inner walls of the circular tube are opposite in rotation directions, and the opposite end faces of the four alternative switching gears are meshed with smooth faces at the two ends of the thrust circular tube to transmit mutual axial force so as to realize power switching; the helical gears on the outer walls of the two axial thrust gear round tubes are respectively meshed with the helical gears of the two alternate switching gears, spline straight teeth of the axial thrust gears serve as power output ends to be externally connected with a half shaft, and a thrust spring is arranged between the axial thrust gears and the end cover baffle plate.

The result of this is that only slip is possible, but the power on both sides is equally distributed.

Claims

1. A dynamic differential, comprising: casing, end cover, meshing closed loop differential unit, alternate switching gear one, axial thrust gear and thrust spring, characterized by: the shell is in a circular tube shape, at least two differential gear shaft holes are radially arranged in the middle of the shell, the axial section of the end cover is in a step shape and is provided with a half shaft hole, an inward annular end cover baffle is integrally arranged at the outlet end of the half shaft hole, and the shell and an end cover screw are connected to form a supporting main body of the dynamic differential mechanism;

The meshing closed-loop differential unit is characterized in that a bevel gear differential mechanism is arranged between two planetary gear mechanisms, conical backs of two output gears of the bevel gear differential mechanism are integrally provided with planetary gear shafts or holes as planetary carriers of the two planetary gear differential mechanisms, sun gears of the two planetary gear mechanisms are circular tube-shaped conjoined sun gears, two ends of the conjoined sun gears are smooth surfaces and are provided with power switching gears, and the power switching gears are radially distributed plane contour teeth with pressure angles; spline straight teeth are arranged on the annular inner wall of the gear ring end plate, and teeth meshed with power switching gears at two ends of the conjoined sun gear are arranged on the opposite end surfaces of the gear ring end plate and are meshed with each other in half; or the inner walls of two output gears of the bevel gear differential mechanism are provided with inner teeth serving as inner teeth of gear rings of the two planetary gear differential mechanism, two planetary carriers are respectively and independently arranged to serve as power output ends, the planetary carriers are circular discs, the opposite surfaces of the two planetary carriers are provided with convex planetary gear shafts or holes, the opposite surfaces of the two planetary carriers are provided with teeth meshed with a power switching gear on the conjoined sun gear and are semi-meshed, and the annular inner walls of the two planetary carriers are provided with spline straight teeth;

The first alternate switching gears are in a circular tube shape, teeth meshed with spline straight teeth of the inner wall of the end plate of the gear ring or the annular inner wall of the planet carrier are arranged on the outer wall of the circular tube and meshed, the inner wall of the circular tube is provided with a bevel gear, the rotation directions of the bevel gears on the left side and the right side are opposite, and the opposite end surfaces of the first alternate switching gears are attached to smooth surfaces at the two ends of the conjoined sun gear to transfer mutual axial force so as to realize power switching;

The axial thrust gear is a circular tube outer end plate, the diameter of the outer end plate outer wall of the axial thrust gear is smaller than that of the inner wall of the gear ring end plate or the annular inner wall of the planet carrier, teeth meshed with the helical gears of the alternative switching gears are arranged on the outer wall of the circular tube and meshed with the helical gears, spline straight teeth are arranged on the inner wall of the circular tube and serve as an external half shaft of the power output end, and a thrust spring is arranged between the axial thrust gear and the end cover baffle.

2. The dynamic differential of claim 1: the meshing closed-loop differential unit is two parallel planetary gear differential mechanisms, a planet carrier is integrally arranged in the middle of the inner wall of the shell, planetary gears are connected or separated cylindrical gears, and power switching gears are respectively arranged on the surfaces between the connected sun gear and the end plate of the gear ring; the second alternate switching gear is a circular tube outer end plate, two sides of the outer end plate are provided with teeth meshed with the gear ring end plate and the power switching gear on the conjoined sun gear and are semi-meshed, the inner wall of the circular tube is provided with a bevel gear, the rotation directions of the bevel gears on the left side and the right side are opposite, and the opposite end surfaces of the two circular tubes of the second alternate switching gear are jointed to transmit mutual axial force to realize power switching; the helical gears of the outer walls of the two axial thrust gear round tubes are respectively meshed with the helical gears of the two alternate switching gears II, and 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 gear ring end plates and are provided with rotary support by the annular inner walls of the two gear ring end plates; or the two end covers are respectively used as planetary carriers, the convex planetary gear shafts or holes are integrally arranged on the inner sides of the end covers, the gear rings are arranged to be connected with the gear rings, the outer wall of the connected gear rings is in fit with the inner wall of the shell and is supported by the rotation of the inner wall of the shell, the middle part of the inner wall of the connected gear rings is integrally provided with the annular gear ring end plates, the two sun gears are in round tube shape, the inner walls of the end faces of the two sun gears, which are opposite (are the back faces of opposite faces), are integrally provided with annular sun gear end plates, the two ends of the two sun gears are respectively in fit with the gear ring end plates and the planetary carriers to limit the axial movement of the sun gear end plates, the opposite faces of the sun gear end plates and the two sides of the gear ring end plates are respectively provided with power switching gears, the power switching gears of the second alternate switching gears are respectively in half-mesh with the power switching gears on the sun gear end plates and the gear ring end plates, the opposite end faces of the second alternate switching gears are in fit to transmit mutual axial force to realize power switching, the bevel gears of the outer walls of the two axial thrust gear tubes are respectively in mesh with the bevel gears of the second alternate switching gears, the outer end plates of the two axial thrust gears are respectively in fit with the annular inner walls of the two sun end plates of the two sun gear end plates of the two end plates and are respectively supported by rotation of the rotating support.

3. The dynamic differential of claim 1: the meshing closed-loop differential unit is composed of two planetary gear differential mechanisms and reversing gears, a planetary gear set is composed of two cylindrical gears with equal lengths and partially meshed with each other, a planetary carrier is integrally arranged in the middle of the inner wall of a shell, at least three groups of planetary gear set mounting holes and three reversing gear shafts are uniformly arranged on two sides of the planetary carrier, a planetary gear set and a reversing gear are mounted on the planetary carrier, the reversing gear is meshed with the planetary gears of the non-meshed part of the side, power switching gears are arranged on the surfaces of two gear ring end plates (namely the back surfaces of opposite surfaces), and power switching gears are arranged on the opposite end surfaces of two sun gears; the gear ring end plate and the sun gear are rotatably arranged on the outer wall of the circular tube, two annular discs are arranged at two ends of the circular tube, one annular disc is separately arranged with the circular tube and fixedly connected by a spline, the other annular disc is integrally arranged with the circular tube, the integrally arranged annular disc is provided with teeth meshed with the power switching gear on the gear ring end plate and is semi-meshed with the teeth meshed with the power switching gear on the sun gear, the opposite end surfaces of the two alternately switching gears (the annular discs which are separately arranged) are jointed to transmit mutual axial force to realize power switching, and the bevel gears of the two axial thrust gears are respectively meshed with the bevel gears of the two alternately switching gears; or the surfaces between the gear ring end plate and the sun gear are respectively provided with a power switching gear, the alternate switching gear III is a circular pipe outer end plate, two surfaces of the outer end plate are provided with teeth meshed with the gear ring end plate and the power switching gear on the sun gear and are semi-meshed, the inner wall of the circular pipe is provided with a bevel gear, the rotation directions of the bevel gears on the left side and the right side are opposite, the opposite end surfaces of the three circular pipes of the two alternate switching gears are jointed to transmit mutual axial force to realize power switching, the bevel gears on the outer walls of the circular pipes of the two axial thrust gears are meshed with the bevel gears of the two alternate switching gears III respectively, and the outer walls of the outer end plates of the two axial thrust gears are respectively jointed with the annular inner walls of the two gear ring end plates and are provided with rotary support by the annular inner walls of the two gear ring end plates.

4. The dynamic differential of claim 1: the meshing closed-loop differential unit is a double-layer bevel gear differential mechanism, the double-layer differential gear axially forms an integrated inner differential gear and an integrated outer differential gear by two bevel gears with equal modulus, and a through hole is arranged in the axial center of the double-layer differential gear; the two outer layer output gears are respectively meshed with the outer layer differential gears in the axial direction by 90 degrees, the two inner layer output gears are respectively meshed with the inner layer differential gears in the axial direction by 90 degrees, the double-layer differential gear frame is in a round tube shape, double-layer differential gear shafts with the same number as the double-layer differential gears are integrally arranged on the outer wall of the round tube, the double-layer differential gears are arranged on the double-layer differential gear shafts on the double-layer differential gear frame, and the double-layer differential gear frame is arranged in the mounting holes of the double-layer differential gear frames on the two integrated end covers; the outer layer output gear and the inner layer output gear are axially provided with through holes, the cone back of the outer layer output gear is integrally provided with an inward annular end plate, and the surfaces between the annular end plate of the outer layer output gear and the inner layer output gear are respectively provided with a power switching gear; the four alternate switching gears are circular tubes with outer end plates, teeth meshed with the annular end plates of the outer layer output gears and the power switching gears on the inner layer output gears are arranged on two sides of the outer end plates and are semi-meshed, bevel gears are arranged on the inner walls of the circular tubes, the rotation directions of the bevel gears on the left side and the right side are opposite, the opposite end faces of the four circular tubes of the two alternate switching gears are jointed to transfer axial force to each other to realize power switching, the bevel gears on the outer walls of the two circular tubes of the two axial thrust gears are meshed with the bevel gears of the four alternate switching gears respectively, and the outer walls of the outer end plates of the two axial thrust gears are respectively jointed with the annular inner walls of the annular end plates of the two outer layer output gears and are provided with rotary support by the annular inner walls of the annular end plates of the outer layer output gears; or the meshing closed-loop differential unit is a bevel gear differential mechanism, the differential gear frame is in a circular tube shape, the outer wall of the circular tube is integrally provided with differential gear shafts with the same number as that of the differential gears, the differential gears are arranged on the differential gear shafts on the differential gear frame, and the differential gear frame is arranged in the mounting holes of the differential gear frames on the two integrated end covers; at least two differential gears are axially meshed with each other by 90 degrees, through holes are axially formed in the two output gears, spline straight teeth are formed in the inner walls of the through holes, power switching gears are arranged on the end faces between the two output gears, a thrust circular tube is arranged between the two output gears, teeth meshed with the power switching gears on the end faces of the output gears are arranged on the end faces of the two ends of the thrust circular tube and are meshed with each other in a half mode, the outer wall of the thrust circular tube is meshed with the inner walls of differential gear frames and is provided with rotary support, the four alternative switching gears are in a circular tube shape, teeth meshed with the spline straight teeth of the inner walls of the through holes of the output gears are arranged on the outer walls of the circular tube and meshed with the spline straight teeth of the inner walls of the through holes of the output gears, helical gears on the inner walls of the circular tube are opposite in rotation directions, and the opposite end faces of the four alternative switching gears are meshed with smooth faces at the two ends of the thrust circular tube to transmit mutual axial force so as to realize power switching; the helical gears on the outer walls of the two axial thrust gear round tubes are respectively meshed with the helical gears of the two alternate switching gears, and spline straight teeth of the axial thrust gears serve as power output ends to be externally connected with a half shaft.

5. The dynamic differential of claim 1: the outer wall of the housing may also be integrally provided with a main reduction gear for external power input to the dynamic differential.