Transmission device, clutch device and differential lock

Abstract

The invention discloses a transmission device, a clutch device and a differential lock, belongs to the technical field of mechanical transmission, and aims to solve the problems of an existing clutch device. The transmission device comprises eccentric discs and an outer support, the outer support is provided with two opposite supporting walls, the two eccentric discs are located between the two supporting walls, the thickness of the eccentric discs changes along with the central angle, the opposite sides of the two eccentric discs axially extend to form torque shafts, the torque shafts penetrate through the outer support through the corresponding supporting walls, and when any one torque shaft rotates, the torque shafts rotate along with the corresponding supporting walls. And the two eccentric discs are mutually extruded and reversely pushed, and the two eccentric discs are respectively extruded and locked with the corresponding supporting walls. The stepless adjustable differential lock has the characteristics of stepless adjustable power output torque, simple structure, low manufacturing cost, high transmission efficiency and the like, is wide in application, and can be combined with a planetary gear transmission mechanism to realize the functions of a differential lock, a clutch device in power transmission, a brake device, a power shunting device and the like.

Description

Technical Field

[0001] The present invention belongs to the technical field of mechanical transmission, and particularly relates to a transmission device, a clutch device and a differential lock. Background Art

[0002] The clutch device is crucial in the field of mechanical transmission. The torque converter is a type of clutch device. The existing torque converters mainly include hydraulic torque converters and friction plate torque converters. Although the hydraulic torque converter can change the output torque of power, its transmission efficiency is low and the manufacturing cost is high. For the friction plate torque converter, the friction material is not allowed to slide with the pressure plate and the flywheel for a long time, so the torque output cannot be adjusted for a long time, and it has a large volume and a short service life. And the jaw clutch device cannot adjust the output torque. Summary of the Invention

[0003] The purpose of the present invention is to provide a transmission device, a clutch device and a differential lock to solve the problems existing in the existing clutch devices. The technical solutions adopted by the present invention are as follows:

[0004] A transmission device includes an eccentric disk and an outer bracket. The outer bracket has two opposite support walls. Two eccentric disks are located between the two support walls. The thickness of the eccentric disk changes with the central angle. On the opposite sides of the two eccentric disks, first torque shafts axially extend. The first torque shafts pass through the outer bracket by the corresponding support walls. When any one of the first torque shafts rotates, the two eccentric disks squeeze and push against each other, and the two eccentric disks are respectively locked by squeezing with the corresponding support walls.

[0005] Further, the two support walls of the outer bracket are correspondingly replaced with shoulder structures and adjusting nuts. Any one of the first torque shafts is threadedly connected to the adjusting nut. The shoulder structure is arranged on the other first torque shaft. The two first torque shafts are connected and respectively penetrate through the two eccentric disks.

[0006] Further, annular grooves are formed on the opposite end faces of the two eccentric disks. The axis of the annular groove coincides with the axis of the eccentric disk. A number of end face balls are respectively in rolling fit with the annular grooves of the two eccentric disks.

[0007] Further, it further includes an axial transmission mechanism. The axial transmission mechanism includes an inner bracket. The inner bracket is arranged between the two eccentric disks. A number of parallel transmission rods are slidably arranged on the inner bracket. When any one of the first torque shafts rotates, the two eccentric disks squeeze and push against each other through the transmission rods, and the two eccentric disks are respectively locked by squeezing with the opposite support walls.

[0008] Further, the eccentric disk includes a disk seat and a disk surface. The disk surface and the disk seat are rotationally matched.

[0009] Further, it further includes a universal transmission mechanism. The universal transmission mechanism includes an outer guide sleeve and an inner transmission block. The inner transmission block is arranged between two eccentric disks. A plurality of circumferential balls are arranged on the outer periphery of the inner transmission block. A plurality of first guide grooves are arranged on the inner periphery of the outer guide sleeve. The plurality of circumferential balls are in rolling fit with the plurality of first guide grooves one by one.

[0010] Further, it further includes a universal transmission mechanism. The universal transmission mechanism includes an outer transmission sleeve and an inner fixing block. The inner fixing block is arranged between two eccentric disks. Take any one of the eccentric disks and the corresponding torque shaft as a passive component. The torque shaft of the passive component passes through the eccentric disk and is connected to the inner fixing block. A plurality of circumferential balls are arranged on the outer periphery of the inner fixing block. A plurality of first guide grooves are arranged on the inner periphery of the outer transmission sleeve. The plurality of circumferential balls are in rolling fit with the plurality of first guide grooves one by one. The outer transmission sleeve is arranged between two eccentric disks. When any one of the first torque shafts rotates, the two eccentric disks are mutually extruded and pushed back through the outer transmission sleeve. The two eccentric disks are respectively locked by extrusion with the opposite support walls.

[0011] The present invention also provides a pitch-changing device, which is realized relying on the above transmission device. Mark one of the eccentric disks and the corresponding first torque shaft as the first eccentric device, and mark the other eccentric disk and the corresponding first torque shaft as the second eccentric device. Mark the opposite side ends of the two eccentric disks as the first extrusion surfaces, mark the opposite side end faces of the two eccentric disks as the second extrusion surfaces, and mark the opposite side end faces of the two support walls as the third extrusion surfaces. The eccentric disk of the first eccentric device is fixedly connected to the first torque shaft. A spline groove is arranged on the first extrusion surface of the first eccentric mechanism. A through spline hole is arranged along the axis on the eccentric disk of the second eccentric mechanism. The spline groove is coaxial with the spline hole. A spline shaft section is arranged at one end of the first torque shaft of the second eccentric mechanism close to the first eccentric mechanism. The spline shaft section is in sliding fit with the spline hole and is in plug-in fit or separation with the spline groove.

[0012] The present invention also provides another pitch-changing device, which is realized relying on the above transmission device. It further includes a meshing sleeve. An internal gear structure is arranged on the inner periphery of the meshing sleeve. External gear structures are arranged on the outer peripheries of the two eccentric disks. The internal gear structure of the meshing sleeve meshes with the external gear structure of any one of the eccentric disks, and the internal gear structure of the meshing sleeve meshes with or separates from the other eccentric disk.

[0013] The present invention also provides a differential lock, which is realized relying on the above transmission device. It further includes a differential or a planetary gear train. The planetary gear train includes a sun gear and a ring gear meshed by a plurality of planetary gears. A housing is arranged outside the planetary gear train. The planetary shafts of the plurality of planetary gears are all connected to the housing of the planetary gear train. The sun gear is sleeved on one end of the second torque shaft, and the ring gear is connected to one end of the third torque shaft. The other ends of the second torque shaft and the third torque shaft both extend outside the housing of the planetary gear train;

[0014] The outer bracket is connected to the housing of the differential, and any one of the first torque shafts extends into the housing of the differential and is sleeved and connected with any one of the half-axle gears of the differential;

[0015] Alternatively, the outer bracket is connected to the housing of the planetary gear train, and any one of the first torque shafts is coaxially connected with the second torque shaft;

[0016] Alternatively, the outer bracket is connected to the housing of the planetary gear train, and any one of the first torque shafts is coaxially connected with the third torque shaft.

[0017] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0018] 1. Among the two torque shafts of the transmission device of the present invention, any one can be used as the power input end, and the other can be used as the no-load end. Moreover, the outer bracket serves as the power output end. When combined with the differential or the planetary gear train, the function of the differential lock can be realized. When combined with the transmission teeth, the function of the clutch can be realized. It has the characteristics of steplessly adjustable output torque of the power, simple structure, low manufacturing cost, high transmission efficiency, etc. Moreover, it has a wide range of uses and can realize functions such as differential lock, clutch device, braking device, power splitting device, etc. When used as a power splitting device, the power is input from the input end, the no-load end is the full-time power output end, and the power input end is the timely power output end.

[0019] 2. The universal transmission device is used in cooperation with the adjustable disk surface. When the present invention is used on an automobile, the disk surface is driven to rotate through the push rod of the actuator of the vehicle's clutch system or braking system and the actuator motor. Then, when adjusting the inclination angle of the first pressing surface, the disk surface with the adjusted inclination angle presses the disk surface of another eccentric disk through the inner transmission block, so as to synchronously adjust the inclination angle of the disk surface of the other eccentric disk.

[0020] 3. The transmission device of the present invention combines the meshing between the tooth-shaped structures to realize the clutch function. Taking any one of the torque shafts as the power input end and the outer bracket as the power output end, the disconnection between the power input end and the power output end can be realized, and the clutch function of the torque converter can be realized. The structure is simple, the manufacturing cost is low, and the transmission efficiency is high.

[0021] 4. When the transmission device of the present invention is used in combination with the differential or the planetary gear train, the function of the differential lock can be realized. When the first eccentric mechanism and the second eccentric mechanism are locked with the outer bracket, the half-axle gear (or ring gear) connected to the eccentric mechanism is simultaneously locked with the housing of the differential (planetary gear train) through the transmission device, so as to realize the simultaneous rotation of both sides of the wheels or the front and rear axles of the vehicle. Brief Description of the Drawings

[0022] Figure 1 is the structural schematic diagram of Embodiment 1 of the present invention;

[0023] Figure 2 is the schematic diagram of the locked state of Embodiment 1 of the present invention;

[0024] Figure 3 is a schematic structural view of the outer bracket of the embodiment of the present invention;

[0025] Figure 4 is a schematic structural view of the first eccentric mechanism;

[0026] Figure 5 is an axonometric view of Embodiment 1 of the present invention;

[0027] Figure 6 is a front view of Embodiment 2 of the present invention;

[0028] Figure 7 is a sectional axonometric view of Embodiment 3 of the present invention;

[0029] Figure 8 is a schematic view of the cooperation between the eccentric disc and a plurality of end face ball bearings in Embodiment 3 of the present invention;

[0030] Figure 9 is a sectional axonometric view of Embodiment 4 of the present invention;

[0031] Figure 10 is a schematic structural view of the eccentric disc in Embodiment 5 of the present invention;

[0032] Figure 11 is a schematic structural view of the disc seat in Embodiment 5 of the present invention;

[0033] Figure 12 is a schematic structural view of the disc surface in Embodiment 5 of the present invention;

[0034] Figure 13 is a schematic structural view of Embodiment 6 of the present invention;

[0035] Figure 14 is a schematic structural view of the outer guide sleeve in Embodiment 6 of the present invention;

[0036] Figure 15 is a schematic structural view of the inner transmission block in Embodiment 6 of the present invention;

[0037] Figure 16 is a schematic structural view of Embodiment 7 of the present invention;

[0038] Figure 17 is a schematic structural view of Embodiment 8 of the present invention;

[0039] Figure 18 is a schematic structural view of Embodiment 9 of the present invention;

[0040] Figure 19 is a schematic structural view of the combination of the transmission device and the differential in Embodiment 10 of the present invention;

[0041] Figure 20It is a schematic structural diagram of the combination of the transmission device and the planetary gear train in Embodiment 10 of the present invention.

[0042] In the figure, 1. Eccentric disk, 2. Torque shaft, 3. Outer bracket, 4. Support wall, 5. Third extrusion surface, 6. First extrusion surface, 7. Second extrusion surface, 8. Shoulder structure, 9. Inner bracket, 10. Transmission rod, 11. Adjusting nut, 12. Disk seat, 13. Disk surface, 14. Pusher block, 15. Slide groove, 16. Limit lug, 17. Outer guide sleeve, 18. Inner transmission block, 19. Ball, 20. Cage, 21. First guide groove, 22. Second guide groove, 23. Outer transmission sleeve, 24. Inner fixing block, 25. Spline shaft section, 26. Spline groove, 27. Outer gear structure, 28. Engagement sleeve, 29. Differential, 30. Planetary gear train, 31. Ring gear, 32. Planetary gear, 33. Planetary gear shaft, 34. Sun gear, 35. Third torque shaft. Detailed implementation mode

[0043] To make the objectives, technical solutions and advantages of the present invention clearer and more understandable, the present invention will be described below through specific embodiments shown in the drawings. However, it should be understood that these descriptions are only exemplary and do not limit the scope of the present invention. In addition, in the following description, the descriptions of well-known structures and technologies are omitted to avoid unnecessarily confusing the concepts of the present invention.

[0044] The connections mentioned in the present invention are divided into fixed connections and detachable connections. The fixed connections are non-detachable connections, including but not limited to conventional fixed connection methods such as hemming connection, rivet connection, bonding connection and welding connection. The detachable connections include but not limited to conventional disassembly methods such as bolt connection, snap connection, pin connection and hinge connection. When the specific connection method is not clearly defined, it is default that at least one connection method can be found among the existing connection methods to achieve this function, and those skilled in the art can select according to their needs. For example: welding connection is selected for fixed connection, and bolt connection is selected for detachable connection.

[0045] The present invention will be further described in detail below with reference to the drawings. The following embodiments are explanations of the present invention, and the present invention is not limited to the following embodiments.

[0046] Embodiment 1: As Figures 1 to 5 shown, a transmission device includes an eccentric disk 1 and an outer bracket 3. The outer bracket 3 has two opposite support walls 4. Two eccentric disks 1 are located between the two support walls 4. The thickness of the eccentric disk 1 changes with the central angle. Axial extensions of the first torque shafts 2 are provided on the opposite sides of the two eccentric disks 1. The first torque shafts 2 pass through the outer bracket 3 by the corresponding support walls 4. When any one of the first torque shafts 2 rotates, the two eccentric disks 1 squeeze and push against each other, and the two eccentric disks 1 are respectively locked by squeezing with the corresponding support walls 4.

[0047] The outer bracket 3 is a hollow housing. To facilitate the installation of the eccentric disc 1, the outer bracket 3 can be made into two half-shells, which form the outer bracket 3 after being connected by bolts. As Figure 3 shown, one of the eccentric discs 1 and the corresponding torque shaft 2 are marked as the first eccentric device, and the other eccentric disc 1 and the corresponding torque shaft 2 are marked as the second eccentric device. The eccentric disc 1 is preferably a disc. The end faces of the two eccentric discs 1 facing each other are marked as the first pressing surface 6, the end faces of the two eccentric discs 1 facing away from each other are marked as the second pressing surface 7, and the end faces of the two support walls 4 facing each other are marked as the third pressing surface 5. The eccentric disc 1 and the corresponding torque shaft 2 are preferably coaxially arranged, and the two torque shafts 2 are preferably coaxially arranged;

[0048] When the first pressing surface 6 is an inclined surface or a continuous curved surface, the second pressing surface 7 and the third pressing surface 5 can be both flat surfaces, inclined surfaces or continuous curved surfaces. When the first pressing surface 6 is a flat surface, that is, when the first pressing surface 6 is perpendicular to the torque shaft 2, then the second pressing surface 7 and the third pressing surface 5 are both inclined surfaces or continuous curved surfaces. Taking the first pressing surface 6 as an inclined surface and the second pressing surface 7 and the third pressing surface 5 as flat surfaces as an example, that is, the second pressing surface 7 and the third pressing surface 5 are both perpendicular to the torsion shaft. This embodiment is described. The distance between the two third pressing surfaces 5 is greater than the sum of the thicknesses of the thickest and thinnest parts of the eccentric disc 1, and less than the sum of the thicknesses of the thickest parts of the two eccentric discs 1;

[0049] In the initial state, the thickest part of one eccentric disc 1 is opposite to the thinnest part of the other eccentric disc 1, and there is a gap between the two first pressing surfaces 6, and / or there is a gap between the second pressing surface 7 and the corresponding third pressing surface 5. When the first eccentric device or the second eccentric device rotates, the positions of the thickest parts of the two eccentric discs 1 undergo relative torsion, that is, the thickest part of one eccentric disc 1 is no longer opposite to the thinnest part of the other eccentric disc 1. As the relative torsion of the two eccentric discs 1 continues, the sum of the thicknesses of the two eccentric discs 1 in a certain circumferential direction is equal to the distance between the two third pressing surfaces 5, so that the two first pressing surfaces 6 can be mutually extruded and pushed back, and the second pressing surface 7 abuts against the corresponding third pressing surface 5 to achieve locking, realizing the common rotation of the first eccentric device, the second eccentric device and the outer bracket 3. Among them, the driven torque shaft 2 can be used as the power input end, the other torque shaft 2 as the no-load end, and the outer bracket 3 as the power output end to transmit torque.

[0050] In the two torque shafts 2 of the transmission device of the present invention, any one of them can be used as the power input end, and the other as the no-load end, and the outer bracket 3 is used as the power output end. Combining with a differential or a planetary gear train can realize the function of a differential lock, and combining with transmission teeth can also realize the function of a clutch. It has the characteristics of stepless adjustable output torque, simple structure, low manufacturing cost, high transmission efficiency, etc., and has a wide range of uses. It can realize functions such as differential lock, clutch device, braking device, and power splitting device. When used as a power splitting device, power is input from the input end, the no-load end is the power full-time output end, and the power input end is the timely power output end.

[0051] Embodiment 2: This embodiment is described in combination with Embodiment 1. As Figure 6 shown, the two support walls 4 of the outer bracket 3 are correspondingly replaced with shoulder structures 8 and adjusting nuts 11. Any one of the first torque shafts 2 is threadedly connected to the adjusting nut 11, and the shoulder structure 8 is arranged on the other first torque shaft 2. The two first torque shafts 2 are connected and respectively penetrate through the two eccentric disks 1.

[0052] This embodiment gives another embodiment of the outer bracket 3. When the two eccentric disks 1 are extruded and pushed back, they can be correspondingly extruded and locked with the shoulder structure 8 and the adjusting nut 11. The driven eccentric disk 1 is used as the power input end, and the other eccentric disk 1 can be used as the no-load end, and the torque shaft 2 is used as the power output end to realize the transmission function. The technical solution of the transmission device given in this embodiment can adjust the relative position of the torque shaft 2 and the adjusting nut 11 to change the distance between the two support walls 4, and further adjust the locking rate of the two eccentric disks 1.

[0053] Embodiment 3: This embodiment is described in combination with Embodiment 1. As Figure 7 、 Figure 8 shown, annular grooves are respectively formed on the opposite end faces of the two eccentric disks 1. The axis of the annular groove coincides with the axis of the eccentric disk 1. A number of end face balls 36 are respectively in rolling fit with the annular grooves of the two eccentric disks 1. By arranging a number of end face balls 36 between the two eccentrics 1, the rotational friction between the two eccentric disks 1 can be reduced, the transmission efficiency can be improved, and the wear can be reduced.

[0054] Embodiment 4: This embodiment is described in combination with Embodiment 1. As Figure 9 shown, it further includes an axial transmission mechanism. The axial transmission mechanism includes an inner bracket 9. The inner bracket 9 is arranged between the two eccentric disks 1. A number of mutually parallel transmission rods 10 are slidably arranged on the inner bracket 9. When any one of the first torque shafts 2 rotates, the two eccentric disks 1 are mutually extruded and pushed back through the transmission rods 10, and the two eccentric disks 1 are respectively extruded and locked with the opposite support walls 4.

[0055] The transmission rod 10 is arranged along the axial direction of the eccentric disc 1. The difference between the distance between the two third extrusion surfaces 5 and the length of the transmission rod 10 is greater than the sum of the thicknesses of the thickest and thinnest parts of the eccentric disc 1, and is less than the sum of the thicknesses of the thickest parts of the two eccentric discs 1. In the initial state, the thickest part of one eccentric disc 1 is opposite to the thinnest part of the other eccentric disc 1. When the first eccentric device or the second eccentric device rotates, the positions of the thickest parts of the two eccentric discs 1 are relatively twisted, that is, the thickest part of one eccentric disc 1 is no longer opposite to the thinnest part of the other eccentric disc 1. When the two eccentric discs 1 are at a certain When the sum of the circumferential thicknesses is equal to the difference between the spacing between the two third extrusion surfaces 5 and the length of the transmission rod 10, the rotating eccentric disk 1 pushes the transmission rod 10 to abut against the other eccentric disk 1, and the two first extrusion surfaces 6 can be squeezed and pushed back against each other through the transmission rod 10, and the second extrusion surface 7 is pressed and locked against the corresponding third extrusion surface 5, so that the first eccentric device, the second eccentric device and the outer bracket 3 can rotate together, wherein the driven torque shaft 2 can be used as the power input end, the other torque shaft 2 as the no-load end, and the outer bracket 3 as the power output end to transmit torque.

[0056] In order to reduce the friction between the eccentric disc 1 and the transmission rod 10 , balls 36 may be provided at both ends of the transmission rod 10 .

[0057] Example 5: This embodiment is described in conjunction with Example 1. Figures 10 to 12 As shown, the eccentric disk 1 includes a disk seat 12 and a disk surface 13, and the disk surface 13 and the disk seat 12 are rotationally matched.

[0058] The end surface of the disc base 12 facing away from the disc surface 13 is the second extrusion surface 7, and the end surface of the disc surface 13 facing away from the disc base 12 is the first extrusion surface 6. One or more slide grooves 15 are provided on the end surface of the disc base 12 facing the disc surface 13. The bottom surface of the slide groove 15 is an arc surface. One or more limiting protrusions 16 are provided on the end surface of the disc surface 13 facing the disc base 12. The top surface of the limiting protrusion 16 is an arc surface. The top surface of the limiting protrusion 16 is rotated against the bottom surface of the corresponding slide groove 15.

[0059] A shift block 14 is provided on one side of the disc 13. When the transmission device of the present invention is used in an automobile, the shift block 14 can be connected to a push rod or an actuator motor of an actuator mechanism (such as a clutch system wheel cylinder or a brake system wheel cylinder) of the vehicle's clutch system or brake system. When the clutch system or brake system of the vehicle is operating, the push rod and the actuator motor of the actuator can gradually push the disc 13 to rotate on the disc base 12, thereby adjusting the inclination angle of the first extrusion surface 6 and thereby adjusting the locking ratio between the second extrusion surface 7 and the third extrusion surface 5.

[0060] The lock-up ratio is used to change the output torque of the power output. The higher the lock-up ratio, the greater the torque output of the power output. When the torque is fully distributed to the power output, the power input and power output are combined.

[0061] Embodiment 6: This embodiment is described in combination with Embodiment 1. As Figures 13 to 15 shown, it further includes a universal transmission mechanism, which includes an outer guide sleeve 17 and an inner transmission block 18. The inner transmission block 18 is arranged between two eccentric disks 1. A number of circumferential balls 19 are provided on the outer periphery of the inner transmission block 18, and a number of first guide grooves 21 are provided on the inner periphery of the outer guide sleeve 17. The number of circumferential balls 19 and the number of first guide grooves 21 are in one-to-one rolling fit.

[0062] The outer guide sleeve 17 is connected to the outer bracket 3. The difference between the distance between the two third pressing surfaces 5 and the thickness of the inner transmission block 18 is greater than the sum of the thicknesses of the thickest and thinnest parts of the eccentric disk 1, and less than the sum of the thicknesses of the thickest parts of the two eccentric disks 1. In the initial state, the thickest part of one eccentric disk 1 is opposite to the thinnest part of the other eccentric disk 1. When the first eccentric device or the second eccentric device rotates, the positions of the thickest parts of the two eccentric disks 1 are relatively twisted, that is, the thickest part of one eccentric disk 1 is no longer opposite to the thinnest part of the other eccentric disk 1. When the sum of the thicknesses of the two eccentric disks 1 in a certain circumferential direction is equal to the difference between the distance between the two third pressing surfaces 5 and the thickness of the inner transmission block 18, the rotating eccentric disk 1 pushes the inner transmission block 18 to abut against the other eccentric disk 1. The two first pressing surfaces 6 can mutually press and push against each other through the inner transmission block 18, and the second pressing surface 7 abuts against the corresponding third pressing surface 5 to be tightly locked, so that the first eccentric device, the second eccentric device and the outer bracket 3 rotate together. Any one of the torque shafts 2 can be used as the power input end, the other torque shaft 2 as the no-load end, and the outer bracket 3 as the power output end to transmit torque. The inner transmission block 18 does not rotate, but can swing reciprocally between the two eccentric disks 1. The function of the outer guide sleeve 17 and the number of first guide grooves 21 is to provide guidance for the swinging of the inner transmission block 18. When the inner transmission block 18 swings, its center always remains at the center of the outer guide sleeve 17. The first guide grooves 21 are arc-shaped grooves, that is, the array diameter in the middle of the number of first guide grooves 21 is larger than the array diameter at both ends, so that the number of circumferential balls 19 can roll along an arc track in the first guide grooves 21 around the center of the inner transmission block 18. The universal transmission device is used in cooperation with the adjustable disk surface 13. When the present invention is used in an automobile, when the push rod of the actuator (clutch system slave cylinder, brake system slave cylinder) of the vehicle's clutch system or brake system and the actuator motor drive the disk surface 13 to rotate, and then adjust the inclination angle of the first pressing surface 6, the disk surface 13 with the adjusted inclination angle presses the disk surface 13 of the other eccentric disk 1 through the inner transmission block 18, so that the inclination angle of the disk surface 13 of the other eccentric disk 1 can be synchronously adjusted.

[0063] The outer periphery of the inner transmission block 18 is spindle-shaped, thick in the middle and thin at both ends. To facilitate the assembly of the circumferential balls 19, a number of second guiding grooves 22 may be formed on the outer periphery of the inner transmission block. The second guiding grooves 22 are formed from one end to the other along the profile of the outer periphery of the inner transmission block 18 and are through grooves. A number of circumferential balls 19 are in rolling fit with the number of second guiding grooves 22 one by one. To make the circumferential balls 19 located in the middle of the second guiding grooves 22, a cage 20 may be sleeved on the outer periphery of the inner transmission block. The cage 20 is a spindle-shaped sleeve thick in the middle and thin at both ends. A number of ball holes are formed on the cage 20. The number of ball holes is adapted to the ball diameter of the number of circumferential balls 19, and the diameter of the cage 20 is set according to the ball centers of the number of circumferential balls 19. Both ends of the inner transmission block 18 are respectively abutted against two first pressing surfaces. To prevent the cage 20 from being deformed by extrusion, the thickness of the cage 20 is slightly smaller than the thickness of the inner transmission block 18, and both ends of the cage 20 are respectively close to the two first pressing surfaces. The function of the cage 20 is to limit the relative positions of the number of circumferential balls 19 and the inner transmission block 18 to remain unchanged.

[0064] Embodiment 7: This embodiment is described in combination with Embodiment 1. As Figure 16 shown, it further includes a universal transmission mechanism. The universal transmission mechanism includes an outer transmission sleeve 23 and an inner fixing block 24. The inner fixing block 24 is arranged between two eccentric disks 1. Regarding any one of the eccentric disks 1 and the corresponding torque shaft 2 as a passive component, the torque shaft 2 of the passive component passes through the eccentric disk 1 and is connected to the inner fixing block 24. A number of circumferential balls 19 are arranged on the outer periphery of the inner fixing block 24. A number of first guiding grooves 21 are arranged on the inner periphery of the outer transmission sleeve 23. The number of circumferential balls 19 is in rolling fit with the number of first guiding grooves 21 one by one. The outer transmission sleeve 23 is arranged between two eccentric disks 1. When any one of the first torque shafts 2 rotates, the two eccentric disks 1 are mutually extruded and pushed back through the outer transmission sleeve 23, and the two eccentric disks 1 are respectively locked by extrusion against the opposite supporting walls 4.

[0065] This embodiment provides another implementation manner of the universal transmission mechanism. The difference from Embodiment 6 is that the outer transmission sleeve 23 is not connected to the outer bracket 3. The outer transmission sleeve 23 is arranged between two eccentric disks 1. The inner fixing block 24 is connected to any one of the torsion shafts 2. Through the cooperation of the number of first guiding grooves 21 and the number of circumferential balls 19, the outer transmission sleeve 23 can swing reciprocally between the two eccentric disks 1. In the initial state, the thickest part of one eccentric disk 1 is arranged opposite to the thickest part of the other eccentric disk 1. When any one of the torque shafts 2 rotates, the thickest parts of the two eccentric disks 1 are torsionally opposite to each other. The two end faces of the outer transmission sleeve 23 are respectively extruded and pushed back by the two first pressing surfaces 6, so that the second pressing surface 7 is extruded and locked against the corresponding third pressing surface 5.

[0066] The function of the universal transmission mechanism in this embodiment is the same as that in Embodiment 6.

[0067] Embodiment 8: This embodiment is described in combination with Embodiments 1 to 7. As Figure 17 shown, a clutch device is realized relying on the transmission device described in Embodiments 1 to 7. One eccentric disk 1 and the corresponding torque shaft 2 are marked as the first eccentric device, and the other eccentric disk 1 and the corresponding torque shaft 2 are marked as the second eccentric device. One side end where the two eccentric disks 1 face each other is marked as the first pressing surface 6, and the side end faces where the two eccentric disks 1 face away from each other are marked as the second pressing surface 7. One side end faces where the two support walls 4 face each other are marked as the third pressing surface 5. The eccentric disk 1 of the first eccentric device is fixedly connected to the torque shaft 2. A spline groove 26 is provided on the first pressing surface 6 of the first eccentric mechanism. A through spline hole is axially formed in the eccentric disk 1 of the second eccentric mechanism. The spline groove 26 and the spline hole are coaxial. A spline shaft section 25 is provided at one end of the torque shaft 2 of the second eccentric mechanism close to the first eccentric mechanism. The spline shaft section 25 is in sliding fit with the spline hole and is in plug-in fit or separation with the spline groove 26.

[0068] When the present invention is applied to an automobile, the torque shaft 2 of the second eccentric mechanism is connected to the push rod or the actuating motor of the actuating mechanism (the clutch system slave cylinder or the brake system slave cylinder) of the automobile's clutch system or brake system. When the push rod and the actuating motor of the actuating mechanism gradually push the torque shaft 2 of the second eccentric mechanism to be plugged into or separated from the spline groove 26 of the first eccentric mechanism, when the torque shaft 2 of the second eccentric mechanism retracts into the eccentric disk 1 of the second eccentric mechanism, the first eccentric mechanism and the second eccentric mechanism form the transmission device as described in Embodiment 1. When any one of the torque shafts 2 rotates, the two first pressing surfaces 6 press against each other and push back. The second pressing surface 7 abuts against the corresponding third pressing surface 5 and is tightly locked, realizing the common rotation of the first eccentric device, the second eccentric device and the outer bracket 3. Any one of the torque shafts 2 can be used as the power input end, the other torque shaft 2 as the no-load end, and the outer bracket 3 as the power output end to transmit torque;

[0069] When there is a gap between the two eccentric disks 1, the spline shaft section 25 of the second eccentric mechanism is plugged and engaged with the spline groove 26 of the first eccentric mechanism. After any one of the torque shafts 2 rotates, the two eccentric disks 1 and the other torque shaft 2 rotate synchronously. The thickest parts of the two swash plates no longer undergo relative torsion. A gap can always be maintained between the two first pressing surfaces 6 or between the second pressing surface 7 and the opposite third pressing surface 5. The two eccentric disks 1 no longer press and lock with the corresponding support walls 4. Taking any one of the torque shafts 2 as the power input end and the outer bracket 3 as the power output end, the disconnection between the power input end and the power output end can be realized, achieving the clutch function of the torque converter, with a simple structure, low manufacturing cost and high transmission efficiency.

[0070] When used in a vehicle braking system, the clutch device is connected in series or in parallel to the power transmission part. Any one end of the first eccentric mechanism, the second eccentric mechanism, or the outer bracket 3 is selected as the power input end of the clutch device and is connected to the power transmission part or the wheel of the vehicle. One end is used as the power output end of the clutch device and is connected to the axle, the gearbox housing, or the vehicle frame, and the other end is used as the no-load end.

[0071] When used in a vehicle clutch, the clutch device is connected in series to the power transmission part. Any one end of the first eccentric mechanism, the second eccentric mechanism, or the outer bracket 3 is selected as the power input end, one end is used as the power output end of this device and is connected to the transmission device of the vehicle, and the other end is used as the no-load end.

[0072] Embodiment 9: This embodiment is described in combination with Embodiments 1 to 7, as Figure 18 shown, a clutch device, realized relying on the transmission device described in Embodiments 1 to 7, further includes a meshing sleeve 28. The inner circumference of the meshing sleeve 28 is provided with an internal gear structure, and the outer circumferences of both eccentric discs 1 are provided with external gear structures 27. The internal gear structure of the meshing sleeve 28 meshes with the external gear structure 27 of any one eccentric disc 1, and the internal gear structure of the meshing sleeve 28 meshes or disengages from the external gear structure 27 of the other eccentric disc 1.

[0073] This embodiment gives another implementation manner of the clutch device. The meshing sleeve 28 is connected to the push rod and the actuator motor of the clutch system or the braking system actuator (clutch system slave cylinder, braking system slave cylinder) of the vehicle. When the clutch system and the braking system work, the push rod and the actuator motor of the actuator gradually push the meshing sleeve 28 to move axially, meshing or disengaging from the external gear structure 27 of the first eccentric mechanism.

[0074] One of the eccentric discs 1 and the corresponding torque shaft 2 are marked as the first eccentric device, and the other eccentric disc 1 and the corresponding torque shaft 2 are marked as the second eccentric device. The meshing sleeve 28 always remains meshed with the external gear 27 of the second eccentric mechanism. When the meshing sleeve 28 completely moves between the first pressing surface 6 and the second pressing surface 7 of the second eccentric mechanism, any one torque shaft 2 rotates, and the two first pressing surfaces 6 can be pressed against each other to lock, and the two eccentric discs 1 are respectively pressed against and locked with the opposite support walls 4.

[0075] When used in a vehicle braking system, the clutch device is connected in series or in parallel to the power transmission part. Any one end of the first eccentric mechanism, the second eccentric mechanism, or the outer bracket 3 is selected as the power input end of the clutch device and is connected to the power transmission part or the wheel of the vehicle. One end is used as the power output end of the clutch device and is connected to the axle, the gearbox housing, or the vehicle frame, and the other end is used as the no-load end.

[0076] When used for a vehicle clutch, the clutch device is connected in series on the power transmission part. Any one end of the first eccentric mechanism, the second eccentric mechanism, or the outer bracket 3 is selected as the power input end, one end is used as the power output end of this device and is connected to the transmission device of the vehicle, and the other end is used as the no-load end.

[0077] Embodiment 10: This embodiment will be described in combination with Embodiments 1 to 7. As Figure 19 、 Figure 20 shown, a differential lock is realized relying on the transmission device described in Embodiments 1 to 7, and further includes a differential 29 or a planetary gear train 30. The planetary gear train 30 includes a sun gear 34 and a ring gear 31 meshed by a plurality of planetary gears 32. A housing is provided outside the planetary gear train 30. The planetary shafts 33 of the plurality of planetary gears 32 are all connected to the housing of the planetary gear train 30. The sun gear 34 is sleeved on one end of the second torque shaft, and the ring gear 31 is connected to one end of the third torque shaft 35. The other ends of the second torque shaft and the third torque shaft 35 both extend outside the housing of the planetary gear train 30;

[0078] The outer bracket 3 is connected to the housing of the differential 29. Any one first torque shaft 2 extends into the housing of the differential 29 and is sleeved and connected to any one of the side gears of the differential 29;

[0079] Or, the outer bracket 3 is connected to the housing of the planetary gear train 30, and any one first torque shaft 2 is coaxially connected to the second torque shaft;

[0080] Or, the outer bracket 3 is connected to the housing of the planetary gear train 30, and any one first torque shaft 2 is coaxially connected to the third torque shaft 35.

[0081] When used for the differential lock, the transmission device is used in combination with the differential 29 or the planetary gear train 30:

[0082] For example, any one first torque shaft 2 extends into the housing of the differential 29 and is sleeved and connected to any one of the side gears of the differential 29. The other first torque shaft 2 and the other side gear are respectively connected to the wheels on both sides of the vehicle or the front and rear drive axles;

[0083] Or any one first torque shaft 2 is coaxially connected to the second torque shaft, and the other first torque shaft 2 and the third torque shaft 35 are respectively connected to the wheels on both sides of the vehicle or the front and rear drive axles;

[0084] Or, any one first torque shaft 2 is coaxially connected to the third torque shaft 35, and the other first torque shaft 2 and the second torque shaft are respectively connected to the wheels on both sides of the vehicle or the front and rear drive axles;

[0085] During operation, power is input from the housing of the differential 29 and simultaneously distributed to the half-axle gears on both sides through the bevel gears of the differential 29. The half-axle gear on one side directly drives the wheel or the front and rear axles on the same side, while the half-axle gear on the other side is connected to the torque shaft 2 and drives the wheel or the front and rear axles on the other side through the first eccentric mechanism and the second eccentric mechanism.

[0086] Alternatively, power is input from the housing of the planetary gear train 30 and simultaneously distributed to the sun gears 34 and the ring gear 31 on both sides through the planetary gears 32 of the cylindrical gear differential 30. The sun gear 34 on one side directly drives the wheel or the front and rear axles on one side. The ring gear 31 of the half-axle gear on the other side is connected to the torque shaft 2 and drives the wheel or the front and rear axles on the other side through the first eccentric mechanism and the second eccentric mechanism.

[0087] At this time, an axial extrusion reaction thrust is generated between the first eccentric mechanism and the second eccentric mechanism, and the first eccentric mechanism and the second eccentric mechanism are locked to the outer bracket 3. Since one of the eccentric mechanisms is connected to the half-axle gear (or sun gear) on one side through the torque shaft 2, when the first eccentric mechanism and the second eccentric mechanism are locked to the outer bracket 3, the half-axle gear (or ring gear 31) connected to the eccentric mechanism is simultaneously locked to the housing of the differential 29 (planetary gear train 30) through the transmission device, realizing the simultaneous rotation of the wheels on both sides or the front and rear axles.

[0088] The above embodiments are only illustrative descriptions of the present invention and do not limit its protection scope. Those skilled in the art can also make partial changes to it. As long as it does not exceed the spirit of the present invention, it is within the protection scope of the present invention.

Claims

1. A transmission device, characterized in that: It includes an eccentric disk (1) and an outer support (3). The outer support (3) has two opposite support walls (4). Two eccentric disks (1) are located between the two support walls (4). The thickness of the eccentric disk (1) varies with the central angle. On the opposite sides of the two eccentric disks (1), a first torque shaft (2) extends axially. The first torque shaft (2) passes through the outer support (3) by the corresponding support wall (4). When any first torque shaft (2) rotates, the two eccentric disks (1) are squeezed and pushed against each other, and the two eccentric disks (1) are respectively squeezed and locked with the corresponding support walls (4).

2. The transmission device according to claim 1, wherein: Replace the two support walls (4) of the outer support (3) with a shoulder structure (8) and an adjusting nut (11) correspondingly. Any first torque shaft (2) is threadedly connected to the adjusting nut (11). The shoulder structure (8) is arranged on the other first torque shaft (2). The two first torque shafts (2) are connected and respectively penetrate through the two eccentric disks (1).

3. A transmission device according to claim 1, characterized in that: Circular grooves are formed on the opposite end faces of the two eccentric disks (1). The axis of the circular groove coincides with the axis of the eccentric disk (1). A number of end face balls (36) are respectively in rolling fit with the circular grooves of the two eccentric disks (1).

4. A transmission device according to claim 1, characterized in that: It further includes an axial transmission mechanism. The axial transmission mechanism includes an inner support (9). The inner support (9) is arranged between the two eccentric disks (1). A number of parallel transmission rods (10) are slidably arranged on the inner support (9). When any first torque shaft (2) rotates, the two eccentric disks (1) are squeezed and pushed against each other through the transmission rods (10), and the two eccentric disks (1) are respectively squeezed and locked with the opposite support walls (4).

5. A transmission device according to claim 1, characterized in that: The eccentric disk (1) includes a disk base (12) and a disk surface (13). The disk surface (13) and the disk base (12) are rotationally matched.

6. A transmission device according to claim 5, characterized in that: It further includes a universal transmission mechanism. The universal transmission mechanism includes an outer guide sleeve (17) and an inner transmission block (18). The inner transmission block (18) is arranged between the two eccentric disks (1). A number of circumferential balls (19) are arranged on the outer periphery of the inner transmission block (18). A number of first guide grooves (21) are arranged on the inner periphery of the outer guide sleeve (17). The number of circumferential balls (19) is in one-to-one rolling fit with the number of first guide grooves (21).

7. A transmission device according to claim 5, characterized in that: It further includes a universal transmission mechanism. The universal transmission mechanism includes an outer transmission sleeve (23) and an inner fixing block (24). The inner fixing block (24) is arranged between the two eccentric disks (1). Regarding any eccentric disk (1) and the corresponding torque shaft (2) as a passive component, the torque shaft (2) of the passive component passes through the eccentric disk (1) and is connected to the inner fixing block (24). A number of circumferential balls (19) are arranged on the outer periphery of the inner fixing block (24). A number of first guide grooves (21) are arranged on the inner periphery of the outer transmission sleeve (23). The number of circumferential balls (19) is in one-to-one rolling fit with the number of first guide grooves (21). The outer transmission sleeve (23) is arranged between the two eccentric disks (1). When any first torque shaft (2) rotates, the two eccentric disks (1) are squeezed and pushed against each other through the outer transmission sleeve (23), and the two eccentric disks (1) are respectively squeezed and locked with the opposite support walls (4).

8. A clutch device, implemented relying on the transmission device according to any one of claims 1-7, characterized in that: One of the eccentric discs (1) and the corresponding first torque shaft (2) are marked as the first eccentric device, and the other eccentric disc (1) and the corresponding first torque shaft (2) are marked as the second eccentric device. The opposite side ends of the two eccentric discs (1) are marked as the first pressing surface (6), and the opposite side end faces of the two eccentric discs (1) are marked as the second pressing surface (7). The opposite side end faces of the two support walls (4) are marked as the third pressing surface (5). The eccentric disc (1) of the first eccentric device is fixedly connected to the first torque shaft (2). A spline groove (26) is provided on the first pressing surface (6) of the first eccentric mechanism. A through spline hole is axially formed in the eccentric disc (1) of the second eccentric mechanism. The spline groove (26) is coaxial with the spline hole. A spline shaft section (25) is provided at one end of the first torque shaft (2) of the second eccentric mechanism close to the first eccentric mechanism. The spline shaft section (25) is slidably mated with the spline hole, and the spline shaft section (25) is inserted and mated or separated from the spline groove (26).

9. A clutch device, implemented based on the transmission device described in any one of claims 1-7, characterized in that: It further includes a dog clutch (28). The inner circumference of the dog clutch (28) is provided with an internal gear structure. The outer circumferences of the two eccentric discs (1) are both provided with an external gear structure (27). The internal gear structure of the dog clutch (28) is meshed with the external gear structure (27) of any one of the eccentric discs (1). The internal gear structure of the dog clutch (28) is meshed with or separated from the other eccentric disc (1).

10. A differential lock, realized based on the transmission device described in any one of claims 1-7, characterized in that: It further includes a differential (29) or a planetary gear train (30). The planetary gear train (30) includes a sun gear (34) and a ring gear (31) meshed through a plurality of planetary gears (32). A housing is provided outside the planetary gear train (30). The sun gear (34) is sleeved on one end of the second torque shaft. The ring gear (31) is connected to one end of the third torque shaft (35). The other ends of the second torque shaft and the third torque shaft (35) both extend outside the housing of the planetary gear train (30); The outer bracket (3) is connected to the housing of the differential (29). Any one of the first torque shafts (2) extends into the housing of the differential (29) and is sleeved and connected to any one of the half-axle gears of the differential (29); Alternatively, the outer bracket (3) is connected to the housing of the planetary gear train (30). Any one of the first torque shafts (2) is coaxially connected to the second torque shaft; Alternatively, the outer bracket (3) is connected to the housing of the planetary gear train (30). Any one of the first torque shafts (2) is coaxially connected to the third torque shaft (35).

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