阅读说明：本技术 带电磁式凸轮离合功能的差速器 (Differential with electromagnetic cam clutch function ) 是由 张宇荣 于 2020-12-31 设计创作，主要内容包括：本发明公开了一种带电磁式凸轮离合功能的差速器,属于差速器技术领域,其包括差速器壳体,设于差速器壳体内的行星齿轮架、端齿离合盘,以及致动器,行星齿轮架可相对差速器壳体旋转,端齿离合盘轴向可移动、周向随差速器壳体同步旋转,行星齿轮架与端齿离合盘的相对端面上设有相互配合的端齿,致动器包括凹轮盘和螺线管线圈,凹轮盘与端齿离合盘具有相互配合的凹部和凸缘部,螺线管线圈的通电可吸引凹轮盘使其相对端齿离合盘转动,从而致使端齿离合盘轴向移动与行星齿轮架啮合。该差速器能在需要时切断驱动电机与车轮轴之间的传动连接,从而避免驱动电机因转速过高或被车轮轴反拖而造成零部件磨损和燃料消耗。(The invention discloses a differential with an electromagnetic cam clutch function, which belongs to the technical field of differentials and comprises a differential shell, a planet carrier, an end tooth clutch disc and an actuator, wherein the planet carrier, the end tooth clutch disc and the actuator are arranged in the differential shell, the planet carrier can rotate relative to the differential shell, the end tooth clutch disc can axially move and circumferentially synchronously rotate along with the differential shell, end teeth which are matched with each other are arranged on the opposite end surfaces of the planet carrier and the end tooth clutch disc, the actuator comprises a concave wheel disc and a solenoid coil, the concave wheel disc and the end tooth clutch disc are provided with a concave part and a flange part which are matched with each other, and the solenoid coil can be electrified to attract the concave wheel disc to enable the opposite end tooth clutch disc to rotate, so that the end tooth clutch disc axially moves. The differential can cut off the transmission connection between the driving motor and the wheel shaft when needed, thereby avoiding the abrasion of parts and fuel consumption caused by overhigh rotating speed of the driving motor or the reverse dragging of the wheel shaft.)

1. Differential mechanism with electromagnetic cam clutch function, including differential mechanism casing and left side axle gear, right side axle gear, planetary gear, the planet wheel axle of locating in the differential mechanism casing, rotatable bearing of differential mechanism casing is located in the axle reducing gear box, and the differential mechanism casing links firmly drive gear outward, and the input gear axle meshing transmission who wears to locate in the axle reducing gear box, its characterized in that: an annular planet gear carrier and an annular end tooth clutch disc are also arranged in the differential shell; the planetary gear carrier is rotatably arranged on the inner peripheral wall of the differential shell, the planetary gear shaft and the planetary gear are arranged in the planetary gear carrier, and the planetary gear shaft and the planetary gear carrier are fixed; the end tooth clutch disc is positioned on the right side of the planet carrier and is arranged on the inner periphery of the differential shell in an axially movable mode, a plurality of axially-distributed axial protrusions are arranged on the right end face of the end tooth clutch disc, through holes with the same number are formed in corresponding positions of the right end wall of the differential shell, the axially-distributed protrusions penetrate through the through holes so that the end tooth clutch disc can synchronously rotate along with the differential shell, and flange portions with high middle and gradually-low circumferential directions are formed at the end portions of the axially-distributed protrusions;

the right end face of the planet gear carrier is provided with a circle of first end teeth, the left end face of the end tooth clutch disc is provided with second end teeth matched with the first end teeth, the right side of the end tooth clutch disc is provided with an actuator used for pushing the end tooth clutch disc to move leftwards to be meshed with the planet gear carrier, and a return spring is arranged between the end tooth clutch disc and the differential shell;

the actuator comprises a concave wheel and an electromagnetic actuating assembly; the concave wheel disc is rotatably held on the differential shell in a mode relative to the differential shell and the axle reduction box, the left end face of the concave wheel disc is provided with a concave part matched with the axially protruding flange part, and the concave wheel disc rotates relative to the end tooth clutch disc to enable the end tooth clutch disc to axially move leftwards to be meshed with the planet carrier; the electromagnetic actuating assembly comprises a solenoid coil which is adjacently arranged on the right side of the concave wheel disc and fixed with the axle reduction box, and the concave wheel disc can be attracted by electrifying the solenoid coil to enable the concave wheel disc to rotate relative to the end tooth clutch disc.

2. The differential with electromagnetic cam clutch function according to claim 1, characterized in that: the flange part is an isosceles triangle, the angle of the vertex angle of the flange part is 145 degrees, and the concave part of the concave wheel disc is matched with the flange part in shape and angle.

3. The differential with electromagnetic cam clutch function according to claim 1 or 2, characterized in that: the number of the axial protrusions, the through holes and the concave wheel disc concave parts is at least 2.

4. The differential with electromagnetic cam clutch function according to claim 3, characterized in that: the number of the axial protrusions, the through holes and the concave wheel disc concave parts is 4.

5. The differential with electromagnetic cam clutch function according to claim 1 or 2, characterized in that: the inner side wall of the right end of the differential shell is provided with a convex ring which axially protrudes inwards, and the reset spring is sleeved between the outer peripheral wall of the convex ring and the inner peripheral wall of the end tooth clutch disc; the position that the bulge loop periphery wall is close to the left side sets firmly the spring retainer ring, and the axial protrusion of end tooth clutch disc has the radial protrusion of the discontinuity of arranging along end tooth clutch disc inner periphery, and reset spring's left end supports on the spring retainer ring, the right-hand member supports on the radial protrusion, and reset spring exerts the power of keeping away from the planet carrier to end tooth clutch disc when compressing.

6. The differential with electromagnetic cam clutch function according to claim 1 or 2, characterized in that: the axial protrusion comprises a protrusion body and a flange part, the flange part is formed at the end part of the protrusion body, the protrusion body is in a regular trapezoid shape with a wide base part and a narrow end part, two side surfaces in the circumferential direction of the protrusion body are first inclined surfaces, and two hole walls in the circumferential direction of the through hole are provided with second inclined surfaces matched with the first inclined surfaces.

7. The differential with electromagnetic cam clutch function according to claim 6, characterized in that: and the included angle between the first inclined plane and the second inclined plane and the central rotating shaft is 15 degrees.

Technical Field

The invention relates to the technical field of differentials, in particular to a differential with an electromagnetic cam clutch function for an electric automobile.

Background

In recent years, in the face of energy crisis and environmental deterioration, the demand for energy saving and environmental protection of automobiles is increasing, and therefore the development of electric automobiles has become the focus of research and development of the automobile industry. In the conventional electric vehicle, in order to simplify the structure and reduce the cost, a clutch device is not provided in a power transmission path between a driving motor of the electric vehicle and a wheel shaft, and the driving motor is always in transmission connection with the wheel shaft through a speed reducer, a differential gear and the like. For the electric automobile, when the vehicle runs down a slope and other working conditions, the rotating speed of the driving motor may exceed the maximum allowable rotating speed, which causes wear of parts (such as bearings) of a motor transmission system, shortens the service life, and when the motor reaches a certain rotating speed or above, the driving motor is difficult to provide driving force for the vehicle, and is dragged to consume energy, so that the vehicle efficiency is reduced and the fuel consumption is increased. For the electric four-wheel drive automobile, the mode of switching from four-wheel drive to two-wheel drive is to close the driving motor of one of the axles, and the rotation of the wheel axle of the electric four-wheel drive automobile with the structure is switched to two-wheel drive to drive the driving motor to rotate in turn, so that the abrasion of parts and the energy consumption are also increased.

Disclosure of Invention

The present invention is directed to overcome the above problems, and an object of the present invention is to provide a differential with an electromagnetic cam clutch function for an electric vehicle, which can cut off a transmission connection between a driving motor and a wheel axle when necessary, thereby preventing the driving motor from being worn by parts and fuel consumption due to an excessively high rotation speed or being dragged by the wheel axle.

The technical scheme of the invention is as follows:

differential mechanism with electromagnetic cam clutch function, including differential mechanism casing and left side axle gear, right side axle gear, planetary gear, the planet wheel axle of locating in the differential mechanism casing, rotatable bearing of differential mechanism casing is located in the axle reducing gear box, and the differential mechanism casing links firmly drive gear outward, and the input gear axle meshing transmission who wears to locate in the axle reducing gear box, its characterized in that: an annular planet gear carrier and an annular end tooth clutch disc are also arranged in the differential shell; the planetary gear carrier is rotatably arranged on the inner peripheral wall of the differential shell, the planetary gear shaft and the planetary gear are arranged in the planetary gear carrier, and the planetary gear shaft and the planetary gear carrier are fixed; the end tooth clutch disc is positioned on the right side of the planet carrier and is arranged on the inner periphery of the differential shell in an axially movable mode, a plurality of axially-distributed axial protrusions are arranged on the right end face of the end tooth clutch disc, through holes with the same number are formed in corresponding positions of the right end wall of the differential shell, the axially-distributed protrusions penetrate through the through holes so that the end tooth clutch disc can synchronously rotate along with the differential shell, and flange portions with high middle and gradually-low circumferential directions are formed at the end portions of the axially-distributed protrusions;

the right end face of the planet gear carrier is provided with a circle of first end teeth, the left end face of the end tooth clutch disc is provided with second end teeth matched with the first end teeth, the right side of the end tooth clutch disc is provided with an actuator used for pushing the end tooth clutch disc to move leftwards to be meshed with the planet gear carrier, and a return spring is arranged between the end tooth clutch disc and the differential shell;

the actuator comprises a concave wheel and an electromagnetic actuating assembly; the concave wheel disc is rotatably held on the differential shell in a mode relative to the differential shell and the axle reduction box, the left end face of the concave wheel disc is provided with a concave part matched with the axially protruding flange part, and the concave wheel disc rotates relative to the end tooth clutch disc to enable the end tooth clutch disc to axially move leftwards to be meshed with the planet carrier; the electromagnetic actuating assembly comprises a solenoid coil which is adjacently arranged on the right side of the concave wheel disc and fixed with the axle reduction box, and the concave wheel disc can be attracted by electrifying the solenoid coil to enable the concave wheel disc to rotate relative to the end tooth clutch disc.

By suitably controlling the actuator, the end-tooth clutch plate can be moved axially relative to the carrier so as to be engaged with or disengaged from each other, wherein in the engaged state, the carrier is coupled to and rotated synchronously with the differential case via the end-tooth clutch plate, torque transmission between the input gear shaft and the planetary gear train is ensured, power transmission of the drive motor to the wheel shaft is achieved, and in the disengaged state, torque transmission is interrupted, and power transmission of the wheel shaft to the drive motor is disconnected.

Meanwhile, the actuator is matched with the relative rotation actuation by adopting electromagnetic actuation, secondary transmission force application is realized, larger thrust is obtained by using lower power consumption for controlling the electromagnetic actuation assembly to overcome the acting force of the return spring, and the actuator has the advantages of high response speed and stable and reliable performance.

Preferably, in the differential gear with the electromagnetic cam clutch function, the flange portion is an isosceles triangle, an angle of a vertex angle thereof is 145 degrees, and the concave portion of the concave sheave is fitted to the flange portion in shape and angle.

Further, in the above differential with electromagnetic cam clutch function, the number of the axial protrusions, the through holes, and the recessed sheave recess is at least 2.

Preferably, in the above differential with electromagnetic cam clutch function, the number of the axial protrusions, the through holes, and the recessed sheave recess is 4.

Further, in the differential with the electromagnetic cam clutch function, a convex ring protruding inwards in the axial direction is arranged on the inner side wall of the right end of the differential shell, and the reset spring is sleeved between the outer peripheral wall of the convex ring and the inner peripheral wall of the end tooth clutch disc; the position that the bulge loop periphery wall is close to the left side sets firmly the spring retainer ring, and the axial protrusion of end tooth clutch disc has the radial protrusion of the discontinuity of arranging along end tooth clutch disc inner periphery, and reset spring's left end supports on the spring retainer ring, the right-hand member supports on the radial protrusion, and reset spring exerts the power of keeping away from the planet carrier to end tooth clutch disc when compressing.

Preferably, in the differential gear with the electromagnetic cam clutch function, the axial projection includes a projection body and the flange portion, the flange portion is formed at an end portion of the projection body, the projection body has a trapezoidal shape with a wide base portion and a narrow end portion, both side surfaces in the circumferential direction of the projection body are formed with first inclined surfaces, and both hole walls in the circumferential direction of the through hole are formed with second inclined surfaces that are engaged with the first inclined surfaces. The inclined surface matching design is adopted between the axial protrusion and the through hole, so that the differential shell drives the end tooth clutch disc to rotate, and simultaneously, a certain thrust component force is applied to the end tooth clutch disc in the axial direction by the rotating torque force, and the thrust component force can further prevent the end tooth clutch disc from being disengaged from the planet carrier after the torque is transmitted.

Preferably, in the differential with the electromagnetic cam clutch function, an included angle between the first inclined surface and the central rotating shaft is 15 degrees.

The invention has the beneficial effects that:

1. by utilizing the planet gear carrier, the end tooth clutch disc and the actuator, the transmission connection between the driving motor and the wheel shaft can be cut off under the working conditions of vehicle downhill and the like, so that the abrasion of motor transmission system parts (such as bearings) and fuel consumption caused by overhigh rotating speed or reverse dragging of the driving motor by the wheel shaft are avoided, the service life of the driving motor is prolonged, and the energy consumption is reduced; the device is used for an electric four-wheel drive automobile, can cut off the transmission connection between a driving motor and a wheel shaft when four-wheel drive is switched to two-wheel drive, also reduces the abrasion of motor parts, reduces energy consumption and improves the vehicle efficiency;

2. the combination of the end tooth clutch disc and the planet carrier is achieved through two-stage force transmission realized by matching of electromagnetic actuation and relative rotation actuation, large thrust is obtained to overcome the acting force of a return spring with low power consumption required for controlling an electromagnetic actuation assembly, and the electromagnetic actuator is high in response speed and stable and reliable in performance.

Drawings

Fig. 1 is a schematic structural diagram of an embodiment of the present invention.

FIG. 2 is a cross-sectional view of the differential case in an embodiment of the present invention.

FIG. 3 is a cross-sectional view of an end tooth clutch plate in an embodiment of the present invention.

Fig. 4 is a perspective view of an end tooth clutch plate according to an embodiment of the invention.

Fig. 5 is a perspective view of a concave wheel disk according to an embodiment of the present invention.

Detailed Description

The invention will now be further described with reference to the accompanying drawings and examples:

in the description of the present invention, it is to be understood that the terms "left", "right", "inside", "outside", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of describing the present invention, and do not indicate or imply that the device or element referred to must have a specific orientation, and thus, should not be construed as limiting the present invention.

Referring to fig. 1, the differential with the electromagnetic cam clutch function provided in this embodiment is used in an axle of an electric vehicle, and includes a differential case 1, and a left half axle gear 11, a right half axle gear 12, a planetary gear 13, and a planetary gear shaft 14 that are disposed in the differential case 1, where the differential case 1 is rotatably supported in an axle reduction box (not shown in the figure), and the differential case 1 is fixedly connected with a transmission gear 2 outside, and is in meshing transmission with an input gear shaft (not shown in the figure) that is disposed in the axle reduction box. An annular planet carrier 3 and an annular end-tooth clutch plate 4 are also arranged in the differential housing 1.

The planetary gear carrier 3 is rotatably supported on the inner peripheral wall of the differential case 1, the planetary gear shaft 14 and the planetary gears 13 are arranged in the planetary gear carrier 3, the planetary gear shaft 14 is a cross shaft, the four planetary gears 13 are respectively and rotatably sleeved on four shaft necks of the planetary gear shaft 14, the planetary gear carrier 3 is provided with four holes, the end parts of the four shaft necks of the planetary gear shaft 14 correspondingly penetrate into the four holes and are fixed with the planetary gear carrier 3, the four planetary gears 13 are simultaneously engaged with the left half shaft gear 11 and the right half shaft gear 12, and the right end face of the planetary gear carrier 3 is also provided with a circle of end teeth one 31.

The end tooth clutch plate 4 is positioned at the right side of the planet carrier 3 and is supported on the inner circumference of the differential shell 1 in an axially movable mode, the left end surface of the end tooth clutch plate 4 is provided with a second end tooth 41 matched with the first end tooth 31, and the right side of the end tooth clutch plate 4 is provided with an actuator used for pushing the end tooth clutch plate 4 to move leftwards to be meshed with the planet carrier 3. As shown in fig. 1, 2, 3 and 4, the right end surface of the end-tooth clutch plate 4 is provided with a plurality of axial protrusions 42 distributed circumferentially, corresponding positions of the differential case 1 are provided with the same number of through holes 15, and the axial protrusions 42 penetrate through the through holes 15 to enable the end-tooth clutch plate 4 to synchronously rotate with the differential case 1, so that the end-tooth clutch plate 4 is meshed with the planet carrier 3, the planet carrier 3 is coupled with the differential case 1 and synchronously rotates, and torque transmission between the input gear shaft and the planetary gear train is realized. The axial projection 42 is further formed at its end with flange portions 43 having a high middle portion and gradually lowered on both sides in the circumferential direction, and the flange portions 43 are projected to the outside of the differential case 1 in an isosceles triangle shape with an apex angle of 145 degrees. The number of the axial protrusions 42 and the through holes 15 is at least 2, and in the present embodiment, the number of the axial protrusions 42 and the through holes 15 is 4.

The actuator described above comprises a concave wheel disc 5 and an electromagnetic actuation assembly. As shown in fig. 1, the roulette plate 5 is held on the differential case 1 so as to be rotatable with respect to the differential case 1 and the axle reduction gearbox, the left end surface of the roulette plate 5 has at least 2 circumferentially distributed recesses 51 (see fig. 5), the recesses 51 are fitted to the flange portions 43 of the axial protrusions 42 in terms of number, position, shape, and angle, and in the present embodiment, the number of the recesses 51 is 4. Under the condition of no influence of other external force, the concave part 51 of the concave wheel disc 5 is tightly attached to the flange part 43 of the axial protrusion 42 of the end tooth clutch disc 4, the concave wheel disc 5 rotates synchronously with the end tooth clutch disc 4, and the concave wheel disc 5 rotates relative to the end tooth clutch disc 4 to enable the flange part 43 to move and climb along the circumferential direction of the concave part 51, so that the end tooth clutch disc 4 is driven to move leftwards in the axial direction to be meshed with the planet carrier 3. The electromagnetic actuating assembly comprises a solenoid coil 61 and a coil seat 62, the solenoid coil 61 is adjacently arranged on the right side of the concave wheel disc 5 and is fixed with the axle reduction box, a conducting wire extends into the box seat and is electrically connected with the solenoid coil 61, and the conducting wire can attract the concave wheel disc 5 to enable the concave wheel disc 5 to rotate relative to the end tooth clutch disc 4 when the conducting wire is electrified. Specifically, the method comprises the following steps: the right end of the differential case 1 is formed with a sleeve portion 16 extending axially, the concave wheel disk 5 is sleeved on the sleeve portion 16, the solenoid coil 61 is also arranged on the sleeve portion 16 by means of a coil holder 62, a plane bearing 63 allowing relative rotation between the concave wheel disk 5 and the coil holder 62 is arranged between the two, and the right side of the coil holder 62 is further provided with an elastic collar 64 embedded on the outer peripheral surface of the sleeve portion 16 for limiting the axial position of the coil holder 62 and the concave wheel disk 5 on the sleeve portion 16.

A return spring 7 is also provided between the end-tooth clutch plate 4 and the differential housing 1, the return spring 7 applying a force to the end-tooth clutch plate 4 away from the planet carrier 3 when compressed, pushing the end-tooth clutch plate 4 to disengage from the planet carrier 3 to return to the initial position when the actuator is not applied. Specifically, the method comprises the following steps: the inner side wall of the right end of the differential case 1 is provided with a convex ring 17 (refer to fig. 2) which axially protrudes inwards, the return spring sleeve 7 is arranged between the outer peripheral wall of the convex ring 17 and the inner peripheral wall of the end tooth clutch disc 4, a spring retainer 18 is fixedly arranged at the position close to the left of the outer peripheral wall of the convex ring 17, an axial protrusion 42 of the end tooth clutch disc 4 is provided with a discontinuous radial protrusion 44 (refer to fig. 3 and 4) which is arranged along the inner periphery of the end tooth clutch disc 4, the left end of the return spring 7 abuts against the spring retainer 18, and the right end abuts against the radial protrusion 44.

The working principle of the embodiment is as follows:

when the solenoid coil 61 is not electrified, the end-tooth clutch disc 4 and the planet gear carrier 3 are in a separated state, no torque is transmitted between the differential housing 1 and the planetary gear train, namely no power is transmitted between the driving motor and the wheel shaft;

when the solenoid coil 61 is energized, the attracting recessed disk 5 is caused to rotate relative to the end-tooth clutch disk 4, the flange portion 43 of the axial projection 42 of the end-tooth clutch disk 4 moves up in the circumferential direction of the recessed portion 51 of the recessed disk 5, thereby driving the end tooth clutch disk 4 to move axially towards the planet carrier 3 against the acting force of the return spring 7 until the end tooth second 41 of the end tooth clutch disk 4 is meshed with the end tooth first 31 of the planet carrier 3, the end tooth clutch disk 4 is combined with the planet carrier 3, since the end-gear clutch disk 4 rotates synchronously with the differential case 1, the carrier 3 is coupled to the differential case 1 and rotates synchronously, at this time, the torque output from the drive motor is transmitted to the input gear shaft, the power is transmitted to a planetary gear train through a transmission gear 2, a differential housing 1, an end tooth clutch disc 4 and a planetary gear carrier 3, so that a wheel shaft is driven, and the transmission from a driving motor to the wheel shaft to power is realized;

when the power supply to the solenoid coil 61 is cut off, the concave wheel disk 5 loses the attraction force, the flange portion 43 of the axial protrusion 42 returns to the state of being closely attached to the concave portion 51 of the concave wheel disk 5 by the action of the return spring 7, the end-tooth clutch disk 4 moves rightward in the axial direction until being detached from the planetary carrier 3, the torque transmission is interrupted, and the power transmission between the driving motor and the wheel shaft is cut off.

As another preferred embodiment (not shown in the drawings), the axial protrusions of the end-tooth clutch plate and the through holes of the differential case may be designed by a bevel fit, specifically: the axial protrusion comprises a protrusion body and a flange part, the flange part is formed at the end part of the protrusion body, the protrusion body is in a regular trapezoid shape with a wide base part and a narrow end part, two side surfaces in the circumferential direction are first inclined surfaces, two hole walls in the circumferential direction of the through hole are provided with second inclined surfaces matched with the first inclined surfaces, and included angles between the first inclined surfaces and the second inclined surfaces and the central rotating shaft are 15 degrees. With this configuration, the differential case rotates the end-tooth clutch plate, and the rotational torque force exerts a thrust component force on the end-tooth clutch plate in the axial direction, which further prevents the end-tooth clutch plate from disengaging from the carrier after the torque is transmitted.

It is understood that various other changes and modifications may be made by those skilled in the art based on the technical idea of the present invention, and all such changes and modifications should fall within the protective scope of the claims of the present invention.