CN214305134U - Differential mechanism with electromagnetic thrust clutch function - Google Patents
Differential mechanism with electromagnetic thrust clutch function Download PDFInfo
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- CN214305134U CN214305134U CN202023292821.7U CN202023292821U CN214305134U CN 214305134 U CN214305134 U CN 214305134U CN 202023292821 U CN202023292821 U CN 202023292821U CN 214305134 U CN214305134 U CN 214305134U
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Abstract
The utility model discloses a differential with electromagnetic thrust clutch function, belonging to the technical field of differentials, which comprises a differential shell, a planet gear carrier rotatably supported in the differential shell and an end tooth clutch disc axially movably supported in the differential shell; the right end face of the end tooth clutch disc is provided with a plurality of axial protrusions which are distributed circumferentially, and the axial protrusions penetrate through holes arranged at corresponding positions of the differential case so that the end tooth clutch disc can synchronously rotate along with the differential case; 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, and an actuator for pushing the end tooth clutch disc to move and be meshed with the planet carrier is arranged on the right side of the end tooth clutch disc; the contact mating surface of the axial protrusion and the through hole in the circumferential direction is an inclined surface. 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.
Description
Technical Field
The utility model relates to a differential mechanism technical field, especially a take differential mechanism of electromagnetism thrust separation and reunion function for 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.
SUMMERY OF THE UTILITY MODEL
The utility model aims to solve the technical problem that overcome above-mentioned problem, and provide a take electromagnetic thrust clutch function's differential mechanism for electric automobile, can cut off the transmission between driving motor and the axletree when needs and be connected to avoid driving motor to cause spare part wearing and tearing and fuel consumption because of the rotational speed is too high or by the anti-dragging of axletree.
The technical scheme of the utility model is that:
take differential mechanism of electromagnetic thrust 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, in the axle reduction box was located to rotatable the bearing of differential mechanism casing, the differential mechanism casing linked firmly drive gear outward, with wear to locate the input gear axle meshing transmission in the axle reduction 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, and the axially-distributed axial protrusions penetrate through the through holes so that the end tooth clutch disc can synchronously rotate along with the differential shell; 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 axial protrusion is in a regular trapezoid shape with a wide base and a narrow end, two side faces in the circumferential direction of the axial protrusion are first inclined faces, and two hole walls in the circumferential direction of the through hole are provided with second inclined faces matched with the first inclined faces.
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.
The axial protrusion of the end tooth clutch disc and the through hole of the differential shell are designed in a bevel fit mode, so that the differential shell drives the end tooth clutch disc to rotate, meanwhile, a certain thrust component force is applied to the end tooth clutch disc in the axial direction by the rotation torque force, and the thrust component force can 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 thrust clutch function, an included angle between the first inclined plane and the central rotating shaft is 15 degrees.
Further, in the differential with the electromagnetic thrust clutch function, the actuator is an electromagnetic thrust assembly and comprises an electromagnet fixed with the axle reduction box and an axially movable piston sleeve, the piston sleeve is at least indirectly connected to the end-tooth clutch disc, and the electromagnet is electrified to actuate the piston sleeve to move axially to push the end-tooth clutch disc to move leftwards to be meshed with the planet carrier.
Further, in the differential with the electromagnetic thrust clutch function, a boosting snap spring is arranged between the actuator and the end tooth clutch disc so as to transmit torque between the actuator and the end tooth clutch disc.
Further, in above-mentioned differential mechanism of taking electromagnetic thrust clutch function, the boosting jump ring includes annular disc and the elastic connection portion that extend a plurality of circumference distributions of buckling formation to the axial direction by the radial inboard of annular disc, the piston sleeve butt of annular disc and actuator, the distribution of elastic connection portion is corresponding with the axial bulge of end tooth clutch disc, and the contained angle of elastic connection portion and annular disc is the acute angle, and the axial bulge of end tooth clutch disc has the draw-in groove of the discontinuity of arranging along end tooth clutch disc inner periphery, and elastic connection portion stretches into the radial inboard of axial bulge and its tip embedding in the draw-in groove in order to fix boosting jump ring and axial bulge. The boosting snap spring is provided with an elastic connecting part, so that flexible connection between the actuator and the end tooth clutch disc can be realized, the tooth hitting phenomenon when the end tooth clutch disc is pushed to move axially to be meshed with the planet gear carrier is avoided, and the service life of the machine is prolonged.
Further, in the differential with the electromagnetic thrust clutch function, a return spring is provided between the end tooth clutch disc and the differential case, and the return spring applies a force to the end tooth clutch disc away from the carrier when compressed. The return spring acts to disengage the end tooth clutch plate from the planet carrier and return it to its original position when the actuator is not active.
Further, in the differential with the electromagnetic thrust clutch function, 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.
Further, in the differential with an electromagnetic thrust clutch function, the number of the axial protrusions and the number of the through holes are at least 2.
Preferably, in the differential with an electromagnetic thrust clutch function, the number of the axial protrusions and the number of the through holes are 4.
The utility model has the advantages 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 inclined plane design is adopted at the matching part of the end tooth clutch disc and the differential shell, so that when the differential shell drives the end tooth clutch disc to rotate, a certain thrust component force is applied to the end tooth clutch disc by the rotating torque force in the axial direction, and the thrust component force can prevent the end tooth clutch disc from being separated from the planet gear carrier after the torque is transmitted, thereby ensuring the reliability of vehicle operation.
Drawings
Fig. 1 is a schematic structural diagram of an embodiment of the present invention.
Fig. 2 is a cross-sectional view of a differential case according to an embodiment of the present invention.
Fig. 3 is a perspective view of the differential case according to the embodiment of the present invention.
Fig. 4 is a cross-sectional view of an end tooth clutch plate according to an embodiment of the present invention.
Fig. 5 is a three-dimensional structure diagram of an end tooth clutch disc in the embodiment of the present invention.
Fig. 6 is a cross-sectional view of the boosting snap spring in the embodiment of the present invention.
Fig. 7 is a perspective structure diagram of the boosting snap spring in the 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 should be understood that the directions or positional relationships indicated by the terms "left", "right", "inside", "outside", and the like are the directions or positional relationships shown in the drawings, and are only for convenience of description of the present invention, and do not indicate or imply that the device or element referred to must have a specific direction, and therefore, should not be construed as limiting the present invention.
Referring to fig. 1, the differential with the electromagnetic thrust 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 5 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, 3, 6 and 7, the right end surface of the end-tooth clutch plate 4 is provided with a plurality of circumferentially distributed axial protrusions 42, the 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 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. In order to prevent the end tooth clutch plate 4 from being separated from the planet carrier 3 after torque transmission, a bevel matching design is adopted between the axial protrusion 42 and the through hole 15, and specifically: the axial protrusion 42 is in a trapezoidal shape with a wide base and a narrow end, two side surfaces in the circumferential direction are first inclined surfaces 43, two hole walls in the circumferential direction of the through hole 15 are formed with second inclined surfaces 16 matched with the first inclined surfaces 43, and the included angles between the first inclined surfaces 43 and the second inclined surfaces 16 and the central rotating shaft are 15 degrees.
As shown in fig. 1, the actuator 5 is an electromagnetic thrust assembly, and comprises an electromagnet fixed with the axle reduction box and an axially movable piston sleeve 51, the piston sleeve 51 is at least indirectly connected to the end-tooth clutch plate 4, and the energization of the electromagnet can actuate the piston sleeve 51 to move axially to push the end-tooth clutch plate 4 to move leftwards to be meshed with the planet carrier 3. Specifically, the electromagnet comprises an annular shell 52, an electromagnetic coil 53 arranged in the annular shell 52 and an annular supporting sleeve 54 arranged on the radial inner side of the annular shell 52, a lead extends into the axle reduction gearbox and is electrically connected with the electromagnetic coil 53, and the piston sleeve 51 is axially movably arranged between the annular shell 52 and the annular supporting sleeve 54. A sleeve portion 17 is formed to extend axially at the right end portion of the differential case 1, and an annular case 52 is fitted over the sleeve portion 17 via an annular support sleeve 54.
A boosting snap spring 6 is arranged between the actuator 5 and the end-tooth clutch plate 4 to transmit torque between the two. As shown in fig. 6 and 7, the boosting snap spring 6 includes an annular disc 61 and a plurality of elastic connection portions 62 distributed circumferentially, the elastic connection portions 62 are formed by radially inward extending and bending the annular disc 61 in an axial direction, and an included angle between the elastic connection portions and the annular disc 61 is an acute angle, and in this embodiment, the included angle is 80 degrees. The annular plate 61 is fitted over the sleeve portion 17 of the differential case 1, the right side thereof abuts against the piston sleeve 51 of the actuator 5, the elastic connecting portions 62 are distributed to correspond to the axial protrusions 42 of the end-tooth clutch plate 4, the axial protrusions 42 of the end-tooth clutch plate 4 have intermittent catching grooves 44 (refer to fig. 4 and 5) arranged along the inner periphery of the end-tooth clutch plate, and the elastic connecting portions 62 extend radially inward of the axial protrusions 42 and have end portions thereof fitted into the catching grooves 44 to fix the thrust-assist catching springs 6 to the axial protrusions 42. The boosting snap spring 6 can realize flexible connection between the actuator 5 and the end tooth clutch disc 4, and avoid tooth beating when the end tooth clutch disc 4 is pushed to be meshed with the planet carrier 3.
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 away from the planet carrier 3 to return to the initial position when the actuator 5 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 18 (refer to fig. 2 and 3) which axially protrudes inwards, the return spring sleeve 7 is arranged between the outer peripheral wall of the convex ring 18 and the inner peripheral wall of the end tooth clutch disc 4, a spring retainer 19 is fixedly arranged at the position close to the left of the outer peripheral wall of the convex ring 18, an axial protrusion 42 of the end tooth clutch disc 4 is provided with a discontinuous radial protrusion 45 (refer to fig. 4 and 5) 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 19, and the right end abuts against the radial protrusion 45.
The working principle of the utility model is as follows:
when the electromagnetic coil 53 of the actuator 5 is not electrified, the end-tooth clutch disc 4 and the planet carrier 3 are in a separated state, no torque is transmitted between the differential case 1 and the planetary gear train, namely no power is transmitted between the driving motor and the wheel shaft;
when the electromagnetic coil 53 is electrified, magnetic field force which points to the end tooth clutch disc 4 axially is generated, so that the piston sleeve 51 moves leftwards axially, the end tooth clutch disc 4 is driven by the boosting snap spring 6 to move axially to the planet carrier 3 against the acting force of the return spring 7 until the end tooth second 41 of the end tooth clutch disc 4 is meshed with the end tooth first 31 of the planet carrier 3, the end tooth clutch disc 4 is combined with the planet carrier 3, the end tooth clutch disc 4 rotates synchronously with the differential housing 1, so that the planet carrier 3 is connected with the differential housing 1 and rotates synchronously, at the moment, the torque output by the driving motor is transmitted to the input gear shaft, and is transmitted to the planet gear train through the transmission gear 2, the differential housing 1, the end tooth clutch disc 4 and the planet carrier 3, and then the wheel shaft is driven, and the power transmission from the driving motor to the wheel shaft is realized;
after the power supply of the electromagnetic coil 53 is cut off, the magnetic field force disappears, the end tooth clutch disc 4 is separated from the planet carrier 3 under the action of the return spring 7, the torque transmission is interrupted, and the power transmission between the driving motor and the wheel shaft is cut off.
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.
Claims (8)
1. Take differential mechanism of electromagnetic thrust 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, in the axle reduction box was located to rotatable the bearing of differential mechanism casing, the differential mechanism casing linked firmly drive gear outward, with wear to locate the input gear axle meshing transmission in the axle reduction 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, and the axially-distributed axial protrusions penetrate through the through holes so that the end tooth clutch disc can synchronously rotate along with the differential shell;
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 axial protrusion is in a regular trapezoid shape with a wide base and a narrow end, two side faces in the circumferential direction of the axial protrusion are first inclined faces, and two hole walls in the circumferential direction of the through hole are provided with second inclined faces matched with the first inclined faces.
2. The differential with electromagnetic thrust clutch function according to claim 1, 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.
3. The differential with electromagnetic thrust clutch function according to claim 1 or 2, characterized in that: the actuator is an electromagnetic thrust assembly and comprises an electromagnet and an axially movable piston sleeve, wherein the electromagnet is fixed with the axle reduction box, the piston sleeve is at least indirectly connected to the end-tooth clutch disc, and the electromagnet is electrified to actuate the piston sleeve to move axially so as to push the end-tooth clutch disc to move leftwards to be meshed with the planet carrier.
4. The differential with electromagnetic thrust clutch function according to claim 3, characterized in that: and a boosting snap spring is arranged between the actuator and the end tooth clutch disc so as to transmit torque between the actuator and the end tooth clutch disc.
5. The differential with electromagnetic thrust clutch function according to claim 4, characterized in that: the boosting snap spring comprises an annular disc and a plurality of elastic connecting portions which are formed by bending and extending the radial inner side of the annular disc towards the axial direction, wherein the elastic connecting portions are distributed in the circumferential direction, the annular disc is abutted to a piston sleeve of the actuator, the elastic connecting portions are distributed corresponding to the axial protrusions of the end tooth clutch disc, the included angles of the elastic connecting portions and the annular disc are acute angles, the axial protrusions of the end tooth clutch disc are provided with discontinuous clamping grooves which are arranged along the inner periphery of the end tooth clutch disc, and the elastic connecting portions stretch into the radial inner side of the axial protrusions and are embedded into the end portions of the axial protrusions to fix the boosting snap spring and the axial protrusions.
6. The differential with electromagnetic thrust 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.
7. The differential with electromagnetic thrust clutch function according to claim 1 or 2, characterized in that: the number of the axial protrusions and the number of the through holes are at least 2.
8. The differential with electromagnetic thrust clutch function according to claim 7, characterized in that: the number of the axial protrusions and the number of the through holes are 4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202023292821.7U CN214305134U (en) | 2020-12-31 | 2020-12-31 | Differential mechanism with electromagnetic thrust clutch function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202023292821.7U CN214305134U (en) | 2020-12-31 | 2020-12-31 | Differential mechanism with electromagnetic thrust clutch function |
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| Publication Number | Publication Date |
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| CN214305134U true CN214305134U (en) | 2021-09-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202023292821.7U Active CN214305134U (en) | 2020-12-31 | 2020-12-31 | Differential mechanism with electromagnetic thrust clutch function |
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| Country | Link |
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| CN (1) | CN214305134U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115095610A (en) * | 2022-06-14 | 2022-09-23 | 中国第一汽车股份有限公司 | Power transmission disconnecting mechanism and vehicle |
-
2020
- 2020-12-31 CN CN202023292821.7U patent/CN214305134U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115095610A (en) * | 2022-06-14 | 2022-09-23 | 中国第一汽车股份有限公司 | Power transmission disconnecting mechanism and vehicle |
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