CN111365437A - Vehicle drive device - Google Patents
Vehicle drive device Download PDFInfo
- Publication number
- CN111365437A CN111365437A CN201911041645.9A CN201911041645A CN111365437A CN 111365437 A CN111365437 A CN 111365437A CN 201911041645 A CN201911041645 A CN 201911041645A CN 111365437 A CN111365437 A CN 111365437A
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- China
- Prior art keywords
- plate
- drive
- driven plate
- driving force
- driven
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
- F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
- F16D43/2022—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement
- F16D43/2024—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/25—Automatic clutches actuated entirely mechanically controlled by thermo-responsive elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/30—Systems of a plurality of automatic clutches
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention provides a vehicle drive device, which can constitute a driven plate separating mechanism by a simple structure and can work in a space-saving and energy-saving way. A vehicle drive device is provided with a differential device (5), wherein the drive force of a drive source (3) is transmitted to the differential device (5) through a speed reduction mechanism (4), a drive force cutoff mechanism (9) for releasing the connection between the speed reduction mechanism (4) and the differential device (5) is provided between the speed reduction mechanism (4) and the differential device (5), the drive force cutoff mechanism (9) is provided with a drive plate (45b) of the speed reduction mechanism (4) and a driven plate (8) on the differential device (5) side, which can be engaged with and disengaged from each other, a cam (45c) is provided on the surfaces of the drive plate (45b) and the driven plate (8) facing each other, and a contact body (61) is provided, wherein the contact body (61) holds the drive force cutoff mechanism (9) in a connected state and releases the connected state by melting.
Description
Technical Field
The present invention relates to a vehicle drive device.
Background
In a vehicle drive device using both an engine and an electric motor as a drive source, there is known a vehicle drive device including an electric motor, a reduction mechanism for the electric motor, and a differential device, and configured to be disengaged and engaged between the electric motor and wheels by a clutch. Further, the following vehicle drive device is known: the electric motor is prevented from rotating due to the driving rotation of the wheel by cutting off the driving force path between the electric motor and the wheel, and the regulator circuit and the like are protected from the electromotive force of the electric motor (for example, patent document 1).
Documents of the prior art
Patent document 1: japanese patent laid-open publication No. 2003-104073
Disclosure of Invention
Problems to be solved by the invention
However, as described in patent document 1, a multi-plate clutch is used as the clutch. Therefore, the number of parts of the clutch is large, and a complicated structure is required. In addition, in the case of using the wet clutch, a brake device for preventing the motoring rotation of the electric motor by utilizing the viscous resistance of the lubricating oil is provided.
Thus, the space occupied by the device itself increases, and a driving device and energy for releasing the clutch are required.
In view of the above-described conventional drawbacks, an object of the present invention is to provide a vehicle drive device that can constitute a drive force cutoff mechanism with a simple structure and can achieve space saving and energy saving.
Means for solving the problems
In order to achieve the above object, a vehicle drive device according to the present invention includes a drive source and a differential device, a drive force of the drive source being transmitted to the differential device via a reduction mechanism, the vehicle drive device including a drive force cutoff mechanism configured to release a connection between the reduction mechanism and the differential device by moving in a rotation axis direction between the reduction mechanism and the differential device, the drive force cutoff mechanism including a drive plate connected to the reduction mechanism and a driven plate connected to the differential device, the drive plate and the driven plate being capable of engaging with and disengaging from each other, cams engaging with each other being provided on surfaces of the drive plate and the driven plate facing each other, the cams being urged in a release direction by rotation of the drive plate, and an abutting body being provided on the vehicle drive device, the abutting body holds the driving plate and the driven plate in a connected state, and releases the connected state of the driving plate and the driven plate by melting.
Thus, the driven plate can be configured to have a simple structure, and the driven plate can be released by the driving force of the vehicle driving device.
In the above configuration, the vehicle drive device may include: a piston that extends in a rotation axis direction of the driven plate and moves integrally with the driven plate; a guide hole, provided in the differential device, into which the piston is inserted; and a partition wall provided inside the guide hole, forming an inflow chamber into which the melted abutting body flows, the abutting body being provided between the piston and the partition wall.
Accordingly, the driving force cutoff mechanism can be configured with a simple structure and with a small space. The melted abutting body can be held in the inflow chamber.
In the above-described configuration, a plurality of guide holes may be provided, the abutting body may be provided in a part of the guide holes, and an elastic body that urges the drive plate and the driven plate in a direction to connect the drive plate and the driven plate may be provided in the remaining guide holes.
Further, in the structure, the abutting body may be formed of a low melting point alloy.
Accordingly, the temperature at which the driving force cutoff mechanism operates can be set with a space-saving and simple structure by using the low-melting-point alloy.
Effects of the invention
According to the vehicle drive device of the present embodiment, the hydraulic mechanism or the electric mechanism for cutting off the drive force is not required between the speed reduction mechanism and the differential device, and the drive force cutting mechanism can be configured simply and in a space-saving manner. Further, the driving force transmitted to the vehicle drive device can be used, and a space-saving driving force cutoff mechanism can be configured.
Drawings
Fig. 1 is a sectional view showing the structure of a speed reduction mechanism and a differential device of a vehicle drive device.
Fig. 2 is a side view of the driving force cutoff mechanism.
Fig. 3 is a diagram illustrating a cutting operation of the driving force cutting mechanism.
Description of the reference symbols
1: a vehicle drive device;
3: an electric motor (drive source);
4: a speed reduction mechanism;
5: a differential device;
8: a driven plate;
8 b: a driven cam;
8 c: a piston;
8 d: an inclined surface;
8 e: an inclined surface;
9: a driving force cutoff mechanism;
45: a ring gear;
45 b: a drive plate;
45 c: a drive cam;
45 d: an inclined surface;
45 e: an inclined surface;
51 c: a guide hole;
60: a bushing;
60 a: an inflow hole;
60 b: a partition wall;
60 c: an inflow chamber;
61: a contact body (contact body).
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
A vehicle drive device 1 according to an embodiment of the present invention will be described with reference to fig. 1 to 3.
Fig. 1 is a sectional view showing the structure of a speed reduction mechanism and a differential device of a vehicle drive device, and fig. 2 is a side view of a driving force cutoff mechanism. Fig. 3 is a diagram showing a cutting operation of the driving force cutting mechanism.
The overall configuration of the vehicle drive device 1 will be described with reference to fig. 1.
In fig. 1, "up" indicates an upper direction, and "left" indicates a left direction. In fig. 1, a vehicle drive device 1 includes an electric motor 3 as a drive source, a reduction mechanism 4, and a differential device 5 in a case 2. An axle 6 and an axle 7 are connected to the differential device 5.
The electric motor 3 disposed in the housing 2 has an output shaft 31 and outputs electric power as driving force. The output shaft 31 of the electric motor 3 is a hollow shaft, and the axle 6 is inserted into a hollow portion of the output shaft 31. A sun gear 41 is provided at one end of the output shaft 31, and the sun gear 41 is rotationally driven integrally with the output shaft 31. The sun gear 41 transmits a driving force to the speed reduction mechanism 4.
The reduction mechanism 4 is constituted by a sun gear 41, a first planetary gear 42, a second planetary gear 43, a shaft 44, and a ring gear 45.
The first planetary gear 42 rotatably supported by the carrier 46 meshes with the sun gear 41, and the first planetary gear 42 is formed integrally with the second planetary gear 43 via the shaft 44. The first planetary gears 42 rotate integrally with the second planetary gears 43, and the number of teeth of the first planetary gears 42 is formed to be larger than that of the second planetary gears 43.
The second planetary gears 43 of the reduction mechanism 4 mesh with the ring gear 45. The ring gear 45 rotates on the same rotation axis as the sun gear 41 by the driving force transmitted from the second planetary gears 43. The ring gear 45 is connected to the differential device 5 via the driving force cutoff mechanism 9. The driving force cutoff mechanism 9 is constituted by a driving plate 45b that rotates integrally with the ring gear 45 and a driven plate 8 that rotates integrally with a differential case 51 of the differential device 5.
The carrier 46 is fixed to the case 2, and the reduction mechanism 4 is a star-shaped planetary reduction mechanism.
The differential device 5 is composed of a differential case 51, a pinion shaft 52, two pinions 53, a left side gear 54, and a right side gear 55. In the differential case 51, the pinion shaft 52 is fixed to be orthogonal to the axle 6 and the axle 7. The pinion shaft 52 is fitted with 2 pinions 53, and the pinions 53 mesh with a side gear 54 and a side gear 55, respectively.
The side gear 54 is fixed to one end of the axle 6 in the differential case 51 and rotates integrally with the axle 6. The side gear 55 is fixed to one end of the axle 7 in the differential case 51 and rotates integrally with the axle 7.
A driven plate 8 is attached to an outer peripheral surface of the differential case 51, and an output of the electric motor 3 is transmitted to the differential case 51 via the driving force cutoff mechanism 9.
The differential case 51 is disposed at a position overlapping the ring gear 45 of the reduction mechanism 4 in the rotation axis direction of the reduction mechanism 4. That is, as shown in fig. 1, a part of the differential case 51 is inserted inside the ring gear 45.
In this way, in the vehicle drive device 1, the drive force of the electric motor 3 is decelerated by the deceleration mechanism 4 and transmitted to the axle 6 and the axle 7 via the differential device 5 connected to the deceleration mechanism 4.
The ring gear 45 has internal teeth on the entire inner circumference of the end portion 45a on the differential case 51 side, and external teeth on the entire outer circumference of the drive plate 45b disposed inside the ring gear 45. The internal teeth of the end portion 45a engage with the external teeth of the drive plate 45b, and the ring gear 45 rotates integrally with the drive plate 45 b. The differential case 51 disposed inside the drive plate 45b is rotatable relative to the drive plate 45b about the axle 6 as a rotation axis.
A stopper 51a is formed on the outer periphery of the differential case 51 so as to extend a part of the differential case 51 outward in the radial direction. The surface of the drive plate 45b on the ring gear 45 side can be in contact with one side surface of the stopper 51a, whereby the movement of the drive plate 45b toward the ring gear 45 side is regulated.
The differential case 51 is disposed inside the drive plate 45b, and the stopper 51a is located inside the ring gear 45.
A guide block 51b is provided on the outer peripheral portion of the differential case 51. The guide shoes 51b are provided on the differential case 51 over the entire circumference thereof on the side closer to the axle 7 than the portion of the differential case 51 holding the pinion shaft 52. A guide hole 51c is opened in the rotation axis direction on the ring gear 45 side of the guide block 51 b. The guide hole 51c is open on the ring gear 45 side, and the guide hole 51c is closed on the axle 7 side. The plurality of guide holes 51c are provided at regular intervals in the circumferential direction of the differential case 51.
Further, a cylindrical driven plate 8 is attached to the outer periphery of the differential case 51 along the outer peripheral surface of the differential case 51. The driven plate 8 has inner teeth 8a with tooth surfaces parallel to the rotation axis direction on its inner peripheral surface, and meshes with spline teeth 51d provided on the outer peripheral surface of the differential case 51. Thereby, the driven plate 8 is rotated integrally with the differential case 51, and the driven plate 8 can move in the direction of the rotation axis of the differential case 51 (the direction of the axle 6 or the axle 7).
In the driving force cutoff mechanism 9, the driven plate 8 engages with the driving plate 45b, and the reduction mechanism 4 is connected to the differential device.
A plurality of driven cams 8b are formed at the end of the driven plate 8 on the drive plate 45b side. The driven cam 8b has a substantially trapezoidal shape with a shorter side on the drive plate 45b side, and the driven cam 8b protruding in the rotation axis direction of the driven plate 8 is provided over the entire circumference of the driven plate 8. The inclined surface 8d and the inclined surface 8e are provided in the rotational direction of the driven cam 8b, and the inclined surface 8d and the inclined surface 8e are provided so as to be inclined with respect to the rotational direction of the driven cam 8b, respectively.
A plurality of drive cams 45c are provided at the driven plate 8 side end of the drive plate 45b fixed to the ring gear 45. The drive cam 45c is substantially trapezoidal in shape with a short side on the driven plate 8 side, and the drive cam 45c protruding in the rotation axis direction of the ring gear 45 is provided over the entire circumference of the ring gear 45. The drive cam 45c is provided with an inclined surface 45d and an inclined surface 45e, and the inclined surface 45d and the inclined surface 45e are each provided so as to be inclined with respect to the rotational direction of the drive cam 45 c.
As shown in fig. 2, the driven cam 8b and the driving cam 45c are configured to mesh with each other, and the inclined surface 8d of the driven cam 8b abuts against the inclined surface 45d of the driving cam 45c, and the inclined surface 8e abuts against the inclined surface 45 e.
The inclined surfaces 45d and 45e transmit the force in the rotation direction and the rotation axis direction of the ring gear 45 to the engaged inclined surfaces 8d and 8e by the rotation of the ring gear 45. Since the inclined surfaces 8d and 8e have surfaces inclined with respect to the rotation direction, a part of the force in the rotation direction is transmitted to the driven plate 8 as the force in the rotation axis direction.
Similarly, the inclined surfaces 8d and 8e are configured to transmit the force in the rotation direction and the rotation axis direction of the driven plate 8 to the inclined surfaces 45d and 45e by the rotation of the driven plate 8.
A plurality of pistons 8c protruding in the extending direction of the axle 7 are provided at the end portion of the driven plate 8 on the axle 7 side, at regular intervals over the entire circumference of the driven plate 8. The pistons 8c are disposed at the same intervals as the guide holes 51c, and 1 piston 8c is inserted into 1 guide hole 51 c. The cross-sectional shape of the piston 8c orthogonal to the extending direction substantially coincides with the shape of the guide hole 51c, and the piston 8c is provided slidably in the guide hole 51 c. The piston 8c has a cylindrical shape, and the outer diameter of the piston 8c is set to be smaller than the inner diameter of the guide hole 51 c. The cross-sectional shape of the piston 8c may be a polygon such as a circle, an ellipse, a triangle, or a quadrangle, and the cross-sectional shape of the guide hole 51c matches the cross-sectional shape of the piston 8 c.
Thus, the driven plate 8 is configured to be movable in the rotation axis direction along the outer peripheral surface of the differential case 51 in a state where the piston 8c is inserted into the guide hole 51 c.
In the 1 guide hole 51c, 1 bushing 60 and 1 abutting body 61 are inserted. The hub 60 has a cylindrical shape along the inside of the guide hole 51c, and an inflow hole 60a is provided in a partition wall 60b at one end of the hub 60. The hub 60 is disposed in the guide hole 51c such that the side provided with the inflow hole 60a faces the abutting body 61. The partition wall 60b abuts against the contact body 61, and positions the contact body 61 in the guide hole 51 c.
In the guide hole 51c, the bush 60, the contact body 61, and the piston 8c are inserted from the closed side.
The axle 7 side of the hub 60 abuts against the closed portion of the guide hole 51c, and the guide hole 51c and the inner side of the hub 60 form an inflow chamber 60 c. The inflow chamber 60c communicates with the opening side of the guide hole 51c via the inflow hole 60 a.
The end portion of the guide hole 51c on the axle 7 side into which the piston 8c is inserted is abutted against the abutment body 61. The abutting body 61 is held between the piston 8c and the partition wall 60b of the bushing 60.
Further, the shape of the hub 60 is not particularly limited as long as the positioning of the abutting body 61 in the guide hole 51c and the formation of the inflow chamber 60c can be performed by the hub 60.
The abutting body 61 is formed in a cylindrical shape matching the shape of the guide hole 51 c. The abutting body 61 abuts against the piston 8c in a state of being inserted into the guide hole 51c, and the movement of the driven plate 8 toward the axle 7 side is restricted by the abutting body 61.
The contact body 61 is made of a low melting point alloy, and melts at a predetermined temperature or higher. The low melting point alloy is an alloy material that melts below the melting point of tin. As low melting point alloys, lead-tin alloys, lead-antimony alloys, tin-lead-antimony alloys, bismuth-lead-tin-cadmium alloys, bismuth-tin alloys, wood alloys, gallium indium tin alloys (Galinstan), and the like are known.
In addition, as for the low melting point alloy, an alloy is generally provided which is adjusted in the compounding ratio in accordance with the target temperature range and set to a predetermined temperature in accordance with the application. By using the low melting point alloy, the contact body 61 is less likely to be affected by the lubricating oil at a predetermined temperature or lower, and the durability of the contact body 61 can be improved. In the present embodiment, a low-melting point alloy is used for the contact body 61, but a material that melts at a predetermined temperature may be used for the contact body 61.
When the abutment body 61 is in a solid state, the drive plate 45b of the ring gear 45 and the driven plate 8 are engaged with each other via the drive cam 45c and the driven cam 8b, and the movement of the driven plate 8 toward the axle 7 is restricted by the abutment body 61. This maintains the connection between the ring gear 45 and the differential case 51, and enables transmission of the driving force between the ring gear 45 and the differential case 51.
When the abutting body 61 is melted and becomes in a liquid state, the melted abutting body 61 can flow into the inflow chamber 60c through the inflow hole 60 a. When the driven plate 8 receives a force from the driving plate 45b toward the axle 7, the molten abutting body 61 enters the inflow chamber 60c by the piston 8c, and the driven plate 8 can move toward the axle 7.
Next, the operation of the driven plate 8 will be described.
In the casing 2 of the vehicle drive device 1, a certain amount of lubricating oil is stored while supplying lubricating oil. The lubricating oil is flooded by the rotation of the electric motor 3, the reduction mechanism 4, and the differential device 5 in the case 2, and the inside of the case 2 is lubricated with the splashed lubricating oil. The lubricating oil in the casing 2 is at a substantially uniform temperature due to the lubricating oil being splashed or splashed.
When the temperature of the lubricating oil rises, the heat of the lubricating oil is also transmitted to the differential case 51 that is in contact with the lubricating oil in the housing 2. For example, when abnormal heat is generated in the case 2, the heat is transmitted to the differential case 51 via the lubricating oil. When the temperature of the differential case 51 becomes equal to or higher than a predetermined temperature, the contact body 61 in the guide block 51b is melted by heat.
When the contact body 61 is melted, the driven plate 8 can move toward the axle 7.
In a state where the driving force is transmitted from the ring gear 45 to the driven plate 8, the driving cam 45c rotating integrally with the ring gear 45 applies a force in the rotational direction and a force in the rotational axis direction to the driven cam 8b of the driven plate 8 via the inclined surface 45 d. The driven plate 8 is moved toward the axle 7 by the force in the rotation axis direction from the drive cam 45 c. Thereby, the piston 8c is pressed into the guide hole 51 c.
The piston 8c pressed into the guide hole 51c causes the molten abutting body 61 to flow from the inflow hole 60a into the inflow chamber 60 c. As the abutting body 61 flows into the inflow chamber 60c, the driven plate 8 pressed by the drive cam 45c moves toward the axle 7 while rotating. The melted abutting body 61 is held in the inflow chamber 60 c.
When the driven cams 8b of the driven plate 8 are separated from the driving cams 45c, the engagement between the driving plate 45b and the driven plate 8 is released, and the transmission of the driving force from the ring gear 45 to the differential case 51 is released.
Further, the abutting body 61 in the inflow chamber 60c can be recovered and reused.
The length of the piston 8c and the length of the bush 60 are set to such lengths: in a state where the engagement of the ring gear 45 and the driven plate 8 is released, the piston 8c does not contact the bush 60.
Even when the driving force is transmitted from the driven plate 8 to the ring gear 45, the inclined surface 8e exerts a force in the rotational direction and a reaction to the force toward the axle 6 on the inclined surface 45e, so that the driven plate 8 moves toward the axle 7 and the transmission of the driving force is released by the driving force cutoff mechanism 9.
When the temperature of the lubricating oil is lower than a predetermined temperature in the state where the driven plate 8 is released, the contact body 61 is solidified in the inflow chamber 60 c. The driven plate 8 is held on the axle 7 side in the differential case 51, and the state where the transmission of the driving force from the ring gear 45 to the differential case 51 is released is maintained.
With this configuration, the vehicle drive device 1 can be used to prevent reactivation in a situation where the cause of the increase in the temperature of the lubricating oil is not removed after the temperature of the lubricating oil has increased to a predetermined temperature or higher.
In this way, the transmission of the driving force can be canceled by the driving force cutoff mechanism 9 using the driving force transmitted to the driven plate 8 and the temperature of the lubricating oil. Therefore, the transmission of the driving force can be canceled using the temperature of the lubricating oil as an index without requiring any other power, and the highly reliable driving force cutoff mechanism 9 can be configured.
As described above, in the present embodiment, the vehicle drive device 1 includes: an electric motor 3 as a drive source; and a differential device 5 to which a driving force of the electric motor 3 is transmitted via the reduction mechanism 4, wherein a driving force cutoff mechanism 9 for releasing the connection between the reduction mechanism 4 and the differential device 5 by moving in a rotation axis direction is provided between the reduction mechanism 4 and the differential device 5, wherein the driving force cutoff mechanism 9 includes a driving plate 45b connected to the reduction mechanism 4 and a driven plate 8 connected to the differential device 5, wherein the driving plate 45b and the driven plate 8 are capable of engaging with and disengaging from each other, wherein a driving cam 45c and a driven cam 8b that engage with each other are provided on surfaces of the driving plate 45b and the driven plate 8 that face each other, wherein the driving cam 45c and the driven cam 8b are urged in a releasing direction by rotation of the driving plate 45b, wherein a contact body 61 that holds the driving plate 45b and the driven plate 8 in a connected state is provided in the vehicle driving device 1, and the connection state of the driving plate 45b and the driven plate 8 is released by the melting.
Thus, the driven plate 8 can be moved by the driving force transmitted to the vehicle drive device 1, and the transmission of the driving force can be canceled by the thermal energy in the vehicle drive device 1. Further, even in a situation where the power supply to the vehicle drive device 1 is disconnected, the vehicle drive device 1 with high reliability of canceling the transmission of the driving force can be provided.
Further, the mechanism for canceling the transmission of the driving force can be made compact with a simple configuration, and since the mechanism operates by thermal energy, the driven plate 8 can be separated even when the sliding portion such as the bearing is burned or broken, in addition to the electric heat generation.
Further, the following highly safe vehicle drive device 1 can be provided: since the transmission of the driving force is released by melting of the abutting body 61, the driven plate 8 maintains the released state, and the transmission of the driving force by the driven plate 8 is not easily restored.
Further, the apparatus comprises: a piston 8c extending in the rotation axis direction of the driven plate 8 and moving integrally with the driven plate 8; a guide hole 51c, which is provided in the differential device 5 and into which the piston 8c is inserted; and a partition wall 60b provided inside the guide hole 51c, forming an inflow chamber 60c into which the molten abutting body 61 flows, and providing the abutting body 61 between the piston 8c and the partition wall 60 b.
This enables the driving force cutoff mechanism 9 to be configured with a simple structure, and the driving force cutoff mechanism 9 to be downsized. Further, by holding the abutting body 61 in the inflow chamber 60c, it is possible to reduce the influence on other components of the vehicle drive device 1, and to easily collect the melted abutting body 61.
Further, the abutting body 61 is formed of a low melting point alloy.
This makes it possible to configure a highly reliable release mechanism in which the driving force cutoff mechanism 9 operates at a predetermined lubricating oil temperature. Further, the driving force cutoff mechanism 9 can be configured with a simple structure. Further, the driving force cutoff mechanism 9 which is less susceptible to chemical influence of the lubricating oil and has high durability can be configured, and the contact body 61 can be reused.
Next, a modified example of the vehicle drive device 1 will be described.
In the vehicle drive device 1 described above, the driving force cutoff mechanism 9 may be provided with a torque limiting function by providing the abutting body 61 in a part of the guide holes 51c and providing the elastic body that biases the driving plate 45b in the direction of connecting to the driven plate 8 in the remaining guide holes 51 c.
The elastic body is capable of expanding and contracting in the rotation axis direction, and is held in the guide hole 51c in a state where the elastic body presses the piston 8c of the driven plate 8 toward the drive plate 45 b. Further, the movement of the driven plate 8 in the rotation axis direction is restricted by the remaining abutting body 61, and the connected state of the driving force cutoff mechanism 9 is maintained.
In this state, when the temperature of the lubricating oil becomes equal to or higher than a predetermined temperature and the abutting body 61 melts, the driven plate 8 can move in the rotation axis direction. Then, the driven plate 8 is moved in the release direction by the driving plate 45b, and the piston 8c presses the abutting body 61 into the inflow chamber 60 c.
However, after the transmission of the driving force is released by the driving force cutoff mechanism 9, the driven plate 8 is urged toward the driving plate 45b by the elastic body, and the driven plate 8 is engaged with the driving plate 45 b.
When the driving force of the driving plate 45b is equal to or less than a predetermined torque, the driving force is transmitted to the driven plate 8. When the driving force of the driving plate 45b is larger than the predetermined torque, the engagement between the driven plate 8 and the driving plate 45b is released. This enables the driving force cutoff mechanism 9 to be used as a mechanism for transmitting a driving force equal to or less than a predetermined torque.
In the case where the total elastic force of the elastic body is larger than the force in the rotation axis direction received by the driven cam 8b from the driving cam 45c, the driving force is transmitted from the driving cam 45c to the driven cam 8 b.
When the total elastic force of the elastic body is smaller than the force in the rotation axis direction received by the driven cam 8b from the driving cam 45c, the driven plate 8 moves toward the axle 7 side, and the transmission of the driving force is released in the driving force cutoff mechanism 9.
The magnitude of the driving force transmitted to the driven plate 8 can be adjusted by the number, elastic modulus, and natural length of the elastic bodies inserted into the guide holes 51 c. Further, as the elastic body, a spring or the like can be used.
The magnitude of the power transmitted to the driven plate 8 can also be adjusted by the shapes of the inclined surfaces 45d and 45e of the driving cam 45c and the shapes of the inclined surfaces 8d and 8e of the driven cam 8 b.
According to this configuration, the driving force cutoff mechanism 9 can be caused to function as the torque limiting clutch even after the lubricating oil has reached a predetermined temperature or higher and the contact body has melted.
In addition to the guide hole 51c, the elastic body may be disposed at a position where the driven plate 8 can be biased toward the drive plate 45 b.
As described above, the plurality of guide holes 51c are provided, the abutting body 61 is provided in a part of the guide holes 51c, and the elastic body that biases the drive plate 45b in the direction of connecting to the driven plate 8 is provided in the remaining guide holes 51 c.
This makes it possible to provide the driving force cutoff mechanism 9 with a function of releasing the driving force at a predetermined temperature or higher, and to provide a mechanism that becomes a torque limiting clutch after the abutting body 61 is melted and transmission of the driving force is released by the driving force cutoff mechanism 9.
Thus, the vehicle drive device 1 that limits the drive force at the time of failure can be realized with a simple configuration. Further, in the case where a moving measure is required even in a failure state, the vehicle can be driven.
In the above embodiment, the abutting body 61 can also be made to function as a torque limiting clutch by being changed to a spring.
The above embodiment is merely one embodiment of the present invention, and any modification and application can be made without departing from the scope of the present invention.
Claims (4)
1. A vehicle drive device including a drive source and a differential device to which a drive force of the drive source is transmitted via a speed reduction mechanism, the vehicle drive device being characterized in that,
a driving force cutoff mechanism configured to release a connection between the speed reduction mechanism and the differential device by moving in a rotation axis direction is provided between the speed reduction mechanism and the differential device,
the driving force cutoff mechanism is provided with a driving plate connected to the speed reduction mechanism and a driven plate connected to the differential device, the driving plate and the driven plate being engageable with and disengageable from each other,
cams that engage with each other are provided on surfaces of the drive plate and the driven plate that face each other, the cams being biased in a releasing direction by rotation of the drive plate,
the vehicle drive device is provided with a contact body that maintains the drive plate and the driven plate in a connected state and releases the connected state of the drive plate and the driven plate by melting.
2. The vehicular drive apparatus according to claim 1,
the vehicle drive device includes:
a piston that extends in a rotation axis direction of the driven plate and moves integrally with the driven plate;
a guide hole, provided in the differential device, into which the piston is inserted; and
a partition wall provided inside the guide hole and forming an inflow chamber into which the molten abutting body flows,
the abutment is disposed between the piston and the partition wall.
3. The vehicular drive apparatus according to claim 2,
the guide hole is provided with a plurality of guide holes,
the abutting body is provided in a part of the guide holes, and an elastic body that urges the drive plate and the driven plate in a direction of connecting the drive plate and the driven plate is provided in the remaining guide holes.
4. The vehicular drive apparatus according to any one of claims 1 to 3,
the abutment is formed from a low melting point alloy.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018242763A JP2020106048A (en) | 2018-12-26 | 2018-12-26 | Vehicle drive unit |
| JP2018-242763 | 2018-12-26 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111365437A true CN111365437A (en) | 2020-07-03 |
Family
ID=71210359
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911041645.9A Withdrawn CN111365437A (en) | 2018-12-26 | 2019-10-30 | Vehicle drive device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2020106048A (en) |
| CN (1) | CN111365437A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115349791A (en) * | 2022-07-29 | 2022-11-18 | 宁波方太厨具有限公司 | A walking module and cleaner for cleaner |
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| DE3223926A1 (en) * | 1982-06-26 | 1983-12-29 | Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt | Rotor driven by a belt or the like |
| JPS634458U (en) * | 1986-06-26 | 1988-01-12 | ||
| JP2833016B2 (en) * | 1989-06-17 | 1998-12-09 | 井関農機株式会社 | Power transmission system for powered vehicles |
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| JP2009068342A (en) * | 2007-09-10 | 2009-04-02 | Toyota Industries Corp | Compressor with pulley |
| DE102010024599A1 (en) * | 2010-06-22 | 2011-12-22 | Schaeffler Technologies Gmbh & Co. Kg | Power shift transmission for vehicle, has cylindrical gear teeth arrangement for transmitting driving force for vehicle by entrance of power shift transmission at outlet |
| US9574618B2 (en) * | 2014-11-20 | 2017-02-21 | Hamilton Sundstrand Corporation | Thermal disconnect assembly with flight control permanent magnet generator for integrated drive generator |
| US10183577B2 (en) * | 2016-02-15 | 2019-01-22 | Borgwarner Inc. | Transfer case with four wheel lock |
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| GB1474495A (en) * | 1974-04-15 | 1977-05-25 | Mc Donnell Douglas Corp | Torque coupling with thermal disconnecting means |
| JP2009078598A (en) * | 2007-09-25 | 2009-04-16 | Ntn Corp | Driving force transmission device of hybrid vehicle |
| CN104553767A (en) * | 2013-09-27 | 2015-04-29 | 汽车交通工程有限公司 | A device for driving a vehicle |
| CN107444111A (en) * | 2016-04-14 | 2017-12-08 | 株式会社捷太格特 | Drive force transfering device and four-wheel drive vehicle |
| CN206277947U (en) * | 2016-09-28 | 2017-06-27 | 精进电动科技股份有限公司 | A kind of vehicle electrical drive assembly |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115349791A (en) * | 2022-07-29 | 2022-11-18 | 宁波方太厨具有限公司 | A walking module and cleaner for cleaner |
| CN115349791B (en) * | 2022-07-29 | 2024-04-16 | 宁波方太厨具有限公司 | Walking module for cleaning machine and cleaning machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2020106048A (en) | 2020-07-09 |
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