JP2013148117A - Vehicle driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicle driving device that can suppress power loss even if a gear ratio is increased in reverse travel.SOLUTION: A vehicle driving device includes: a motor 2 that outputs rotation power; a speed reduction mechanism 3 that decelerates the rotation power from the motor 2 and outputs it; and a differential mechanism 4 that outputs the rotation power from the speed reduction mechanism 3 to right and left wheels 7, 8 so that they can be differentiated. The speed reduction mechanism 3 has a first planetary gear mechanism 21 that reduces the rotation power from the motor 2 in a first rotation direction and outputs it, a first interrupting/coupling mechanism 23 that transmits the rotation power from the first planetary gear mechanism to the differential mechanism 4 to be interruptible and couplable, a second planetary gear mechanism 22 that reduces the rotation power from the first planetary gear mechanism 21 in a second rotation direction opposite to the first rotation direction and outputs it, and a second interrupting/coupling mechanism 24 that transmits the rotation power from the second planetary gear mechanism 22 to the differential mechanism 4 to be interruptible and couplable.

Description

  The present invention relates to a vehicle drive device that drives wheels via a reduction mechanism and a differential mechanism by a driving force of a motor.

  Some vehicles using a motor as a power source include a vehicle drive device having a speed reduction mechanism and a differential mechanism in a power transmission path between the motor and wheels. There is a reduction mechanism that employs two sets of planetary gear mechanisms (forward planetary gear mechanism, reverse planetary gear mechanism) (see, for example, Patent Document 1). By adopting a planetary gear mechanism, it is said that it is possible to reduce the size and weight while obtaining a high reduction ratio, and to effectively reduce the drive system loss.

JP 2011-102039 A

  The following analysis is given by the inventor.

  However, in the speed reduction mechanism described in Patent Document 1, the gear becomes large when the reverse gear ratio is large, and the agitation resistance of the lubricating oil and friction increase at the time of frequent use, leading to an increase in power loss. . Further, in the speed reduction mechanism described in Patent Document 1, the rotor of the motor and the differential mechanism are always connected. Therefore, when power is not required, lubricating oil stirring resistance and friction resistance are applied to the gear of the speed reduction mechanism. Since this state is always applied, the power loss increases.

  The main subject of this invention is providing the vehicle drive device which can suppress a power loss even if the gear ratio at the time of reverse drive is enlarged.

  In one aspect of the present invention, in a vehicle drive device, a motor that outputs rotational power, a speed reduction mechanism that decelerates and outputs rotational power from the motor, and the rotational power from the speed reduction mechanism are directed to left and right wheels. And a differential mechanism that outputs differentially, wherein the speed reduction mechanism decelerates and outputs rotational power from the motor in a first rotational direction, and the first planetary gear mechanism. A first connection / disconnection mechanism that transmits the rotational power from the first differential gear mechanism to the differential mechanism in a connectable manner, and the rotational power from the first planetary gear mechanism is shifted in a second rotation direction opposite to the first rotation direction. And a second planetary gear mechanism that outputs the second planetary gear mechanism and a second connection / disconnection mechanism that transmits the rotational power from the second planetary gear mechanism to the differential mechanism in a connectable manner.

  According to the present invention, since the power transmission paths on the forward side and the reverse side are different in the speed reduction mechanism, the speed reduction mechanism and the differential mechanism can be separated from the motor by providing a connection / disconnection mechanism in each path, When it is not necessary, it can be used as a normal differential mechanism, so there is no friction loss in the speed reduction mechanism, and power loss can be suppressed even if the gear ratio during reverse is increased.

It is the block diagram which showed typically the structure of the vehicle drive device which concerns on Example 1 of this invention. FIG. 4A is a skeleton diagram schematically showing the configuration of the drive device in the vehicle drive device according to the first embodiment of the present invention, and FIG. 5B is a velocity diagram of a speed reduction mechanism in the drive device. FIG. 5A is a skeleton diagram schematically showing the configuration of a drive device in a vehicle drive device according to a second embodiment of the present invention, and FIG. 5B is a velocity diagram of a speed reduction mechanism in the drive device. It is the block diagram which showed typically the structure of the vehicle drive device which concerns on Example 3 of this invention. FIG. 5A is a skeleton diagram schematically showing a configuration of a drive device in a vehicle drive device according to a third embodiment of the present invention, and FIG. 5B is a velocity diagram of a speed reduction mechanism in the drive device. (A) Skeleton diagram showing power transmission path during forward movement of drive device in vehicle drive apparatus according to Embodiment 3 of the present invention, (B) Skeleton diagram showing power transmission path during backward travel.

[Outline of Embodiment]
In the vehicle drive device according to the embodiment of the present invention, a motor (2 in FIG. 2) that outputs rotational power, a speed reduction mechanism (3 in FIG. 2) that speeds down and outputs the rotational power from the motor, and the deceleration A differential mechanism (4 in FIG. 2) that differentially outputs rotational power from the mechanism toward left and right wheels (7 and 8 in FIG. 2), and the speed reduction mechanism is rotated from the motor. A first planetary gear mechanism (21 in FIG. 2) that decelerates and outputs power in the first rotation direction, and a first disconnection that transmits the rotational power from the first planetary gear mechanism to the differential mechanism in a connectable manner. And a second planetary gear mechanism (22 in FIG. 2) that outputs the rotational power from the first planetary gear mechanism in a second rotational direction opposite to the first rotational direction. ) And a second connecting / disconnecting device that transmits the rotational power from the second planetary gear mechanism to the differential mechanism so as to be connected / disconnected. It comprises a (24 in FIG. 2), a.

  In the vehicle drive device according to the present invention, the first planetary gear mechanism includes a first sun gear that receives rotational power from the motor, and a first sun gear that meshes with the first sun gear so as to be able to revolve outside the first sun gear. A pinion gear and the first pinion gear are rotatably supported, and rotational power when the first pinion gear revolves with respect to the first sun gear is directed toward the differential device via the second connection / disconnection mechanism. A first ring gear that is fixed to be non-rotatable and meshes with the first pinion gear on the inside; and the second planetary gear mechanism receives rotational power from the first carrier. A second sun gear, a second pinion gear meshing with the second sun gear so as to be able to revolve outside the second sun gear, and a non-rotatably fixed second gear. A second carrier that rotatably supports the pinion gear; and a second ring gear that meshes with the second pinion gear on the inside and outputs rotational power to the differential device via the second connection / disconnection mechanism. It is preferable.

  In the vehicle drive device of the present invention, the first planetary gear mechanism includes a first sun gear to which rotational power from the motor is input, a first pinion gear that meshes with the first sun gear outside the first sun gear, A first carrier that is fixed to be non-rotatable and that rotatably supports the first pinion gear, and meshes with the first pinion gear on the inside, and rotational power is transmitted to the differential mechanism via the second connection / disconnection mechanism. A second ring gear that outputs rotational power to the differential mechanism via the second connecting / disconnecting mechanism, and the second sun gear. A second pinion gear meshing with the second sun gear on the outside, a second carrier fixed to be non-rotatable and rotatably supporting the second pinion gear, and a front on the inside Meshing with the second pinion gear, a second ring gear rotational power from the first ring gear is input via the first disengaging mechanism is preferably provided with a.

  The vehicle drive device according to the present invention preferably includes an electronic control unit that controls the first connection / disconnection mechanism and the second connection / disconnection mechanism.

  In the vehicle drive device of the present invention, the electronic control unit controls the first connecting / disconnecting mechanism to be in contact with the first connecting / disconnecting mechanism when moving forward and the second connecting / disconnecting mechanism to be disconnected. It is preferable that the mechanism is disconnected and the second connecting / disconnecting mechanism is controlled to be in contact.

  In the vehicle drive device of the present invention, each of the first connecting / disconnecting mechanism and the second connecting / disconnecting mechanism is any one of a friction clutch, a synchro gear, a dog clutch, an electromagnetic clutch, a meshing clutch, and an automatic clutch. It is preferable that

  Note that, in the present application, where reference numerals are attached to the drawings, these are only for the purpose of helping understanding, and are not intended to be limited to the illustrated embodiments. Hereinafter, embodiments will be described with reference to the drawings.

  A vehicle drive device according to a first embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a block diagram schematically showing the configuration of the vehicle drive device according to the first embodiment of the present invention. 2A and 2B are a skeleton diagram schematically showing the configuration of the drive device (A) in the vehicle drive device according to the first embodiment of the present invention, and FIG. 2B is a velocity diagram of the speed reduction mechanism in the drive device.

  Referring to FIG. 1, a vehicle drive device 1 is a device that drives a vehicle. The vehicle drive device 1 is mounted on an electric vehicle having a motor generator 2 as a power source. The vehicle drive device 1 includes, as main components, a drive device 16 (a motor generator 2, a speed reduction mechanism 3, a differential mechanism 4), axles 5 and 6, wheels 7 and 8, an inverter 10, and a battery 11. The motor generator control device 12, the battery control device 13, the speed reduction mechanism control device 14, and the main control device 15 are included.

  The drive device 16 is a device that drives the wheels 7 and 8 through the speed reduction mechanism 3, the differential mechanism 4, and the axles 5 and 6 by the rotational power of the motor generator 2 (see FIGS. 1 and 2A). The drive device 16 includes the motor generator 2, the speed reduction mechanism 3, and the differential mechanism 4.

  The motor generator 2 is a synchronous generator motor that is driven as an electric motor and also as a generator (see FIGS. 1 and 2A). Motor generator 2 exchanges power with battery 11 via inverter 10. The motor generator 2 is attached to a housing (not shown) of the speed reduction mechanism 3. In the motor generator 2, a rotor 2b serving as a rotor is disposed inside a stator 2a serving as a stator. The rotor 2 b is connected to the input shaft 20 of the speed reduction mechanism 3 and rotates integrally with the input shaft 20. An axle shaft 5 is inserted inside the rotor 2b. The motor generator 2 uses the rotational power transmitted from the wheels 7 and 8 via the axles 5 and 6, the differential mechanism 4, and the speed reduction mechanism 3 to regenerate and charge the battery 11, and to supply power from the battery 11. Can be used to output rotational power. The motor generator 2 is controlled by the motor generator control device 12 via the inverter 10.

  The speed reduction mechanism 3 is a gear mechanism that decelerates the rotational power from the motor generator 2 and outputs it to the differential mechanism 4 (see FIGS. 1 and 2A). The speed reduction mechanism 3 includes, as main components, an input shaft 20, a first planetary gear mechanism 21, a second planetary gear mechanism 22, a first connection / disconnection mechanism 23, a second connection / disconnection mechanism 24, and an output shaft. 25.

  The input shaft 20 is a shaft for inputting rotational power from the motor generator 2 to the speed reduction mechanism 3 (see FIG. 2A). The input shaft 20 is rotatably supported by a housing (not shown) of the speed reduction mechanism 3. The input shaft 20 is a hollow shaft, and the axle 5 is inserted inside. Input shaft 20 rotates integrally with rotor 2 b of motor generator 2. The input shaft 20 rotates integrally with the first sun gear S <b> 1 of the first planetary gear mechanism 21.

  The first planetary gear mechanism 21 is a forward speed reduction mechanism (see FIG. 2A). The first planetary gear mechanism 21 includes a first sun gear S1, a first pinion gear P1, a first ring gear R1, and a first carrier C1. The first sun gear S <b> 1 is an external gear that rotates integrally with the input shaft 20. The first pinion gear P1 is an external gear tooth that meshes with the first sun gear S1 so as to be able to revolve on the outer periphery of the first sun gear S1. The first ring gear R1 is an internal gear that is fixed to a housing (not shown) of the speed reduction mechanism 3 and meshes with the first pinion gear P1 on the inside. The first carrier C1 is a member that rotatably holds the first pinion gear P1 and rotates integrally with the second sun gear S2. The first carrier C <b> 1 directs rotational power when the first pinion gear P <b> 1 revolves (decelerates) on the outer periphery of the first sun gear S <b> 1 toward the second sun gear S <b> 2 and the first connecting / disconnecting mechanism 23 of the second planetary gear mechanism 22. Output. The power transmission path from the first carrier C1 to the second sun gear S2 and the first connecting / disconnecting mechanism 23 is hollow, and the axle 5 is inserted inside thereof.

  The second planetary gear mechanism 22 is a reverse speed reduction mechanism for obtaining a large reduction gear ratio during reverse travel (see FIG. 2A). The second planetary gear mechanism 22 has a second sun gear S2, a second pinion gear P2, a second ring gear R2, and a second carrier C2. The second sun gear S <b> 2 is an external gear that rotates integrally with the first carrier C <b> 1 of the first planetary gear mechanism 21. The second pinion gear P2 is an external gear tooth that meshes with the second sun gear S2 on the outer periphery of the second sun gear S2. The second ring gear R <b> 2 is an internal gear that meshes with the second pinion gear P <b> 2 on the inside and outputs the rotational power from the second pinion gear P <b> 2 toward the second connection / disconnection mechanism 24. The second carrier C2 is a member that is fixed to a housing (not shown) of the speed reduction mechanism 3 and that rotatably holds the second pinion gear P2.

  The first connecting / disconnecting mechanism 23 is a mechanism capable of transmitting the rotational power from the first carrier C1 of the first planetary gear mechanism 21 to the output shaft 25 so as to be connected / disconnected (see FIG. 2A). The first connecting / disconnecting mechanism 23 is used in a contact state when moving forward and in a disconnected state when moving backward. The connection / disconnection operation of the first connection / disconnection mechanism 23 is performed by an actuator (not shown) driven and controlled by the speed reduction mechanism control device 14.

  The second connection / disconnection mechanism 24 is a mechanism capable of transmitting the rotational power from the second ring gear R2 of the second planetary gear mechanism 22 to the output shaft 25 so as to be connected / disconnected (see FIG. 2A). The second connection / disconnection mechanism 24 is used in a disconnected state during forward travel and in a contact state during backward travel. The connection / disconnection operation of the second connection / disconnection mechanism 24 is performed by an actuator (not shown) driven and controlled by the speed reduction mechanism control device 14.

  The first connecting / disconnecting mechanism 23 and the second connecting / disconnecting mechanism 24 include, for example, a friction clutch (disk, cone, wet, dry, single plate, multi-plate), gear engagement / disengagement (synchro gear, dog clutch), electromagnetic clutch, and the like. A meshing clutch (claw clutch), an automatic clutch (centrifugal, fluid, powder) or the like can be used.

  The output shaft 25 is a shaft for outputting the rotational power from the first connecting / disconnecting mechanism 23 or the second connecting / disconnecting mechanism 24 toward the differential mechanism 4 (see FIG. 2A). The output shaft 25 is rotatably supported by a housing (not shown) of the speed reduction mechanism 3. The output shaft 25 is a hollow shaft, and the axle 5 is inserted inside.

  As the operation of the speed reduction mechanism 3, the first connecting / disconnecting mechanism 23 is brought into a contact state (a state in which the first carrier C1 of the first planetary gear mechanism 21 and the output shaft 25 rotate integrally), and the second connecting / disconnecting mechanism 24 is operated. The forward gear is achieved by setting the disconnected state (the state in which the second ring gear R2 of the second planetary gear mechanism 22 and the output shaft 25 rotate relative to each other). On the other hand, the first connecting / disconnecting mechanism 23 is disconnected (the first carrier C1 of the first planetary gear mechanism 21 and the output shaft 25 are relatively rotated), and the second connecting / disconnecting mechanism 24 is connected (second). By setting the second ring gear R2 of the planetary gear mechanism 22 and the output shaft 25 to rotate together, a reverse gear is achieved. Note that the rotation direction of the motor generator 2 is the same in the forward speed and the reverse speed.

Here, in the speed reduction mechanism 3, the rotational speed of the input shaft 20 is N _i , the number of teeth of the first sun gear S ₁ of the first planetary gear mechanism 21 is Z _S1 , and the number of teeth of the first ring gear R 1 of the first planetary gear mechanism 21. Assuming Z _R1 , the rotation speed N _fwd (corresponding to the forward rotation speed) of the first carrier C1 of the first planetary gear mechanism 21 is expressed as [Expression 1] (see FIG. 2B).

[Formula 1]

Further, in the speed reduction mechanism 3, the rotation speed of the first carrier C 1 of the first planetary gear mechanism 21 is N _fwd , the number of teeth of the second sun gear S 2 of the second planetary gear mechanism 22 is Z _S2 , and the second planetary gear mechanism 22 the number of teeth _{Z R2} of the second ring gear R2, the rotational speed _{N i} of the input shaft 20, _{Z S1} the number of teeth of the first sun gear S1 of the first planetary gear mechanism 21, the first ring gear R1 of the first planetary gear mechanism 21 Assuming that the number of teeth is Z _R1 , the rotational speed N _rev of the second ring gear R2 of the second planetary gear mechanism 22 is expressed as [Equation 2] (see FIG. 2B).

[Formula 2]

  The differential mechanism 4 is a device that differentially drives the wheels 7 and 8 via the axles 5 and 6 by the rotational power from the output shaft 25 of the speed reduction mechanism 3 (see FIGS. 1 and 2A). .

  The axle 5 is a shaft that transmits the rotational power from the differential mechanism 4 to the wheel 7 (see FIGS. 1 and 2A). The axle 5 is inserted through the hollow output shaft 25, the second sun gear S 2, the first carrier C 1, the input shaft 20, and the rotor 2 b of the motor generator 2. The axle 6 is a shaft that transmits the rotational power from the differential mechanism 4 to the wheel 8 (see FIGS. 1 and 2A).

  The wheel 7 is a wheel on the left side of the vehicle, and the rotational power from the differential mechanism 4 is transmitted through the axle 5 (see FIGS. 1 and 2A). The wheel 8 is a wheel on the right side of the vehicle, and the rotational power from the differential mechanism 4 is transmitted through the axle 6 (see FIGS. 1 and 2A).

  Inverter 10 controls the operation (drive operation, regenerative operation) of motor generator 2 in accordance with a control signal from motor generator control device 12 (see FIG. 1). The inverter 10 is electrically connected to the battery 11 via a buck-boost converter (not shown).

  The battery 11 is a secondary battery that can be discharged and stored (see FIG. 1). The battery 11 is electrically connected to the inverter 10.

  The motor generator control device 12 is a computer (electronic control device) that controls the operation of the motor generator 2 via the inverter 10 (see FIG. 1). The motor generator control device 12 is communicably connected to the inverter 10, various sensors (not shown; for example, a rotation sensor) and the main control device 15. The motor generator control device 12 performs control processing based on a predetermined program (including a database, a map, etc.) in accordance with a control signal from the main control device 15.

  The battery control device 13 is a computer (electronic control device) that manages the state (charge / discharge state, temperature state, etc.) of the battery 11 (see FIG. 1). The battery control device 13 is connected so as to be communicable with the main control device 15. The battery control device 13 performs control processing based on a predetermined program (including a database, a map, and the like) in accordance with a control signal from the main control device 15.

  The speed reduction mechanism control device 14 is a computer (electronic control device) that controls the operation of the speed reduction mechanism 3 (see FIG. 1). The deceleration mechanism control device 14 is communicably connected to various actuators (including the connection / disconnection mechanisms 23 and 24 in FIG. 2), various sensors (not shown; for example, a rotation sensor), and the main control device 15. . The speed reduction mechanism control device 14 performs control processing based on a predetermined program (including a database, a shift map, etc.) in accordance with a control signal from the main control device 15.

  The main control device 15 is a computer (electronic control device) that controls operations of the motor generator control device 12, the battery control device 13, and the deceleration mechanism control device 14 (see FIG. 1). The main control device 15 is communicably connected to the motor generator control device 12, the battery control device 13, and the deceleration mechanism control device 14. The main control device 15 monitors a predetermined situation of the vehicle (remaining battery level, battery temperature, inverter state, motor generator state, engine state, vehicle inclination, etc.), and in accordance with the predetermined situation of the vehicle, Based on the program (including database, map, etc.), a control signal is output to the motor generator control device 12, the battery control device 13, and the speed reduction mechanism control device. The main control device 15 controls driving and regeneration of the motor generator 2 via the motor generator control device 12, manages the battery 11 via the battery control device 13, and disconnects the disconnection of FIG. 2 via the deceleration mechanism control device 14. The connection / disconnection operation of the contact mechanisms 23 and 24 is controlled.

  According to the first embodiment, by combining the first planetary gear mechanism 21 for forward movement with the second planetary gear mechanism 22 for backward movement, the reverse speed reduction ratio can be increased. Further, since only the forward first planetary gear mechanism 21 is used during forward movement, the friction loss of the backward second planetary gear mechanism 22 is eliminated, and power loss can be suppressed.

  Also, according to the first embodiment, the combination of the planetary gear mechanisms 21 and 22 can reverse the rotation direction of the output shaft 25 at the time of reverse movement, so that the rotation direction of the motor generator 2 can be made the same regardless of forward / backward movement. .

  Further, according to the first embodiment, since the power transmission path of the speed reduction mechanism 3 is different between forward travel and reverse travel, by providing the connecting / disconnecting mechanisms 23 and 24 in the respective paths, the motor generator 2 and the speed reduction mechanism 3 When the differential mechanism 4 can be separated from the differential mechanism 4 and power is not required, the differential mechanism 4 can be used as a normal differential gear, so that friction loss is eliminated and power loss can be suppressed.

  A vehicle drive apparatus according to Embodiment 2 of the present invention will be described with reference to the drawings. 3A and 3B are a skeleton diagram schematically showing the configuration of the drive device (A) in the vehicle drive device according to the second embodiment of the present invention, and FIG. 3B is a velocity diagram of the speed reduction mechanism in the drive device.

  The second embodiment is a modification of the first embodiment. In the speed reduction mechanism 3, the connection / disconnection mechanisms 28 and 29 are provided in the power transmission path between the first planetary gear mechanism 21 and the second planetary gear mechanism 22. It is.

  The reduction mechanism 3 is a gear mechanism that decelerates the rotational power from the motor generator 2 and outputs it to the differential mechanism 4 (see FIG. 3A). The speed reduction mechanism 3 includes, as main components, an input shaft 20, a first planetary gear mechanism 21, a first connection / disconnection mechanism 28, a second connection / disconnection mechanism 29, a second planetary gear mechanism 22, and an output shaft. 25.

  The input shaft 20 is a shaft for inputting rotational power from the motor generator 2 to the speed reduction mechanism 3 (see FIG. 3A). The input shaft 20 is rotatably supported by a housing (not shown) of the speed reduction mechanism 3. The input shaft 20 is a hollow shaft, and the axle 5 is inserted inside. Input shaft 20 rotates integrally with rotor 2 b of motor generator 2. The input shaft 20 rotates integrally with the first sun gear S <b> 1 of the first planetary gear mechanism 21.

  The first planetary gear mechanism 21 is a reverse speed reduction mechanism (see FIG. 3A). The first planetary gear mechanism 21 includes a first sun gear S1, a first pinion gear P1, a first ring gear R1, and a first carrier C1. The first sun gear S <b> 1 is an external gear that rotates integrally with the input shaft 20. The first pinion gear P1 is an external gear tooth that meshes with the first sun gear S1 so as to be able to revolve relative to the first sun gear S1 on the outer periphery of the first sun gear S1. The first ring gear R1 is an internal gear that meshes with the first pinion gear P1 on the inside. The first ring gear R1 can be output toward the second ring gear R2 of the second planetary gear mechanism 22 via the first connecting / disconnecting mechanism 28. The first ring gear R <b> 1 can output toward the output shaft 25 via the second connection / disconnection mechanism 29. The first carrier C1 is a member that rotatably holds the first pinion gear P1. The first carrier C1 is fixed to a housing (not shown) of the speed reduction mechanism 3. The shaft of the second sun gear S2 is hollow, and the axle 5 is inserted inside the shaft.

  The second planetary gear mechanism 22 is a forward speed increasing mechanism (see FIG. 3A). The second planetary gear mechanism 22 has a second sun gear S2, a second pinion gear P2, a second ring gear R2, and a second carrier C2. The second sun gear S2 rotates integrally with the output shaft 25. The second pinion gear P2 is an external gear tooth that meshes with the second sun gear S2 so as to be able to revolve relative to the second sun gear S2 on the outer periphery of the second sun gear S2. The second ring gear R2 is an internal gear that meshes with the first pinion gear P1 on the inside. The second ring gear R2 can be connected to the first ring gear R1 of the first planetary gear mechanism 21 via the first connecting / disconnecting mechanism 28. The second carrier C2 is a member that rotatably holds the second pinion gear P2, and is fixed to a housing (not shown) of the speed reduction mechanism 3.

  The first connecting / disconnecting mechanism 28 is a mechanism capable of transmitting rotational power from the first ring gear R1 of the first planetary gear mechanism 21 to the second ring gear R2 of the second planetary gear mechanism 22 so as to be connectable / disconnectable ( (See FIG. 3A). The first connecting / disconnecting mechanism 28 is used in a contact state when moving forward and in a disconnected state when moving backward. The connection / disconnection operation of the first connection / disconnection mechanism 28 is performed by an actuator (not shown) driven and controlled by a speed reduction mechanism control device (corresponding to 14 in FIG. 1).

  The second connecting / disconnecting mechanism 29 is a mechanism capable of transmitting the rotational power from the first ring gear R1 of the first planetary gear mechanism 21 to the output shaft 25 so as to be connectable / disconnectable (see FIG. 3A). The second connection / disconnection mechanism 29 is used in a disconnected state during forward travel and in a contact state during backward travel. The connection / disconnection operation of the second connection / disconnection mechanism 29 is performed by an actuator (not shown) driven and controlled by a speed reduction mechanism control device (corresponding to 14 in FIG. 1).

  The first connecting / disconnecting mechanism 28 and the second connecting / disconnecting mechanism 29 include, for example, a friction clutch (disk, cone, wet, dry, single plate, multi-plate), gear engagement / disengagement (synchro gear, dog clutch), electromagnetic clutch, and the like. A meshing clutch (claw clutch), an automatic clutch (centrifugal, fluid, powder) or the like can be used.

  The output shaft 25 is a shaft for outputting the rotational power from the second connecting / disconnecting mechanism 29 or the second sun gear S2 toward the differential mechanism 4 (see FIG. 3A). The output shaft 25 is rotatably supported by a housing (not shown) of the speed reduction mechanism 3. The output shaft 25 is a hollow shaft, and the axle 5 is inserted inside.

  As the operation of the speed reduction mechanism 3, the first connection / disconnection mechanism 28 is brought into a contact state (a state in which the first ring gear R1 of the first planetary gear mechanism 21 and the second ring gear R2 of the second planetary gear mechanism 22 rotate integrally), and The second connecting / disconnecting mechanism 29 is in a disconnected state (a state in which the second ring gear R2 of the second planetary gear mechanism 22 and the output shaft 25 rotate relative to each other), thereby moving forward. On the other hand, the first connection / disconnection mechanism 28 is disconnected (the first ring gear R1 of the first planetary gear mechanism 21 and the second ring gear R2 of the second planetary gear mechanism 22 are relatively rotated), and the second connection / disconnection is performed. When the mechanism 29 is in a contact state (a state in which the second ring gear R2 of the first planetary gear mechanism 22 and the output shaft 25 rotate together), the reverse gear is achieved. Note that the rotation direction of the motor generator 2 is the same in the forward speed and the reverse speed.

Here, in the speed reduction mechanism 3, the rotational speed of the input shaft 20 is N _i , the number of teeth of the first sun gear S ₁ of the first planetary gear mechanism 21 is Z _S1 , and the number of teeth of the first ring gear R 1 of the first planetary gear mechanism 21. Assuming Z _R1 , the rotational speed N _rev (corresponding to the reverse rotational speed) of the first ring gear R1 of the first planetary gear mechanism 21 is expressed as [Equation 3] (see FIG. 3B).

[Formula 3]

In the reduction mechanism 3, the rotation speed of the first ring gear R 1 of the first planetary gear mechanism 21 is N _rev , the number of teeth of the second sun gear S 2 of the second planetary gear mechanism 22 is Z _S2 , and the second planetary gear mechanism 22 the number of teeth _{Z R2} of the second ring gear R2, the rotational speed _{N i} of the input shaft 20, _{Z S1} the number of teeth of the first sun gear S1 of the first planetary gear mechanism 21, the first ring gear R1 of the first planetary gear mechanism 21 Assuming that the number of teeth is Z _R1 , the rotational speed N _fwd of the second sun gear S2 of the second planetary gear mechanism 22 is expressed as [Equation 4] (see FIG. 3B).

[Formula 4]

  Other configurations in the second embodiment are the same as those in the first embodiment.

  According to the second embodiment, the same effect as the first embodiment is obtained.

  It should be noted that the embodiments and examples may be changed and adjusted within the scope of the entire disclosure (including claims and drawings) of the present invention and based on the basic technical concept. Various combinations or selections of various disclosed elements (including each element of each claim, each element of each embodiment or example, each element of each drawing, etc.) are included within the scope of the claims of the present invention. Is possible. That is, the present invention naturally includes various variations and modifications that could be made by those skilled in the art according to the entire disclosure including the claims and the drawings, and the technical idea.

DESCRIPTION OF SYMBOLS 1 Vehicle drive device 2 Motor generator (motor)
2a Stator 2b Rotor 3 Deceleration mechanism 4 Differential mechanism 5, 6 Axle 7, 8 Wheel 10 Inverter 11 Battery 12 Motor generator control device 13 Battery control device 14 Deceleration mechanism control device (electronic control device)
15 main control device 16 drive device 20 input shaft 21 first planetary gear mechanism S1 first sun gear P1 first pinion gear C1 first carrier R1 first ring gear 22 second planetary gear mechanism S2 second sun gear P2 second pinion gear C2 second carrier R2 Second ring gear 23 First connection / disconnection mechanism 24 Second connection / disconnection mechanism 25 Output shaft 26 First one-way clutch 27 Second one-way clutch 28 First connection / disconnection mechanism 29 Second connection / disconnection mechanism

Claims (6)

A motor that outputs rotational power;
A speed reduction mechanism that decelerates and outputs rotational power from the motor;
A differential mechanism for differentially outputting rotational power from the speed reduction mechanism toward the left and right wheels;
With
The deceleration mechanism is
A first planetary gear mechanism that decelerates and outputs rotational power from the motor in a first rotational direction;
A first connecting / disconnecting mechanism for transmitting the rotational power from the first planetary gear mechanism to the differential mechanism in a connectable manner;
A second planetary gear mechanism that shifts and outputs rotational power from the first planetary gear mechanism in a second rotational direction opposite to the first rotational direction;
A second connecting / disconnecting mechanism for transmitting rotational power from the second planetary gear mechanism to the differential mechanism in a connectable manner;
A vehicle drive device comprising: The first planetary gear mechanism is
A first sun gear to which rotational power from the motor is input;
A first pinion gear meshing with the first sun gear so as to be able to revolve outside the first sun gear;
The first pinion gear is rotatably supported, and rotational power when the first pinion gear revolves with respect to the first sun gear is output to the differential device via the second connection / disconnection mechanism. One carrier,
A first ring gear fixed in a non-rotatable manner and meshing with the first pinion gear on the inside;
With
The second planetary gear mechanism is
A second sun gear to which rotational power from the first carrier is input;
A second pinion gear meshing with the second sun gear so as to be able to revolve outside the second sun gear;
A second carrier fixed in a non-rotatable manner and rotatably supporting the second pinion gear;
A second ring gear that meshes with the second pinion gear on the inside and outputs rotational power to the differential device via the second connection / disconnection mechanism;
The vehicle drive device according to claim 1, further comprising: The first planetary gear mechanism is
A first sun gear to which rotational power from the motor is input;
A first pinion gear meshing with the first sun gear outside the first sun gear;
A first carrier fixed in a non-rotatable manner and rotatably supporting the first pinion gear;
A first ring gear that meshes with the first pinion gear on the inside and outputs rotational power toward the differential mechanism via the second connection / disconnection mechanism;
With
The second planetary gear mechanism is
A second sun gear that outputs rotational power to the differential mechanism via the second connecting / disconnecting mechanism;
A second pinion gear meshing with the second sun gear outside the second sun gear;
A second carrier fixed in a non-rotatable manner and rotatably supporting the second pinion gear;
A second ring gear that meshes with the second pinion gear on the inside and receives rotational power from the first ring gear via the first connection / disconnection mechanism;
The vehicle drive device according to claim 1, further comprising:   4. The vehicle drive device according to claim 1, further comprising an electronic control unit that controls the first connecting / disconnecting mechanism and the second connecting / disconnecting mechanism. 5.   The electronic control device controls the first connecting / disconnecting mechanism to contact and the second connecting / disconnecting mechanism to disconnect when traveling forward, disconnects the first connecting / disconnecting mechanism during backward travel, and the second 5. The vehicle drive device according to claim 4, wherein the connection / disconnection mechanism is controlled to be in contact.   The first connecting / disconnecting mechanism and the second connecting / disconnecting mechanism are respectively one of a friction clutch, a synchro gear, a dog clutch, an electromagnetic clutch, a meshing clutch, and an automatic clutch. The vehicle drive device according to any one of 1 to 5.

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