JP6197469B2 - Vehicle drive device - Google Patents

Description

  The present invention relates to a transmission that shifts the rotation of an input member that is drivingly connected to an internal combustion engine and transmits it to an output member, a differential gear mechanism that distributes driving force to a plurality of wheels, and a reduction in the rotation of the output member. The present invention also relates to a vehicle drive device including a counter gear mechanism that transmits to the differential gear mechanism and a rotating electrical machine.

  As the above-described vehicle drive device, for example, devices described in Patent Documents 1 to 4 below are already known. In the technique of Patent Document 1, the front wheels are driven by the driving force of the internal combustion engine transmitted via the transmission, and the rear wheels are driven by the driving force of the rotating electrical machine.

  In the technique of Patent Document 2, the transmission includes an input shaft 34 to which a drive gear corresponding to each gear is fixed, and a driven gear of each gear that is parallel to the input shaft 34 and meshes with the drive gear. The output shaft 42 is fixed, and the drive gear 49 that rotates integrally with the output shaft 42 meshes with the differential gear 14 that is connected to the wheels. The rotating electrical machine is configured to be coupled to the differential gear 14 via a dedicated counter gear mechanism.

  In the technique of Patent Document 3, the transmission is a belt-and-pulley type continuously variable transmission, and includes a drive shaft 11 that rotates integrally with the drive-side pulley, a shaft parallel to the drive shaft 11 and a driven-side pulley. The output shaft 13 that rotates integrally with the driven shaft 12 is configured to mesh with the first ring gear 43 of the differential gear mechanism that is drivingly connected to the wheels. ing. The rotating electric machine is configured to be drivingly connected to the second ring gear 44 of the differential gear mechanism via a dedicated counter gear mechanism.

  In the technique of Patent Document 4, the transmission is a belt-and-pulley type continuously variable transmission, and includes an input shaft 11 that rotates integrally with the driving pulley, an axis parallel to the input shaft 11, and a driven pulley. The output shaft 12 that rotates integrally with the output shaft 12 has a two-shaft configuration, and the output gear 20 that rotates integrally with the output shaft 12 is connected to the ring gear 25 of the differential gear mechanism that is drivingly connected to the wheels via the counter gear mechanism. It is configured to be drive-coupled. The rotating electrical machine is also configured to be drivingly connected to the ring gear 25 of the differential gear mechanism via the counter gear mechanism.

JP2013-129511A JP 2007-221962 A JP 2008-239125 A JP 2000-278809 A

However, in the technique of Patent Document 1, since the internal combustion engine that is a driving force source and the rotating electric machine are driven and connected separately to the front wheels and the rear wheels, a gear mechanism, a case, and the like are separately provided to include the rotating electric machine. There is a problem that the cost of the apparatus becomes high.
In the techniques of Patent Documents 2 to 4, a rotating electrical machine is provided on the output side of the transmission, and a dedicated gear gear mechanism for the rotating electrical machine is provided, so that the reduction ratio of the wheel from the rotating electrical machine is also ensured. Yes. However, since the number of axes is large, there is a problem that the vehicle drive device is enlarged.

  Therefore, it is desired to realize a vehicle drive device that can suppress an increase in the size of the vehicle drive device even if a rotating electrical machine is provided and can suppress an increase in the cost of the device due to the provision of a gear mechanism.

According to the present invention, a transmission for shifting the rotation of an input member drivingly connected to an internal combustion engine and transmitting it to an output member, a differential gear mechanism for distributing driving force to a plurality of wheels, and rotation of the output member A characteristic configuration of a vehicle drive device including a counter gear mechanism that decelerates and transmits to the differential gear mechanism, and a rotating electrical machine,
A torque converter,
The speed change device is configured to change a speed change ratio, convert torque of the input member according to the speed change ratio, and transmit the torque to the output member.
The input member and the output member of the transmission are disposed on a first virtual axis;
The rotating electrical machine is disposed on a second virtual axis;
The counter gear mechanism is disposed on a third virtual axis , and is disposed so as to overlap with each of the transmission, the rotating electrical machine, the output differential gear mechanism, and the torque converter as viewed in the axial direction. And it is arranged between the torque converter and the rotating electrical machine in the axial direction, and is configured such that the counter input gear and the counter output gear having a smaller diameter than the counter input gear rotate integrally.
A speed change output gear provided on the output member meshes with the counter input gear,
The electric output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear and has a smaller diameter than the counter input gear,
The differential input gear provided in the differential gear mechanism is in mesh with the counter output gear.

In the present application, the “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that functions as both a motor and a generator as necessary.
Further, in the present application, “driving connection” refers to a state where two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or It is used as a concept including a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like. Further, as such a transmission member, an engagement device that selectively transmits rotation and driving force, for example, a friction engagement device or a meshing engagement device may be included.

According to the above characteristic configuration, the speed change output gear provided on the output member of the transmission meshes with the counter input gear, and the electric machine output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear. The counter output gear meshes with the differential input gear of the differential gear mechanism. As described above, the electric machine output gear of the rotating electric machine is configured to mesh with the counter input gear that meshes with the transmission output gear of the transmission, so that the rotating electric machine can be used as a wheel without providing a counter gear mechanism dedicated to the rotating electric machine. Drive-coupled.
Moreover, according to said characteristic structure, the electric machine output gear of a rotary electric machine is smaller diameter than a counter input gear, and a counter output gear is smaller diameter than a counter input gear. Therefore, the rotation of the rotating electrical machine is decelerated at a predetermined speed ratio (reduction ratio) by the electrical machine output gear and the counter gear mechanism, and is transmitted to the differential gear mechanism. Therefore, the rotation of the rotating electrical machine can be reduced to at least two stages and transmitted to the wheels without providing a counter gear mechanism dedicated to the rotating electrical machine.
Therefore, even if a rotating electrical machine is provided, an increase in cost due to provision of a gear mechanism or the like can be suppressed.

According to the present invention, a transmission for shifting the rotation of an input member drivingly connected to an internal combustion engine and transmitting it to an output member, a differential gear mechanism for distributing driving force to a plurality of wheels, and rotation of the output member Another characteristic configuration of the vehicle drive device including a counter gear mechanism that decelerates and transmits to the differential gear mechanism, and a rotating electrical machine,
The transmission is a possible change the gear ratio, is configured to transfer to the output member and converts the torque of the input member in response to the gear ratio, the gear mechanism and the engagement device as a constituent member With
The input member and the output member of the transmission are disposed on a first virtual axis;
The rotating electrical machine is disposed on a second virtual axis;
The counter gear mechanism is arranged on the third virtual axis, and is configured such that the counter input gear and the counter output gear having a smaller diameter than the counter input gear rotate integrally.
A speed change output gear provided on the output member meshes with the counter input gear,
The component member of the transmission is divided into a first region and a second region arranged in the axial direction of the first virtual axis, and the transmission output gear is between the first region and the second region. Arranged,
The electric output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear and has a smaller diameter than the counter input gear,
The differential input gear provided in the differential gear mechanism is in mesh with the counter output gear.

According to the above characteristic configuration, the speed change output gear provided on the output member of the transmission meshes with the counter input gear, and the electric machine output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear. The counter output gear meshes with the differential input gear of the differential gear mechanism. Thus, by configuring the electric machine output gear of the rotating electric machine to engage with the counter input gear with which the transmission output gear of the transmission is engaged, the rotating electric machine can be used as a wheel without providing a counter gear mechanism dedicated to the rotating electric machine. Drive-coupled.
Moreover, according to said characteristic structure, the electric machine output gear of a rotary electric machine is smaller diameter than a counter input gear, and a counter output gear is smaller diameter than a counter input gear. Therefore, the rotation of the rotating electrical machine is decelerated at a predetermined speed ratio (reduction ratio) by the electrical machine output gear and the counter gear mechanism, and is transmitted to the differential gear mechanism. Therefore, the rotation of the rotating electrical machine can be reduced to at least two stages and transmitted to the wheels without providing a counter gear mechanism dedicated to the rotating electrical machine.
Therefore, even if a rotating electrical machine is provided, an increase in cost due to provision of a gear mechanism or the like can be suppressed.
Further, according to this configuration, since the transmission output gear is arranged in the intermediate region between the first region and the second region in the axial direction of the transmission, the counter input gear meshing with the transmission output gear is It arrange | positions in the space of the radial direction outer side of the transmission in an area | region. An electric machine output gear that meshes with the counter input gear is also arranged in a space radially outside the transmission in the intermediate region. Therefore, the counter output gear can be arranged in the space of the first region or the second region with respect to the space of the intermediate region in which the counter input gear is arranged, and the rotating electric machine can be arranged in the middle in which the electric machine output gear is arranged. With respect to the space of the region, the counter output gear can be disposed in the space of the first region and the second region where the counter output gear is not disposed. That is, the rotating electrical machine and the counter gear mechanism (counter output gear) can be allocated and arranged in the radially outer space of the transmission in the first region and the second region, and the radially outer space of the transmission is axially arranged. Can be used effectively. Therefore, even if a rotating electrical machine is provided, it is possible to suppress an increase in the axial length of the vehicle drive device while suppressing an increase in the length in the direction orthogonal to the axial direction of the vehicle drive device, An increase in the size of the vehicle drive device can be suppressed.

According to the present invention, a transmission for shifting the rotation of an input member drivingly connected to an internal combustion engine and transmitting it to an output member, a differential gear mechanism for distributing driving force to a plurality of wheels, and rotation of the output member Another characteristic configuration of the vehicle drive device including a counter gear mechanism that decelerates and transmits to the differential gear mechanism, and a rotating electrical machine,
The speed change device is configured to change a speed change ratio, convert torque of the input member according to the speed change ratio, and transmit the torque to the output member.
The input member and the output member of the transmission are disposed on a first virtual axis;
The rotating electrical machine is disposed on a second virtual axis;
The counter gear mechanism is arranged on the third virtual axis, and is configured such that the counter input gear and the counter output gear having a smaller diameter than the counter input gear rotate integrally.
A speed change output gear provided on the output member meshes with the counter input gear,
The electric output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear and has a smaller diameter than the counter input gear,
The differential input gear provided in the differential gear mechanism meshes with the counter output gear ,
A parking gear provided to rotate integrally with any one of the rotating elements in the power transmission path from the output member to the differential input gear, and a mechanism for engaging the parking gear and restricting the rotation of the parking gear. A parking lock mechanism having a joint member, wherein the parking gear is disposed on the first virtual axis .

According to the above characteristic configuration, the speed change output gear provided on the output member of the transmission meshes with the counter input gear, and the electric machine output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear. The counter output gear meshes with the differential input gear of the differential gear mechanism. As described above, the electric machine output gear of the rotating electric machine is configured to mesh with the counter input gear that meshes with the transmission output gear of the transmission, so that the rotating electric machine can be used as a wheel without providing a counter gear mechanism dedicated to the rotating electric machine. Drive-coupled.
Moreover, according to said characteristic structure, the electric machine output gear of a rotary electric machine is smaller diameter than a counter input gear, and a counter output gear is smaller diameter than a counter input gear. Therefore, the rotation of the rotating electrical machine is decelerated at a predetermined speed ratio (reduction ratio) by the electrical machine output gear and the counter gear mechanism, and is transmitted to the differential gear mechanism. Therefore, the rotation of the rotating electrical machine can be reduced to at least two stages and transmitted to the wheels without providing a counter gear mechanism dedicated to the rotating electrical machine.
Therefore, even if a rotating electrical machine is provided, an increase in cost due to provision of a gear mechanism or the like can be suppressed.
Further, according to this configuration, the parking gear can be arranged so as not to interfere with the rotating electrical machine arranged on the second virtual axis and the counter gear mechanism arranged on the third virtual axis. It is possible to increase the degree of freedom in arranging the electric machines. Therefore, it becomes easy to arrange the rotating electrical machine to suppress the increase in the size of the vehicle drive device as described above.

According to the present invention, a transmission for shifting the rotation of an input member drivingly connected to an internal combustion engine and transmitting it to an output member, a differential gear mechanism for distributing driving force to a plurality of wheels, and rotation of the output member Another characteristic configuration of the vehicle drive device including a counter gear mechanism that decelerates and transmits to the differential gear mechanism, and a rotating electrical machine,
The transmission can change a transmission ratio, and is configured to convert the torque of the input member according to the transmission ratio and transmit the torque to the output member, and the rotation direction of the input member and the output member The forward rotation transmission state in which the rotation direction is the same and the reverse rotation transmission state in which these rotation directions are reversed can be changed,
The input member and the output member of the transmission are disposed on a first virtual axis;
The rotating electrical machine is disposed on a second virtual axis;
The counter gear mechanism is arranged on the third virtual axis, and is configured such that the counter input gear and the counter output gear having a smaller diameter than the counter input gear rotate integrally.
A speed change output gear provided on the output member meshes with the counter input gear,
The electric output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear and has a smaller diameter than the counter input gear,
The differential input gear provided in the differential gear mechanism is in mesh with the counter output gear.

According to the above characteristic configuration, the speed change output gear provided on the output member of the transmission meshes with the counter input gear, and the electric machine output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear. The counter output gear meshes with the differential input gear of the differential gear mechanism. As described above, the electric machine output gear of the rotating electric machine is configured to mesh with the counter input gear that meshes with the transmission output gear of the transmission, so that the rotating electric machine can be used as a wheel without providing a counter gear mechanism dedicated to the rotating electric machine. Drive-coupled.
Moreover, according to said characteristic structure, the electric machine output gear of a rotary electric machine is smaller diameter than a counter input gear, and a counter output gear is smaller diameter than a counter input gear. Therefore, the rotation of the rotating electrical machine is decelerated at a predetermined speed ratio (reduction ratio) by the electrical machine output gear and the counter gear mechanism, and is transmitted to the differential gear mechanism. Therefore, the rotation of the rotating electrical machine can be reduced to at least two stages and transmitted to the wheels without providing a counter gear mechanism dedicated to the rotating electrical machine.
Therefore, even if a rotating electrical machine is provided, an increase in cost due to provision of a gear mechanism or the like can be suppressed.
Further, according to this configuration, the vehicle drive device does not require a device that reverses the rotation direction in addition to the transmission, and therefore it is possible to suppress a reduction in the degree of freedom in the arrangement of the rotating electrical machines.

  It is preferable that a reduction ratio from the rotor to the differential input gear is larger than a reduction ratio from the output member to the differential input gear.

  A rotating electrical machine that is drivingly connected to the power transmission path on the wheel side from the transmission is less likely to have a larger reduction ratio than an internal combustion engine that is drivingly connected to the wheel side via the transmission. However, according to the above configuration, the reduction ratio from the rotor to the differential input gear is made larger than the reduction ratio from the output member to the differential input gear. Therefore, as described above, the rotation of the rotating electrical machine can be reduced to at least two stages and transmitted to the wheels.

  The rotating electrical machine has a portion that overlaps with the transmission when viewed in the radial direction of the rotating electrical machine, and is disposed so as to have a portion that overlaps with the counter gear mechanism when viewed in the axial direction of the rotating electrical machine. It is preferable.

  As described above, since the input member and the output member of the transmission are arranged on the first virtual axis, the transmission can be arranged in a cylindrical space as a whole. Further, since the counter input gear is arranged so as to mesh with the transmission output gear, the counter gear mechanism is arranged on the radially outer side of the transmission. Since the length of the transmission in the axial direction is often longer than the length of the counter gear mechanism in the axial direction, a space in which the counter gear mechanism is not disposed is formed outside the transmission in the radial direction. According to the above configuration, the rotating electrical machine has a portion that overlaps with the transmission device as viewed in the radial direction of the rotating electrical machine and uses the counter gear as viewed in the axial direction of the rotating electrical machine so as to effectively use the space. It arrange | positions so that it may have a part which overlaps with a mechanism. Therefore, even if a rotating electrical machine is provided, the length in the axial direction of the vehicle drive device can be suppressed, and the length in the direction orthogonal to the axial direction of the vehicle drive device can be suppressed. An increase in the size of the vehicle drive device can be suppressed.

It is a skeleton figure of the drive device for vehicles concerning the embodiment of the present invention. 1 is an axially developed sectional view of a vehicle drive device according to an embodiment of the present invention. FIG. 2 is an arrangement diagram showing an arrangement of each component of the vehicle drive device according to the embodiment of the present invention when viewed in the axial direction. It is an operation | movement table | surface of the transmission which concerns on embodiment of this invention. It is a speed diagram of the transmission which concerns on embodiment of this invention.

  An embodiment of a vehicle drive device 1 according to the present invention will be described with reference to the drawings. FIG. 1 is a skeleton diagram showing a schematic configuration of a vehicle drive device 1 according to the present embodiment, and FIG. 2 shows parts of a counter gear mechanism CG, a rotating electrical machine MG, and an output differential gear mechanism DF in FIG. It is the figure which represented this with the axial direction expanded sectional view. FIG. 3 is an arrangement diagram showing the arrangement of each component of the vehicle drive device 1 when viewed in the axial direction (when viewed in the axial direction from the second axial direction X2 side to the first axial direction X1 side). is there.

In the present embodiment, as shown in FIG. 1, the vehicle drive device 1 includes a plurality of transmission devices TM that change the speed of the transmission input shaft I that is drivingly connected to the internal combustion engine ENG and transmit the rotation to the transmission output member O. An output differential gear mechanism DF that distributes the driving force to the wheels W, a counter gear mechanism CG that decelerates the rotation of the speed change output member O and transmits it to the output differential gear mechanism DF, and a rotating electrical machine MG. I have. In the present embodiment, the transmission input shaft I is drivingly connected to the internal combustion engine ENG via the torque converter TC.
The transmission input shaft I corresponds to the “input member” in the present invention, the transmission output member O corresponds to the “output member” in the present invention, and the output differential gear mechanism DF includes the “differential gear mechanism”. Is equivalent to.

The transmission TM can change the transmission ratio, and is configured to convert the torque of the transmission input shaft I and transmit it to the transmission output member O in accordance with the transmission ratio.
The transmission input shaft I and the transmission output member O of the transmission apparatus TM are disposed on the first virtual axis A1. The rotating electrical machine MG is disposed on the second virtual axis A2. The counter gear mechanism CG is disposed on the third virtual axis A3.
The counter gear mechanism CG is configured such that a counter input gear GCi and a counter output gear GCo having a smaller diameter than the counter input gear GCi rotate integrally.
A speed change output gear GTo provided on the speed change output member O meshes with the counter input gear GCi. The electric machine output gear GMo that rotates integrally with the rotor Ro of the rotary electric machine MG meshes with the counter input gear GCi and has a smaller diameter than the counter input gear GCi. The differential input gear GDi provided in the output differential gear mechanism DF meshes with the counter output gear GCo.
Hereinafter, the vehicle drive device 1 according to the present embodiment will be described in detail.

1. In this embodiment, as shown in FIGS. 1 and 2, the first virtual axis A1, the second virtual axis A2, and the third virtual axis A3 are parallel to each other. Has been placed. Therefore, the axial direction is an axial direction common to these virtual axes. A direction (right side in FIGS. 1 and 2) from the vehicle drive device 1 to the internal combustion engine ENG in the axial direction is defined as an axial first direction X1, and from the internal combustion engine ENG, which is the opposite direction, to the vehicle drive device 1. The direction (left side in FIGS. 1 and 2) is defined as the second axial direction X2.

  As shown in FIG. 1, the hybrid vehicle includes an internal combustion engine ENG and a rotating electrical machine MG as a driving force source for the vehicle. The hybrid vehicle includes a transmission TM, and the transmission TM shifts the rotational speed of the internal combustion engine ENG transmitted to the transmission input shaft I and converts the torque to the transmission output member O.

<Internal combustion engine ENG>
The internal combustion engine ENG is a heat engine that is driven by the combustion of fuel. For example, various known internal combustion engines such as a gasoline engine and a diesel engine can be used. In this example, an internal combustion engine output shaft such as a crankshaft of the internal combustion engine ENG is drivingly connected to a power input shaft Ip that is drivingly connected to the torque converter TC.
The output shaft of the internal combustion engine ENG is arranged on the first virtual axis A1.

<Case CS>
As shown in FIG. 2, the torque converter TC, the transmission TM, the counter gear mechanism CG, the rotating electrical machine MG, and the output differential gear mechanism DF constituting the vehicle drive device 1 are accommodated in the case CS. . The case CS includes an outer wall formed to cover the outside of the vehicle drive device 1. In addition, the case CS partially or entirely covers the torque converter TC, the transmission TM, the counter gear mechanism CG, the rotating electrical machine MG, and the output differential gear mechanism DF in order to support or isolate each. Provided with a partition wall.

<Torque converter TC>
As shown in FIG. 1, the torque converter TC transmits the rotational driving force of the internal combustion engine ENG transmitted to the power input shaft Ip to the transmission device TM side via hydraulic oil filled therein. It is. The torque converter TC includes a pump impeller TCa as an input side rotating member drivingly connected to the power input shaft Ip, a turbine runner TCb as an output side rotating member drivingly connected to the transmission input shaft I, and a gap between them. And a stator TCc provided with a one-way clutch. The torque converter TC transmits driving force between the driving-side pump impeller TCa and the driven-side turbine runner TCb via hydraulic oil filled therein. The oil pump OP is drivingly coupled so as to rotate integrally with the pump impeller TCa, and is configured to rotate integrally with the power input shaft Ip.
The power input shaft Ip and the torque converter TC are disposed on the first virtual axis A1.

  The torque converter TC includes a lockup clutch LC as an engagement device for lockup. This lock-up clutch LC is a clutch that connects the pump impeller TCa and the turbine runner TCb so as to rotate together to eliminate the rotational difference (slip) between the pump impeller TCa and the turbine runner TCb and increase the transmission efficiency. It is. Therefore, when the lockup clutch LC is engaged, the torque converter TC transmits the driving force of the internal combustion engine ENG to the transmission input shaft I without passing through the hydraulic oil. Further, the torque converter TC includes a damper DP.

<Transmission device TM>
The transmission TM shifts the rotation of the transmission input shaft I at a predetermined transmission ratio and transmits it to the transmission output member O, and converts the torque of the transmission input shaft I according to the predetermined transmission ratio to change the transmission output member O. Is configured to communicate. Here, the gear ratio can be changed.
In the present embodiment, the transmission apparatus TM is a stepped automatic transmission apparatus having a plurality of shift stages having different speed ratios. The transmission apparatus TM includes a gear mechanism such as a planetary gear mechanism and an engagement device such as a friction engagement device in order to form the plurality of gear speeds. The transmission TM shifts the rotational speed of the transmission input shaft I at the gear ratio of each gear stage, converts the torque of the transmission input shaft I, and transmits it to the transmission output member O. Torque transmitted from the transmission TM to the transmission output member O is distributed and transmitted to the two left and right axles AX via the counter gear mechanism CG and the output differential gear mechanism DF, and is connected to each axle AX. It is transmitted to the wheel W. Here, the transmission gear ratio is the ratio of the rotational speed of the transmission input shaft I to the rotational speed of the transmission output member O when each gear stage is formed in the transmission apparatus TM. Is divided by the rotational speed of the speed change output member O. That is, the rotational speed obtained by dividing the rotational speed of the transmission input shaft I by the transmission ratio becomes the rotational speed of the transmission output member O. Further, torque obtained by multiplying the torque transmitted from the transmission input shaft I to the transmission TM by the transmission ratio becomes the torque transmitted from the transmission TM to the transmission output member O.

  In the present embodiment, the transmission TM includes four shift speeds (first speed 1st, second speed 2nd, third speed 3rd, and fourth speed 4th) having different speed ratios (reduction ratios) as forward speeds. In order to configure these shift speeds, the transmission TM includes a gear mechanism including a planetary gear mechanism PLG and six engagement devices C1, C2, C3, B1, B2, and F1. Yes. The engagement and disengagement of the plurality of engagement devices C1, B1,... Excluding the one-way clutch F1 are controlled to switch the rotation state of each rotation element of the planetary gear mechanism PLG, and the plurality of engagement devices C1, B1,. ... Are selectively engaged to switch the four shift speeds. Note that the transmission apparatus TM includes a reverse gear Rev in addition to the above four gears.

  In the present embodiment, the planetary gear mechanism PLG is a Ravigneaux type planetary gear mechanism arranged coaxially with the transmission input shaft I. That is, the planetary gear mechanism includes two sun gears, a first sun gear S1 and a second sun gear S2, a ring gear R, a long pinion gear P1, a long pinion gear P1, and a first sun gear S1 that mesh with both the second sun gear S2 and the ring gear R. It has four rotating elements, which are a common carrier CA that supports the meshing short pinion gear P2.

  The second sun gear S2 of the planetary gear mechanism PLG is drive-coupled so as to selectively rotate integrally with the transmission input shaft I via the third clutch C3. The carrier CA is drive-coupled to selectively rotate integrally with the transmission input shaft I via the second clutch C2, and is selected as a case CS as a non-rotating member via the second brake B2 or the one-way clutch F1. Fixed. The ring gear R is drivingly connected so as to rotate integrally with the transmission output member O. The first sun gear S1 is drivably coupled to the transmission input shaft I via the first clutch C1 so as to selectively rotate integrally.

  In the present embodiment, each of the engagement devices C1, C2, C3, B1, and B2 except the one-way clutch F1 is a friction engagement device. Specifically, these are constituted by a multi-plate clutch or a multi-plate brake operated by hydraulic pressure. The engagement states of these engagement devices C1, C2, C3, B1, and B2 are controlled by the hydraulic pressure supplied from the hydraulic control device.

  Next, the four shift speeds realized by the transmission apparatus TM will be described. FIG. 4 is an operation table showing operation states of the plurality of engagement devices C1, B1,. In this figure, “◯” indicates that each engaging device is in an engaged state, and “no mark” indicates that each engaging device is in a released state. “(◯)” indicates that the engagement device is brought into an engaged state when engine braking is performed. “△” indicates a released state when rotating in one direction (the carrier CA rotates in the positive direction) and engaging when rotating in the other direction (the carrier CA rotates in the negative direction). It shows that it will be in the state.

  FIG. 5 is a speed diagram of the transmission apparatus TM. In this velocity diagram, the vertical axis corresponds to the rotational speed of each rotating element. That is, “0” described corresponding to the vertical axis indicates that the rotation speed is zero, the upper side is positive rotation (rotation speed is positive), and the lower side is negative rotation (rotation speed is negative). is there. Each of the plurality of vertical lines arranged in parallel corresponds to each rotating element of the planetary gear mechanism PLG. That is, “S1”, “R”, “CA”, and “S2” described above each vertical line are respectively connected to the first sun gear S1, the ring gear R, the carrier CA, and the second sun gear S2 of the planetary gear mechanism PLG. It corresponds. The interval between the plurality of vertical lines arranged in parallel is based on the gear ratio λ of the planetary gear mechanism PLG (the gear ratio between the sun gear and the ring gear = [the number of teeth of the sun gear] / [the number of teeth of the ring gear]). It is determined.

  In addition, “●” indicates that the engaging device connected to each rotating element is in the direct engagement state. “C1”, “C2”, “C3”, “B1”, “B2”, and “F1” written adjacent to each “●” indicate the engagement devices in the direct engagement state. Yes. “☆” indicates the state of the rotational speed of the rotating element (ring gear R of the planetary gear mechanism PLG) connected to the transmission output member O. Note that “1st”, “2nd”, “3rd”, “4th”, and “Rev”, which are described adjacent to each “☆”, indicate the shift speeds that are formed.

  As shown in FIGS. 4 and 5, the first stage 1st is realized by the cooperation of the engagement of the first clutch C1 and the one-way clutch F1. That is, when the rotational driving force of the transmission input shaft I is transmitted to the first sun gear S1 with the first clutch C1 engaged, the one-way clutch F1 is engaged and fixed to the case CS. Then, the rotational driving force of the first sun gear S1 is decelerated based on the gear ratio λ1 and transmitted to the transmission output member O.

  Further, the first stage 1st is realized even when the engagement of the first clutch C1 and the engagement of the second brake B2 cooperate when performing engine braking or the like. When the first clutch C1 is engaged, the rotational driving force of the transmission input shaft I is transmitted to the first sun gear S1. Further, when the second brake B2 is engaged, the carrier CA is fixed to the case CS. Then, the rotational driving force of the first sun gear S1 is decelerated based on the gear ratio λ1 and transmitted to the transmission output member O.

  The second stage 2nd is realized by cooperation of the engagement of the first clutch C1 and the engagement of the first brake B1. That is, when the first clutch C1 is engaged, the rotational driving force of the transmission input shaft I is transmitted to the first sun gear S1. Further, when the first brake B1 is engaged, the second sun gear S2 is fixed to the case CS. Then, the rotational driving force of the first sun gear S1 is decelerated based on the gear ratios λ1 and λ2 and transmitted to the transmission output member O.

  The third stage 3rd is realized by the engagement of the first clutch C1 and the engagement of the second clutch C2. That is, when the first clutch C1 is engaged, the rotational driving force of the transmission input shaft I is transmitted to the first sun gear S1. When the second clutch C2 is engaged, the rotational driving force of the transmission input shaft I is transmitted to the second sun gear S2. Then, the second sun gear S2 and the first sun gear S1 rotate at the same speed, so that the rotational driving force of the transmission input shaft I is transmitted to the transmission output member O as it is.

  The fourth stage 4th is realized by cooperation between the engagement of the second clutch C2 and the engagement of the first brake B1. That is, when the second clutch C2 is engaged, the rotational driving force of the transmission input shaft I is transmitted to the carrier CA. Further, when the first brake B1 is engaged, the second sun gear S2 is fixed to the case CS. Then, the rotational driving force of the carrier CA is increased based on the gear ratio λ2 and transmitted to the transmission output member O.

  These forward speeds are, in descending order of the speed ratio (reduction ratio) between the speed change input shaft I and the speed change output member O, the first speed 1st, the second speed 2nd, the third speed 3rd, and the fourth speed 4th. It has become.

  The reverse speed Rev is realized by the engagement of the third clutch C3 and the engagement of the second brake B2. That is, when the third clutch C3 is engaged, the rotational driving force of the transmission input shaft I is transmitted to the second sun gear S2. Further, when the second brake B2 is engaged, the carrier CA is fixed to the case CS. Then, the rotational driving force of the second sun gear S2 is decelerated based on the gear ratio λ2, and the rotational direction is reversed and transmitted to the transmission output member O.

  As described above, the transmission apparatus TM includes the forward gears 1st, 2nd,... And the reverse gear Rev so that the rotational direction of the transmission input shaft I is the same as the rotational direction of the transmission output member O. The forward rotation transmission state and the reverse rotation transmission state in which these rotation directions are reversed can be changed.

<Rotary electric machine MG>
As illustrated in FIG. 1, the rotating electrical machine MG includes a stator St fixed to the case CS and a rotor Ro that is rotatably supported on the radially inner side of the stator St. The rotor Ro is drivably coupled to the electric machine output gear GMo via the rotor shaft SR. The rotating electrical machine MG is disposed on the second virtual axis A2.

As shown in FIG. 2, the rotor shaft SR is supported by the case CS so as to be rotatable via a bearing. In the example illustrated in FIG. 2, the rotor shaft SR includes a rotor support shaft SR1 that supports the rotor Ro, and an output gear support shaft SR2 that supports the electric machine output gear GMo. The rotor support shaft SR1 is spline-fitted to the outer peripheral surface of the end portion of the output gear support shaft SR2 on the side of the second shaft direction X2 of the output gear support shaft SR2 so that the rotor support shaft SR1 has the rotor support shaft SR1. And the output gear support shaft SR2 are configured to rotate integrally.
Ends on both sides in the axial direction of the rotor support shaft SR1 and ends on both sides in the axial direction of the output gear support shaft SR2 are supported by the case CS so as to be rotatable via bearings. An electric machine output gear GMo is formed on the outer peripheral surface of the output gear support shaft SR2.

  The rotating electrical machine MG is electrically connected to a battery as a power storage device via an inverter that performs direct current to alternating current conversion. The rotating electrical machine MG can perform a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. It is possible. That is, the rotating electrical machine MG is powered by receiving power supply from the battery via the inverter, or generates power by the rotational driving force transmitted from the internal combustion engine ENG or the wheel W, and the generated power is transmitted via the inverter. It is stored in the battery.

<Counter gear mechanism CG>
As shown in FIG. 1, the counter gear mechanism CG decelerates the rotation of the speed change output member O and transmits it to the output differential gear mechanism DF. The counter gear mechanism CG is configured such that a counter input gear GCi and a counter output gear GCo having a smaller diameter than the counter input gear GCi are connected by a counter shaft SC and rotate integrally. As shown in FIG. 2, both ends of the counter shaft SC in the axial direction are supported by the case CS in a rotatable state via bearings. The counter gear mechanism CG is disposed on the third virtual axis A3.
The counter input gear GCi meshes with a transmission output gear GTo provided on the transmission output member O. Further, the counter input gear GCi meshes with the electric machine output gear GMo that rotates integrally with the rotor Ro of the rotary electric machine MG at a position different from the transmission output gear GTo in the circumferential direction (see FIG. 3). The counter output gear GCo meshes with a differential input gear GDi provided in the output differential gear mechanism DF.

<Output differential gear mechanism DF>
The output differential gear mechanism DF has a differential input gear GDi, and distributes torque transmitted to the differential input gear GDi to the plurality of wheels W for transmission. In this example, the output differential gear mechanism DF is a differential gear mechanism using a plurality of bevel gears DF1 and DF2 meshing with each other, and distributes torque transmitted to the differential input gear GDi, This is transmitted to the left and right wheels W via the axle AX. The output differential gear mechanism DF is disposed on the fourth virtual axis A4. The fourth virtual axis A4 is arranged in parallel with the first virtual axis A1, the second virtual axis A2, and the third virtual axis A3.

  In the present embodiment, the output differential gear mechanism DF includes a differential carrier DF4 that rotates integrally with the differential input gear GDi. In the differential carrier DF4, a pair of side gears DF2 that rotate integrally with the respective axles AX, and a pair of pinion gears DF1 that connect the two side gears DF2 and rotate together with the differential carrier DF4 are accommodated.

The differential carrier DF4 includes a pinion rotation shaft DF3 that rotates integrally with the differential carrier DF4, and the pinion gear DF1 is supported so as to be capable of rotating about the pinion rotation shaft DF3.
Each pinion gear DF1 meshes with both the left and right two side gears DF2. When the differential carrier DF4 rotates, the left and right side gears DF2 rotate via the pinion gear DF1 that rotates together with the differential carrier DF4, and each axle AX that is drivingly connected to each side gear DF2 rotates. When each axle AX rotates, each wheel W that is drivingly connected to each axle AX rotates. Each pinion gear DF1 rotates around the pinion rotation axis DF3 to differentially operate the left and right side gears DF2.

2. Detailed Configuration of Vehicle Drive Device 1 Next, a detailed configuration of the vehicle drive device 1 according to the present embodiment will be described.
As shown in FIGS. 1 to 3, the transmission output gear GTo provided on the transmission output member O of the transmission TM is engaged with the counter input gear GCi. Further, the electric machine output gear GMo that rotates integrally with the rotor Ro of the rotary electric machine MG is engaged with the counter input gear GCi. The counter output gear GCo meshes with the differential input gear GDi of the output differential gear mechanism DF. In this way, the electric machine output gear GMo of the rotating electric machine MG is configured to mesh with the counter input gear GCi that meshes with the transmission output gear GTo of the transmission apparatus TM, so that a counter gear mechanism dedicated to the rotating electric machine MG is not provided. The rotating electrical machine MG can be drivingly connected to the wheel W.

  Further, the electric machine output gear GMo of the rotating electric machine MG has a smaller diameter than the counter input gear GCi, and the counter output gear GCo has a smaller diameter than the counter input gear GCi. Therefore, the rotation of the rotating electrical machine MG is decelerated at a predetermined speed ratio (reduction ratio) by the electrical machine output gear GMo and the counter gear mechanism CG, and is transmitted to the output differential gear mechanism DF. Therefore, the rotation of the rotating electrical machine MG can be decelerated in two stages and transmitted to the wheels W without providing a counter gear mechanism dedicated to the rotating electrical machine MG.

  The rotating electrical machine MG that is drivably coupled to the power transmission path on the wheel W side from the transmission TM is less likely to increase the reduction ratio than the internal combustion engine ENG that is drivably coupled to the wheel W via the transmission TM. However, in the present embodiment, as shown in FIGS. 1 and 2, the electric machine output gear GMo has a smaller diameter than the transmission output gear GTo of the transmission apparatus TM, and the reduction ratio from the rotor Ro to the differential input gear GDi. Is greater than the reduction ratio from the transmission output member O to the differential input gear GDi. Therefore, it is possible to balance the reduction ratio from the internal combustion engine ENG to the wheel W and to reduce the rotation of the rotating electrical machine MG in two stages and transmit it to the wheel W.

  The transmission input shaft I and the transmission output member O of the transmission apparatus TM are disposed on the first virtual axis A1. For this reason, the gear mechanism and the engagement device that constitute the transmission TM are also arranged on the first virtual axis A1. Therefore, the gear mechanism and the engagement device of the transmission device TM are arranged around the first virtual axis A1, and the transmission device TM can be arranged in a cylindrical space parallel to the axial direction as a whole. Further, since the counter input gear GCi is disposed so as to mesh with the transmission output gear GTo, the counter gear mechanism CG is disposed on the radially outer side of the transmission apparatus TM. However, since the axial length of the transmission device TM is long and shorter than the axial length of the counter gear mechanism CG, a space in which the counter gear mechanism CG is not arranged is formed outside the transmission device TM in the radial direction. Therefore, the rotating electrical machine MG has a portion that overlaps with the transmission device TM when viewed in the radial direction of the rotating electrical machine MG, and the counter gear mechanism when viewed in the axial direction of the rotating electrical machine MG so as to effectively use the space. It arrange | positions so that it may have a part which overlaps with CG (refer FIG. 3). Therefore, even if the rotating electrical machine MG is provided, it is possible to prevent the length of the vehicle drive device 1 from increasing in the axial direction and to increase the length of the vehicle drive device 1 in the direction orthogonal to the axial direction. Can be suppressed.

As shown in FIG. 1, the transmission TM includes a gear mechanism and an engagement device as components, and at least the components excluding the gear shift output gear GTo are arranged in the first region D1 and the first region D1 aligned in the axial direction of the first virtual axis A1. The transmission output gear GTo is disposed in an intermediate region DM between the first region D1 and the second region D2.
In the present embodiment, a region set on the first axial direction X1 side with respect to the intermediate region DM is referred to as a first region D1, and a region set on the second axial direction X2 side with respect to the intermediate region DM is referred to as a second region D2. To do. A second clutch C2 as a component is disposed in the first region D1, and a planetary gear mechanism PLG, a first clutch C1, a third clutch C3, a first brake B1, and a second as components are disposed in the second region D2. A brake B2 and a one-way clutch F1 are arranged. A shift output gear GTo and a shift output member O as constituent members are arranged in the intermediate region DM.

  Therefore, in the illustrated example, the intermediate region DM is disposed closer to the first axial direction X1 side in the axial length of the transmission device TM. In other words, the axial length of the second region D2 is longer than the axial length of the first region D1, and the space outside the radial direction of the transmission device TM in the second region D2 is the speed change in the first region D1. It is made wider in the axial direction than the space on the radially outer side of the device TM. Therefore, as will be described later, a rotating electrical machine MG having a longer axial length than the counter output gear GCo can be disposed in the space outside the second region D2 in the radial direction, and the space outside the first region D1 in the radial direction. As will be described later, the counter output gear GCo having a relatively short axial length can be disposed without generating a useless space.

  A counter input gear GCi meshes with the transmission output gear GTo disposed in the intermediate region DM, and the counter input gear GCi is disposed in a space radially outside the transmission device TM in the intermediate region DM. The counter output gear GCo is disposed on the first axial direction X1 side of the counter input gear GCi, and is disposed in a space radially outward of the transmission apparatus TM in the first region D1. Therefore, in the space outside the radial direction of the transmission TM in the second region D2, the gears GCi and GCo of the counter gear mechanism CG are not arranged, and a space for arranging the rotating electrical machine MG is secured.

  In the present embodiment, the rotating electrical machine MG is disposed in a radially outer space of the transmission apparatus TM in the second region D2. When viewed in the radial direction of the rotating electrical machine MG or the transmission TM, the entire rotor Ro and stator St of the rotating electrical machine MG are arranged so as to overlap with a portion of the second region D2 of the transmission TM. As shown in FIG. 2, the rotating electrical machine MG and the portion of the second region D2 of the transmission apparatus TM are disposed adjacent to each other in the radial direction via the wall of the case CS.

  The rotating electrical machine MG is disposed in a space on the second axial direction X2 side of the counter gear mechanism CG (counter input gear GCi). As shown in FIG. 2, the rotating electrical machine MG and the counter gear mechanism CG are disposed adjacent to each other in the axial direction via the wall of the case CS.

  As shown in FIG. 3, when viewed in the axial direction of the rotating electrical machine MG or the counter gear mechanism CG, the rotating electrical machine MG is a part of the counter input gear GCi and the counter output gear GCo (1/4 or more of the total (in this example, About 1/3)). This is because the electric machine output gear GMo has a smaller diameter than the counter input gear GCi, and the rotating electric machine MG can be arranged close to the third virtual axis A3 on which the counter gear mechanism CG is arranged.

  Further, as shown in FIGS. 1 and 2, the counter output gear GCo is disposed on the side of the first axis direction X1 with respect to the counter input gear GCi, and the rotating electrical machine MG has a shaft with respect to the counter input gear GCi. Since it is arranged on the second direction X2 side, the electric machine output gear GMo of the rotary electric machine MG can be meshed with the counter input gear GCi. Further, the axial interval between the rotor Ro of the rotating electrical machine MG and the electrical machine output gear GMo can be shortened, and the strength of the rotor shaft SR can be easily secured.

As shown in FIG. 3, the first virtual axis A1, the second virtual axis A2, and the fourth virtual axis A4 are arranged such that a line connecting these virtual axes forms a triangle when viewed in the axial direction. .
The transmission TM, the rotating electrical machine MG, and the output differential gear mechanism DF arranged on the virtual axes A1, A2, and A4 have a circular shape with the virtual center as the center when viewed in the axial direction. Since they are arranged adjacent to each other when viewed in the axial direction, the gap between them can be minimized when viewed in the axial direction.

The third virtual axis A3 is arranged inside a triangle formed by the virtual axes A1, A2, and A4 when viewed in the axial direction. The counter gear mechanism CG corresponding to the third virtual axis A3 overlaps with each of the transmission TM, the rotating electrical machine MG, and the output differential gear mechanism DF that are arranged adjacent to each other in the axial direction. The counter gear mechanism CG is arranged without providing a gap for arranging the counter gear mechanism CG between the transmission device TM, the rotating electrical machine MG, and the output differential gear mechanism DF as viewed in the axial direction. Have been able to.
Therefore, the components of the vehicle drive device 1 can be arranged close to each other to reduce the overall outer shape of the vehicle drive device 1.

<Parking lock mechanism PR>
The vehicle drive device 1 includes a parking lock mechanism PR. The parking lock mechanism PR includes a parking gear PG and an engagement member PS that engages with the parking gear PG and restricts the rotation of the parking gear PG. The parking gear PG is provided so as to rotate integrally with any of the rotating elements in the power transmission path from the speed change output member O to the differential input gear GDi. In the present embodiment, the parking gear PG is disposed on the first virtual axis A1 and provided to rotate integrally with the speed change output member O, as shown in FIGS. Therefore, the parking gear PG can be disposed so as not to interfere with the rotating electrical machine MG disposed on the second virtual axis A2 and the counter gear mechanism CG disposed on the third virtual axis A3. The degree of freedom of MG arrangement can be increased.

The parking gear PG has a smaller diameter than the speed change output gear GTo, and is disposed closer to the shaft first direction X1 than the speed change output gear GTo.
Further, as shown in FIG. 3, the engaging member PS can swing around a swinging fulcrum PS1 fixed to the case CS, and a claw portion PS2 is integrally formed on the engaging member PS. Yes. The engagement member PS is swung within a predetermined movable range by a cam mechanism (not shown) or the like. In a state in which the pawl portion PS2 is engaged with the parking gear PG and these are engaged, the parking lock mechanism PR forcibly stops the rotation of the transmission output member O. On the other hand, the parking lock mechanism PR allows the transmission output member O to rotate in a state in which the pawl portion PS2 does not mesh with the parking gear PG and is disengaged.

  The engaging member PS is disposed at a circumferential position different from the circumferential position of the first virtual axis A1 where the transmission output gear GTo meshes with the counter input gear GCi. For example, the engaging member PS is disposed at a circumferential position that is 90 degrees or more different from the meshing position of the transmission output gear GTo (in this example, a circumferential position that is 180 degrees different). By arranging in this way, the parking lock mechanism PR does not interfere with the counter gear mechanism CG and the rotating electrical machine MG, so that the degree of freedom of arrangement of the counter gear mechanism CG and the rotating electrical machine MG can be increased.

[Other Embodiments]
Finally, other embodiments of the present invention will be described. Note that the configuration of each embodiment described below is not limited to being applied independently, and can be applied in combination with the configuration of other embodiments as long as no contradiction arises.

(1) In the above embodiment, the transmission TM is configured to include a Ravigneaux planetary gear mechanism PLG and six engagement devices C1, C2, C3, B1, B2, and F1. Was described as an example. However, the embodiment of the present invention is not limited to this. That is, the transmission apparatus TM may be provided with an arbitrary gear mechanism such as a double pinion type planetary gear mechanism as long as the transmission input shaft I and the transmission output member O are disposed on the first virtual axis A1. Any number of gear mechanisms may be provided, and any number of engagement devices may be provided.
Even in this case, the speed change device TM is arranged by dividing the gear mechanism and the engagement device into the first region D1 and the second region D2 arranged in the axial direction of the first virtual axis A1, and the first region D1 and the second region It is preferable that the speed change output gear GTo is disposed in the intermediate region DM between D2.

(2) In the above embodiment, the case where one counter input gear GCi is provided has been described as an example. However, the embodiment of the present invention is not limited to this. That is, two counter input gears GCi may be provided, that is, a first counter input gear GCi that meshes with the transmission output gear GTo and a second counter input gear GCi that meshes with the electric machine output gear GMo.
Even in this case, the first and second counter input gears GCi have a larger diameter than the counter output gear GCo, and the electric machine output gear GMo of the rotating electric machine MG has a smaller diameter than the second counter input gear GCi. Further, the reduction ratio from the rotor Ro to the differential input gear GDi is made larger than the reduction ratio from the transmission output member O to the differential input gear GDi.
The second counter input gear GCi is disposed on the second axial direction X2 side of the first counter input gear GCi, and the counter output gear GCo is disposed on the first axial direction X1 side of the first counter input gear GCi. Be placed.

(3) In the above embodiment, the case where the reduction ratio from the rotor Ro to the differential input gear GDi is greater than the reduction ratio from the transmission output member O to the differential input gear GDi has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the reduction ratio from the rotor Ro to the differential input gear GDi may be smaller than the reduction ratio from the transmission output member O to the differential input gear GDi.

(4) In the above embodiment, the transmission TM includes a gear mechanism and an engagement device as constituent members, and the constituent members are arranged in the axial direction of the first virtual axis A1 in the first region D1 and the second region D2. The case where the transmission output gear GTo is disposed in the intermediate region DM between the first region D1 and the second region D2 has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the gear mechanism and the engaging device of the transmission TM are not arranged separately in the first region D1 and the second region D2, and the region of the end portion of the transmission TM on the first axial direction X1 side, or The speed change output gear GTo may be disposed in the end region on the second axial direction X2 side.
In the case where the transmission output gear GTo is disposed in the region of the end portion of the transmission apparatus TM on the first shaft direction X1 side, the rotating electrical machine MG is in the second shaft direction X2 with respect to the counter input gear GCi meshing with the transmission output gear GTo. Is disposed in a space outside the transmission device TM in the radial direction. The counter output gear GCo may be arranged on the first shaft direction X1 side with respect to the counter input gear GCi, or on the second shaft direction X2 side with respect to the counter input gear GCi and with respect to the rotating electrical machine MG. You may arrange | position at the 1st direction X1 side.
In the case where the transmission output gear GTo is disposed in the region of the end portion of the transmission apparatus TM on the second shaft direction X2 side, the rotating electrical machine MG is in the first shaft direction X1 with respect to the counter input gear GCi meshing with the transmission output gear GTo. Is disposed in a space outside the transmission device TM in the radial direction. The counter output gear GCo may be arranged on the second shaft direction X2 side with respect to the counter input gear GCi, or on the first shaft direction X1 side with respect to the counter input gear GCi and with respect to the rotating electrical machine MG. You may arrange | position at the 2nd direction X2 side.

  The present invention relates to a transmission that shifts the rotation of an input member that is drivingly connected to an internal combustion engine and transmits it to an output member, a differential gear mechanism that distributes driving force to a plurality of wheels, and a reduction in the rotation of the output member. Thus, the present invention can be suitably used for a vehicle drive device including a counter gear mechanism that transmits to the differential gear mechanism and a rotating electrical machine.

1: Vehicle drive device A1: 1st virtual axis A2: 2nd virtual axis A3: 3rd virtual axis A4: 4th virtual axis CG: Counter gear mechanism CS: Case D1: 1st area | region D2: 2nd area | region DM: Middle region DF: differential gear mechanism for output (differential gear mechanism)
ENG: Internal combustion engine GCi: Counter input gear GCo: Counter output gear GDi: Differential input gear GMo: Electric output gear GTo: Shift output gear I: Shift input shaft (input member)
Ip: Power input shaft LC: Lock-up clutch MG: Rotating electric machine O: Shifting output member (output member)
PLG: planetary gear mechanism PG: parking gear PR: parking lock mechanism PS: engagement member Ro: rotor SC: counter shaft SR: rotor shaft TC: torque converter TM: transmission device W: wheel X1: shaft first direction X2: shaft Second direction

Claims (6)

A transmission for shifting the rotation of an input member drivingly connected to an internal combustion engine and transmitting it to an output member, a differential gear mechanism for distributing driving force to a plurality of wheels, and reducing the rotation of the output member to reduce the difference A vehicle drive device comprising a counter gear mechanism that transmits to a dynamic gear mechanism, and a rotating electrical machine,
A torque converter,
The speed change device is configured to change a speed change ratio, convert torque of the input member according to the speed change ratio, and transmit the torque to the output member.
The input member and the output member of the transmission are disposed on a first virtual axis;
The rotating electrical machine is disposed on a second virtual axis;
The counter gear mechanism is disposed on a third virtual axis , and is disposed so as to overlap with each of the transmission, the rotating electrical machine, the output differential gear mechanism, and the torque converter as viewed in the axial direction. And it is arranged between the torque converter and the rotating electrical machine in the axial direction, and is configured such that the counter input gear and the counter output gear having a smaller diameter than the counter input gear rotate integrally.
A speed change output gear provided on the output member meshes with the counter input gear,
The electric output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear and has a smaller diameter than the counter input gear,
A differential drive gear provided in the differential gear mechanism is a vehicle drive device that meshes with the counter output gear. A transmission for shifting the rotation of an input member drivingly connected to an internal combustion engine and transmitting it to an output member, a differential gear mechanism for distributing driving force to a plurality of wheels, and reducing the rotation of the output member to reduce the difference A vehicle drive device comprising a counter gear mechanism that transmits to a dynamic gear mechanism, and a rotating electrical machine,
The transmission is a possible change the gear ratio, is configured to transfer to the output member and converts the torque of the input member in response to the gear ratio, the gear mechanism and the engagement device as a constituent member With
The input member and the output member of the transmission are disposed on a first virtual axis;
The rotating electrical machine is disposed on a second virtual axis;
The counter gear mechanism is arranged on the third virtual axis, and is configured such that the counter input gear and the counter output gear having a smaller diameter than the counter input gear rotate integrally.
A speed change output gear provided on the output member meshes with the counter input gear,
The component member of the transmission is divided into a first region and a second region arranged in the axial direction of the first virtual axis, and the transmission output gear is between the first region and the second region. Arranged,
The electric output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear and has a smaller diameter than the counter input gear,
A differential drive gear provided in the differential gear mechanism is a vehicle drive device that meshes with the counter output gear. A transmission for shifting the rotation of an input member drivingly connected to an internal combustion engine and transmitting it to an output member, a differential gear mechanism for distributing driving force to a plurality of wheels, and reducing the rotation of the output member to reduce the difference A vehicle drive device comprising a counter gear mechanism that transmits to a dynamic gear mechanism, and a rotating electrical machine,
The speed change device is configured to change a speed change ratio, convert torque of the input member according to the speed change ratio, and transmit the torque to the output member.
The input member and the output member of the transmission are disposed on a first virtual axis;
The rotating electrical machine is disposed on a second virtual axis;
The counter gear mechanism is arranged on the third virtual axis, and is configured such that the counter input gear and the counter output gear having a smaller diameter than the counter input gear rotate integrally.
A speed change output gear provided on the output member meshes with the counter input gear,
The electric output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear and has a smaller diameter than the counter input gear,
The differential input gear provided in the differential gear mechanism meshes with the counter output gear ,
A parking gear provided to rotate integrally with any one of the rotating elements in the power transmission path from the output member to the differential input gear, and a mechanism for engaging the parking gear and restricting the rotation of the parking gear. And a parking lock mechanism having a joint member, wherein the parking gear is disposed on the first virtual axis . A transmission for shifting the rotation of an input member drivingly connected to an internal combustion engine and transmitting it to an output member, a differential gear mechanism for distributing driving force to a plurality of wheels, and reducing the rotation of the output member to reduce the difference A vehicle drive device comprising a counter gear mechanism that transmits to a dynamic gear mechanism, and a rotating electrical machine,
The transmission can change a transmission ratio, and is configured to convert the torque of the input member according to the transmission ratio and transmit the torque to the output member, and the rotation direction of the input member and the output member The forward rotation transmission state in which the rotation direction is the same and the reverse rotation transmission state in which these rotation directions are reversed can be changed,
The input member and the output member of the transmission are disposed on a first virtual axis;
The rotating electrical machine is disposed on a second virtual axis;
The counter gear mechanism is arranged on the third virtual axis, and is configured such that the counter input gear and the counter output gear having a smaller diameter than the counter input gear rotate integrally.
A speed change output gear provided on the output member meshes with the counter input gear,
The electric output gear that rotates integrally with the rotor of the rotating electric machine meshes with the counter input gear and has a smaller diameter than the counter input gear,
A differential drive gear provided in the differential gear mechanism is a vehicle drive device that meshes with the counter output gear. 5. The vehicle drive device according to claim 1, wherein a reduction ratio from the rotor to the differential input gear is larger than a reduction ratio from the output member to the differential input gear. 6. The rotating electrical machine has a portion that overlaps with the transmission when viewed in the radial direction of the rotating electrical machine, and is disposed so as to have a portion that overlaps with the counter gear mechanism when viewed in the axial direction of the rotating electrical machine. The vehicle drive device according to any one of claims 1 to 5 .

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