JP2015047946A - Vehicle drive unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a vehicle drive unit which can suppress the enlargement of the device even if the device has a rotating electric machine, can suppress an increase of a cost of the device resulting from the installation of a gear mechanism, and can suppress an energy loss.SOLUTION: In a vehicle drive unit, an input member and an output member of a change gear are arranged on a first virtual axis, a counter gear mechanism is arranged on a third virtual axis, a counter input gear and a counter output gear which is smaller than the counter input gear in diameter are constituted so as to integrally rotate, a gear change output gear of the output member is engaged with the counter input gear, a differential input gear of a differential gear mechanism is engaged with the counter output gear, a rotating electric machine and an electric machine output gear of the rotating electric machine are arranged on a second virtual axis, and the electric machine output gear is made smaller than the counter input gear in diameter, and engaged with the counter input gear. The vehicle drive unit comprises an engagement device which can bring about a state that a rotor of the rotating electric machine and the electric machine output gear are connected to each other, and a state that the connection of these items is released.

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.
Further, even if the number of shafts is reduced and the vehicle drive device is downsized, the structure in which the rotating electrical machine and the internal combustion engine are always driven and connected, when the vehicle is driven only by the torque of the internal combustion engine, that is, the vehicle is driven. Even when the torque of the rotating electrical machine is not necessary for this, the rotor of the rotating electrical machine rotates. As a result, the energy of the internal combustion engine is lost, and there is a problem that the driving force transmitted from the internal combustion engine to the wheels can be reduced.

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

  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 The characteristic configuration of the vehicle drive device that includes a counter gear mechanism that decelerates and transmits the differential gear mechanism and a rotating electrical machine is such that the speed change device can change a speed change ratio, and Accordingly, the torque of the input member is converted and transmitted to the output member, the input member and the output member of the transmission are arranged on a first virtual axis, The counter gear mechanism is arranged on the second 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. Set on the output member The variable speed output gear meshed with the counter input gear, the differential input gear provided in the differential gear mechanism meshed with the counter output gear, and the electric machine output gear arranged on the second virtual shaft was An engagement device that is smaller in diameter than the counter input gear and meshes with the counter input gear, and is capable of realizing a state in which the rotor of the rotating electrical machine is connected to the electrical machine output gear and a state in which the connection is released. It is in the point provided.

  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 this 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.
Moreover, according to said characteristic structure, since the engagement apparatus which cancels | releases connection with a rotor and an electrical machinery output gear is provided, a rotary electric machine can be cut off from an internal combustion engine and a wheel. Therefore, for example, when driving a vehicle using only the torque of the internal combustion engine, such as during high-speed cruise, it is possible to suppress energy loss caused by rotating the rotor of the rotating electrical machine in a situation where the torque of the rotating electrical machine is unnecessary. it can.

  Here, a rotor shaft that rotates integrally with the rotor and an electric machine output gear shaft that rotates integrally with the electric machine output gear are provided, and the electric machine output gear shaft is formed in a cylindrical shape having an internal through hole penetrating in the axial direction. And at least a part of the transmission member that rotates in synchronization with one of the rotor shaft and the electric machine output gear shaft is inserted into the internal through-hole, and in the engaged state of the engagement device, the transmission member is It is preferable that the rotor shaft and the electric machine output gear shaft are connected via each other.

  According to this configuration, since the space inside the electric machine output gear shaft is effectively used as the space for arranging the transmission member, there is no need to separately provide the space for arranging the transmission member, and the vehicle drive device is enlarged. This can be suppressed.

  In addition, the transmission member is a moving engagement member configured to be movable in the axial direction of the second virtual axis and constituting a part of the engagement device, and the position of the moving engagement member in the axial direction Accordingly, it is preferable that the state in which the rotor shaft and the electric machine output gear shaft are connected and the state in which the connection is released are switched.

  According to this configuration, the rotor shaft and the electric machine output gear shaft can be switched between a connected state and a released state in which the connection is released with a relatively simple configuration.

  The rotor shaft has a cylindrical shape and first inner teeth are formed on the inner peripheral surface. The electric machine output gear shaft is cylindrical and has second inner teeth on the inner peripheral surface. The moving engagement member has a cylindrical shape or a columnar shape, and the first outer teeth and the first outer teeth are provided at different positions in the axial direction on the outer peripheral surface of the moving engagement member. A second external tooth is formed, and the first external tooth is one of the first internal tooth and the second internal tooth regardless of the position of the moving engagement member in the axial direction. Selective meshing that meshes with a constant meshing internal tooth, and the second external tooth is one of the first internal tooth and the second internal tooth according to the position of the moving engagement member in the axial direction. It is preferable to switch between the state engaged with the internal teeth and the state disengaged from the selected internal teeth.

  According to this configuration, the engagement device can be provided inside the rotor shaft and the electric machine output gear shaft. Therefore, for example, it is possible to suppress the location of the members disposed on the outer peripheral surface of the electric motor output gear shaft and the rotor shaft such as the electric motor output gear and the bearing, and to increase the size of the vehicle drive device. Can be suppressed.

  The engagement device is configured to operate by an engagement drive force. When the engagement drive force is not applied, the engagement device is connected to the rotor and the electric machine output gear. In a state where a force is applied, it is preferable that the engagement device is a normally closed type device in which the connection between the rotor and the electric machine output gear is released.

Generally, when the vehicle is driven only with the torque of the internal combustion engine, it is preferable to disconnect the rotating electrical machine from the internal combustion engine. In this case, since the internal combustion engine should be rotating at a certain high rotational speed, it is relatively easy to obtain the engagement driving force necessary for the engagement device. For example, when the engagement driving force is hydraulic, sufficient oil pressure is generated from the oil pump driven by the internal combustion engine. For example, when the engagement driving force is electromagnetic force, the power generation driven by the internal combustion engine is performed. Since sufficient power is generated from the machine, it is easy to obtain the necessary engagement driving force. On the other hand, the situation where the vehicle is driven by the torque of the rotating electrical machine includes a case where the internal combustion engine is stopped. When the internal combustion engine is stopped, it may be difficult to obtain sufficient engagement driving force as described above.
According to the above configuration, since the normally closed type engagement device is used, for example, when the vehicle is driven only by the torque of the internal combustion engine, that is, when the torque of the rotating electrical machine is not required, the rotor and the electrical output The connection with the gear is released. In this case, since the internal combustion engine should be rotating at a certain high rotational speed, the engagement driving force for releasing the connection can be easily obtained. On the other hand, for example, when the torque of the rotating electric machine is required, the rotor and the electric machine output gear are connected. According to the above configuration, the rotor and the electric machine output are not applied with the engagement driving force. Since the gear is connected, the rotor and the electric machine output gear can be connected even when it is difficult to obtain sufficient engagement driving force when the internal combustion engine is stopped. It becomes.
In this way, it is possible to realize a configuration in which the engagement device can be easily operated in accordance with the situation whether or not the torque of the rotating electrical machine is necessary.

  The transmission member is a through shaft that rotates integrally with the rotor shaft and penetrates the internal through hole in the axial direction, and the engaging device is on the opposite side of the through shaft from the rotor shaft side. It is preferable that the friction engagement device can connect the end portion and the electric machine output gear shaft.

  Generally, since the rotating electrical machine is larger than other members, the space on the side opposite to the rotor shaft side (rotating electrical machine side) with respect to the through shaft is relatively space rather than the vicinity of the space where the rotating electrical machine is disposed. There are many cases where there is a margin. According to the above configuration, since the friction engagement device can be disposed in the space opposite to the rotor shaft side with respect to the through shaft having a relatively sufficient margin, the space can be effectively utilized, and as a result. The enlargement of the vehicle drive device can be suppressed.

  The reduction ratio from the rotor to the differential input gear is preferably larger than the 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 device as 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 that

  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. It is an axial direction expanded sectional view of the rotation electrical machinery and engagement device concerning the 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. It is an axial direction expanded sectional view of the rotary electric machine and engagement device concerning other embodiments of the present invention. It is an axial direction expanded sectional view of the rotary electric machine and engagement device concerning other embodiments of the present invention. It is an axial direction expanded sectional view of the rotary electric machine and engagement device concerning other embodiments of the present invention. It is an axial direction expanded sectional view of the rotary electric machine and engagement device concerning other embodiments of the present invention.

[First embodiment]
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 is a counter gear mechanism CG, a rotating electrical machine MG, an output differential gear mechanism DF and an engagement in FIG. It is the figure which represented the part of the apparatus 50 by the axial direction expanded sectional view. FIG. 3 is an enlarged view of the rotating electric machine MG and the engaging device 50 in FIG. FIG. 4 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, a rotating electrical machine MG, and a rotation An engagement device 50 capable of realizing a state in which the electric machine MG and the counter gear mechanism CG are connected and a state in which the connection is released and a hydraulic control device 45 are provided. In the present embodiment, the transmission input shaft I is drivingly connected to the internal combustion engine ENG via the torque converter TC. In the present embodiment, the vehicle drive device 1 uses a meshing engagement device DG (dog clutch mechanism) as the engagement device 50.
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 corresponds to the “difference” in the present invention. It corresponds to "dynamic gear mechanism".

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 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. Specifically, the case CS includes a first case member CS1, a second case member CS2, and a third case member CS3, as shown in FIGS. The first case member CS1 houses main parts of the transmission TM, the counter gear mechanism CG, and the rotating electrical machine MG. The second case member CS2 accommodates a part of the counter gear mechanism CG, the output differential gear mechanism DF, the torque converter TC, and the damper DP. The third case member CS3 is formed so as to cover the ends of the rotating electrical machine MG and the transmission apparatus TM on the second axial direction X2 side.

<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 45.

  Next, the four shift speeds realized by the transmission apparatus TM will be described. FIG. 5 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. 6 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. 5 and 6, the first stage 1st is realized by 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 shown in FIG. 2, 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 rotating electrical machine MG is disposed on the second virtual axis A2. In the present embodiment, the stator St is fixed to a partition wall between the inner peripheral surface of the outer wall of the first case member CS1 and the transmission device TM.

  The rotor Ro is drivably coupled to the electric machine output gear GMo via the rotor shaft SR1, the meshing engagement device DG as the engagement device 50, and the electric machine output gear shaft SR2. In a state where the meshing engagement device DG is engaged, the rotor shaft SR1 and the electric machine output gear shaft SR2 are connected via the moving engagement member 21 (described later), and the rotor Ro and the electric machine output gear GMo are integrated. It will be in a rotating state. On the other hand, in a state where the meshing engagement device DG is released, the connection between the rotor shaft SR1 and the electric machine output gear shaft SR2 is released, and rotation and torque are not transmitted between the rotor Ro and the electric machine output gear GMo. .

  The rotor shaft SR1 has a cylindrical shape, and first inner teeth 26 are formed on the inner peripheral surface. In the present embodiment, the rotor shaft SR1 is cylindrical, and the first inner teeth 26 are formed on the inner peripheral surface of the end portion on the side of the first shaft direction X1 over the entire circumferential direction. Further, as shown in FIG. 3, the rotor shaft SR1 is supported by the case CS so as to be rotatable via the first rotor bearing 32 at both end portions in the axial direction. Specifically, the end of the rotor shaft SR1 on the side in the first axial direction X1 is radially outward from the second axial protrusion 35 of the support wall 31 of the first case member CS1 via the first rotor bearing 32. It is supported from. Further, the end of the rotor shaft SR1 on the side in the second axial direction X2 is an inner circumferential surface of the first shaft direction protrusion 43 formed integrally with the third case member CS3 via the first rotor bearing 32. Is supported from the outside in the radial direction.

  The electric machine output gear shaft SR2 is formed in a cylindrical shape having an internal through hole 36 penetrating in the axial direction, and second internal teeth 27 are formed on the inner peripheral surface. An electric machine output gear GMo is formed on the outer peripheral surface of the electric machine output gear shaft SR2. The electric machine output gear shaft SR2 is supported by the case CS so as to be rotatable via the second rotor bearing 33 at both ends in the axial direction. Specifically, as illustrated in FIG. 3, the end of the electric machine output gear shaft SR2 on the side in the second axial direction X2 is connected to the shaft first of the support wall 31 of the first case member CS1 via the second rotor bearing 33. The unidirectional protrusion 37 is supported from the outside in the radial direction. The end of the electric machine output gear shaft SR2 on the side in the first axial direction X1 is supported from the outer side in the radial direction by the second axial projection 44 provided on the second case member CS2 via the second rotor bearing 33. Yes.

  In addition, on the outer peripheral surface of the electric machine output gear shaft SR2, the electric machine output gear GMo is formed at a position adjacent to the first axial direction X1 side with respect to the arrangement region of the second rotor bearing 33 on the second axial direction X2 side. . In the present embodiment, the second internal teeth 27 are formed at positions on the inner peripheral surface of the electric machine output gear shaft SR2 that overlaps with the axial arrangement region of the electric machine output gear GMo in the radial direction. Further, since the rotor shaft SR1 and the electric machine output gear shaft SR2 are arranged on the second virtual axis A2, the electric machine output gear GMo is also arranged on the second virtual axis A2. The electric machine output gear GMo has a smaller diameter than the counter input gear GCi and meshes with the counter input gear GCi.

  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.

<Engagement device 50>
As described above, in the present embodiment, the meshing engagement device DG is used as the engagement device 50. In the present embodiment, as shown in FIG. 3, the meshing engagement device DG includes a moving engagement member 21, an elastic member 22, a disk-like member 23, a hydraulic chamber 24, and a shaft member 25. ing. The meshing engagement device DG uses the hydraulic pressure supplied to the hydraulic chamber 24 and the elastic force of the elastic member 22 to move the moving engagement member 21 in the axial direction, so that the moving engagement member 21 is moved in the axial direction. Depending on the position, engagement and release are switched. Then, the rotor shaft SR1 and the electric machine output gear shaft SR2 are connected in a state in which the meshing engagement device DG is engaged, and the rotor shaft SR1 and the electric machine output gear shaft SR2 in a state in which the meshing engagement device DG is released. The connection with is released. Hereinafter, a specific configuration of each member of the meshing engagement device DG in the present embodiment will be described. FIG. 3 shows different states between the upper side and the lower side across the second virtual axis A2, and a state where the meshing engagement device DG is engaged with the second virtual axis A2 on the upper side. And the meshing engagement device DG is disengaged below the second virtual axis A2.

  The moving engagement member 21 is cylindrical or columnar. The moving engagement member 21 of this embodiment is configured in a shape in which two cylindrical members having different diameters arranged on the same axis are connected. Specifically, the moving engagement member 21 includes a cylindrical large-diameter portion 30C having a large diameter, a cylindrical small-diameter portion 30B having a smaller diameter than the large-diameter portion 30C, and the axial direction of the large-diameter portion 30C. And a radially extending portion 30A that extends radially inward from one end portion and is connected to one axial end portion of the small diameter portion 30B. In the present embodiment, the radially extending portion 30A is an annular member that connects the end portion on the axial first direction X1 side of the large diameter portion 30C and the end portion on the axial second direction X2 side of the small diameter portion 30B. . In other words, in the present embodiment, the large-diameter portion 30C is disposed closer to the second axial direction X2 side than the small-diameter portion 30B. Then, the step portion 30 is formed by the large diameter portion 30C, the small diameter portion 30B, and the radially extending portion 30A. The inner peripheral surface of the large-diameter portion 30C and the surface on the axial second direction X2 side of the radially extending portion 30A are part of the members constituting the hydraulic chamber 24. Further, at least a part of the moving engagement member 21 is inserted into the internal through hole 36 of the electric machine output gear shaft SR2. In the present embodiment, the small diameter portion 30B of the moving engagement member 21 is inserted into the internal through hole 36 of the electric machine output gear shaft SR2.

  The moving engagement member 21 is a member that rotates in synchronization with either the rotor shaft SR1 or the electric machine output gear shaft SR2. Here, the first outer teeth 28 and the second outer teeth 29 provided at positions different from the first outer teeth 28 in the axial direction are formed on the outer peripheral surface of the moving engagement member 21. Further, the moving engagement member 21 is configured to be movable in the axial direction of the second virtual axis A2. The first external teeth 28 are always engaged with the second internal teeth 27 that are meshing internal teeth regardless of the position of the movement engaging member 21 in the axial direction, and the second external teeth 29 are engaged with the moving engagement member 21. In accordance with the position in the axial direction, the state is switched between the state engaged with the first internal tooth 26 which is the selective internal tooth and the state disengaged from the first internal tooth 26. In the present embodiment, the first outer teeth 28 are formed on the outer peripheral surface of the small diameter portion 30B inserted into the internal through hole 36 of the electric machine output gear shaft SR2, and the outer periphery of the large diameter portion 30C inserted into the rotor shaft SR1. Second external teeth 29 are formed on the surface. In addition, the arrangement area of the first external teeth 28 of the moving engagement member 21 is formed smaller than the arrangement area of the second internal teeth 27 of the electric machine output gear shaft SR2 in the radial direction. The second inner teeth 27 are formed over the entire movement range of the first outer teeth 28 accompanying the movement of the combined member 21. Accordingly, the first external teeth 28 are always engaged with the second internal teeth 27 regardless of the position of the moving engagement member 21 in the axial direction. Therefore, in this embodiment, the moving engagement member 21 is configured to rotate integrally with the electric machine output gear shaft SR2.

  Further, the moving engagement member 21 is moved from the first axial direction X1 side to the second axial direction X2 side, and the second external teeth 29 are completely engaged with the first internal teeth 26 that are selective meshing teeth. Thus, the rotor shaft SR1 and the electric machine output gear shaft SR2 are connected via the moving engagement member 21. That is, the meshing engagement device DG is engaged. The position in the axial direction of the moving engagement member 21 in the engaged state of the meshing engagement device DG is defined as an engaged state position. On the other hand, the moving engagement member 21 is moved from the second axial direction X2 side to the first axial direction X1 side, and the second external tooth 29 is completely disengaged from the first internal tooth 26. The connection with the output gear shaft SR2 is released. That is, the meshing engagement device DG is released. Further, the position in the axial direction of the moving engagement member 21 in the released state of the meshing engagement device DG is defined as a released state position. Note that, in the released state position, the end surface on the second axial direction X2 side of the electric machine output gear shaft SR2 and the surface on the first axial direction X1 side of the radial extending portion 30A are in contact.

  The elastic member 22 of the present embodiment is a compression coil spring. The elastic member 22 is disposed around the outer peripheral surface of the shaft member 25. The elastic member 22 is disposed between the moving engagement member 21 and the locking projection 38 of the shaft member 25 in the axial direction. The elastic member 22 moves to the first axial direction X1 side of the moving engagement member 21 by the movement engaging member 21 moving to the first axial direction X1 side by hydraulic pressure supplied to a hydraulic chamber 24 described later. The elastic member 22 is compressed by being pressed in the first axial direction X1 by the end portion. Thereby, the elastic member 22 urges the moving engagement member 21 in the second axial direction X2. When the oil is no longer supplied to the hydraulic chamber 24, the elastic member 22 expands by its own elastic force, and the end of the moving engagement member 21 on the first axial direction X1 side is moved to the second axial direction X2 side. Press. Thereby, the movement engagement member 21 moves to the axial second direction X2 side.

  The shaft member 25 rotates integrally with the electric machine output gear shaft SR2 and is accommodated in the internal through hole 36. In the present embodiment, the shaft member 25 has a cylindrical shape, and a first oil passage 41 is formed inside. Further, the end portion of the shaft member 25 on the side in the second axial direction X <b> 2 is fitted in a through hole formed in the disk-like member 23 that penetrates in the axial direction. A male screw portion is formed at the end of the shaft member 25 on the second axial direction X2 side, and the disk-like member 23 is moved in the second axial direction X2 with respect to the shaft member 25 by a nut screwed into the male screw portion. It is configured not to move relatively. The shaft member 25 has a radial through-hole penetrating in the radial direction at a position adjacent to the first mating direction X1 side with respect to the portion fitted to the disk-shaped member 23. The radial through hole is a second oil passage 42 that communicates the first oil passage 41 and the hydraulic chamber 24. Further, the shaft member 25 includes a fixed portion 39 fixed to the inner peripheral surface of the electric machine output gear shaft SR2 at the end portion on the first shaft direction X1 side. The outer peripheral surface of the shaft member 25 near the second oil passage 42 is a part of the hydraulic chamber 24.

  Further, the outer diameter of the portion excluding the locking protrusion 38 and the fixed portion 39 of the shaft member 25 is configured to be smaller than the inner diameter of the small diameter portion 30B of the moving engagement member 21, and the small diameter portion 30B of the moving engagement member 21 is The gap between the shaft member 25 and the electric machine output gear shaft SR2 is configured to be reciprocally movable in the axial direction. Further, the shaft member 25 has a locking projection 38. The locking projection 38 is formed as a protruding portion having a diameter larger than the diameter of the region of the shaft member 25 where the elastic member 22 is provided and smaller than the inner diameter of the electric machine output gear shaft SR2. Further, the end of the elastic member 22 abuts on the surface facing the second axial direction X2 side of the locking protrusion 38, and supports the elastic member 22 in the axial direction. A seal member is disposed between the moving engagement member 21 and the shaft member 25.

  The disk-shaped member 23 is one of the members that are attached to the end of the shaft member 25 on the side in the second axial direction X <b> 2 and form the hydraulic chamber 24. In the disk-shaped member 23 of the present embodiment, a through hole penetrating in the axial direction is formed in the central portion, and the shaft member 25 is fitted into the through hole. That is, the disk-shaped member 23 and the shaft member 25 are integrally formed. Further, the outer diameter of the disk-shaped member 23 is configured to be slightly smaller than the inner diameter of the large-diameter portion 30C, and there is a seal member between the outer peripheral surface of the disk-shaped member 23 and the inner peripheral surface of the large-diameter portion 30C. Has been placed. The inner peripheral surface of the large diameter portion 30 </ b> C is configured to be slidable in the axial direction with respect to the outer peripheral surface of the disk-like member 23. Further, the outer diameter of the disk-shaped member 23 is configured to be smaller than the inner diameter of the rotor shaft SR1, and the large-diameter portion 30C of the moving engagement member 21 passes through the gap between the disk-shaped member 23 and the rotor shaft SR1. Is configured to be capable of reciprocating in the axial direction. When the movable engagement member 21 moves to the engaged state position, the surface in the first axial direction X1 side of the disk-shaped member 23 and the second axial direction of the radial extending portion 30A of the movable engagement member 21 The surface on the X2 side is in contact.

  The hydraulic chamber 24 is a portion to which hydraulic pressure for adjusting the movement of the moving engagement member 21 in the axial direction is supplied. In the present embodiment, the hydraulic chamber 24 includes the surface of the disk-like member 23 on the first axial direction X1 side, the outer peripheral surface of the shaft member 25 near the second oil passage 42, and the radially extending portion 30A of the moving engagement member 21. Is formed in a space surrounded by the surface in the second axial direction X2 side and the inner peripheral surface of the large diameter portion 30C. As described above, seal members are disposed between these members, and the hydraulic chamber 24 is an oil-tight space. When oil discharged from an oil pump (not shown) is supplied to the hydraulic chamber 24 via the first oil passage 41 and the second oil passage 42, the radially extending portion is caused by the hydraulic pressure of the hydraulic chamber 24. 30A is pressed toward the first axial direction X1, and the movable engagement member 21 moves to the released state position. On the other hand, in a state where no oil is supplied to the hydraulic chamber 24, the moving engagement member 21 is pressed toward the second axial direction X2 side by the elastic force of the elastic member 22, and the moving engagement member 21 moves to the engagement state position. .

  As described above, the meshing engagement device DG of the present embodiment is configured to operate by hydraulic pressure, and connects the rotor shaft SR1 and the electric machine output gear shaft SR2 when the hydraulic pressure is not applied. The normally closed engagement device is in a state in which the connection between the rotor shaft SR1 and the electric machine output gear shaft SR2 is released when the hydraulic pressure is applied. Note that the hydraulic pressure supplied to the hydraulic chamber 24 of the present embodiment corresponds to the “engagement driving force” of the present invention.

<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.

<Hydraulic control device>
The hydraulic control device 45 is a device that controls the hydraulic pressure supplied to each engagement device of the vehicle drive device 1. In this embodiment, the hydraulic pressure supplied to each engagement device C1, C2, C3, B1, B2 and the meshing engagement device DG except the one-way clutch F1 of the transmission TM is controlled. Specifically, the hydraulic control device 45 adjusts oil discharged by an oil pump (not shown) to a predetermined hydraulic pressure level, and uses the adjusted pressure oil to each engagement device and meshing engagement of the transmission TM. Supply to the hydraulic chamber of the combined device DG. The hydraulic control device 45 of the present embodiment increases the hydraulic pressure supplied to the hydraulic chamber 24 of the meshing engagement device DG when the rotating electrical machine MG is disconnected from the internal combustion engine ENG and the wheels W.

2. Next, the overall configuration of the vehicle drive device 1 according to this 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.

[Second Embodiment]
The meshing engagement device DG of the first embodiment is arranged on the second axial direction X2 side of the elastic member 22 via the first oil passage 41 formed inside the cylindrical shaft member 25. Oil is supplied to the provided hydraulic chamber 24, and the movable engagement member 21 is moved from the second axial direction X2 side to the first axial direction X1 side to be released, and the second axial direction from the first axial direction X1 side. It was the structure which will be in an engagement state by moving to the direction X2 side. In contrast, as shown in FIG. 7, the meshing engagement device DG of the present embodiment uses a columnar shaft member 51 in which an oil passage is not formed instead of the cylindrical shaft member 25. The hydraulic engagement member 54 moves from the first axial direction X1 side to the second axial direction X2 side by supplying hydraulic pressure to the hydraulic chamber 52 disposed on the first axial direction X1 side of the elastic member 22. Thus, the engagement state is switched to the release state. The same members as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted here. FIG. 7 shows a state in which the meshing engagement device DG is released on the upper side with respect to the second virtual axis A2, and the meshing engagement device DG is engaged on the lower side with respect to the second virtual axis A2. It shows a state of matching.

  As shown in FIG. 7, the meshing engagement device DG of the present embodiment includes a shaft member 51, an elastic member 22, a hydraulic chamber 52, a disk-like member 53, and a moving engagement member 54. Yes.

  The moving engagement member 54 is the same in the configuration of the other portions except for the position in the axial direction where the second external teeth 55 are formed as compared with the moving engagement member 21 of the first embodiment. . In the present embodiment, the second external teeth 55 are formed on the outer peripheral surface on the axial second direction X2 side from the vicinity of the center in the axial direction of the large-diameter portion 30C of the moving engagement member 54.

  In the present embodiment, the moving engagement member 54 moves from the first axial direction X1 side to the second axial direction X2 side, and the second external teeth 55 are selected from the first internal teeth 57 that are selective meshing teeth. In a state where it is completely disengaged, the connection between the rotor shaft SR1 and the electric machine output gear shaft SR2 is released, and the meshing engagement device DG is released. On the other hand, the moving engagement member 54 moves from the second axial direction X2 side to the first axial direction X1 side, and the rotor shaft SR1 is in a state where the second external teeth 55 are completely engaged with the first internal teeth 57. Are connected to the electric machine output gear shaft SR2, and the meshing engagement device DG is engaged. The position in the axial direction of the moving engagement member 21 in this engaged state is defined as an engaged state position. In the engaged state position, the end surface on the second axial direction X2 side of the electric machine output gear shaft SR2 is in contact with the first axial direction X1 side surface of the radially extending portion 30A.

  The shaft member 51 has a cylindrical shape and is inserted into the internal through hole 36 of the electric machine output gear shaft SR2. In the present embodiment, a part of the shaft member 51 is fitted into the cylindrical moving engagement member 54, and the shaft member 51 and the moving engagement member 54 are within the internal through hole 36. Operates integrally. In addition, a disc-like member 53 is provided at the end of the electric machine output gear shaft SR2 on the side in the first axial direction X1 so as to close the internal through hole 36. The hydraulic chamber 52 is enclosed in a space surrounded by the surface on the second axial direction X2 side of the disk-shaped member 53, the end surface on the first axial direction X1 side of the shaft member 51, and the inner peripheral surface of the electric machine output gear shaft SR2. Is formed. The disk-like member 53 is provided with a through hole penetrating in the axial direction, and oil is supplied to the hydraulic chamber 52 through the through hole. The elastic member 22 is disposed around the outer peripheral surface of the shaft member 51. The elastic member 22 is, in the axial direction, between a locking projection 46 of the shaft member 51 that operates integrally with the moving engagement member 54 and a step formed on the inner peripheral surface of the electric machine output gear shaft SR2. It is arranged.

  When the hydraulic pressure is supplied to the hydraulic chamber 52, a force toward the second axial direction X2 acts on the end surface of the first axial direction X1 side of the axial member 51, and the axial member 51 moves from the first axial direction X1 side to the axial direction. It moves toward the second direction X2. Accordingly, the moving engagement member 54 that operates integrally with the shaft member 51 also moves in the second axial direction X2 side. When the second external teeth 55 are completely disengaged from the first internal teeth 57, the meshing engagement device DG is released, and the connection between the rotor shaft SR1 and the electric machine output gear shaft SR2 is released. At that time, the elastic member 22 is compressed by the movement of the shaft member 51. Thereby, the elastic member 22 biases the shaft member 51 in the first axial direction X1. On the other hand, when no hydraulic pressure is supplied to the hydraulic chamber 52, the elastic member 22 expands by its own elastic force, and the shaft member 51 and the moving engagement member 54 move from the second axial direction X2 side to the first axial direction X1 side. Moving. As a result, the second external teeth 55 mesh with the first internal teeth 57, the meshing engagement device DG is engaged, and the rotor shaft SR1 and the electric machine output gear shaft SR2 are connected.

[Third embodiment]
In the first and second embodiments described above, as the engagement device 50, the meshing engagement device DG that engages the rotor shaft SR1 and the electric machine output gear shaft SR2 via the moving engagement member 21 (54). The vehicle drive device 1 provided is described as an example. In the present embodiment, the vehicle drive device 1 including the friction engagement device CL will be described as an example of the engagement device 50 with reference to FIG. The friction engagement device CL of the present embodiment corresponds to the “friction engagement device” of the present invention. The same members as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted here.

  The vehicle drive device 1 of the present embodiment further includes a through shaft member 61 that passes through the internal through hole 36 of the electric machine output gear shaft SR2 in the axial direction. The penetrating shaft member 61 has a cylindrical shape (cylindrical in this example), and the end portion on the side in the second axial direction X2 is spline-fitted to the inner peripheral surface of the rotor shaft SR1. That is, the through shaft member 61 and the rotor shaft SR1 are configured to rotate integrally. Further, the through shaft member 61 is supported to be rotatable with respect to the inner peripheral surface of the electric machine output gear shaft SR2 via a bearing.

  The friction engagement device CL of the present embodiment is configured as a wet multi-plate clutch mechanism that operates by hydraulic pressure. The friction engagement device CL includes a clutch drum 62, a friction member 69, a clutch hub 70, a piston 67, a hydraulic chamber 68, and a return spring 71. The friction engagement device CL is configured to be able to connect the end portion of the penetrating shaft member 61 opposite to the rotor shaft SR1 side and the electric machine output gear shaft SR2. The through shaft member 61 corresponds to the “through shaft” of the present invention. As shown in FIG. 8, the friction engagement device CL of the present embodiment has a second case that is closer to the first axial direction X1 side than the cylinder portion 64 that is integrally formed with the first case member CS1 in the axial direction. The member CS2 is disposed at a position closer to the axial second direction X2 side than the partition wall 63. That is, the friction engagement device CL is disposed in the vicinity of the connection portion between the first case member CS1 and the second case member CS2.

  The clutch drum 62 is a member that supports the plurality of rotor Ro-side friction members 69 from the radially outer side. The clutch drum 62 includes an annular plate-like portion that extends in the radial direction between the friction member 69 and the partition wall 63 of the second case member CS2 in the axial direction, and a cylindrical portion that surrounds the radially outer side of the friction member 69. It is formed to have. The radially inner end of the annular plate-like portion of the clutch drum 62 is joined and connected to the end of the penetrating shaft member 61 on the first axial direction X1 side by welding or the like, and the clutch drum 62 and the penetrating shaft are connected. The member 61 is integrally formed. That is, the rotation and torque of the rotating electrical machine MG are transmitted to the clutch drum 62 via the through shaft member 61.

  The clutch hub 70 is a member that supports the plurality of electric output gear GMo-side friction members 69 from the radially inner side. The clutch hub 70 is connected to the electric machine output gear shaft SR2 by spline fitting. That is, the clutch hub 70 and the electric machine output gear shaft SR2 rotate integrally.

  The cylinder part 64 is a recessed part formed in the wall part of the first case member CS1 and facing the first axial direction X1 side. A piston 67 is disposed inside the cylinder portion 64 so as to be slidable along the axial direction with respect to the inner peripheral surface of the cylinder portion 64. A hydraulic chamber 68 is formed on the side of the piston 67 in the second axial direction X2. A seal member such as an O-ring is disposed between the piston 67 and the inner peripheral surface of the cylinder portion 64. Here, since the cylinder part 64 is formed integrally with the first case member CS1, the piston 67 does not rotate. Therefore, a thrust bearing is provided between the piston 67 and the friction member 69.

  A return spring 71 is provided on the radially outer side of the friction engagement device CL, and the piston 67 is urged toward the second axial direction X2. In the present embodiment, the piston 67 is configured to be pressed from the second axial direction X2 side by the hydraulic pressure supplied to the hydraulic chamber 68. Then, when hydraulic pressure is supplied to the hydraulic chamber 68, the piston 67 moves to the first axial direction X1 side, whereby the friction member 69 is also pressed to the first axial direction X1 side, and the friction engagement device CL is engaged. . As a result, the rotor shaft SR1 and the electric machine output gear shaft SR2 are connected and rotate integrally. On the other hand, when the hydraulic pressure is no longer supplied to the hydraulic chamber 68, the piston 67 moves to the second axial direction X2 side by the elastic force of the return spring 71, and the friction engagement device CL is released. As a result, the connection between the rotor shaft SR1 and the electric machine output gear shaft SR2 is released. The friction engagement device CL of the present embodiment is a normally open type that is in a released state when no hydraulic pressure is supplied to the hydraulic chamber 68, but the friction engagement device CL may be a normally closed type.

[Fourth embodiment]
In the present embodiment, the vehicle drive device 1 further including a speed reduction mechanism 81 between the rotor shaft SR1 and the electric machine output gear shaft SR2 will be described as an example. The same members as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted here. Note that FIG. 9 shows a state in which the meshing engagement device DG is engaged with the second virtual axis A2 on the upper side, and the meshing engagement device DG on the lower side with respect to the second virtual axis A2. Indicates the released state.

  In the present embodiment, as shown in FIG. 9, the rotor shaft SR <b> 1 has a shaft first direction protrusion 91 that protrudes closer to the shaft first direction X <b> 1 than the first rotor bearing 32 on the shaft first direction X <b> 1 side. In the rotor shaft SR1 of this embodiment, the sun gear S3 of the speed reduction mechanism 81 is integrally formed on the outer peripheral surface of the shaft first direction protruding portion 91 without providing the first inner teeth on the inner peripheral surface. The rotor shaft SR1 inputs the rotational driving force of the rotating electrical machine MG to the sun gear S3 of the speed reduction mechanism 81 during the power running of the rotating electrical machine MG, and the electrical engagement gear 83 connected to the carrier CA3. This is transmitted to the counter gear mechanism CG via the electric output gear GMo of the shaft SR2. Therefore, the rotation of the rotating electrical machine MG is first decelerated by the speed reduction mechanism 81, and then decelerated between the electrical machine output gear GMo and the counter input gear GCi, and further the counter gear mechanism CG and the output differential gear mechanism DF. The gear is decelerated with the input gear and transmitted to the output differential gear mechanism DF. Therefore, the rotation of the rotating electrical machine MG can be decelerated in three stages and transmitted to the output differential gear mechanism DF without providing a counter gear mechanism dedicated to the rotating electrical machine MG.

  The speed reduction mechanism 81 of the present embodiment is a single pinion type planetary gear mechanism that is arranged coaxially with the second virtual axis A2, the sun gear S3 is formed integrally with the rotor shaft SR1, and the carrier CA3 is moved and engaged. The ring gear R3 is fixed to the inner peripheral surface of the first case member CS1 (the axial first direction projecting portion 37).

  The electric machine output gear shaft SR2 is formed in a cylindrical shape having an internal through hole 36 penetrating in the axial direction, and second internal teeth 93 are formed on the inner peripheral surface. An electric machine output gear GMo is formed on the outer peripheral surface of the electric machine output gear shaft SR2.

  The meshing engagement device DG of this embodiment includes a moving engagement member 83 that engages or releases the rotor shaft SR1 and the electric machine output gear shaft SR2, and the moving engagement member 83 in the axial direction via the relay member 84. And a drive mechanism 85 to be moved.

  The moving engagement member 83 is a cylindrical member in which the fourth outer teeth 94 are formed on the outer peripheral surface and the third inner teeth 95 are formed on the inner peripheral surface. Then, the moving engagement member 83 is inserted into the internal through hole 36 of the electric machine output gear shaft SR2, and the fourth external teeth 94 are always engaged with the second internal teeth 93 of the electric machine output gear shaft SR2, thereby moving the engagement. The member 83 and the electric machine output gear shaft SR2 are configured to rotate integrally. Further, the movement engagement member 83 is configured to be movable in the axial direction in a state where the fourth external teeth 94 of the movement engagement member 83 and the second internal teeth 93 of the electric machine output gear shaft SR2 are always engaged. Yes. In addition, the moving engagement member 83 of the present embodiment has an axial length shorter than the axial length of the electric machine output gear shaft SR2, and the entire moving engagement member 83 is the electric machine output gear shaft as viewed in the radial direction. It arrange | positions so that it may be contained in the arrangement | positioning area | region of the axial direction of SR2. The moving engagement member 83 of this embodiment corresponds to the “transmission member” of the present invention.

  Further, the meshing engagement device DG of the present embodiment is provided integrally with the third internal tooth 95 of the moving engagement member 83 and the carrier CA3 as shown on the upper side with respect to the second virtual axis A2 of FIG. The engaged state is established when the external teeth are engaged with each other. Further, in the meshing engagement device DG of the present embodiment, as shown on the lower side with respect to the second virtual axis A2 in FIG. 9, the moving engagement member 83 is moved from the second axial direction X2 side to the first axial direction X1. When the third inner teeth 95 are moved to the side and brought into a disengaged state from the external teeth integrally provided on the carrier CA3, the released state is established.

  The drive mechanism 85 is a mechanism for moving the moving engagement member 83 in the axial direction, and includes a moving member 86, a first hydraulic chamber 87, a second hydraulic chamber 88, a partition member 89, and a cylindrical partition member. 90. The moving member 86 is a shaft member that can move in the axial direction. A relay member 84 is attached to the outer peripheral surface on the second axial direction X2 side of the central portion of the moving member 86 in the axial direction. The relay member 84 is a bearing, and the moving engagement member 83 is rotatable relative to the moving member 86. Further, the relay member 84 and the moving engagement member 83 are interlocked with the moving member 86 in the axial direction. The cylindrical partition wall member 90 is provided on the axial second direction X2 side with respect to the partition member 89 in the axial direction, extends in the axial direction, and extends in the radial direction to a space on the axial first direction X1 side. It is comprised from the partition part which divides | segments the space of the axial 2nd direction X2 side. The cylindrical partition wall member 90 is fixed to the second case member CS2. The partition member 89 has a cylindrical portion extending in the axial direction and a partition portion extending in the radial direction. The partition member 89 is attached to the moving member 86 and is configured to be movable in the axial direction together with the moving member 86.

  The second hydraulic chamber 88 is formed in a space surrounded by the partition wall portion of the cylindrical partition wall member 90, the inner peripheral surface of the second case member CS 2, and the partition portion of the partition member 89. A first hydraulic chamber 87 is formed in an adjacent space on the first axial direction X1 side with respect to the second hydraulic chamber 88 with the partition portion of the partition member 89 interposed therebetween. That is, the first hydraulic chamber 87 is formed in a space surrounded by the partition portion of the partition member 89 and the inner peripheral surface of the second case member CS2. A seal member is disposed between these members, and the first hydraulic chamber 87 and the second hydraulic chamber 88 are oil-tight spaces.

  When hydraulic pressure is supplied to the first hydraulic chamber 87, a force in the second axial direction X2 side acts on the partition member 89, and the partition member 89 and the moving member 86 move in the second axial direction X2 side. Then, the moving engagement member 83 is also moved to the second axial direction X2 side via the relay member 84, and the third inner teeth 95 formed on the inner peripheral surface of the movement engaging member 83 are carriers of the speed reduction mechanism 81. The meshing engagement device DG is engaged with the external teeth formed integrally with CA3. On the other hand, when hydraulic pressure is supplied to the second hydraulic chamber 88, a force in the first axial direction X1 side acts on the partition member 89, and the partition member 89 and the moving member 86 move in the first axial direction X1 side. To do. Then, the moving engagement member 83 also moves to the first axial direction X1 side via the relay member 84, and the third internal teeth 95 formed on the inner peripheral surface of the movement engaging member 83 become the carrier of the speed reduction mechanism 81. The meshing engagement with the external teeth integrally formed with CA3 is released, and the meshing engagement device DG is released.

[Fifth embodiment]
In the fourth embodiment, the vehicle includes the speed reduction mechanism 81 between the rotor shaft SR1 and the electric machine output gear shaft SR2, and the drive mechanism 85 that moves the moving engagement member 83 in the axial direction using hydraulic pressure. The drive device 1 has been described as an example. In the present embodiment, as shown in FIG. 10, a vehicle drive device 1 including a drive mechanism 100 that moves the moving member 102 in the axial direction using an electromagnetic actuator 101 instead of hydraulic pressure will be described as an example. The same members as those in the fourth embodiment are denoted by the same reference numerals, and description thereof is omitted here. FIG. 10 also shows a state in which the meshing engagement device DG is engaged with the second virtual axis A2 on the upper side, and the meshing engagement device DG on the lower side with respect to the second virtual axis A2. Indicates the released state.

  As shown in FIG. 10, the plunger portion 103 of the electromagnetic actuator 101 is attached to the outer peripheral surface of the moving member 102. On the other hand, the solenoid part 104 of the electromagnetic actuator 101 is fixed to the second case member CS2. When the coil of the solenoid unit 104 is excited, the plunger unit 103 moves in the axial direction, and the moving member 102 also moves in the axial direction via the plunger unit 103. A plurality of recesses (two in this example) are formed on the outer peripheral surface of the moving member 102 at different positions in the axial direction. The concave portion is a locking portion that holds the position of the moving member 102 in the axial direction at a fixed position, and is configured to accommodate a part of the holding member 107. The current flowing through the electromagnetic actuator 101 is controlled by a control device (not shown).

  In the present embodiment, the plunger portion 103 is fixed to the outer peripheral surface on the axial first direction X1 side with respect to the central portion of the moving member 102 in the axial direction. Further, on the outer peripheral surface of the moving member 102, a first concave portion 105 and a second concave portion 106 are formed in order from the axial first direction X1 side between the relay member 84 and the plunger portion 103 in the axial direction. In the present embodiment, the holding member 107 is a detent mechanism, and includes a spherical member that is urged radially inward by a spring. When the spherical member is fitted into one of the first recess 105 and the second recess 106, the holding member 107 locks the moving member 102 at one of the two positions. When the moving member 102 moves to the second axial direction X2 side by the electromagnetic actuator 101, the moving engagement member 83 and the carrier CA3 of the speed reduction mechanism 81 are connected, and the meshing engagement device DG is engaged. At this time, since the holding member 107 is fitted into the first recess 105, the axial position of the moving member 102 can be held at a position where the meshing engagement device DG is engaged. On the other hand, when the moving member 102 moves to the first axial direction X1 side by the electromagnetic actuator 101, the connection between the moving engagement member 83 and the carrier CA3 of the speed reduction mechanism 81 is released, and the meshing engagement device DG is released. Become. At this time, since the holding member 107 is fitted into the second recess 106, the axial position of the moving member 102 can be held at a position where the meshing engagement device DG is in the released state. Therefore, even when the current flowing to the coil is stopped, the engaged state or the released state of the meshing engagement device DG can be maintained, so that power consumption can be reduced.

[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. It is the side and is arrange | positioned in the space of the radial direction outer side of the transmission apparatus TM. 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. It is the side and is arrange | positioned in the space of the radial direction outer side of the transmission apparatus TM. 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.

(5) In the first embodiment described above, the constantly meshing internal tooth is the second internal tooth 27 provided on the electric machine output gear shaft SR2, and the selective meshing internal tooth is provided on the rotor shaft SR1. Teeth 26. However, the present invention is not limited to this. The constantly meshing internal teeth may be the first internal teeth 26, and the selective meshing internal teeth may be the second internal teeth 27. In this case, for example, the disposition area of the external teeth formed on the outer peripheral surface of the large-diameter portion 30C in the radial direction is formed smaller than the disposition area of the first internal teeth 26, and the moving engagement is performed. The first internal teeth 26 are formed over the entire movement range of the external teeth formed on the outer peripheral surface of the large diameter portion 30 </ b> C accompanying the movement of the member 21. Thereby, the external teeth formed on the outer peripheral surface of the large diameter portion 30 </ b> C always mesh with the first internal teeth 26 regardless of the position of the moving engagement member 21 in the axial direction. In this example, in this embodiment, the external teeth formed on the outer peripheral surface of the large-diameter portion 30C correspond to the first external teeth of the present invention, and the external teeth formed on the outer peripheral surface of the small-diameter portion 30B are the main teeth. This corresponds to the second external tooth of the invention.

(6) In the first embodiment described above, the normally closed type engagement device is used as the engagement device for executing engagement or release between the rotor shaft SR1 and the electric machine output gear shaft SR2. Embodiment of invention is not limited to this, The structure using a normally open type engaging device may be sufficient.

(7) In the first embodiment, the moving engagement member 21 has the large diameter portion 30C and the small diameter portion 30B. However, the embodiment of the present invention is not limited to this. For example, the moving engagement member 21 may be formed in a cylindrical shape having the same inner diameter over the entire axial direction.

  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)
DG: meshing engagement device (engagement device)
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 SR1: Rotor shaft SR2: Electric machine output gear shaft CL: Friction engagement devices 21, 54, 83: Moving engagement member (transmission member)
26: 1st internal tooth 27: 2nd internal tooth 28: 1st external tooth 29,55: 2nd external tooth 36: Internal through-hole 50: Engagement device 61: Through-shaft member (transmission member)

Claims (8)

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 differential input gear provided in the differential gear mechanism meshes with the counter output gear,
The electric machine output gear disposed on the second virtual axis has a smaller diameter than the counter input gear and meshes with the counter input gear,
The vehicle drive device provided with the engagement apparatus which can implement | achieve the state which connected the rotor and the said electrical machinery output gear of the said rotary electric machine, and the state which cancel | released these connections. A rotor shaft that rotates integrally with the rotor, and an electric machine output gear shaft that rotates integrally with the electric machine output gear,
The electric machine output gear shaft is formed in a cylindrical shape having an internal through hole penetrating in the axial direction,
At least a part of a transmission member that rotates in synchronization with any one of the rotor shaft and the electric machine output gear shaft is inserted into the internal through hole,
2. The vehicle drive device according to claim 1, wherein the rotor shaft and the electric machine output gear shaft are coupled via the transmission member when the engagement device is engaged. The transmission member is a movable engagement member configured to be movable in the axial direction of the second virtual axis and constituting a part of the engagement device;
3. The vehicle according to claim 2, wherein a state in which the rotor shaft and the electric machine output gear shaft are connected and a state in which the connection is released are switched according to the position of the moving engagement member in the axial direction. Drive device. The rotor shaft is cylindrical, and first inner teeth are formed on the inner peripheral surface,
The electric machine output gear shaft is cylindrical, and second inner teeth are formed on the inner peripheral surface,
The moving engagement member has a cylindrical shape or a columnar shape, and the first external teeth and the first external teeth are provided on the outer peripheral surface of the moving engagement member at positions different from each other in the axial direction. 2 external teeth are formed,
Regardless of the position of the moving engagement member in the axial direction, the first external tooth meshes with a constantly meshing internal tooth that is one of the first internal tooth and the second internal tooth,
The second external tooth meshes with a selective meshing internal tooth that is one of the first internal tooth and the second internal tooth according to the position of the moving engagement member in the axial direction, and the state The vehicle drive device according to claim 3, wherein the vehicle drive device is switched to a state of being disengaged from the selective meshing internal teeth.   The engagement device is configured to be operated by an engagement driving force. When the engagement driving force is not applied, the engagement device is in a state where the rotor and the electric machine output gear are connected, and the engagement driving force is 5. The vehicle drive device according to claim 1, wherein the vehicle drive device is a normally closed engagement device that is in a state in which the connection between the rotor and the electric machine output gear is released in an acted state. 6. The transmission member is a through shaft that rotates integrally with the rotor shaft and penetrates the internal through hole in the axial direction;
The vehicle drive device according to claim 2, wherein the engagement device is a friction engagement device capable of connecting an end portion of the penetrating shaft opposite to the rotor shaft side and the electric machine output gear shaft.   The vehicle drive device according to any one of claims 1 to 6, 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.   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 7.

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