JP2022156871A - Vehicular driving device - Google Patents

Abstract

To provide a vehicular driving device configured to comprise a rotation sensor for detecting rotation of a rotor of a rotating electric machine and an oil pump, whose dimension in an axial direction can be easily suppressed to be small.SOLUTION: An oil pump 7 comprises a pump rotor 71 arranged at a shaft different from a shaft of a rotor RT of a rotating electric machine MG. A transmitting mechanism 8 which transmits driving force of a rotating member RM provided in a power transmission passage joining the rotating electric machine MG to an output member to the oil pump 7 is arranged along a radial direction R so as to transmit power between the rotating member RM arrange concentrically with the rotating electric machine MG and the pump rotor 71. A sensor stator 21 of a rotary sensor 20 is arranged in a limited area in a circumferential direction to oppose in an axial direction L to a sensor rotor 22 of the rotary sensor 20, and also is arrange not to overlap with the transmitting mechanism 8 in view in the axial direction along the axial direction L, where an area in the axial direction L in which the sensor stator 21 is arranged and an area in the axial direction L in which the transmitting mechanism 8 is arranged overlap with each other.SELECTED DRAWING: Figure 2

Description

The present invention provides an input member that is drivingly connected to an internal combustion engine, an output member that is drivingly connected to wheels, a rotating electric machine, a transmission, and a fluid arranged in a power transmission path between the rotating electric machine and the transmission. The present invention relates to a vehicle drive device including a joint, a rotation sensor for detecting rotation of a rotor of a rotary electric machine, an oil pump, and a case accommodating them.

An example of such a vehicle drive system is disclosed in Patent Document 1 below. In the following descriptions of "Background Art" and "Problems to be Solved by the Invention," reference numerals in Patent Document 1 are quoted in parentheses.

A vehicle drive device (1) of Patent Document 1 includes a rotating electric machine (MG), a fluid coupling (TC), a rotation sensor (27) for detecting rotation of a rotor (22) of the rotating electric machine (MG), oil a pump (9); The rotation sensor (27) includes a sensor stator (27a) supported by the case (2) and a sensor rotor (27b) coupled to rotate integrally with the rotor (22).

JP 2011-106629 A

The sensor stator (27a) of the rotation sensor (27) is arranged between the rotor (22) of the rotary electric machine (MG) and the rotor (22) in the axial direction (the left side of FIG. 2 in Patent Document 1). (2) and the wall (4) in the axial direction. The sensor stator (27a) is supported by the wall (4). The sensor rotor (27b) of the rotation sensor (27) is arranged to face the sensor stator (27a) from the inside in the radial direction. The sensor rotor (27b) is coupled to rotate integrally with a rotor support member (23) that supports the rotor (22) of the rotary electric machine (MG). On the other hand, the oil pump (9) is coaxial with the rotor (22) and arranged on the side opposite to the side where the rotary electric machine (MG) is arranged across the fluid coupling (TC) in the axial direction. .

As described above, in the vehicle drive system (1) of Patent Document 1, the oil pump (9) and the rotation sensor (27) are arranged coaxially with each other at different positions in the axial direction. , it is necessary to ensure a large area in these axial directions. Therefore, the vehicle drive device (1) of Patent Document 1 has a configuration that tends to increase in size in the axial direction.

Therefore, it is desired to realize a vehicle driving device that can easily reduce the size in the axial direction in a configuration that includes a rotation sensor that detects rotation of a rotor of a rotary electric machine and an oil pump.

In view of the above, the characteristic configuration of the vehicle drive system is as follows.
an input member drivingly connected to an internal combustion engine;
an output member drivingly connected to the wheel;
a rotating electric machine having a rotor and functioning as a driving force source for the wheels;
a transmission that changes the speed of the rotation transmitted from the rotating electric machine and transmits it to the output member;
a fluid coupling arranged in a power transmission path between the rotating electric machine and the transmission;
a rotation sensor that detects rotation of the rotor;
an oil pump;
a transmission mechanism for transmitting a driving force of a rotating member provided in a power transmission path connecting the rotating electric machine and the output member to the oil pump;
a case that houses the rotating electric machine, the transmission, the fluid coupling, the rotation sensor, the oil pump, and the transmission mechanism,
The fluid coupling includes a pump impeller and a turbine runner that rotate relative to each other, and a rotary housing that accommodates the pump impeller and the turbine runner and is connected to the pump impeller so as to rotate integrally therewith. ,
The oil pump has a pump rotor arranged on a separate axis from the rotor,
A direction along the rotation axis of the rotor is defined as an axial direction, a direction orthogonal to the rotation axis is defined as a radial direction, and a direction around the rotation axis is defined as a circumferential direction,
The transmission mechanism is arranged along the radial direction so as to perform power transmission between the rotating member arranged coaxially with the rotating electric machine and the pump rotor,
The rotation sensor includes a sensor stator supported by the case, and a sensor rotor connected to rotate integrally with the rotor,
The sensor stator is arranged in a partial region in the circumferential direction so as to face the sensor rotor in the axial direction, and is arranged so as not to overlap the transmission mechanism when viewed in the axial direction along the axial direction. is,
The axial arrangement area of the sensor stator overlaps with the axial arrangement area of the transmission mechanism.

According to this characteristic configuration, the pump rotor of the oil pump is arranged on a separate axis from the rotor of the rotary electric machine. Therefore, compared to a configuration in which the pump rotor is arranged coaxially with the rotor of the rotary electric machine, it is easier to reduce the axial dimension of the vehicle drive device. In addition, according to this configuration, the sensor stator of the rotation sensor can be arranged using an axial region that overlaps with the axial arrangement region of the transmission mechanism for driving the pump rotor of the separate shaft. Specifically, since the sensor stator is not arranged in the entire circumferential direction, but is arranged in a part of the circumferential direction, the region does not overlap with the transmission mechanism when viewed in the axial direction along the axial direction. , the sensor stator can be arranged by utilizing the region overlapping the axial arrangement region of the transmission mechanism. This makes it easier to reduce the axial dimension of the vehicle drive device compared to a configuration in which the axial arrangement area of the sensor stator and the axial arrangement area of the transmission mechanism do not overlap. Therefore, in the configuration in which the vehicle drive device includes the rotation sensor for detecting the rotation of the rotor of the rotary electric machine and the oil pump, it is easy to reduce the axial dimension of the vehicle drive device.

1 is a schematic diagram showing a schematic configuration of a vehicle drive system according to an embodiment; Partial cross-sectional view along the axial direction of the vehicle drive device according to the embodiment Partial enlarged sectional view in FIG. Partial enlarged sectional view in FIG. Diagram showing the positional relationship between the rotation sensor and the transmission mechanism

A vehicle drive system 100 according to an embodiment will be described below with reference to the drawings. A vehicle drive system 100 according to the present embodiment is configured to be mounted on a front engine front drive (FF) vehicle.

As shown in FIG. 1, the vehicle drive system 100 is a system for driving a vehicle (hybrid vehicle) that uses one or both of an internal combustion engine EG and a rotating electric machine MG as a driving force source for wheels W. As shown in FIG. That is, the vehicle drive device 100 is configured as a drive device for a so-called one-motor parallel hybrid vehicle.

The rotary electric machine MG functions as a driving force source for the wheels W. As shown in FIG. The rotary electric machine MG includes a stator ST and a rotor RT. The rotary electric machine MG has a function as a motor (electric motor) that receives power supply and generates power, and a function as a generator (generator) that receives power supply and generates power. Therefore, the rotary electric machine MG is electrically connected to a power storage device (battery, capacitor, etc.). The rotary electric machine MG is powered by being supplied with electric power from the power storage device, or supplies electric power generated by the torque of the internal combustion engine EG or the inertial force of the vehicle to the power storage device and stores it.

The internal combustion engine EG functions as a driving force source for the wheels W, similar to the rotary electric machine MG. The internal combustion engine EG is a prime mover (gasoline engine, diesel engine, etc.) that is driven by combustion of fuel to take out power.

In the following description, the direction along the rotation axis of the rotor RT of the rotary electric machine MG is defined as "axial direction L". One side in the axial direction L is referred to as "first axial side L1", and the other side in the axial direction L is referred to as "second axial side L2". In the present embodiment, in the axial direction L, the side on which the internal combustion engine EG is arranged with respect to the rotary electric machine MG is defined as the first axial side L1, and the opposite side is defined as the second axial side L2. Further, the direction orthogonal to the rotation axis of the rotor RT of the rotary electric machine MG is defined as "radial direction R". In the radial direction R, the rotation axis side of the rotor RT is defined as "radial inner side R1", and the opposite side is defined as "radial outer side R2". Also, the direction around the rotation axis of the rotor RT is defined as "circumferential direction C". The direction of each member represents the direction when they are assembled to the vehicle drive device 100 . Also, the terms relating to the direction, position, etc. of each member are concepts that include the state of having a difference due to an allowable manufacturing error.

As shown in FIG. 1, the vehicle drive system 100 includes an input member 1, an output member 2, a transmission 3, a fluid coupling 5, and a case 9 in addition to the rotating electric machine MG. there is In this embodiment, the vehicle drive device 100 further includes a disconnecting engagement device 4, a counter gear mechanism CG, and a differential gear mechanism DF.

The input member 1 is drivingly connected to the internal combustion engine EG. It is preferable that the input member 1 is drivingly connected to an output shaft (crankshaft, etc.) of the internal combustion engine EG via a damper device (not shown) that damps fluctuations in transmitted torque.

Here, in the present application, "driving connection" refers to a state in which 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. It includes a state in which two rotating elements are connected so as to be able to transmit driving force via one or more transmission members. Such transmission members include various members that transmit rotation at the same speed or at different speeds, such as shafts, gear mechanisms, belts, and chains. The transmission member may include an engagement device for selectively transmitting rotation and driving force, such as a friction engagement device and a mesh type engagement device.

The disconnecting engagement device 4 is arranged in the power transmission path between the input member 1 and the rotary electric machine MG. The disconnecting engagement device 4 is an engagement device that connects and disconnects power transmission between the input member 1 and the rotary electric machine MG.

The transmission 3 is configured to change the speed of the rotation transmitted from the rotary electric machine MG side and transmit it to the output member 2 side. In this embodiment, the transmission 3 includes a transmission input shaft 31 as an input element of the transmission 3 and a transmission output gear 32 as an output element of the transmission 3 . As the transmission 3, for example, various known automatic transmissions such as a stepped automatic transmission capable of switching between a plurality of gear stages and a continuously variable automatic transmission capable of steplessly changing the gear ratio are available. Used.

A fluid coupling 5 is arranged in a power transmission path between the rotary electric machine MG and the transmission 3 . In this embodiment, the fluid coupling 5 is arranged on the second axial side L2 with respect to the rotary electric machine MG. The fluid coupling 5 has a pump impeller 51 , a turbine runner 52 and a rotary housing 54 . In this embodiment, the fluid coupling 5 is a torque converter further including a stator 53 and a lockup clutch 55 .

The pump impeller 51 and the turbine runner 52 are supported so as to rotate relative to each other. In this embodiment, the pump impeller 51 is arranged to face the turbine runner 52 in the axial direction L on the axial second side L2. Further, in this embodiment, the pump impeller 51 is connected to the rotary housing 54 so as to rotate integrally. The turbine runner 52 is connected to the speed change input shaft 31 of the transmission 3 so as to rotate integrally therewith.

The stator 53 is a member that straightens the flow of oil from the turbine runner 52 toward the pump impeller 51 . The stator 53 is arranged between the pump impeller 51 and the turbine runner 52 in the axial direction L.

A rotating housing 54 houses the pump impeller 51 and the turbine runner 52 . In this embodiment, the rotating housing 54 further houses the stator 53 . The rotating housing 54 is connected to rotate integrally with the pump impeller 51 . In this embodiment, the rotary housing 54 is also coupled to rotate integrally with the rotor RT of the rotary electric machine MG. Further, in the present embodiment, the rotary housing 54 is arranged on the axial second side L2 with respect to the rotor RT.

The lockup clutch 55 is configured to be changeable between a direct engagement state and a disengaged state. When the lockup clutch 55 is directly engaged, the pump impeller 51 and the turbine runner 52 rotate integrally. On the other hand, when the lockup clutch 55 is released, the pump impeller 51 and the turbine runner 52 transmit power via fluid. Thus, the lockup clutch 55 is an engagement device that connects and disconnects power transmission between the pump impeller 51 and the turbine runner 52 .

The counter gear mechanism CG includes a counter input gear G1 as an input element of the counter gear mechanism CG and a counter output gear G2 as an output element of the counter gear mechanism CG. The counter input gear G1 meshes with the transmission output gear 32 of the transmission 3 . The counter output gear G2 is connected to rotate integrally with the counter input gear G1. In this embodiment, the counter input gear G1 and the counter output gear G2 are connected via a counter shaft CS extending along the axial direction L so as to rotate integrally.

The differential gear mechanism DF has a differential input gear G3 that meshes with the counter output gear G2 of the counter gear mechanism CG. The differential gear mechanism DF distributes the rotation of the differential input gear G3 as an input element of the differential gear mechanism DF to the pair of output members 2 .

The output member 2 is drivingly connected to the wheels W. As shown in FIG. In this embodiment, each of the pair of output members 2 is drivingly connected to the wheel W via the drive shaft DS.

The case 9 houses the rotary electric machine MG, the transmission 3 and the fluid coupling 5 . In this embodiment, the case 9 also houses a pair of output members 2, a disconnecting engagement device 4, a counter gear mechanism CG, and a differential gear mechanism DF. Further, in the present embodiment, the case 9 accommodates the input member 1 so that the end of the input member 1 on the first axial side L<b>1 is exposed to the outside of the case 9 .

As shown in FIG. 2 , in this embodiment, the case 9 includes a peripheral wall portion 91 , a first side wall portion 92 , a second side wall portion 93 and a third side wall portion 94 .

The peripheral wall portion 91 is formed so as to cover the rotary electric machine MG and the radial outer side R2 of the fluid coupling 5 . The peripheral wall portion 91 is formed in a tubular shape extending in the axial direction L and the circumferential direction C. As shown in FIG. The first side wall portion 92 and the second side wall portion 93 are formed to extend radially inward R1 from the peripheral wall portion 91 . That is, the first side wall portion 92 and the second side wall portion 93 are formed so as to extend in the radial direction R and the circumferential direction C. As shown in FIG. The first side wall portion 92 is formed to cover the first axial side L1 of the rotary electric machine MG. The second side wall portion 93 is formed to cover the second axial side L2 of the fluid coupling 5 . The second side wall portion 93 corresponds to a “wall portion” arranged on the second side L2 in the axial direction with respect to the rotary housing 54 of the fluid coupling 5 and extending in the radial direction R and the circumferential direction C. As shown in FIG. The third side wall portion 94 is arranged on the second side L2 in the axial direction from the second side wall portion 93 . The third side wall portion 94 is formed to extend in the radial direction R and the circumferential direction C. As shown in FIG.

A stator ST of the rotary electric machine MG includes a stator core STC fixed to a non-rotating member (case 9 in this case). A rotor RT of the rotary electric machine MG includes a rotor core RTC that rotates relative to the stator ST. In this embodiment, each of the stator core STC and the rotor core RTC is formed by stacking a plurality of annular plate-shaped magnetic bodies (for example, electromagnetic steel sheets) in the axial direction L.

In the present embodiment, since the rotating electric machine MG is an inner rotor type rotating electric machine, the rotor core RTC is arranged radially inside R1 relative to the stator core STC.

Further, in the present embodiment, the rotating electrical machine MG is a rotating field type rotating electrical machine. Therefore, the stator coil is wound around the stator core STC so that coil end portions CE projecting from the stator core STC to both sides in the axial direction L (the first side L1 in the axial direction and the second side L2 in the axial direction) are formed. It is A permanent magnet (not shown) is provided in the rotor core RTC.

As shown in FIG. 2 , in this embodiment, the vehicle drive system 100 further includes an oil pump 7 , a transmission mechanism 8 , and a rotation sensor 20 . The oil pump 7 , transmission mechanism 8 and rotation sensor 20 are housed in a case 9 .

The oil pump 7 is a so-called mechanical oil pump that is driven by driving force transmitted through a power transmission path that connects the rotary electric machine MG and the output member 2 . The oil pump 7 has a pump rotor 71 arranged on a different axis from the rotor RT of the rotary electric machine MG. The pump rotor 71 is drivingly connected to the transmission mechanism 8 . In this embodiment, the pump rotor 71 is housed in a pump housing portion 95 provided in the case 9 .

The transmission mechanism 8 is configured to transmit the driving force of the rotating member RM to the oil pump 7 . That is, the transmission mechanism 8 performs power transmission between the rotating member RM and the pump rotor 71 . The rotating member RM is provided in a power transmission path that connects the rotating electric machine MG and the output member 2 . The rotating member RM is arranged coaxially with the rotating electric machine MG. In this embodiment, the rotary housing 54 of the fluid coupling 5 functions as the rotary member RM.

In this embodiment, the transmission mechanism 8 includes a first sprocket 81 , a second sprocket 82 , a chain 83 and a pump drive shaft 84 .

The first sprocket 81 is arranged to rotate about an axis along the axial direction L. As shown in FIG. In this embodiment, the first sprocket 81 is arranged coaxially with the rotary member RM (here, the rotary housing 54). The first sprocket 81 is connected to rotate integrally with the rotary member RM (here, the rotary housing 54). The second sprocket 82 is arranged to rotate about an axis along the axial direction L that is different from the rotation axis of the first sprocket 81 . That is, the second sprocket 82 is arranged apart from the first sprocket 81 in the radial direction R. A chain 83 is wound around the first sprocket 81 and the second sprocket 82 so as to rotate together. As described above, in the present embodiment, the first sprocket 81 and the second sprocket 82 that constitute the transmission mechanism 8 are arranged side by side along the radial direction R. A portion connecting the two sprockets 82 is arranged along the radial direction R. Therefore, the entire transmission mechanism 8 is arranged along the radial direction R. As shown in FIG. In this embodiment, the first sprocket 81 , the second sprocket 82 , and the chain 83 are arranged between the second side wall portion 93 and the third side wall portion 94 of the case 9 in the axial direction L.

The pump drive shaft 84 is drivingly connected to the pump rotor 71 . The pump drive shaft 84 is connected to rotate integrally with the second sprocket 82 . In the illustrated example, the pump drive shaft 84 and the second sprocket 82 are connected by spline engagement. In this embodiment, the pump drive shaft 84 is formed to extend from the second sprocket 82 to the axial second side L2. Therefore, in the present embodiment, the transmission mechanism 8 is arranged on the second side L2 in the axial direction with respect to the second side wall portion 93 .

In this embodiment, the pump drive shaft 84 is arranged so as to pass through the pump rotor 71 in the axial direction L. As shown in FIG. Portions of the pump drive shaft 84 that protrude from the pump rotor 71 to both sides in the axial direction L of the pump drive shaft 84 are rotatably supported with respect to the pump housing portion 95 of the case 9 . An end portion of the drive shaft 84 on the axial first side L<b>1 is rotatably supported with respect to the second side wall portion 93 of the case 9 .

Thus, in this embodiment, the first sprocket 81 rotates as the rotation housing 54 of the fluid coupling 5 rotates. As the first sprocket 81 rotates, the second sprocket 82 rotates via the chain 83, and the pump drive shaft 84 connected to the second sprocket 82 also rotates. As a result, the pump rotor 71 drivingly connected to the pump drive shaft 84 is driven.

In this embodiment, the pump rotor 71 is an internal gear pump. Therefore, pump rotor 71 includes an inner rotor 711 and an outer rotor 712 .

The inner rotor 711 is connected to the pump drive shaft 84 so as to rotate integrally therewith. In this embodiment, the inner rotor 711 is formed with a through hole penetrating in the axial direction L, and the pump drive shaft 84 is fitted into the through hole. The outer rotor 712 is arranged outside in the radial direction R with respect to the inner rotor 711 . Internal teeth formed on the inner peripheral surface of outer rotor 712 mesh with external teeth formed on the outer peripheral surface of inner rotor 711 . In this way, the outer rotor 712 also rotates because the inner rotor 711 rotates with the rotation of the pump drive shaft 84 .

The inner rotor 711 and the outer rotor 712 have eccentric rotation axes, and the radial distance R of the space sandwiched between the outer teeth of the inner rotor 711 and the inner teeth of the outer rotor 712 varies depending on the position in the circumferential direction. there is Therefore, the space sandwiched between the outer teeth of the inner rotor 711 and the inner teeth of the outer rotor 712 is, at each position in the circumferential direction, after the space in the radial direction R is gradually enlarged by the rotation of the inner rotor 711 and the outer rotor 712. It changes so that it gradually shrinks. As a result, the space sandwiched between the outer teeth of the inner rotor 711 and the inner teeth of the outer rotor 712 serves as a pump chamber whose volume changes as the inner rotor 711 and the outer rotor 712 rotate.

The rotation sensor 20 is a sensor that detects rotation of the rotor RT of the rotary electric machine MG. The rotation sensor 20 has a sensor stator 21 and a sensor rotor 22 .

The sensor stator 21 is supported by the case 9 . In this embodiment, the sensor stator 21 includes a stator body portion 211 and a stator fixing portion 212 . The stator main body 211 is arranged to face the sensor rotor 22 in the axial direction L. As shown in FIG. In this embodiment, the stator main body 211 is arranged to face the sensor rotor 22 from the axial second side L2. The stator fixing portion 212 is fixed to the case 9 . In this embodiment, the stator fixing portion 212 is fixed to the second side wall portion 93 of the case 9 .

The sensor rotor 22 is coupled to rotate integrally with the rotor RT of the rotary electric machine MG. That is, the sensor rotor 22 is rotatably supported relative to the sensor stator 21 . In this embodiment, the sensor rotor 22 is coupled to rotate integrally with the rotary housing 54 of the fluid coupling 5 . Further, in this embodiment, the sensor rotor 22 is arranged between the second side wall portion 93 of the case 9 and the rotary housing 54 in the axial direction L. As shown in FIG.

As shown in FIG. 3 , the disconnecting engagement device 4 includes a pair of first friction members 41 , a first piston portion 42 and a first hydraulic oil chamber 43 .

The pair of first friction members 41 are supported so as to be relatively rotatable. A pair of first friction members 41 includes a first inner friction material 411 and a first outer friction material 412 . In this embodiment, the first inner friction material 411 and the first outer friction material 412 are both formed in the shape of an annular plate and arranged coaxially with each other. In addition, in this embodiment, a plurality of first inner friction members 411 and a plurality of first outer friction members 412 are provided, and these are alternately arranged along the axial direction L. As shown in FIG. One of the first inner friction material 411 and the first outer friction material 412 can be a friction plate, and the other can be a separate plate.

The first piston portion 42 is a member that presses the pair of first friction members 41 so as to contact each other. The first hydraulic oil chamber 43 is configured to be supplied with oil for operating the first piston portion 42 . Therefore, the first piston portion 42 presses the first friction member 41 with pressure corresponding to the hydraulic pressure supplied to the first hydraulic oil chamber 43 .

The lockup clutch 55 includes a pair of second friction members 56 , a second piston portion 57 and a second hydraulic oil chamber 58 .

The pair of second friction members 56 are supported so as to be relatively rotatable. A pair of second friction members 56 includes a second inner friction material 561 and a second outer friction material 562 . In this embodiment, the second inner friction material 561 and the second outer friction material 562 are both formed in the shape of an annular plate and arranged coaxially with each other. In addition, in this embodiment, a plurality of second inner friction materials 561 and a plurality of second outer friction materials 562 are provided, and these are alternately arranged along the axial direction L. As shown in FIG. One of the second inner friction material 561 and the second outer friction material 562 can be a friction plate, and the other can be a separate plate.

The second piston portion 57 is a member that presses the pair of second friction members 56 so as to contact each other. The second hydraulic oil chamber 58 is configured to be supplied with oil for operating the second piston portion 57 . Therefore, the second piston portion 57 presses the second friction member 56 with pressure corresponding to the hydraulic pressure supplied to the second hydraulic oil chamber 58 .

In this embodiment, the disconnecting engagement device 4 and the lockup clutch 55 are arranged so as to overlap each other when viewed in the radial direction R. As shown in FIG. Further, in the present embodiment, both the disconnecting engagement device 4 and the lockup clutch 55 are arranged so as to overlap the rotor RT of the rotary electric machine MG when viewed in the radial direction R. Here, regarding the arrangement of two elements, "overlapping in a particular direction view" means that when a virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line, the virtual straight line is two It refers to the existence of at least a part of an area that intersects two elements. In other words, when viewed from a particular direction, two elements partially overlap each other, and one element entirely overlaps the other element, both of which correspond to the state of "overlapping."

In this embodiment, the disconnecting engagement device 4 is arranged radially inward R1 with respect to the rotor RT. The lockup clutch 55 is arranged radially inward R1 with respect to the disconnecting engagement device 4 . More specifically, the pair of first friction members 41, the first piston portion 42, and the first hydraulic oil chamber 43 in the disconnecting engagement device 4 are arranged radially inward R1 from the rotor RT. are placed. The pair of second friction members 56, the second piston portion 57, and the second hydraulic oil chamber 58 in the lockup clutch 55 are also arranged radially inward R1 from the rotor RT. Here, the positional relationship in the radial direction R between the disconnecting engagement device 4 and the lockup clutch 55 focuses on the positional relationship between the pair of friction members provided in each engagement device. That is, the entire pair of second friction members 56 of the lockup clutch 55 are arranged radially inward R1 from the pair of first friction members 41 of the disconnecting engagement device 4 . The second piston portion 57 and the second hydraulic fluid chamber 58 of the lockup clutch 55 are positioned radially inward R1 as a whole compared to the first piston portion 42 and the first hydraulic fluid chamber 43 of the disconnecting engagement device 4. Although they are arranged to be shifted, they are arranged so as to overlap when viewed in the axial direction along the axial direction L.

In this embodiment, the arrangement area of the first friction member 41 in the axial direction L and the arrangement area of the second friction member 56 in the axial direction L overlap each other. In the present embodiment, the "arrangement region of the first friction member 41 in the axial direction L" is the axial direction L of the first inner friction members 411 and the first outer friction members 412 that are alternately arranged along the axial direction L. refers to the entire placement area of Further, in the present embodiment, when the arrangement regions of two elements in the axial direction L overlap each other, at least part of the arrangement regions of the two elements in the axial direction L are arranged at the same position in the axial direction L. point to In the example shown in FIG. 3, the "arrangement area in the axial direction L of the first friction member 41" includes the end face of the first inner friction member 411 located on the second axial side L2, and It refers to the region between the end surface of the first outer friction material 412 on the first axial side L1 and the axial direction L1.

In addition, in the present embodiment, the “arrangement region of the second friction member 56 in the axial direction L” is the axial direction L of the second inner friction members 561 and the second outer friction members 562 that are alternately arranged along the axial direction L. refers to the entire placement area of In the example shown in FIG. 3, the "arrangement area of the second friction member 56 in the axial direction L" includes the end surface of the second inner friction member 561 located on the second axial side L2, It refers to the region between the axially first side L1 end face of the second outer friction material 562 positioned closest to the axially first side L1 in the axial direction L. In this example, the second friction material 411 positioned closest to the second axial side L2 is located on the second axial side L2 of the end surface of the first inner friction material 411 located closest to the second axial side L2. The end surface of the inner friction member 561 on the second axial side L2 is arranged. The first outer friction member 562 positioned closest to the first axial side L1 is located on the first axial side L1 of the end face of the second outer friction member 562 on the first axial side L1. An end surface of the friction material 412 on the first side L1 in the axial direction is arranged.

Further, in the present embodiment, the arrangement area of the first friction member 41 in the axial direction L overlaps the arrangement area of the rotor RT in the axial direction L. As shown in FIG. The arrangement area of the second friction member 56 in the axial direction L overlaps the arrangement area of the rotor RT in the axial direction L. As shown in FIG. In the present embodiment, the "arrangement region of the rotor RT in the axial direction L" is the magnetic body located closest to the first side L1 in the axial direction among the plurality of annular plate-shaped magnetic bodies constituting the rotor core RTC. It refers to a region between the end face on the first axial side L1 and the end face on the second axial side L2 of the magnetic body located closest to the second axial side L2 in the axial direction L.

In the example shown in FIG. 3, the first magnetic body positioned closest to the first axial side L1 is located on the second axial side L2 of the end face of the magnetic body located closest to the first axial side L1 in the axial direction L1. The end surface of the outer friction material 412 on the axial first side L1 is arranged. The first inner friction member 411 positioned closest to the second axial side L2 on the first axial side L1 of the end surface of the magnetic body on the second axial side L2 positioned on the second axial side L2. The end face on the second axial side L2 is arranged. In addition, in the example shown in FIG. 3 , the magnetic body is located on the second axial side L2 and closest to the first axial side L1 of the end surface of the magnetic body located on the first axial side L1 closest to the first axial side L1. The end face of the first outer friction material 412 on the axial first side L1 is arranged. Then, the second outer friction member 562 positioned closest to the first axial side L1 on the first axial side L1 of the end surface of the second axial side L2 of the magnetic body positioned closest to the second axial side L2. An end face on the first axial side L1 is arranged. Then, the second inner friction member 561 positioned closest to the second axial side L2 is located on the second axial side L2 of the end surface of the magnetic body positioned closest to the second axial side L2. The end face on the second axial side L2 is arranged.

A specific configuration for realizing the positional relationship between the rotor RT, the first engagement device CL1, and the second engagement device CL2 as described above will be described later.

In this embodiment, the disconnecting engagement device 4 further comprises a first inner support member 44 and a first outer support member 45 .

The first inner support member 44 supports one of the pair of first friction members 41 from the radial inner side R1. The first outer support member 45 supports the other of the pair of first friction members 41 from the radial outer side R2. In this embodiment, the first inner support member 44 supports the first inner friction material 411 from the radially inner side R1. The first outer support member 45 supports the first outer friction material 412 from the radial outer side R2.

In this embodiment, the first inner support member 44 includes a first inner engaging portion 441 and a first connecting portion 442 .

The first inner engaging portion 441 is formed to engage with one of the pair of first friction members 41 . In this embodiment, the first inner engaging portion 441 is formed in a tubular shape having an axial center along the axial direction L. As shown in FIG. In the present embodiment, although not shown, the first inner engaging portion 441 has a plurality of convex portions protruding radially outward R2 and concave portions protruding radially inner R1 alternately in the circumferential direction C. It has a shape arranged one by one. Each of these protrusions and recesses is formed to extend in the axial direction L. As shown in FIG. The inner peripheral portion of the first inner friction material 411 is formed so as to be engaged with these protrusions and recesses. Thus, in the present embodiment, the first inner friction member 411 engages with the first inner engaging portion 441 so that the first inner friction member 411 is axially rotated in a state where relative rotation with respect to the first inner engaging portion 441 is restricted. L is slidably supported.

The first connecting portion 442 connects the first inner engaging portion 441 and the rotor support member 10 so that the first inner engaging portion 441 rotates integrally with the rotor support member 10 . In this embodiment, the first connecting portion 442 is formed to extend along the radial direction R. As shown in FIG. More specifically, the first connecting portion 442 in this example is formed in an annular plate shape.

The rotor support member 10 is a member that supports the rotor RT of the rotary electric machine MG. In this embodiment, the rotor support member 10 is formed in a tubular shape having an axis along the axial direction L. As shown in FIG. The rotor support member 10 supports the rotor RT from the radially inner side R1 so as to rotate together with the rotor RT.

In the present embodiment, the end portion of the first inner engaging portion 441 on the axial second side L2 and the end portion of the first connecting portion 442 on the radial inner side R1 are connected to each other. The radially outer R2 end portion of the first connecting portion 442 and the axial second side L2 end portion of the rotor support member 10 are connected to each other. In the illustrated example, the first inner engaging portion 441, the first connecting portion 442, and the rotor support member 10 are integrally formed.

In this embodiment, the first outer support member 45 includes a first outer engaging portion 451 and a first radially extending portion 452 .

The first outer engaging portion 451 is formed to engage with the other of the pair of first friction members 41 . In this embodiment, the first outer engaging portion 451 is formed to engage with the first outer friction material 412 . Moreover, in this embodiment, the first outer engaging portion 451 is formed in a tubular shape having an axis along the axial direction L. As shown in FIG. The first outer engaging portion 451 is arranged radially inward R<b>1 from the rotor support member 10 . In the present embodiment, although not shown, the first outer engaging portion 451 has a plurality of convex portions protruding radially outward R2 and concave portions protruding radially inner R1 alternately in the circumferential direction C. It has a shape arranged one by one. Each of these protrusions and recesses is formed to extend in the axial direction L. As shown in FIG. The outer peripheral portion of the first outer friction material 412 is formed so as to be engaged with these protrusions and recesses. In this way, in the present embodiment, the first outer friction material 412 engages with the first outer engaging portion 451 so that the first outer engaging portion 451 is prevented from rotating relative to the first outer engaging portion 451 and is axially rotated. L is slidably supported.

The first radially extending portion 452 is formed to extend in the radial direction R. As shown in FIG. In this embodiment, the first radially extending portion 452 includes a first outer support portion 453 , a first inner support portion 454 and a first connection portion 455 .

The first outer support portion 453 supports the first piston portion 42 from the radial outer side R2. In this embodiment, the first outer support portion 453 is formed in a tubular shape having an axial center along the axial direction L. As shown in FIG. The first outer support portion 453 has an inner peripheral surface formed so that the first piston portion 42 can slide in the axial direction L. As shown in FIG. Further, in the present embodiment, the first outer supporting portion 453 is arranged radially inward R1 from the first outer engaging portion 451 . The end portion of the first outer support portion 453 on the second axial side L2 and the end portion of the first outer engaging portion 451 on the first axial side L1 are connected to each other. In the illustrated example, the first outer supporting portion 453 and the first outer engaging portion 451 are integrally formed.

The first inner support portion 454 is arranged radially inward R<b>1 from the first outer support portion 453 . The first inner support portion 454 supports the first piston portion 42 from the radial inner side R1. In this embodiment, the first inner support portion 454 is formed in an annular shape having an axial center along the axial direction L. As shown in FIG. The first inner support portion 454 has an outer peripheral surface formed so that the first piston portion 42 can slide in the axial direction L. As shown in FIG.

The first connection portion 455 is formed to connect the first outer support portion 453 and the first inner support portion 454 . In the present embodiment, the radially outer R2 end of the first connection portion 455 and the axially first side L1 end of the first outer support portion 453 are connected to each other. In addition, the radially inner R1 end of the first connecting portion 455 and the axially first side L1 end of the first inner supporting portion 454 are connected to each other. In the illustrated example, the first connection portion 455 and the first outer support portion 453 are integrally formed. The first connection portion 455 and the first inner support portion 454 are connected to each other by welding or the like.

In this embodiment, the lockup clutch 55 further includes a second inner support member 59 and a second outer support member 60 .

The second inner support member 59 supports one of the pair of second friction members 56 from the radial inner side R1. The second outer support member 60 supports the other of the pair of second friction members 56 from the radial outer side R2. In this embodiment, the second inner support member 59 supports the second inner friction material 561 from the radially inner side R1. The second outer support member 60 supports the second outer friction material 562 from the radial outer side R2.

In this embodiment, the second inner support member 59 includes a second inner engaging portion 591 and a second connecting portion 592 .

The second inner engaging portion 591 is formed to engage one of the pair of second friction members 56 . In this embodiment, the second inner engaging portion 591 is formed to engage with the second inner friction material 561 . Moreover, in this embodiment, the second inner engaging portion 591 is formed in a tubular shape having an axis along the axial direction L. As shown in FIG. In this embodiment, although not shown, the second inner engaging portion 591 has a plurality of convex portions protruding radially outward R2 and concave portions protruding radially inner R1 alternately in the circumferential direction C. It has a shape arranged one by one. Each of these protrusions and recesses is formed to extend in the axial direction L. As shown in FIG. The inner peripheral portion of the second inner friction material 561 is formed so as to be engaged with these protrusions and recesses. In this way, in the present embodiment, the second inner friction material 561 engages with the second inner engaging portion 591 so that the second inner friction member 561 is restricted in relative rotation with respect to the second inner engaging portion 591 and rotates in the axial direction. L is slidably supported.

The second connecting portion 592 connects the second inner engaging portion 591 and the turbine runner 52 so that the second inner engaging portion 591 rotates integrally with the turbine runner 52 of the fluid coupling 5 . In this embodiment, the second connecting portion 592 is formed to extend along the radial direction R. As shown in FIG. The radially outer R2 end of the second connecting portion 592 and the axially second side L2 end of the second inner engaging portion 591 are connected to each other. In the illustrated example, the second connecting portion 592 and the second inner engaging portion 591 are integrally formed.

In this embodiment, the second outer support member 60 includes a second outer engaging portion 601 and a second radially extending portion 602 .

The second outer engaging portion 601 is formed to engage with the other of the pair of second friction members 56 . In this embodiment, the second outer engaging portion 601 is formed to engage the second outer friction material 562 . Further, in this embodiment, the second outer engaging portion 601 is formed in a tubular shape having an axis along the axial direction L. As shown in FIG. The outer peripheral surface of the second outer engaging portion 601 is positioned so that the inner peripheral surface of the first inner engaging portion 441 of the first inner supporting member 44 extends from the radially inner side R1. arranged to face each other. In this embodiment, although not shown, the second outer engaging portion 601 has a plurality of convex portions protruding radially outward R2 and concave portions protruding radially inner R1 alternately in the circumferential direction C. It has a shape arranged one by one. Each of these protrusions and recesses is formed to extend in the axial direction L. As shown in FIG. The outer peripheral portion of the second outer friction material 562 is formed so as to engage with the protrusions and recesses. In this way, in the present embodiment, the second outer friction material 562 engages with the second outer engaging portion 601 so that the second outer engaging portion 601 is restricted in relative rotation with respect to the axial direction. L is slidably supported.

The second radially extending portion 602 is formed to extend in the radial direction R. As shown in FIG. The second radially extending portion 602 is arranged on the first side L1 in the axial direction with respect to the pair of second friction members 56 . Further, the second radially extending portion 602 is arranged on the second axial side L2 with respect to the first radially extending portion 452 . In this embodiment, the second radially extending portion 602 comprises a second outer support portion 603 , a second inner support portion 604 and a second connection portion 605 .

The second outer support portion 603 supports the second piston portion 57 from the radial outer side R2. In this embodiment, the second outer support portion 603 is formed in a tubular shape having an axial center along the axial direction L. As shown in FIG. The second outer support portion 603 has an inner peripheral surface formed so that the second piston portion 57 can slide in the axial direction L. As shown in FIG. Further, in the present embodiment, the second outer supporting portion 603 is arranged radially inward R1 from the second outer engaging portion 601 . The end portion of the second outer support portion 603 on the second axial side L2 and the end portion of the second outer engaging portion 601 on the first axial side L1 are connected to each other. In the illustrated example, the second outer supporting portion 603 and the second outer engaging portion 601 are integrally formed.

The second inner support portion 604 is arranged radially inward R<b>1 from the second outer support portion 603 . The second inner support portion 604 supports the second piston portion 57 from the radial inner side R1. In this embodiment, the second inner support portion 604 is formed in a tubular shape having an axial center along the axial direction L. As shown in FIG. The second inner support portion 604 has an outer peripheral surface formed so that the second piston portion 57 can slide in the axial direction L. As shown in FIG.

The second connection portion 605 is formed to connect the second outer support portion 603 and the second inner support portion 604 . In the present embodiment, the radially outer R2 end of the second connection portion 605 and the axially first side L1 end of the second outer support portion 603 are connected to each other. The radially inner end R1 of the second connecting portion 605 and the portion of the second inner supporting portion 604 protruding radially outward R2 from the outer peripheral surface on which the second piston portion 57 slides are connected to each other. there is In the illustrated example, the second connection portion 605 and the second outer support portion 603 are integrally formed. The second connection portion 605 and the second inner support portion 604 are connected to each other by welding or the like. As described above, in this example, the second outer support member 60 is provided so as to form part of the housing surrounding the space in which the pump impeller 51, turbine runner 52, and lockup clutch 55 are accommodated. The second outer support member 60 thus functions as part of the rotating housing 54 .

In this embodiment, the first piston portion 42 includes a first sliding portion 421 and a first pressing portion 422 .

The first sliding portion 421 is configured to slide in the axial direction L between the inner peripheral surface of the first outer support portion 453 and the outer peripheral surface of the first inner support portion 454 . In the illustrated example, the first sliding portion 421 includes an annular plate-shaped portion extending along the radial direction R and the circumferential direction C, an end portion of the radially inner side R1 of the annular plate-shaped portion and a radial and two cylindrical portions extending from each of the ends of the outer side R2 to the second side L2 in the axial direction.

In this embodiment, the first sliding portion 421 is arranged on the first side L1 in the axial direction with respect to the second radially extending portion 602 . The first sliding portion 421 is arranged so as to face the second radially extending portion 602 in the axial direction L. As shown in FIG.

The first pressing portion 422 presses the pair of first friction members 41 in the axial direction L so as to bring them into contact with each other. In this embodiment, the first pressing portion 422 is arranged on the first side L1 in the axial direction with respect to the first friction member 41 . In the illustrated example, the first pressing portion 422 extends from the cylindrical portion on the radially outer side R2 of the first sliding portion 421 toward the axial second side L2 and further extends to the radially outer side R2. is formed as

In this embodiment, the first hydraulic oil chamber 43 includes the first sliding portion 421 of the first piston portion 42, the first outer support portion 453, the first inner support portion 454 of the first outer support member 45, and the first inner support portion 454 of the first outer support member 45. 1 connecting portion 455. As shown in FIG.

In this embodiment, the second piston portion 57 includes a second sliding portion 571 and a second pressing portion 572 .

The second sliding portion 571 is configured to slide in the axial direction L between the inner peripheral surface of the second outer support portion 603 and the outer peripheral surface of the second inner support portion 604 . In the illustrated example, the second sliding portion 571 is formed in an annular plate shape extending along the radial direction R and the circumferential direction C. As shown in FIG.

The second pressing portion 572 presses the pair of second friction members 56 in the axial direction L so as to bring them into contact with each other. In this embodiment, the second pressing portion 572 is arranged on the first side L1 in the axial direction with respect to the second friction member 56 . In the illustrated example, the second pressing portion 572 is formed to protrude from a portion of the second sliding portion 571 that faces the second friction member 56 in the axial direction L to the second axial side L2.

In this embodiment, the second hydraulic oil chamber 58 includes the second slide portion 571 of the second piston portion 57, the second outer support portion 603, the second inner support portion 604 of the second outer support member 60, and the second inner support portion 604. 2 connecting portion 605.

In this embodiment, the first working oil chamber 43 and the second working oil chamber 58 are arranged so as to overlap each other when viewed in the axial direction L. As shown in FIG. Further, in the present embodiment, the arrangement area of the first hydraulic oil chamber 43 in the axial direction L overlaps the arrangement area of the rotor RT in the axial direction L. As shown in FIG. In the illustrated example, the entire arrangement area in the axial direction L of the first hydraulic oil chamber 43 is contained within the arrangement area in the axial direction L of the rotor RT. Further, in the present embodiment, the arrangement area of the second hydraulic oil chamber 58 in the axial direction L overlaps the arrangement area of the rotor RT in the axial direction L. As shown in FIG. In the illustrated example, the entire arrangement area in the axial direction L of the second hydraulic oil chamber 58 is contained within the arrangement area in the axial direction L of the rotor RT. Here, the arrangement area of the first hydraulic oil chamber 43 in the axial direction L changes depending on the operation of the first piston portion 42 . Similarly, the arrangement area of the second hydraulic oil chamber 58 in the axial direction L changes depending on the operation of the second piston portion 57 . In this embodiment, the arrangement region of the first hydraulic oil chamber 43 in the axial direction L is the first axial direction L of the first hydraulic oil chamber 43 in a state where the first hydraulic oil chamber 43 is also the largest in the axial direction L. It refers to the area between the end of the side L1 and the end of the second axial side L2 in the axial direction L. Similarly, the arrangement area of the second hydraulic oil chamber 58 in the axial direction L is the first axial side L1 of the second hydraulic oil chamber 58 in the state where the second hydraulic oil chamber 58 is also the largest in the axial direction L. and the end of the second axial side L2 in the axial direction L.

In this embodiment, the input member 1 includes an input tubular portion 11 and an input connecting portion 12 . The input tubular portion 11 is formed in a tubular shape having an axial center along the axial direction L. As shown in FIG. In this embodiment, the input tubular portion 11 is formed so as to cover the radially outer side R2 of the end portion of the shift input shaft 31 of the transmission 3 on the axial first side L1. The input connecting portion 12 is connected to rotate integrally with the first outer supporting member 45 . In this embodiment, the input coupling portion 12 is coupled to a first inner support portion 454 of a first radially extending portion 452 of the first outer support member 45 . In the illustrated example, the input connecting portion 12 is formed to protrude radially outward R2 from the end portion of the input tubular portion 11 on the second axial side L2. The input connection portion 12 is connected to the first inner support portion 454 by welding or the like. Thus, the input member 1 is connected to rotate integrally with the first outer support member 45 .

In this embodiment, the vehicle drive device 100 further includes a first bearing B1 and a second bearing B2. In this embodiment, the first bearing B1 and the second bearing B2 are arranged so as to overlap each other when viewed in the radial direction R. As shown in FIG.

The first bearing B<b>1 is a bearing that supports the rotor support member 10 with respect to the input member 1 so that the rotor support member 10 that supports the rotor RT rotates relative to the input member 1 . In this embodiment, the first bearing B1 is arranged between the first outer support portion 453 of the first radially extending portion 452 of the first outer support member 45 and the rotor support member 10 in the radial direction R. there is In the illustrated example, in the first bearing B1, the inner peripheral surface of the first bearing B1 and the outer peripheral surface of the first outer support portion 453 are in contact with each other, and the outer peripheral surface of the first bearing B1 and the inner surface of the rotor support member 10 are in contact with each other. It is arranged so as to be in contact with the peripheral surface. As described above, in this embodiment, the input member 1 is coupled to rotate integrally with the first outer support member 45 . Therefore, in this embodiment, the first bearing B<b>1 supports the rotor support member 10 to the input member 1 via the first outer support member 45 so that the rotor support member 10 rotates relative to the input member 1 . I support it.

The second bearing B<b>2 is a bearing that supports the input member 1 with respect to the case 9 so that the input member 1 rotates relative to the case 9 . In this embodiment, the second bearing B<b>2 includes the first inner support portion 454 of the first radially extending portion 452 of the first outer support member 45 and the bearing support portion 921 of the first side wall portion 92 of the case 9 . are arranged between the radial directions R of The bearing support portion 921 is formed in a tubular shape covering the radially outer side R2 of the input tubular portion 11 of the input member 1 . In this embodiment, the bearing support portion 921 is formed to protrude from the radially inner side R1 end portion of the first side wall portion 92 toward the axial second side L2.

In the illustrated example, the inner peripheral surface of the second bearing B2 and the outer peripheral surface of the bearing support portion 921 are in contact with each other, and the outer peripheral surface of the second bearing B2 and the inner peripheral surface of the first inner support portion 454 are in contact with each other. It is arranged so as to be in contact with the peripheral surface. As described above, in this embodiment, the input member 1 is coupled to rotate integrally with the first outer support member 45 . Therefore, in this embodiment, the second bearing B2 supports the input member 1 with respect to the case 9 via the first outer support member 45 so that the input member 1 rotates relative to the case 9. ing.

In this embodiment, the arrangement area in the axial direction L of the first hydraulic oil chamber 43 overlaps the arrangement area in the axial direction L of the first bearing B1. Further, the arrangement area in the axial direction L of the first hydraulic oil chamber 43 overlaps the arrangement area in the axial direction L of the second bearing B2.

As shown in FIG. 4, in this embodiment, the rotary housing 54 of the fluid coupling 5 includes a turbine housing portion 541, a pump housing portion 542, a radially extending portion 543, and a cylindrical portion 544. there is

The turbine housing portion 541 is formed so as to cover the turbine runner 52 . In the present embodiment, the turbine housing portion 541 has a radially outer R2 end portion located radially outwardly R2 relative to the turbine runner 52, and gradually becomes axially first radially inward R1. It is formed so as to be positioned on the side L1.

In this embodiment, the turbine housing portion 541 is coupled to rotate integrally with the second outer support member 60 . In the illustrated example, the radially inner end portion R1 of the turbine accommodating portion 541 and the axially second side L2 end portion of the second outer engaging portion 601 of the second outer support member 60 are welded to each other. Concatenated. Further, in the present embodiment, the turbine accommodating portion 541 is connected to rotate integrally with the first inner support member 44 . In the illustrated example, the turbine housing portion 541 and the first connecting portion 442 are connected to each other by welding or the like while the first connecting portion 442 is in contact with the turbine housing portion 541 from the axial direction first side L1. . Thus, in this embodiment, the second outer engaging portion 601 and the first connecting portion 442 are connected to each other through the turbine accommodating portion 541 so as to rotate integrally.

The pump accommodating portion 542 is formed so as to cover the pump impeller 51 . In the present embodiment, the pump accommodating portion 542 has a radially outer R2 end portion located radially outwardly R2 relative to the pump impeller 51, and gradually becomes axially second radially inward R1. It is positioned on the side L2, and is formed so as to be positioned gradually on the axial first side L1 as it goes radially inward R1. That is, in the present embodiment, the pump accommodating portion 542 extends outward in the axial direction L (here, the second axial side L2) from the accommodating chamber CM that accommodates the pump impeller 51 and the turbine runner 52 in the rotary housing 54. It corresponds to the "expansion part" formed so that it may expand.

The radially extending portion 543 is formed to extend along the radial direction R. As shown in FIG. In this embodiment, the radially extending portion 543 is formed to extend from the radially inner R1 end portion of the pump accommodating portion 542 toward the radially inner R1. In other words, in the present embodiment, the radially extending portion 543 is arranged closer to the first axial side L1 than the portion of the pump accommodating portion 542 located closest to the second axial side L2. In other words, the pump accommodating portion 542 is formed to swell from the radially extending portion 543 toward the axial second side L2.

The tubular portion 544 is formed in a tubular shape having an axis along the axial direction L. As shown in FIG. In the present embodiment, the cylindrical portion 544 is formed to extend from the radially inner side R1 end portion of the radially extending portion 543 toward the axial second side L2. Further, in the present embodiment, the cylindrical portion 544 is arranged so as to pass through the second side wall portion 93 of the case 9 in the axial direction L. As shown in FIG. The cylindrical portion 544 is rotatably supported with respect to the second side wall portion 93 via the third bearing B3. In addition, in the present embodiment, the first sprocket 81 of the transmission mechanism 8 is connected to a portion of the cylindrical portion 544 located on the axial second side L2 relative to the second side wall portion 93 . In the present embodiment, an engagement portion 544a in which unevenness is alternately formed along the circumferential direction C is provided in a portion of the cylindrical portion 544 located on the second side L2 in the axial direction relative to the second side wall portion 93. ing. An engaged portion 81a that engages with the engaging portion 544a is provided on the inner peripheral portion of the first sprocket 81. As shown in FIG. Thereby, the first sprocket 81 and the rotary housing 54 are connected so as to rotate integrally.

In this embodiment, the pump impeller 51 of the fluid coupling 5 has pump wings 511 . The pump blade portion 511 includes a plurality of pump blades arranged side by side in the circumferential direction C. As shown in FIG. In this embodiment, the pump vane portion 511 is coupled to rotate integrally with the pump accommodating portion 542 of the rotary housing 54 .

In this embodiment, the turbine runner 52 of the fluid coupling 5 includes a turbine blade portion 521 and a turbine support portion 522 . The turbine blade portion 521 includes a plurality of turbine blades arranged side by side in the circumferential direction C. As shown in FIG. The turbine support portion 522 is configured to extend radially inward R1 from the turbine blade portion 521 . In this embodiment, the turbine support portion 522 includes a support tubular portion 523 and a support connection portion 524 .

The support tubular portion 523 is formed in a tubular shape having an axis along the axial direction L. As shown in FIG. The support tubular portion 523 is arranged to cover the radially outer side R2 of the transmission input shaft 31 of the transmission 3 . The support tubular portion 523 is connected to the speed change input shaft 31 so as to rotate integrally therewith. In this embodiment, an inner peripheral spline engaging portion 523a is formed on the inner peripheral surface of the support tubular portion 523. As shown in FIG. On the other hand, an outer peripheral spline engaging portion 31a that engages with the inner peripheral spline engaging portion 523a is formed on the outer peripheral surface of the shift input shaft 31 . Thus, in the present embodiment, the inner spline engagement portion 523a and the outer spline engagement portion 31a are engaged with each other, so that the turbine runner 52 and the transmission input shaft 31 are connected so as to rotate integrally. there is

The support connection portion 524 is formed to connect the turbine blade portion 521 and the support tubular portion 523 . In this embodiment, the support connection portion 524 is formed to extend radially outward R2 from the support tubular portion 523 . The support connection portion 524 is connected to the turbine blade portion 521 and the second inner support member 59 so as to rotate together. In the illustrated example, the radially outer R2 end portion of the support connecting portion 524, the radially inner R1 end portion of the turbine blade portion 521, and the second connecting portion 592 of the second inner supporting member 59 are connected by rivets. connected to each other.

In this embodiment, the stator 53 of the fluid coupling 5 includes stator vane portions 531 and one-way clutch portions 532 . The stator blade portion 531 includes a plurality of stator blades arranged side by side in the circumferential direction C. As shown in FIG. The one-way clutch portion 532 is an engagement device that restricts rotation of the stator blade portion 531 with respect to the case 9 on one side in the circumferential direction C. As shown in FIG. In this embodiment, the one-way clutch portion 532 is arranged on the axial second side L2 with respect to the support connection portion 524 of the turbine support portion 522 . The one-way clutch portion 532 is arranged on the first side L1 in the axial direction with respect to the radially extending portion 543 of the rotary housing 54 . That is, in the present embodiment, the one-way clutch portion 532 is arranged between the support connecting portion 524 and the radially extending portion 543 in the axial direction L.

The one-way clutch portion 532 has an outer race 533 and an inner race 534 .

Outer race 533 is coupled to rotate integrally with stator vane 531 . The outer race 533 supports the stator blade portion 531 from the radially inner side R1. The outer race 533 is supported in a state in which relative rotation on one side in the circumferential direction C with respect to the inner race 534 is restricted and relative rotation on the other side in the circumferential direction C is permitted. In this embodiment, the outer race 533 is supported in the axial direction L so as to be relatively rotatable with respect to the support connecting portion 524 of the turbine support portion 522 via the fourth bearing B4. The outer race 533 is supported in the axial direction L so as to be relatively rotatable with respect to the radially extending portion 543 of the rotary housing 54 via the fifth bearing B5.

The inner race 534 is arranged radially inward R1 with respect to the outer race 533 . The inner race 534 is arranged radially outward R2 with respect to the support tubular portion 523 of the turbine support portion 522 . The inner race 534 is supported by an inner race support portion 96 provided on the case 9 . In this embodiment, the inner race support portion 96 is formed in a tubular shape having an axial center along the axial direction L. As shown in FIG. The inner race support portion 96 is connected to the inner race 534 and the third side wall portion 94 while being in contact therewith from the radially inner side R1.

As shown in FIG. 5, the sensor stator 21 of the rotation sensor 20 is arranged in a partial area in the circumferential direction C. As shown in FIG. In this embodiment, the stator main body portion 211 of the sensor stator 21 is formed in an arc shape along the circumferential direction C. As shown in FIG. Moreover, in this embodiment, the sensor rotor 22 is formed in the shape of an annular plate along the circumferential direction C. As shown in FIG. A plurality of protruding portions 22a that protrude radially inward R1 are formed on the inner peripheral portion of the sensor rotor 22 so as to be arranged in the circumferential direction C at regular intervals. The plurality of protruding portions 22a are arranged so as to face the stator body portion 211 of the sensor stator 21 in the axial direction L. As shown in FIG. With such a configuration, as the sensor rotor 22 rotates, the facing area between the sensor rotor 22 and the sensor stator 21 (here, the stator main body 211) changes periodically. In this embodiment, the rotation sensor 20 is an inductive sensor (inductive proximity sensor) that detects the rotation speed of the sensor rotor 22 based on changes in eddy current loss according to the facing area between the sensor rotor 22 and the sensor stator 21. is. In this example, the plurality of projecting portions 22a are formed on the inner peripheral portion of the sensor rotor 22, but the plurality of projecting portions 22a may be formed on the outer peripheral portion of the sensor rotor 22.

As shown in FIG. 5, the sensor stator 21 is arranged so as not to overlap the transmission mechanism 8 when viewed in the axial direction L. As shown in FIG. In this embodiment, the stator body 211 of the sensor stator 21 is arranged on the opposite side of the second sprocket 82 in the radial direction R with the first sprocket 81 of the transmission mechanism 8 interposed therebetween. The stator body portion 211 is formed in an arc shape along the outer shape of the first sprocket 81 .

2 and 4, the sensor stator 21 is arranged such that the arrangement area of the sensor stator 21 in the axial direction L and the arrangement area of the transmission mechanism 8 in the axial direction L overlap. In this embodiment, the arrangement area of the stator fixing portion 212 in the axial direction L overlaps the arrangement areas of the first sprocket 81 , the second sprocket 82 , the chain 83 , and the pump drive shaft 84 in the axial direction L. On the other hand, the arrangement area of the stator main body 211 in the axial direction L does not overlap with the arrangement area of the transmission mechanism 8 in the axial direction L. As shown in FIG.

As described above, the vehicle drive system 100
an input member 1 drivingly connected to the internal combustion engine EG;
an output member 2 drivingly connected to the wheel W;
a rotating electrical machine MG that includes a rotor RT and functions as a driving force source for the wheels W;
a transmission 3 that changes the speed of the rotation transmitted from the rotary electric machine MG and transmits it to the output member 2;
a fluid coupling 5 arranged in a power transmission path between the rotary electric machine MG and the transmission 3;
a rotation sensor 20 that detects the rotation of the rotor RT;
an oil pump 7;
a transmission mechanism 8 for transmitting the driving force of the rotary member RM provided in the power transmission path connecting the rotary electric machine MG and the output member 2 to the oil pump 7;
A case 9 that houses the rotary electric machine MG, the transmission 3, the fluid coupling 5, the rotation sensor 20, the oil pump 7, and the transmission mechanism 8,
The fluid coupling 5 includes a pump impeller 51 and a turbine runner 52 that rotate relative to each other, and a rotary housing 54 that accommodates the pump impeller 51 and the turbine runner 52 and is connected to the pump impeller 51 so as to rotate integrally. , and
The oil pump 7 has a pump rotor 71 arranged on a separate axis from the rotor RT,
The transmission mechanism 8 is arranged along the radial direction R so as to perform power transmission between the rotating member RM arranged coaxially with the rotary electric machine MG and the pump rotor 71,
The rotation sensor 20 includes a sensor stator 21 supported by the case 9 and a sensor rotor 22 connected to rotate integrally with the rotor RT,
The sensor stator 21 is arranged in a partial area in the circumferential direction C so as to face the sensor rotor 22 in the axial direction L, and is arranged so as not to overlap the transmission mechanism 8 when viewed in the axial direction L. is,
The arrangement area of the sensor stator 21 in the axial direction L and the arrangement area of the transmission mechanism 8 in the axial direction L overlap.

According to this configuration, the pump rotor 71 of the oil pump 7 is arranged on a separate axis from the rotor RT of the rotary electric machine MG. Therefore, compared to a configuration in which the pump rotor 71 is arranged coaxially with the rotor RT of the rotary electric machine MG, it is easier to reduce the dimension in the axial direction L of the vehicle drive device 100 . Further, according to this configuration, the sensor of the rotation sensor 20 can be detected by utilizing the region in the axial direction L that overlaps with the arrangement region in the axial direction L of the transmission mechanism 8 for driving the pump rotor 71 of the separate shaft. A stator 21 can be arranged. Specifically, since the sensor stator 21 is not arranged in the entire circumferential direction C, but is arranged in a partial region in the circumferential direction C, it overlaps with the transmission mechanism 8 when viewed in the axial direction L. The sensor stator 21 can be arranged by using the area where the transmission mechanism 8 is not arranged and overlaps with the arrangement area in the axial direction L of the transmission mechanism 8 . This makes it easier to reduce the dimension of the vehicle drive device 100 in the axial direction L compared to a configuration in which the arrangement region of the sensor stator 21 in the axial direction L and the arrangement region of the transmission mechanism 8 in the axial direction L do not overlap. Therefore, in the configuration in which the vehicle drive device 100 includes the rotation sensor 20 for detecting the rotation of the rotor RT of the rotary electric machine MG and the oil pump 7, it is easy to keep the dimension of the vehicle drive device 100 in the axial direction L small. It has become.

As shown in FIG. 4 , in this embodiment, the sensor rotor 22 is arranged so as to overlap the rotation housing 54 of the fluid coupling 5 when viewed in the axial direction L. As shown in FIG. Further, the sensor rotor 22 is arranged so as to overlap with the pump accommodating portion 542 of the rotary housing 54 when viewed in the radial direction R. As shown in FIG.

As described above, in the present embodiment, the rotary housing 54 has a pump accommodation portion as a bulging portion formed to bulge outward in the axial direction L from the accommodation chamber CM that accommodates the pump impeller 51 and the turbine runner 52. 542,
The sensor rotor 22 is arranged so as to overlap the rotary housing 54 when viewed in the axial direction L, and overlap the pump accommodating portion 542 when viewed in the radial direction R.

According to this configuration, the sensor rotor 22 of the rotation sensor 20 can be arranged using the region that overlaps with the rotary housing 54 when viewed in the axial direction and overlaps with the pump accommodating portion 542 of the rotary housing 54 when viewed in the radial direction. can. In other words, the sensor rotor 22 can be arranged using the space formed in the radially inner side R1 or the radially outer side R2 with respect to the pump accommodating portion 542 and overlapping the rotary housing 54 when viewed in the axial direction. . As a result, while suppressing an increase in the dimension of the vehicle drive device 100 in the radial direction R, compared to a configuration in which the sensor rotor 22 is arranged at a position shifted in the axial direction L with respect to the rotation housing 54 , the vehicle drive device 100 can be driven in a more efficient manner. It is easy to reduce the dimension of the device 100 in the axial direction L. Therefore, it is easy to keep the dimension of the vehicle drive device 100 in the axial direction L small.

In the present embodiment, the sensor rotor 22 is arranged radially inward R1 from a portion of the pump accommodating portion 542 that protrudes most outward in the axial direction L (here, the second axial side L2).

According to this configuration, the dimension of the sensor rotor 22 in the radial direction R is reduced compared to the configuration in which the sensor rotor 22 is arranged radially outward R2 from the portion of the pump accommodating portion 542 that protrudes most outward in the axial direction L. can be kept small. Therefore, it is easy to miniaturize the rotation sensor 20 in the radial direction R.

Further, in the present embodiment, the rotor RT is arranged on the first side L1 in the axial direction with respect to the rotary housing 54,
The rotation sensor 20 and the transmission mechanism 8 are arranged on the axial second side L2 with respect to the rotation housing 54 .

According to this configuration, the rotation sensor 20 and the transmission mechanism 8 are arranged on the side opposite to the rotor RT side of the rotary electric machine MG in the axial direction L with respect to the rotation housing 54 . As a result, the rotation sensor 20 and the transmission mechanism 8 can be arranged using a region that does not interfere with the rotary electric machine MG.

As shown in FIG. 4 , in this embodiment, the sensor stator 21 is arranged so as to pass through the second side wall portion 93 of the case 9 in the axial direction L. As shown in FIG. In the illustrated example, the stator fixing portion 212 of the sensor stator 21 is fixed to the second side wall portion 93 with a bolt while being in contact with the second side wall portion 93 from the axial second side L2. The stator fixing portion 212 extends from a fixed portion of the stator fixing portion 212 to the second side wall portion 93 to the axial direction first side L1 so as to pass through the second side wall portion 93 in the axial direction L. . In addition, the stator body portion 211 is connected to the end portion of the stator fixing portion 212 on the first side L1 in the axial direction.

As described above, in the present embodiment, the case 9 includes the second side wall portion 93 as a wall portion arranged on the axial second side L2 with respect to the rotation housing 54 and extending in the radial direction R and the circumferential direction C. prepared,
The sensor rotor 22 is arranged between the second side wall portion 93 and the rotation housing 54 in the axial direction L,
The sensor stator 21 is arranged to pass through the second side wall portion 93 in the axial direction L,
The transmission mechanism 8 is arranged on the second side L<b>2 in the axial direction with respect to the second side wall portion 93 .

According to this configuration, the sensor stator 21 is arranged so as to pass in the axial direction L through the second side wall portion 93 arranged between the sensor rotor 22 and the transmission mechanism 8 in the axial direction L. As shown in FIG. Therefore, even if the case 9 is configured to include the second side wall portion 93, the sensor stator 21, which overlaps the transmission mechanism 8 in the axial direction L, is appropriately arranged to face the sensor rotor 22 in the axial direction L. can be placed.
Further, according to this configuration, the sensor stator 21 can be arranged using the arrangement area of the second side wall portion 93 in the axial direction L. As shown in FIG. As a result, even if the case 9 is configured to include the second side wall portion 93 , it is possible to suppress an increase in size in the axial direction L of the vehicle drive device 100 due to the placement of the sensor stator 21 .

As shown in FIG. 5, in the present embodiment, the stator main body 211 of the sensor stator 21 is located above the rotational axis of the first sprocket 81 coaxially arranged with the rotor RT of the rotary electric machine MG when mounted on the vehicle. are placed in Further, in the present embodiment, the second sprocket 82 is arranged below the first sprocket 81 when mounted on the vehicle. Here, the “vehicle mounted state” refers to a state in which the vehicle drive device 100 is mounted in the vehicle. Note that the arrow "V" in FIG. 5 indicates the vertical direction of the vehicle drive device 100 in the vehicle-mounted state.

Thus, in this embodiment, the sensor stator 21 is arranged above the rotational axis of the rotor RT when mounted on the vehicle.

According to this configuration, sensor stator 21 is arranged at a relatively high position in vehicle drive device 100 . As a result, the oil in the case 9 can be configured to be less likely to adhere to the sensor stator 21 .
Further, according to this configuration, the through hole through which the sensor stator 21 penetrates in the second side wall portion 93 of the case 9 is also arranged at a relatively high position of the vehicle drive device 100 . As a result, it is possible to make it difficult for oil to travel through the space separated by the second side wall portion 93 inside the case 9 through the through hole of the second side wall portion 93 .

[Other embodiments]
(1) In the above embodiment, the arrangement area of the stator fixing portion 212 in the axial direction L overlaps the arrangement area of the transmission mechanism 8 in the axial direction L, and the arrangement area of the stator main body 211 in the axial direction L is the arrangement area of the transmission mechanism 8. A configuration that does not overlap with the arrangement area in the axial direction L has been described as an example. However, without being limited to such a configuration, it is sufficient that at least a portion of the sensor stator 21 is arranged in the axial direction L and at least a portion of the transmission mechanism 8 is arranged in the axial direction L. For example, the arrangement areas of both the stator body portion 211 and the stator fixing portion 212 in the axial direction L may overlap the arrangement area of the transmission mechanism 8 in the axial direction L. FIG. Alternatively, the arrangement area of the stator body 211 in the axial direction L overlaps with the arrangement area of the transmission mechanism 8 in the axial direction L, and the arrangement area of the stator fixing part 212 in the axial direction L is the arrangement area of the transmission mechanism 8 in the axial direction L. A non-overlapping configuration may also be used. Further, depending on the connection structure between the pump drive shaft 84 and the second sprocket 82, the sensor stator 21 overlaps the arrangement area of the first sprocket 81, the second sprocket 82, and the chain 83 in the axial direction L, and the pump A configuration that does not overlap the arrangement region of the drive shaft 84 in the axial direction L may be adopted.

(2) In the above embodiment, the stator main body 211 of the sensor stator 21 is arranged on the opposite side of the second sprocket 82 in the radial direction R across the first sprocket 81 of the transmission mechanism 8. The configuration has been described as an example. However, it is not limited to such a configuration. For example, the stator main body 211 of the sensor stator 21 is configured to be smaller than the illustrated example, and the stator main body 211 is arranged in an area surrounded by the first sprocket 81, the second sprocket 82, and the chain 83 when viewed in the axial direction. It's okay to be Even in this case, the sensor stator 21 does not overlap the transmission mechanism 8 when viewed in the axial direction L. It is possible to arrange the sensor stator 21 so as to overlap with the arrangement area.

(3) In the above-described embodiment, the transmission mechanism 8 includes the first sprocket 81, the second sprocket 82, and the chain 83 wound around them. However, without being limited to such a configuration, for example, the transmission mechanism 8 includes a first gear arranged coaxially with the rotary member RM (here, the rotary housing 54) and a radial direction R from the first gear. It is also possible to have a configuration in which a second gear is arranged apart from the gear and a third gear (idler gear) meshing with those gears. Also in such a configuration, the first gear, the second gear, and the third gear are arranged so as to line up along the radial direction R. Further, as the transmission mechanism 8, a belt may be used instead of the chain 83, and pulleys may be used instead of the first sprocket 81 and the second sprocket 82, respectively. Also in such a configuration, the pair of pulleys are arranged side by side along the radial direction R, and accordingly the portion of the belt that connects the pair of pulleys is arranged along the radial direction R. Therefore, the transmission mechanism 8 is arranged along the radial direction R also in these configurations.

(4) In the above embodiment, the sensor rotor 22 is arranged radially inward R1 from the portion of the pump accommodation portion 542 that protrudes most outward in the axial direction L (here, the axial second side L2), The configuration in which the pump storage portion 542 is arranged so as to overlap with the pump accommodation portion 542 when viewed in the radial direction R has been described as an example. However, without being limited to such a configuration, for example, a configuration in which the sensor rotor 22 is arranged radially outward R2 from the portion of the pump accommodating portion 542 that protrudes most outward in the axial direction L may be employed. Further, the sensor rotor 22 may be arranged so as not to overlap with the pump accommodating portion 542 when viewed in the radial direction R.

(5) In the above embodiment, the configuration in which the rotation sensor 20 and the transmission mechanism 8 are arranged on the side opposite to the rotor RT side of the rotary electric machine MG in the axial direction L with respect to the rotary housing 54 has been described as an example. . However, without being limited to such a configuration, at least one of the rotation sensor 20 and the transmission mechanism 8 may be arranged on the same side as the rotor RT side in the axial direction L with respect to the rotation housing 54 .

(6) In the above embodiment, the configuration in which the sensor stator 21 is arranged to pass through the second side wall portion 93 of the case 9 in the axial direction L has been described as an example. However, without being limited to such a configuration, for example, a configuration in which the case 9 does not include the second side wall portion 93 may be employed.

(7) In the above embodiment, the sensor stator 21 is arranged above the rotational axis of the rotor RT of the rotary electric machine MG in the vehicle-mounted state as an example. However, without being limited to such a configuration, the sensor stator 21 may be arranged below the rotational axis of the rotor RT in the vehicle-mounted state.

(8) It should be noted that the configurations disclosed in the respective embodiments described above can also be applied in combination with configurations disclosed in other embodiments unless there is a contradiction. Regarding other configurations, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications can be made as appropriate without departing from the scope of the present disclosure.

The technology according to the present disclosure is arranged in an input member that is drivingly connected to an internal combustion engine, an output member that is drivingly connected to wheels, a rotating electric machine, a transmission, and a power transmission path between the rotating electric machine and the transmission. The present invention can be used in a vehicle drive device that includes a fluid coupling that is connected to a motor, a rotation sensor that detects rotation of a rotor of a rotating electric machine, an oil pump, and a case that accommodates them.

100: Vehicle Drive Device, 1: Input Member, 2: Output Member, 3: Transmission, 5: Fluid Coupling, 51: Pump Impeller, 52: Turbine Runner, 54: Rotation Housing, 7: Oil Pump, 71: Pump Rotor 8: Transmission Mechanism 9: Case 20: Rotation Sensor 21: Sensor Stator 22: Sensor Rotor MG: Rotating Electric Machine RT: Rotor EG: Internal Combustion Engine W: Wheel L: Axial Direction R : Radial direction, C: Circumferential direction

Claims (5)

an input member drivingly connected to an internal combustion engine;
an output member drivingly connected to the wheel;
a rotating electric machine having a rotor and functioning as a driving force source for the wheels;
a transmission that changes the speed of the rotation transmitted from the rotating electric machine and transmits it to the output member;
a fluid coupling arranged in a power transmission path between the rotating electric machine and the transmission;
a rotation sensor that detects rotation of the rotor;
an oil pump;
a transmission mechanism for transmitting a driving force of a rotating member provided in a power transmission path connecting the rotating electric machine and the output member to the oil pump;
a case that houses the rotating electric machine, the transmission, the fluid coupling, the rotation sensor, the oil pump, and the transmission mechanism,
The fluid coupling includes a pump impeller and a turbine runner that rotate relative to each other, and a rotary housing that accommodates the pump impeller and the turbine runner and is connected to the pump impeller so as to rotate integrally therewith. ,
The oil pump has a pump rotor arranged on a separate axis from the rotor,
A direction along the rotation axis of the rotor is defined as an axial direction, a direction orthogonal to the rotation axis is defined as a radial direction, and a direction around the rotation axis is defined as a circumferential direction,
The transmission mechanism is arranged along the radial direction so as to perform power transmission between the rotating member arranged coaxially with the rotating electric machine and the pump rotor,
The rotation sensor includes a sensor stator supported by the case, and a sensor rotor connected to rotate integrally with the rotor,
The sensor stator is arranged in a partial region in the circumferential direction so as to face the sensor rotor in the axial direction, and is arranged so as not to overlap the transmission mechanism when viewed in the axial direction along the axial direction. is,
The vehicle drive device, wherein the axial arrangement area of the sensor stator and the axial arrangement area of the transmission mechanism overlap. The rotary housing has a bulging portion formed to bulge outward in the axial direction from a housing chamber housing the pump impeller and the turbine runner,
2. The vehicle drive according to claim 1, wherein the sensor rotor is arranged so as to overlap the rotary housing when viewed in the axial direction and overlap the bulging portion when viewed in the radial direction. Device. With one side in the axial direction as the first side in the axial direction and the other side in the axial direction as the second side in the axial direction,
The rotor is arranged on the first side in the axial direction with respect to the rotary housing,
3. The vehicle drive device according to claim 1, wherein said rotation sensor and said transmission mechanism are arranged on said second side in said axial direction with respect to said rotation housing. the case includes a wall portion arranged on the second side in the axial direction with respect to the rotary housing and extending in the radial direction and the circumferential direction;
the sensor rotor is disposed between the wall and the rotary housing in the axial direction;
The sensor stator is arranged to penetrate the wall in the axial direction,
4. The vehicle drive device according to claim 3, wherein said transmission mechanism is arranged on said second side in said axial direction with respect to said wall portion. 5. The vehicle drive device according to claim 4, wherein said sensor stator is arranged above said rotational axis of said rotor in a vehicle-mounted state.

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