JP2014065426A - Vehicular running gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicular running gear including an engagement device capable of coupling or decoupling an internal combustion engine and rotary electric machine while suppressing an increase in an axial-direction length of the entire running gear.SOLUTION: The whole of a power transfer PT is disposed radially inward of a distribution output member 21 while radially overlapping the distribution output member 21. A ring gear R is formed on an inner circumferential surface 21a of the distribution output member 21 as an integral part of the distribution output member 21, and an output gear 22 is formed on the peripheral surface 21b thereof as an integral part thereof. An output bearing 61 that bears the distribution output member 21 from radially inward is disposed on the side of an internal combustion engine beyond the ring gear R. At least part of an engagement device CL that couples or decouples a first input member I1 and second input member I2 which are separately formed is disposed radially inward of the output bearing 61 while radially overlapping the output bearing.

Description

  The present invention includes an input member drivingly connected to an internal combustion engine, a rotating electrical machine, a power distribution device that distributes and transmits torque of the input member to the rotating electrical machine and a distribution output member, and transmission to the distribution output member. The present invention relates to a vehicle drive device provided with an output gear provided so as to be able to output torque to be output to the wheel side.

  Japanese Patent Laying-Open No. 2000-217205 (Patent Document 1) discloses a vehicle drive device that uses an internal combustion engine and a rotating electrical machine as a driving force source of the vehicle. In the device (hybrid device) described in Patent Document 1, as shown in FIGS. 2 and 4 of Patent Document 1, the ring gear (R) serving as the output rotation element of the power distribution device (planetary gear unit 13) is It is integrally formed with the distribution output member on the inner peripheral surface of the distribution output member formed in a cylindrical shape. The distribution output member is connected to a sleeve-like member (output shaft 14) formed so as to surround the input member (output shaft 12) via a flange-like connecting member extending in the radial direction. The sleeve-like member is disposed on the engine side and radially inward in the axial direction with respect to the distribution output member. A counter drive gear (15) as an output gear is formed on the outer peripheral surface of the sleeve-like member at the end of the sleeve-like member on the engine side in the axial direction.

  The rotor and the distribution output member of the rotating electrical machine (generator motor 16), which are rotating members in the case (10), need to be rotatably supported by a non-rotating member such as a case. For this reason, these are each supported by the rotor bearing and the output bearing. Here, in the hybrid device described in Patent Document 1, an output bearing is disposed between the case and the sleeve-like member, and a rotor bearing is disposed between the case and the rotor shaft of the rotating electrical machine. The distribution output member is connected to the rotor shaft of the rotating electrical machine via a ring gear formed integrally with the distribution output member and other rotating elements of the power distribution device, and is connected to the sleeve-like member via the connection member. Has been. Thereby, the distribution output member is rotatably supported by the case via the rotor shaft and the rotor bearing of the rotating electrical machine, and the sleeve-like member and the output bearing. At this time, since the output bearing is disposed in contact with the outer peripheral surface of the sleeve-shaped member having a relatively small diameter, the output bearing having a relatively small diameter can be used. As a result, the cost of the output bearing is reduced, and the overall manufacturing cost of the vehicle drive device is reduced.

  By the way, in the hybrid device of Patent Document 1, since the rotating electrical machine and the engine are connected, when the vehicle is driven and driven only by the rotating electrical machine (when the vehicle is driven as a so-called EV (Electric Vehicle)), the driving force by the rotating electrical machine is used. As a result, the internal combustion engine is also rotated, causing power loss. In view of such a point, Japanese Patent Laying-Open No. 2010-76678 (Patent Document 2) discloses an engagement element that selectively connects an internal combustion engine and an input shaft (reference numeral “12” in FIG. 1 of Patent Document 2). ) Is disclosed. In this device, when the internal combustion engine is stopped, it is possible to prevent the internal combustion engine from being rotated by the driving force of the rotating electrical machine by opening the engagement element. However, when such an engagement element is simply added to the hybrid drive device of Patent Document 1, the length in the axial direction may be increased, which is not preferable for downsizing the device. .

JP 2000-217205 A JP 2010-76678 A

  In view of the above background, it is desired to provide a vehicle drive device including an engagement device capable of connecting or separating an internal combustion engine and a rotating electrical machine while suppressing an increase in the axial length of the entire device. .

In view of the above problems, the characteristic configuration of the vehicle drive device according to the present invention is as follows.
An input member drivingly connected to the internal combustion engine, a rotating electrical machine, a power distribution device that distributes and transmits torque of the input member to the rotating electrical machine and a distributed output member, and torque transmitted to the distributed output member An output gear provided so as to be capable of outputting to the wheel side, and a vehicle drive device comprising:
The power distribution device is entirely disposed so as to overlap with the distribution output member in the radial direction of the distribution output member as viewed in the radial direction, and the ring gear of the power distribution device is connected to the distribution output member. Provided integrally with the distribution output member on the inner peripheral surface,
The output gear is provided integrally with the distribution output member on the outer peripheral surface of the distribution output member,
The input member includes a first input member and a second input member in order from the internal combustion engine side along a power transmission path connecting the internal combustion engine and the power distribution device,
Further, the distribution output member is disposed on the internal combustion engine side in the axial direction of the distribution output member and on the radially inner side with respect to the distribution output member, and supports the distribution output member so as to be rotatable from the radially inner side. An output bearing to
A first case that includes a first case wall portion that extends radially on the internal combustion engine side relative to the output bearing in the axial direction, and that houses the distribution output member;
A first support portion provided integrally with the first case wall portion and supporting the output bearing from the radially inner side;
A second case which is disposed closer to the internal combustion engine than the first case wall and forms an accommodation space with the first case wall;
An engagement device that connects or separates the first input member and the second input member;
At least a part of the engagement device is disposed in the housing space and a space continuous therewith, at a position that is radially inward of the output bearing and overlaps the output bearing when viewed in the radial direction. It is in the point.

“Drive coupling” refers to a state in which two rotating elements are coupled so as to be able to transmit a driving force, and the two rotating elements are coupled so as to rotate integrally, or the two rotations. It is a concept including a state in which elements are connected so as to be able to transmit a driving force via one or more transmission members. The “rotary electric machine” is a concept including any of a motor (electric motor), a generator (generator), and a motor / generator that functions as both a motor and a generator as necessary. In addition, “overlap” in a certain direction for two members means that each of the two members has at least a portion at the same position with respect to the arrangement in the direction.

  According to the above-described characteristic configuration, the entire power distribution device is disposed so as to overlap with the distribution output member in the radial direction (direction orthogonal to the axis) on the radially inner side of the distribution output member. Therefore, the power distribution device can be arranged in the space occupied by the distribution output member in the axial direction. Further, since the output gear is integrally provided on the outer peripheral surface of the distribution output member, the output gear can also be arranged in the space occupied by the distribution output member in the axial direction. Therefore, the power distribution device and the output gear can be accommodated in the space occupied by the distribution output member, and the axial length of the space occupied by the distribution output member, the power distribution device, and the output gear can be shortened. In addition, since the output bearing that rotatably supports the distribution output member is arranged on the radially inner side of the distribution output member, the output gear can be connected to the outer peripheral surface of the distribution output member without being restricted by the axial position of the output bearing. Can be provided integrally. In other words, the degree of freedom regarding the axial position of the output gear can be increased. Therefore, in order to keep the axial accuracy of the distribution output member high, even when the output bearing is arranged so as to support the axial end of the distribution output member, the output gear is overlapped with the output bearing in the axial direction. Thus, the output gear can be arranged close to the axial end of the distribution output member. For this reason, for example, when there are components arranged on the downstream side of the power transmission path with respect to the output gear, these components are also appropriately controlled in the axial direction, such as being brought close to the axial end of the distribution output member. It can be easily placed in position. Furthermore, the engagement device that connects or separates the input member divided and formed into the first input member and the second input member is also an output bearing when at least a part thereof is radially inward of the output bearing and viewed in the radial direction. It is arranged at the position that overlaps. Therefore, even if such an engagement device is provided, it is possible to prevent the axial length of the entire device from increasing. As described above, according to this characteristic configuration, the axial length of the space occupied by each component disposed downstream of the distribution output member, the power distribution device, the output gear, the engagement device, and the output gear is effectively obtained. Can be shortened. That is, according to this characteristic configuration, it is possible to provide a vehicle drive device capable of reducing the axial dimension of the entire device.

  Here, as one aspect, the second input member includes an insertion hole that extends in the axial direction coaxially with the axial center of the second input member and opens at the end on the internal combustion engine side in the axial direction. An insertion end, which is one end of the first input member in the axial direction, is inserted into the insertion hole so as to be rotatable relative to the second input member, and the second input member is inserted into the first case wall. It is preferable that the first support member is rotatably supported by a second support portion formed radially inward of the first support portion, and the first input member is rotatably supported by the second case. is there. According to this configuration, the second input member is supported by the first case that forms the accommodation space that accommodates the engaging device, and the first input member is supported by the second case that forms the accommodation space together with the first case. The That is, since each input member is supported by a case that forms an accommodation space while having an engagement device that connects or separates the first input member and the second input member, each input member that is divided is supported. Therefore, it is possible to suppress an increase in the axial length. Furthermore, the second support part is formed radially inward of the first support part that supports the output bearing. Therefore, if the output bearing and the second support portion are arranged so as to overlap in the radial direction, the axial length can be further suppressed.

  Further, as one aspect, a vehicle drive device is disposed between the inner peripheral surface of the insertion hole and the outer peripheral surface of the insertion end portion, and the insertion end portion can be rotated relative to the insertion hole. It is preferable that an input bearing supported in the radial direction is provided, and the input bearing overlaps with the distribution output member when viewed in the radial direction. Since the first input member is supported by the input bearing arranged at a position overlapping the distribution output member when viewed in the radial direction and the second case on the internal combustion engine side than the distribution output member, the first input member is supported by a long support span. Therefore, stable support is possible.

Skeleton diagram of vehicle drive system Sectional view on a plane orthogonal to the axial direction (II-II sectional view of FIG. 3) An axially developed sectional view of a vehicle drive device Cross-sectional view of the main part of the vehicle drive device Sectional drawing of the principal part of the other structural example of the drive device for vehicles

  An embodiment of a vehicle drive device according to the present invention will be described with reference to the drawings. As shown in FIG. 1, this vehicle drive device 1 is a drive device for a hybrid vehicle that can travel using both an engine E (internal combustion engine) and a rotating electrical machine (MG1, MG2) as drive power sources. . The vehicle drive device 1 according to the present embodiment is disposed adjacent to the engine E placed horizontally in the vehicle in the width direction of the vehicle and in the axial direction of the output shaft (engine output shaft Eo) of the engine E. It is the drive device for FF (Front Engine Front Drive) vehicles of the connected composition.

  The vehicle drive device 1 is configured as a so-called two-motor split type drive device. The vehicle drive device 1 includes a first input shaft I (input member) connected to the engine E, a first rotating electrical machine MG1 having a first rotor Ro1, and a torque of the engine E transmitted to the input shaft I. A power distribution device PT that distributes and transmits to the rotating electrical machine MG1 and the distribution output member 21 and an output gear 22 that is capable of outputting torque transmitted to the distribution output member 21 to the wheel W side are provided. The distribution output member 21 and the output gear 22 are drivably coupled to the second rotating electrical machine MG2 via the counter gear mechanism C.

  As shown in FIGS. 3 and 4, the entire power distribution device PT is arranged in the radial direction of the distribution output member 21 so as to overlap with the distribution output member 21 in the radial direction, and the power distribution device PT of the power distribution device PT. The ring gear R is provided integrally with the distribution output member 21 on the inner peripheral surface 21 b of the distribution output member 21. The output gear 22 is provided integrally with the distribution output member 21 on the outer peripheral surface 21 a of the distribution output member 21. The input shaft I (input member) is divided into a first input member I1 and a second input member I2 in order from the engine E along a power transmission path connecting the engine E and the power distribution device PT. The first input member I1 and the second input member I2 are connected or separated by a clutch CL (engagement device). On the engine E side of the ring gear R in the axial direction of the distribution output member 21 and on the radial inner side of the distribution output member 21, an output bearing (described later) supports the distribution output member 21 so as to be rotatable from the radial inner side. A first output bearing 61 ") is arranged.

  A first front cover 11 (first case) that accommodates the distribution output member 21 is provided on the engine E side of the first output bearing 61 in the axial direction. The first front cover 11 includes a first case wall portion 4 that extends in the radial direction on the engine E side from the first output bearing 61 in the axial direction. The first case wall portion 4 is integrally provided with a first support portion 6 (an axial protruding portion) that supports the first output bearing 61 from the radially inner side. Further, the second front cover 12 (second case) is disposed on the engine E side of the first front cover (first case) with respect to the first case wall 4. A housing space (clutch housing space P2) is formed between the first case wall 4 and the second front cover 12. At least a part of the clutch CL is in the housing space (clutch housing space P2) and a space continuous with the housing space (clutch housing space P2), and is radially inward of the output bearing (first output bearing 61) and seen in the radial direction. It arrange | positions in the position which overlaps with an output bearing (1st output bearing 61).

  With such a configuration, an engagement device (clutch CL) capable of connecting or separating the engine E and the rotating electrical machine (particularly, the first rotating electrical machine MG1) while suppressing an increase in the axial length of the entire device. ) Is provided. Hereinafter, the configuration of the vehicle drive device 1 will be described in detail.

  As shown in FIGS. 1 and 3, the input shaft I (input member) is drivingly connected to the engine E. Here, the engine E is an internal combustion engine that is driven by the combustion of fuel. For example, various known engines such as a gasoline engine and a diesel engine can be used. In this example, a first input member I1 constituting the input shaft I is drivingly connected to an engine output shaft Eo such as a crankshaft of the engine E via a damper D, and the input shaft I (I1, I1, I2) is connected via a clutch CL. I2) is drivingly connected.

  The first rotating electrical machine MG1 and the second rotating electrical machine MG2 function as a motor (electric motor) that generates power by receiving power supply and function as a generator (generator) that generates power by receiving power supply. It is possible to fulfill The first rotating electrical machine MG1 and the second rotating electrical machine MG2 are electrically connected to a power storage device (not shown) (not shown). The battery is a power supply source when the rotating electrical machines (MG1, MG2) function as a motor, and a power supply destination when the rotating electrical machines (MG1, MG2) function as a generator. As the power storage device, it is preferable that a capacitor or the like be used in addition to the battery.

  The first rotating electrical machine MG1 includes a first stator St1 fixed to the exterior case 2 and a first rotor Ro1 that is rotatably supported on the radially inner side of the first stator St1. The first rotor Ro1 is drivably coupled to the sun gear S so as to rotate integrally with the sun gear S of the power distribution device PT. In the present embodiment, the first rotating electrical machine MG1 functions as a generator that generates power using the torque of the input shaft I (the torque of the engine E) mainly input via the power distribution device PT. The generated electric power is used for charging the battery and driving the second rotating electrical machine MG2. However, when the vehicle travels at a high speed or when the engine E is started, the first rotating electrical machine MG1 may also function as a motor that outputs power by driving.

  The second rotating electrical machine MG2 includes a second stator St2 fixed to the outer case 2 and a second rotor Ro2 that is rotatably supported on the radially inner side of the second stator St2. The second rotor Ro2 is drivingly connected to the gear so as to rotate integrally with the second rotating electrical machine output gear 37. In the present embodiment, the second rotating electrical machine MG2 mainly functions as a motor that assists the driving force for running the vehicle. However, when the vehicle decelerates, the second rotating electrical machine MG2 may function as a generator that generates power using the inertial force of the vehicle.

  In the present embodiment, the power distribution device PT is a single pinion type planetary gear mechanism arranged coaxially with the input shaft I. In other words, the power distribution device PT has three rotating elements: a carrier CA that supports a plurality of pinion gears, and a sun gear S and a ring gear R that mesh with the pinion gears. These three rotating elements included in the power distribution device PT are a sun gear S (first rotating element), a carrier CA (second rotating element), and a ring gear R (third rotating element) in order of rotation speed. The “order of rotational speed” is either the order from the high speed side to the low speed side, or the order from the low speed side to the high speed side, depending on the rotational state of the planetary gear mechanism constituting the power distribution device PT. Can be a friend. However, in any case, the rotation elements are arranged in the order of the rotation speed, the sun gear S (first rotation element), the carrier CA (second rotation element), and the ring gear R (third rotation element), and the order does not change. .

  The power distribution device PT distributes and transmits the torque of the engine E transmitted to the input shaft I to the first rotating electrical machine MG1 and the distribution output member 21. The carrier CA that is intermediate in the order of rotational speed is drivably coupled to the input shaft I (second input member I2) so as to rotate integrally with the input shaft I (second input member I2). Further, the sun gear S that is the lowest speed side or the highest speed side in the order of the rotation speed is arranged on the first rotor shaft 31 so as to rotate integrally with the first rotor shaft 31 of the first rotor Ro1 of the first rotating electrical machine MG1. Drive coupled. Further, the ring gear R that is on the side opposite to the sun gear in the order of the rotational speed (the highest speed side or the lowest speed side) is formed integrally with the distribution output member 21 as described above.

  In the vehicle drive device 1 according to the present embodiment, the torque in the positive direction of the engine E is transmitted to the carrier CA that is intermediate in the order of the rotational speed via the input shaft I, and the lowest speed or the most in the order of the rotational speed. A negative torque output from the first rotating electrical machine MG1 is transmitted to the sun gear S2 on the high speed side via the first rotor shaft 31. The torque in the negative direction of the first rotating electrical machine MG1 functions as a reaction force receiver for the torque of the engine E, so that the power distribution device PT is one of the torques of the engine E transmitted to the carrier CA via the input shaft I. Is distributed to the first rotating electrical machine MG1, and torque attenuated with respect to the torque of the engine E is transmitted to the distribution output member 21 via the ring gear R.

  In the present embodiment, the distribution output member 21 is a cylindrical member provided so as to surround the radially outer side of the power distribution device PT. As shown in FIG. 4, the ring gear R of the power distribution device PT is formed integrally with the distribution output member 21 on the inner peripheral surface 21 b of the distribution output member 21. An output gear 22 is formed integrally with the distribution output member 21 on the outer peripheral surface 21 a of the distribution output member 21. That is, in the present embodiment, the ring gear R and the output gear 22 of the power distribution device PT are integrally formed on the inner peripheral surface and the outer peripheral surface of the distribution output member 21. Thereby, the torque transmitted to the distribution output member 21 via the ring gear R of the power distribution device PT can be output to the wheel W side via the output gear 22.

  As shown in FIG. 3, the vehicle drive device 1 according to the present embodiment further includes a counter gear mechanism C. The counter gear mechanism C reverses the rotation direction of the output gear 22 and further transmits the torque output from the output gear 22 to the wheel W side. The counter gear mechanism C includes a counter shaft 41, a first gear 42, and a second gear 43. The first gear 42 meshes with the output gear 22. Further, the first gear 42 meshes with the second rotating electrical machine output gear 37 at a position different from the output gear 22 in the circumferential direction. The second gear 43 meshes with a differential input gear 46 included in an output differential gear device DF described later (see FIG. 1). Therefore, the counter gear mechanism C reverses the rotation direction of the output gear 22 and the second rotating electrical machine output gear 37 and outputs the torque transmitted to the output gear 22 and the torque of the second rotating electrical machine MG2 to the output differential gear device. Communicate to DF.

  As shown in FIG. 1, the output differential gear device DF has a differential input gear 46, and distributes torque transmitted to the differential input gear 46 to a plurality of wheels W for transmission. For example, the output differential gear device DF is a differential gear mechanism that uses a plurality of bevel gears that mesh with each other. The output differential gear unit DF distributes the torque transmitted to the differential input gear 46 via the second gear 43 of the counter gear mechanism C, and transmits the torque to the two left and right wheels W via the axle O, respectively. At this time, the output differential gear device DF transmits the rotation to the wheel W while reversing the rotation direction of the second gear 43. Thereby, the vehicle drive device 1 rotates the wheel W in the same direction as the rotation direction of the input shaft I (engine E) during forward travel, and is the same as the input shaft I (engine E) and the second rotating electrical machine MG2. The vehicle is driven by transmitting the direction torque to the wheels W.

  In the vehicle drive device 1 according to this embodiment, the input shaft I, the power distribution device PT, and the first rotating electrical machine MG1 are arranged as shown in FIG. 2 which is a cross-sectional view taken along the line II-II of FIG. The first axis A1, the second axis A2 where the second rotating electrical machine MG2 is arranged, the third axis A3 where the output differential gear device DF is arranged, and the fourth axis A4 where the counter gear mechanism C is arranged, respectively. A four-axis configuration provided separately. The first axis A1, the second axis A2, the third axis A3, and the fourth axis A4 are arranged in parallel to each other. In the present embodiment, the first axis A1, the second axis A2, and the third axis A3 are viewed from the direction along the axial direction (on the axis orthogonal plane) so that the line connecting these axes forms a triangle. The fourth axis A4 is arranged inside the triangle as viewed from the direction along the axial direction (in the axis orthogonal plane).

  The input shaft I (I1, I2), the first rotating electrical machine MG1, the second rotating electrical machine MG2, the power distribution device PT, the distribution output member 21, the output gear 22, the counter gear mechanism C, and the output differential gear device DF described above. Is housed in the outer case 2. As shown in FIG. 3, in the present embodiment, the exterior case 2 includes a case main body 2a and a first front cover attached to one side of the case main body 2a in the axial direction (the right side in FIG. 3, the axial engine side). 11 (first case), a second front cover 12 (second case) attached to the axial engine side, the first front cover 11 and the second front cover 12 so as to enclose the case main body 2a. A main body front cover 2b attached to the right side and a rear cover 2c attached to the other axial side of the case main body 2a (left side in FIG. 3, opposite to the engine E side with respect to the rotating electrical machine in the axial direction) can be divided. It is configured. The case main body 2a, the main body front cover 2b, and the rear cover 2c are fastened and fixed to each other using a fastening member such as a bolt. In the present embodiment, the first front cover 11 is formed integrally with the main body front cover 2b.

  The case main body 2a mainly accommodates the first rotating electrical machine MG1 and the second rotating electrical machine MG2. Further, in the accommodation space (gear mechanism accommodation space P1) formed between the case body 2a and the first front cover 11, mainly the second input member I2, the power distribution device PT, the distribution output member 21, and the output The gear 22, the counter gear mechanism C, and the output differential gear device DF are accommodated. In a housing space (clutch housing space P2) formed between the first case wall 4 of the first front cover 11 (first case) and the second front cover 12 (second case), a clutch described later is provided. CL is provided. Further, the engine side end of the first input member I1 and the damper D are accommodated in the accommodation space (damper accommodation space P3) formed between the case main body 2a and the main body front cover 2b.

  The case main body 2a closes the case peripheral wall 3 formed in a deformed cylindrical shape so as to cover at least the outer periphery of the first rotary electric machine MG1 and the second rotary electric machine MG2, and the end opening on the axial direction engine side of the case peripheral wall 3. An intermediate support wall 7 is provided. The case peripheral wall 3 and the intermediate support wall 7 are integrally formed. Further, the main body front cover 2 b includes a cylindrical cover peripheral wall 13 and a first front cover 11. The cover peripheral wall 13 and the first front cover 11 are integrally formed. The first front cover 11 is a partition wall formed in a deformed cylindrical shape so as to cover at least the outer periphery of the power distribution device PT, the distribution output member 21, the output gear 22, the counter gear mechanism C, and the output differential gear device DF. 10 and a first case wall 4 as an end support wall extending in the radial direction so as to close an end opening on the axial engine side of the partition wall 10. The partition wall 10 and the first case wall 4 are also integrally formed. The rear cover 2c is formed as a plate-like member having a shape corresponding to the outer shape of the case peripheral wall 3 so as to close the end opening on the other axial side (axial rotating electrical machine side) of the case peripheral wall 3 of the case body 2a. Yes.

  The intermediate support wall 7 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. The intermediate support wall 7 is formed with an axial through hole, and the first rotor shaft 31 of the first rotating electrical machine MG1 inserted through the through hole passes through the intermediate support wall 7 and the gear mechanism housing space P1. Are connected to the sun gear S of the power distribution device PT. The intermediate support wall 7 has a cylindrical shape (boss shape) that protrudes around the first rotor shaft 31 toward the axial engine side (the power distribution device PT side that is the gear mechanism accommodation space P1 side when viewed from the intermediate support wall 7). The axial protrusion part 8 is provided. The axial protrusion 8 is formed integrally with the intermediate support wall 7. A second output bearing 62 is disposed on the radially outer side of the axial protrusion 8.

  Similar to the intermediate support wall 7, the first case wall 4 as an end support wall also has a shape extending at least in the radial direction, and in the present embodiment, extends in the radial direction and the circumferential direction. A through-hole penetrating along the axial direction is formed in the first case wall portion 4. The second input member I2 is inserted into the case body 2a through the through hole. The first case wall portion 4 circulates around the second input member I2 and has a cylindrical shape that protrudes toward the axial rotating electric machine side (the power distribution device PT side that is the gear mechanism housing space P1 side when viewed from the first case wall portion 4). A (boss-shaped) axial protrusion (first support portion 6) is provided. A first output bearing 61 (an output bearing disposed closer to the engine E than the ring gear R) is disposed on the radially outer side of the first support portion 6. Therefore, the 1st support part 6 is provided in the 1st case wall part 4, and supports the 1st output bearing 61 from the radial inside.

  In the present embodiment, an axial protrusion (first support portion 6) formed integrally with the first case wall 4 and an axial protrusion 8 formed integrally with the intermediate support wall 7 Are arranged so as to face each other in the gear mechanism housing space P1. Each axial protrusion (6, 8) supports the first output bearing 61 and the second output bearing 62 from the radially inner side, respectively. The first output bearing 61 and the second output bearing 62 that rotatably support the distribution output member 21 from the inside in the radial direction are arranged at positions overlapping the distribution output member 21 in the radial direction.

  As described above, the rear cover 2c is provided so as to close the end opening of the case peripheral wall 3 on the axial rotating electric machine side. As shown in FIG. 3, a pump cover 2 d is attached to an end surface of the rear cover 2 c on the axial engine side that is the inner side of the exterior case 2. The pump cover 2d is fastened and fixed to the rear cover 2c by a fastening member such as a bolt while being in contact with the rear cover 2c from the axial engine side. A pump chamber is formed between the rear cover 2c and the pump cover 2d. An oil pump 55 such as an inscribed gear pump having an inner rotor and an outer rotor is disposed in the pump chamber. In the present embodiment, the inner rotor of the oil pump 55 is driven by a tubular pump drive shaft 54 that is coupled to rotate integrally with the input shaft I. As shown in FIGS. 3 and 4, the oil discharged by the oil pump 55 passes through the shaft oil passage 52 formed in the inner diameter portion of the pump drive shaft 54 and the input shaft I, and the power distribution device PT, It is supplied to gears, a plurality of bearings, etc., and lubricates and cools them. The pump cover 2d is integrally formed with a cylindrical (boss-shaped) axial protruding portion 9 that protrudes toward the first rotating electrical machine MG1 that is the inner side of the exterior case 2.

  The input shaft I is a shaft for inputting the torque of the engine E into the vehicle drive device 1, and is connected to the engine E at the end on the axial direction engine side as shown in FIGS. . The input shaft I is disposed in a state of penetrating the first front cover 11 and the second front cover 12, and the engine output shaft of the engine E via the damper D on the axial engine side of the second front cover 12. It is connected so as to rotate integrally with Eo. The damper D is a device that transmits the rotation of the engine output shaft Eo to the input shaft I while attenuating torsional vibration of the engine output shaft Eo, and various known devices can be used.

  The first input member I1 constituting the input shaft I is supported by the second front cover 12 (second case) via the first support bearing 69 in a rotatable state. Similarly to the first front cover 11, the second front cover 12 includes a second case wall portion 40 that extends in the radial direction. The radially inner end of the second case wall 40 circulates around the first input member I1 and protrudes toward the axial rotating electrical machine side (the first front cover 11 side as viewed from the second case wall 40). A (boss-shaped) axial protrusion 50 is provided. The first support bearing 69 is provided on the axial projecting portion 50 which is an end surface on the radially inner side of the cylindrical through hole provided in the second front cover 12. Further, oil leakage to the axial engine side (damper D and engine E side) is suppressed between the radially inner end face of the through hole provided in the second front cover 12 and the first input member I1. An oil seal 59 is arranged for this purpose. In the present embodiment, the first support bearing 69 is a needle bearing.

  The second input member I2 constituting the input shaft I is rotatably supported on the radially inner end face of the axial through hole provided in the first case wall 4 of the first front cover 11. That is, the second input member I2 is rotatable to an axial protrusion (second support part 5) formed radially inward of the axial protrusion (first support part 6) in the first case wall part 4. Supported by The second input member I2 includes an insertion hole that extends in the axial direction coaxially with the axis of the second input member I2 and opens at an end on the engine E side in the axial direction. An insertion end, which is one end of the first input member I1 on the axial rotating electric machine side, is inserted into the insertion hole so as to be rotatable relative to the second input member I2. Between the inner peripheral surface of the insertion hole of the first input member I1 and the outer peripheral surface of the insertion end portion of the second input member I2, the insertion end portion is radially rotatable relative to the insertion hole. A support bearing 71 between input members to be supported (input bearing) is provided. The inter-input member support bearing 71 is disposed so as to overlap with the distribution output member 21 when viewed in the radial direction. In the present embodiment, the inter-input member support bearing 71 is disposed so as to overlap the first output bearing 61 (output bearing) when viewed in the radial direction. When the clutch CL is in the engaged state, the first input member I1 and the second input member I2 are engaged and rotate integrally as one input shaft I. In this embodiment, the input member support bearing 71 is a needle bearing.

  The clutch CL is, for example, a dog clutch. By using a dog clutch as the clutch CL, when the first input member I1 and the second input member I2 are in a non-engaged state, dragging by the clutch does not occur and torque cross is suppressed. Further, since the dog clutch has a high strength when engaged, it is possible to stably form one input shaft I when the first input member I1 and the second input member I2 are engaged.

  The clutch CL includes a first engagement tooth 81 having external teeth formed to rotate integrally with the second input member I2, and a second engagement of external teeth formed to rotate integrally with the first input member I1. A tooth 83, a sleeve 83 having an inner tooth selectively engaged with one or both of the first engaging tooth 81 and the second engaging tooth 82, and a sleeve 83 engaged with the sleeve 83 so as to be rotatable relative to the sleeve 83; Fork 84 for moving 83 in the axial direction, and a drive device (not shown) for fork 84 are provided. In the present embodiment, the first engagement teeth 81, the second engagement teeth 82, the sleeve 83, and the fork 84 are accommodated in the clutch accommodation space P2 and a space continuous therewith. The driving device (actuator) may be housed in the clutch housing space P2 and a space continuous therewith, or may be disposed outside the clutch housing space P2 and the space continuous therewith.

  In the present embodiment, the first rotor shaft 31 of the first rotating electrical machine MG1 is also formed in a tubular shape having an axial through hole in the inner diameter portion, and a second input is input to the through hole of the first rotor shaft 31. The end of the member I2 on the axial direction rotating electric machine side is inserted. The second input member I2 is supported by the first rotor shaft 31 in a rotatable state via the second support bearing 70.

  The second input member I2 has a flange portion 51 that extends from the second input member I2 in the radial direction. The flange portion 51 is formed integrally with the second input member I2. The flange 51 passes between the sun gear S connected to the first rotor shaft 31 of the first rotating electrical machine MG1 and the first case wall 4 and is connected to the carrier CA of the power distribution device PT. The first case wall portion 4 and the sun gear S are in contact with both sides in the axial direction of the flange portion 51 via a first thrust bearing 67 and a second thrust bearing 68, respectively.

  The first rotor shaft 31 of the first rotating electrical machine MG1 inputs the torque of the first rotating electrical machine MG1 to the sun gear S of the power distribution device PT (or inputs the torque transmitted to the sun gear S to the first rotating electrical machine MG1. 3), and is spline-connected to the sun gear S at the end on the axial direction engine side, as shown in FIGS. The first rotor shaft 31 is supported by the axial protrusion 8 of the intermediate support wall 7 in a rotatable state via the first rotor bearing 63. In addition, the first rotor shaft 31 is rotatable through the second rotor bearing 64 at a position different from the first rotor bearing 63 in the axial direction (in this example, the end on the axial direction rotating electrical machine side). It is supported by the axial protrusion 9 of the pump cover 2d.

  By the way, the distribution output member 21 is arranged on the outer side in the radial direction so as to surround the sun gear S and the carrier CA. The distribution output member 21 is a cylindrical member that occupies substantially the entire axial direction of the gear mechanism accommodation space P1. A ring gear R of the power distribution device PT is formed integrally with the distribution output member 21 on the inner peripheral surface 21 b of the distribution output member 21. The ring gear R is formed at the center of the distribution output member 21 in the axial direction. In the present embodiment, the distribution output member 21 has two axial step portions (23, 24) on its inner peripheral surface 21b. Here, the “axial step” on the inner peripheral surface is a portion formed at a predetermined position in the axial direction of the distribution output member 21 where the inner diameter of the distribution output member 21 changes at that position. The inner diameter of the portion between the two step portions 23 and 24 in the axial direction is formed to be smaller than the inner diameter of the portion that is on the outer side in the axial direction with respect to the two step portions 23 and 24. . And the ring gear R is formed in the internal peripheral surface 21b of the distribution output member 21 in the said small diameter part. As a result, the entire power distribution device PT is disposed on the radially inner side of the distribution output member 21 so as to overlap the distribution output member 21 in the axial direction.

  The distribution output member 21 is supported in a rotatable state with respect to the exterior case 2 at a plurality of axial positions (here, two positions). In the present embodiment, the distribution output member 21 has an outer case via a first output bearing 61 and a second output bearing 62 that are disposed radially inward of the distribution output member 21 at both axial ends thereof. 2 is supported in a rotatable state. That is, the distribution output member 21 has an axial protrusion (first support portion 6) of the first case wall portion 4 and an axial protrusion portion 8 of the intermediate support wall 7 that are arranged to face each other in the gear mechanism accommodation space P1. In contrast, the two output bearings (61, 62) are rotatably supported from the inside in the radial direction. In this way, by adopting a configuration in which the distribution output member 21 is supported from the radially inner side, the diameter of the two output bearings (61, 62) is reduced compared to a configuration in which the distribution output member 21 is supported from the radially outer side. It becomes possible to do.

  An output gear 22 is formed on the outer peripheral surface 21 a of the distribution output member 21. In other words, in the present embodiment, the output gear 22 is, for example, a relatively small-diameter sleeve formed so as to be radially connected to the distribution output member 21 via another member and to surround the input shaft I. It is not formed on a member (see, for example, FIG. 4 of Patent Document 1) or the like, but is formed integrally with the distribution output member 21 on the outer peripheral surface 21a of the distribution output member 21. As described above, in this embodiment, the distribution output member 21 is supported from the radially inner side by the two output bearings (61, 62), and therefore the output gear 22 formed on the outer peripheral surface 21a of the distribution output member 21 is There is no restriction on the axial position of the two output bearings (61, 62). Therefore, in such a configuration, the degree of freedom regarding the axial position of the output gear 22 is very high.

  In the present embodiment, the output gear 22 is formed in such a position setting that it is arranged close to the end of the distribution output member 21 on the axial engine side. As a result, the components of the counter gear mechanism C, the second rotating electrical machine MG2, the output differential gear device DF, and the like arranged on the downstream side of the power transmission path with respect to the output gear 22 are also brought closer to the axial engine side. Can be arranged. Note that, in the position setting of the output gear 22 as described above, the output gear 22 is axially connected to the first output bearing 61 disposed at the end on the axial engine side on the radially inner side of the distribution output member 21. It will be arranged in duplicate. Thereby, compared with the case where the distribution output member 21, the 1st output bearing 61, and the output gear 22 are arranged side by side in an axial direction, the axial direction length of the space where these are arrange | positioned is shortened.

  The second rotor shaft 36 is a shaft for inputting the driving force of the second rotating electrical machine MG2 to a second rotating electrical machine output gear 37 formed integrally with the shaft member 38. As shown in FIG. The inner peripheral surface of the end portion on the direction engine side is splined to the outer peripheral surface of the end portion on the axial rotating electric machine side of the shaft member 38. The second rotor shaft 36 and the shaft member 38 that rotate integrally are supported by the outer case 2 so as to be rotatable through a plurality of bearings at a plurality of positions in the axial direction.

  The first gear 42 and the second gear 43 constituting the counter gear mechanism C are formed integrally with the counter shaft 41, respectively. As a result, the counter shaft 41, the first gear 42, and the second gear 43 rotate integrally. Further, in this embodiment, the counter shaft 41 is supported in a rotatable state with respect to the exterior case 2 via bearings (first counter bearing 65 and second counter bearing 66) arranged at two positions in the axial direction. Has been. The number of teeth of the second gear 43 is set to be smaller than the number of teeth of the first gear 42. These gear ratios (tooth ratio) can be appropriately changed according to vehicle characteristics and the like.

  As shown in FIGS. 2 and 3, the first gear 42 meshes with both the output gear 22 and the second rotating electrical machine output gear 37. In the present embodiment, since the second rotating electrical machine MG2 basically outputs a relatively large assist torque for driving the vehicle, the maximum value of the torque that can be transmitted from the output gear 22 to the first gear 42 and the second value. When the maximum value of the torque that can be transmitted from the rotary electric machine output gear 37 to the first gear 42 is compared, the latter becomes larger. Therefore, in the vehicle drive device 1 according to the present embodiment, the axial length of the second rotating electrical machine output gear 37 is set to be longer than the axial length of the output gear 22 in order to enable greater torque transmission. Yes. In the present embodiment, the torque of the first gear 42 can be effectively transmitted to the first gear 42 without waste while suppressing the overall axial dimension of the vehicle drive device 1. The axial length is set equal to the axial length of the second rotating electrical machine output gear 37. As a result, the axial length of the first gear 42 is longer than the axial length of the output gear 22. Therefore, the first gear 42 has a portion that is not meshed with the output gear 22 (non-meshing portion N (see FIG. 4)).

  The meshing positions of the first gear 42 and the output gear 22 are set so that the first gear 42 and the output gear 22 are meshed with the end portions on the axial direction rotating electric machine side being aligned. In other words, the meshing positions of the first gear 42 and the output gear 22 are set such that all of the non-meshing portions N of the first gear 42 are on the axial engine side with respect to the output gear 22. . In the present embodiment, the non-meshing portion N is disposed at a position overlapping the first counter bearing 65 disposed adjacent to the first gear 42 on the axial direction engine side in the axial direction. The first case wall portion 4 at the radial position corresponding to the portion (or the non-meshing portion N) where the output gear 22 and the first gear 42 mesh with each other is formed thin in the axial direction as shown in FIG. Has been. Thereby, a space opened radially outward of the first support portion 6 of the first case wall portion 4 on the counter gear mechanism C side is formed, and the non-engagement portion N of the first gear 42 is arranged in the vacant space. The Accordingly, the counter gear mechanism C can be arranged close to the axial engine side (engine E side) as much as possible by effectively utilizing the empty space formed on the radially outer side of the first support portion 6. is there. Accordingly, the second rotating electrical machine MG2 and the output differential gear device DF that are directly drive-coupled to the counter gear mechanism C can be disposed as close to the axial engine side as possible.

  Here, when attention is paid to the arrangement configuration of the respective components centering on the first output bearing 61, in the present embodiment, the output gear 22 is located on the radially outer side of the first output bearing 61 with the first output bearing 61. They are arranged overlapping in the radial direction. As described above, the output gear 22 is integrally formed on the outer peripheral surface 21a of the distribution output member 21 so as to approach the end of the distribution output member 21 on the axial direction engine side. The first output bearing 61 is arranged in contact with the inner peripheral surface 21 b of the distribution output member 21 with the distribution output member 21 and the end on the axial direction engine side aligned. As a result, a part of the output gear 22 on the axial engine side and a part of the first output bearing 61 on the axial rotating electrical machine side (which occupies most in the present embodiment) overlap in the radial direction. Are arranged.

  Further, in the present embodiment, a part of the clutch CL is disposed on the radially inner side of the first output bearing 61 so as to overlap the first output bearing 61 in the axial direction. Specifically, the first engagement teeth 81 are arranged on the radially inner side of the first output bearing 61 so as to overlap the first output bearing 61 in the axial direction. Therefore, even if the clutch CL capable of connecting or disconnecting the engine E and the first rotating electrical machine MG1 is provided, an increase in the axial length of the entire apparatus can be suppressed. Further, the clutch CL is arranged in a space that is continuous with the clutch housing space P2 and the clutch housing space P2. Therefore, the clutch CL can be efficiently arranged using the space formed between the first front cover 11 and the second front cover 12.

  In the vehicle drive device 1 according to the present embodiment, since the output gear 22 is formed on the outer peripheral surface 21a of the distribution output member 21 formed in a cylindrical shape, the distribution output member 21 and the output gear 22 (here, these When another member is inserted between the two, the space length occupied by the other member is equal to the axial length of the distribution output member 21 and is very short. Further, in the present embodiment, the power distribution device PT is disposed radially inward of the distribution output member 21 having a short axial length and overlapping with the distribution output member 21 in the radial direction. That is, since many components such as the power distribution device PT, the first output bearing 61, the second output bearing 62, and the first rotor bearing 63 are arranged in the space occupied by the distribution output member 21 along the axial direction. The axial length of the entire device is suppressed. Further, in the present embodiment, the input shaft I is configured to be divided, so that the clutch CL for connecting or separating the two input members (I1, I2) is provided. Since this clutch CL is also arranged at a position overlapping with the first output bearing 61, axial expansion due to the provision of the clutch CL is also suppressed.

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

(1) In the configuration described above with reference to FIGS. 3 and 4, the configuration using a dog clutch as the clutch CL is exemplified. However, the clutch CL is not limited to a dog clutch, and other types of clutches such as a roller clutch and a friction engagement clutch may be used. As long as it is disposed in the clutch housing space P2 and a space continuous therewith in a position radially inward of the first output bearing 61 and overlapping with the first output bearing 61 (output bearing) when viewed in the radial direction. Any type of clutch may be used. FIG. 5 corresponds to FIG. 4 and illustrates the configuration when a roller clutch is applied as the clutch CL.

  Here, the roller clutch as the clutch CL includes an outer race 85, an inner race 86, a plurality of rollers 87 arranged between the outer race 85 and the inner race 86 in the radial direction, and circumferential positions of the plurality of rollers 87. A retainer 88 that restricts the rotation of the retainer 88, a restriction member 89 that restricts the rotation of the retainer 88, and a drive device (not shown) that drives the restriction member 89. That is, the roller clutch has a structure similar to a roller type one-way clutch. Then, by restricting the rotation of the retainer 88 by the restricting member 89, the plurality of rollers 87 are engaged between the inner peripheral surface of the outer race 85 and the outer peripheral surface of the inner race 86, and the outer race 85 and the inner race 86 are These relative rotations can be regulated regardless of the relative rotation direction. Here, the outer race 85 is connected to rotate integrally with the second input member I2 and the carrier CA of the power distribution device PT, and the inner race 86 is connected to rotate integrally with the first input member I1.

  In this example, the outer race 85, the inner race 86, the plurality of rollers 87, the retainer 88, and the regulating member 89 are accommodated in the clutch accommodating space P2 and a space continuous therewith. In this example, the outer race 85, the inner race 86, the plurality of rollers 87, and the retainer 88 are the first output bearing 61 (output bearing) when viewed radially inward and radially from the first output bearing 61. It is arranged at the overlapping position. The driving device (actuator) may be housed in the clutch housing space P2 and a space continuous therewith, or may be disposed outside the clutch housing space P2 and the space continuous therewith. Thus, when a roller clutch is used as the clutch CL, the switching between the engaged state and the non-engaged state can be made smoother. Therefore, it is possible to suppress a shock when the hybrid traveling using the engine E and the rotating electrical machines (MG1, MG2) as the driving force source and the EV traveling using only the rotating electrical machines (MG1, MG2) as the driving force source are switched. .

(2) In the embodiment described above with reference to FIGS. 3 to 5, the second input member I2 extends in the axial direction coaxially with the axial center of the second input member I2 and at the end on the engine E side in the axial direction. An example of a configuration in which an insertion hole that is open and an insertion end that is one end in the axial direction of the first input member I1 is inserted into the insertion hole so as to be rotatable relative to the second input member I2 is illustrated. Since the first input member I1 is rotatably supported by the second front cover 12, both the input members are inserted by inserting the insertion end of the first input member I1 into the insertion hole of the second input member I2. It is easy to divide and configure the input shaft I with a short axial length while matching the axial centers of the two. However, it is not limited to such a fitting structure, and the end faces in the axial direction of the first input member I1 and the second input member I2 face each other, and the configuration in which the two input members are attached to each other is prevented. is not.

(3) In the form described above with reference to FIGS. 3 to 5, between the inner peripheral surface of the insertion hole provided in the second input member I2 and the outer peripheral surface of the insertion end portion of the first input member I1. The configuration in which the arranged input bearing (input member support bearing 71) is arranged so as to overlap with the distribution output member 21 when viewed in the radial direction is illustrated. With such a configuration, the first input member I1 is supported while securing a long support span between the second front cover 12 and the input member support bearing 71. However, as long as the axis centers of the first input member I1 and the second input member I2 are matched to support these input members stably, it does not prevent the input bearings from being arranged at other positions.

  The present invention can be used in a so-called hybrid vehicle drive device that includes an internal combustion engine and a rotating electrical machine as drive power sources.

1: Vehicle drive device 4: 1st case wall part 5: 1st support part 6: 2nd support part 11: 1st front cover (1st case)
12: Second front cover (second case)
21: Distribution output member 21a: Outer peripheral surface 21b: Peripheral surface 22: Output gear 61: First output bearing (output bearing on the internal combustion engine side than the ring gear)
71: Support bearing between input members (input bearing)
CL: Clutch (engagement device)
E: Engine (internal combustion engine)
I: Input shaft (input member)
I1: First input member I2: Second input member MG1: First rotating electrical machine (rotating electrical machine)
P2: Clutch accommodating space (accommodating space between the first case wall and the second case)
PT: Power distribution device R: Ring gear

Claims (3)

An input member drivingly connected to the internal combustion engine, a rotating electrical machine, a power distribution device that distributes and transmits torque of the input member to the rotating electrical machine and a distributed output member, and torque transmitted to the distributed output member An output gear provided so as to be capable of outputting to the wheel side, and a vehicle drive device comprising:
The power distribution device is entirely disposed so as to overlap with the distribution output member in the radial direction of the distribution output member as viewed in the radial direction, and the ring gear of the power distribution device is connected to the distribution output member. Provided integrally with the distribution output member on the inner peripheral surface,
The output gear is provided integrally with the distribution output member on the outer peripheral surface of the distribution output member,
The input member includes a first input member and a second input member in order from the internal combustion engine side along a power transmission path connecting the internal combustion engine and the power distribution device,
Further, the distribution output member is disposed on the internal combustion engine side in the axial direction of the distribution output member and on the radially inner side with respect to the distribution output member, and supports the distribution output member so as to be rotatable from the radially inner side. An output bearing to
A first case that includes a first case wall portion that extends radially on the internal combustion engine side relative to the output bearing in the axial direction, and that houses the distribution output member;
A first support portion provided integrally with the first case wall portion and supporting the output bearing from the radially inner side;
A second case which is disposed closer to the internal combustion engine than the first case wall and forms an accommodation space with the first case wall;
An engagement device that connects or separates the first input member and the second input member;
At least a part of the engagement device is disposed in the housing space and a space continuous therewith, at a position that is radially inward of the output bearing and overlaps the output bearing when viewed in the radial direction. A vehicle drive device. The second input member includes an insertion hole that extends in the axial direction coaxially with the axis of the second input member and opens at an end portion on the internal combustion engine side in the axial direction.
An insertion end that is one end of the first input member in the axial direction is inserted into the insertion hole so as to be rotatable relative to the second input member,
Further, the second input member is rotatably supported by a second support portion formed on the radially inner side of the first support portion in the first case wall portion,
The vehicle drive device according to claim 1, wherein the first input member is rotatably supported by the second case. An input bearing disposed between an inner peripheral surface of the insertion hole and an outer peripheral surface of the insertion end, and supporting the insertion end in the radial direction so as to be relatively rotatable with respect to the insertion hole;
The vehicle drive device according to claim 2, wherein the input bearing is disposed so as to overlap the distribution output member when viewed in the radial direction.

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