JP2014144760A - Power transmission apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission apparatus which allows reliable arrangement and fitting of an axial load bearing to be arranged between a sun gear and a radial-direction enlarged part of an input member.SOLUTION: A power transmission apparatus 1 is provided with a planetary gear mechanism PG which transmits a torque transmitted from an input member I drive-connected to an internal engine by distributing to an output member O drive-connected to a wheel and a rotary electric machine MG1. A sun gear S has a connection part 11 connected to the rotary electric machine MG1 on the axial first direction side, and the input member I has a penetration part 15 which penetrates the inside, in the radial direction, of the sun gear S and a radial direction enlarged part 16 on the axial second direction X2 side relative to the sun gear S. An axial load bearing 68 is arranged between the sun gear S and the radial direction enlarged part 16, and an engagement member 7 is attached to the outer peripheral surface of the input member I and has a part overlapping with the sun gear S in an axial-direction view.

Description

  The present invention relates to an input member that is drivingly connected to an internal combustion engine, an output member that is drivingly connected to wheels, and a planetary gear mechanism that distributes and transmits torque transmitted from the input member to the output member and the rotating electrical machine. And a power transmission device comprising:

  As the power transmission device as described above, for example, a device described in Patent Document 1 below is already known. In the technique of Patent Document 1, when the power transmission device is assembled, the sun gear can move in the axial direction with respect to the input member and the pinion gear in a state where the sun gear of the planetary gear mechanism is not connected to the rotating electrical machine. For this reason, it is difficult to attach the sun gear to the shaft of the rotating electrical machine while holding the shaft load bearing arranged between the sun gear and the radially enlarged portion of the input member in an appropriate position. It was. In addition, since this axial load bearing is sandwiched between the sun gear and the radially expanded portion of the input member in the assembled state, it is difficult to visually confirm whether or not the shaft load bearing is properly installed. there were.

JP 2011-183946 A

  Therefore, a power transmission device that can ensure the arrangement and attachment of the axial load bearing arranged between the sun gear and the radially enlarged portion of the input member is desired.

  An input member drivingly connected to an internal combustion engine, an output member drivingly connected to a wheel, and a planetary gear for distributing torque transmitted from the input member to the output member and a rotating electrical machine according to the present invention. A power transmission device comprising a mechanism, comprising: an axial load bearing that receives an axial load; and a locking member attached to the input member, wherein the planetary gear mechanism is a carrier that supports a pinion gear. And a sun gear and a ring gear meshing with the pinion gear, the sun gear is drivingly connected to the rotating electrical machine without passing through the carrier and the ring gear, and the ring gear is driven to the output member without passing through the sun gear and the carrier And the carrier is drivingly connected to the input member without passing through the sun gear and the ring gear. The sun gear is formed in a cylindrical shape, and includes a connecting portion with the rotating electrical machine on the first axial direction side that is one side in the axial direction from the meshing portion with the pinion gear, and the input member is connected to the sun gear. A penetrating portion that penetrates the inner side in the radial direction of the sun gear in the axial direction in a state of being relatively rotatable with respect to the sun gear, and the penetrating portion on the second axial direction side opposite to the first axial direction with respect to the sun gear. A radially enlarged portion formed larger in the radial direction, the axial load bearing is disposed between the sun gear and the radially enlarged portion in the axial direction, and the locking member is disposed on the sun gear. On the first axial direction side, it is attached to the outer peripheral surface of the input member in a state in which relative movement in the axial direction is restricted, and has a portion overlapping with the sun gear when viewed in the axial direction.

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

  Unlike the above-described characteristic configuration, when the locking member is not provided, the sun gear is movable in the axial direction with respect to the input member when the power transmission device is assembled. For this reason, after attaching the axial load bearing arrange | positioned between the sun gear and radial direction expansion part in an axial direction, when connecting a sun gear with the connection part of a rotary electric machine, an axial load bearing moves from an appropriate attachment position. there is a possibility. In addition, since this axial load bearing is sandwiched between the sun gear and the radially expanded portion of the input member in the assembled state, it is difficult to visually confirm whether or not the shaft load bearing is properly installed. there were.

  On the other hand, according to the above-described characteristic configuration, the axial load bearing is arranged between the sun gear and the radially enlarged portion of the input member, and then the locking member is attached, so that the arrangement and installation of the axial load bearing are ensured. It can be. For example, in a state where the axial load bearing is attached to an appropriate position with respect to the radially enlarged portion of the input member, the sun gear is assembled at a position in contact with the axial load bearing while meshing with the pinion gear. At this time, since the sun gear is moved and assembled as a single unit, the work is easy and the displacement of the shaft load bearing is unlikely to occur. And after arrangement | positioning of a sun gear, it is controlled that a sun gear moves to an axial first direction side by attaching a locking member to an input member. Thereby, the state by which the arrangement | positioning and attachment of the axial load bearing were ensured can be maintained. Then, after attaching the locking member, the connecting portion of the sun gear is connected to the rotating electrical machine. Thereby, arrangement | positioning and attachment of an axial load bearing can be made reliable.

  Here, a ring gear bearing that rotatably supports the ring gear, and an input bearing that rotatably supports the input member, wherein the rotating member that is drivingly connected to the rotor of the rotating electrical machine includes at least the shaft A cylindrical shaft cylindrical portion that opens in two directions, and the coupling portion is a spline coupling portion that is spline-fitted to the shaft cylindrical portion from the second axial direction side, and the ring gear bearing Supports the ring gear so as to be rotatable with respect to the case on the first axial direction side with respect to the meshing portion with the pinion gear, and also in the first axial direction with respect to the ring gear or a member that rotates integrally with the ring gear. A fitting surface that is fitted from the side, and a fitting surface that is fitted from the second axial direction side to the case, and the input member is disposed on the radially inner side of the shaft tubular portion. An insertion portion that is inserted from the second shaft direction side; and the input bearing supports the insertion portion in a radial direction so as to be rotatable with respect to the shaft tubular portion, and It is preferable that one or both of a fitting part fitted from the second axial direction side and a fitting part fitted from the first axial direction side to the inserted part are provided.

  In such a configuration, when the connecting portion of the sun gear is spline-fitted in the axial cylindrical portion of the rotating member in the axial direction, the inserted portion of the input member is inserted radially inward of the axial cylindrical portion of the rotating member. In addition, it is necessary to fit the input bearing. Moreover, it is necessary to fit the fitting surface of the ring gear bearing to the case, and it is necessary to apply a force for fitting the ring gear bearing in the first axial direction while the spline fitting is performed on the connecting portion of the sun gear. In the conventional structure, a high level of skill is required to simultaneously perform these operations while preventing the displacement of the axial load bearing and the like. However, according to the configuration described above, In addition, it is possible to maintain a state where the arrangement and attachment of the axial load bearing are ensured. Therefore, the arrangement and attachment of the axial load bearing can be ensured.

  Here, an input bearing that rotatably supports the input member is further provided, and the rotary member that is drivingly connected to the rotor of the rotating electrical machine has a cylindrical shaft cylindrical portion that opens at least in the second axial direction side. The input member includes a portion to be inserted which is inserted from the second axial direction side into the radial inner side of the shaft cylindrical portion, and the input bearing holds a plurality of rollers and the plurality of rollers. And is configured to support the inserted portion in a radial direction so as to be rotatable with respect to the shaft tubular portion, and the locking member is in a state where relative movement in the axial direction is restricted. It is preferable that the retainer is attached to the insertion portion.

  According to this configuration, the locking member can be configured by using the input bearing that is required to rotatably support the portion on the first axial direction side of the radially expanded portion of the input member. Therefore, an increase in the number of parts for providing the locking member can be suppressed.

  Here, the rotating member that is drivingly connected to the rotor of the rotating electrical machine includes a contact portion that contacts the sun gear from the first axial direction side, and the locking member includes the contact portion that is the sun gear. It is preferable that the axial clearance be formed between the locking member and the sun gear in a state of being in contact with the sun gear.

  According to this configuration, after the assembly of the power transmission device is completed, it is possible to suppress the occurrence of torque loss due to frictional resistance due to the locking member coming into contact with the sun gear.

  Here, the meshing portion of the ring gear with the pinion gear is formed on an inner peripheral surface of a cylindrical member disposed radially outward with respect to the sun gear and the carrier, and the carrier includes the radial expansion portion. The cylindrical member is connected so as to rotate integrally, and an inner peripheral surface of the cylindrical member is rotatably supported with respect to the case via a first ring gear bearing on the first axial direction side with respect to the meshing portion of the ring gear. And is supported rotatably with respect to the case via a second ring gear bearing on the second axial direction side with respect to the meshing portion of the ring gear. An output gear is provided as a member, and the first ring gear bearing is disposed so as to have a portion overlapping the carrier when viewed in the axial direction, When the second ring gear bearing is arranged so as to have a portion that overlaps with the carrier as viewed in the axial direction it is preferred.

  According to this configuration, when the power transmission device is assembled, by fitting the first ring gear bearing and the second ring gear bearing to the tubular member, the bearings on both sides fitted to the tubular member of the ring gear are The carrier is sandwiched so as to overlap with the carrier when viewed in the axial direction. Therefore, the first ring gear bearing and the second ring gear bearing can function as a regulating member that regulates separation of the ring gear from the carrier and the pinion gear. Further, as described above, the separation of the sun gear from the input member, the carrier, and the pinion gear is restricted by the locking member. Therefore, the entire planetary gear mechanism and the input member constituting the power transmission device can be modularized, and the power transmission device can be efficiently assembled.

It is a skeleton figure of the drive device for vehicles provided with the power transmission device concerning the embodiment of the present invention. It is sectional drawing in the plane containing the rotating shaft center of the planetary gear mechanism of the power transmission device which concerns on 1st embodiment of this invention. It is sectional drawing in the plane containing the rotating shaft center of the planetary gear mechanism in the case of the assembly | attachment of the power transmission device which concerns on 1st embodiment of this invention. It is sectional drawing in the plane containing the rotating shaft center of the planetary gear mechanism after the assembly | attachment of the power transmission device which concerns on 1st embodiment of this invention. It is sectional drawing in the plane containing the rotating shaft center of the planetary gear mechanism in the case of the assembly | attachment of the power transmission device which concerns on 2nd embodiment of this invention. It is sectional drawing in the plane containing the rotating shaft center of the planetary gear mechanism after the assembly | attachment of the power transmission device which concerns on 2nd embodiment of this invention. It is sectional drawing in the plane containing the rotating shaft center of the planetary gear mechanism in the case of the assembly | attachment of the power transmission device which concerns on the comparative example of this invention.

1. 1st embodiment 1st embodiment of the power transmission device 1 which concerns on this invention is described with reference to drawings. FIG. 1 is a skeleton diagram showing a schematic configuration of a vehicle drive device 2 including a power transmission device 1 according to the present embodiment. FIG. 2 is a cross-sectional view of the vehicle drive device 2 including the power transmission device 1 cut along a plane including the rotational axis AX of the planetary gear mechanism PG. In the following description, unless otherwise specified, the axial direction, radial direction, and circumferential direction refer to the axial direction, radial direction, and circumferential direction of the rotational axis AX of the planetary gear mechanism PG.
In this embodiment, as shown in FIGS. 1 and 2, the power transmission device 1 includes an input shaft I that is drivingly connected to the internal combustion engine E, an output gear O that is drivingly connected to the wheels W, and an input shaft I. And a planetary gear mechanism PG for distributing and transmitting the transmitted torque to the output gear O and the first rotating electrical machine MG1.

The power transmission device 1 includes a first shaft load bearing 68 that receives a load in the axial direction X, and a locking member 7 that is attached to the input shaft I.
The planetary gear mechanism PG includes a carrier CA that supports the pinion gear P and a sun gear S and a ring gear R that mesh with the pinion gear P. The sun gear S is drivingly connected to the first rotating electrical machine MG1 without going through the carrier CA and the ring gear R, the ring gear R is drivingly connected to the output gear O without going through the sun gear S and the carrier CA, and the carrier CA is connected to the sun gear S and It is drivingly connected to the input shaft I without going through the ring gear R.
The sun gear S is formed in a cylindrical shape, and the first rotating electrical machine is disposed on the first axial direction X1 side, which is one side in the axial direction X, with respect to the meshing portion 10 with the pinion gear P (hereinafter also referred to as the sun gear meshing portion 10). The connecting part 11 with MG1 is provided.
The input shaft I is disposed so as to penetrate the radially inner side of the sun gear S in the axial direction X while being rotatable relative to the sun gear S, and is opposite to the first shaft direction X1 with respect to the sun gear S. On the side in the second axial direction X2 of the direction, there is provided a radially expanded portion 16 that is expanded in the radial direction from the through portion that penetrates the sun gear S.

The first axial load bearing 68 is disposed between the sun gear S and the radially enlarged portion 16 in the axial direction X.
The locking member 7 is attached to the outer peripheral surface of the input shaft I in a state where relative movement in the axial direction X is restricted on the first shaft direction X1 side with respect to the sun gear S. Has overlapping parts.
In the power transmission device 1 according to the present embodiment, the planetary gear mechanism PG and the input shaft I are arranged coaxially. The internal combustion engine E is arranged coaxially with the planetary gear mechanism PG and on the second axial direction X2 side with respect to the planetary gear mechanism PG. The first rotating electrical machine MG1 is arranged coaxially with the planetary gear mechanism PG and on the first axial direction X1 side with respect to the planetary gear mechanism PG.
The output gear O corresponds to the “output member” in the present invention, the first rotating electrical machine MG1 corresponds to the “rotating electrical machine” in the present invention, and the first shaft load bearing 68 corresponds to the “axial load in the present invention. Corresponds to “bearing”.
Hereinafter, the power transmission device 1 according to the present embodiment will be described in detail.

1-1. Schematic Configurations of Vehicle Drive Device 2 and Power Transmission Device 1 In the present embodiment, as shown in FIG. 1, the vehicle drive device 2 includes a second rotating electrical machine MG2 in addition to the first rotating electrical machine MG1. The second rotating electrical machine MG2 is drivingly connected to a power transmission path between the output gear O and the wheels W. The vehicle drive device 2 is a drive device for a so-called two-motor split type hybrid vehicle.
In the present embodiment, the output gear O is drivingly connected to the wheels W via the counter gear mechanism Ct, the output differential gear device DF, and the like, and the second rotating electrical machine MG2 is drivingly connected to the counter gear mechanism Ct. ing.

  First, the overall configuration of the vehicle drive device 2 according to the present embodiment will be described. As shown in FIG. 1, the input shaft I is drivingly connected to the internal combustion engine E. Here, the internal combustion engine E is a heat engine driven by the combustion of fuel, and for example, various known internal combustion engines such as a gasoline engine and a diesel engine can be used. In this example, the input shaft I is drivably coupled to an internal combustion engine output shaft Eo such as a crankshaft of the internal combustion engine E via a damper DP. A configuration in which the input shaft I is directly connected to the output shaft Eo of the internal combustion engine via a clutch or the like in addition to the damper DP or directly without the damper DP or the clutch is also suitable.

  The first rotating electrical machine MG1 includes a first stator St1 fixed to the case 5 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 of the planetary gear mechanism PG via the first rotating shaft 47. A coil Co1 is attached to the first stator St1, and a coil end portion of the coil Co1 protrudes on both axial sides of the first stator St1. The first rotating electrical machine MG1 can perform a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. It is said that. Therefore, the first rotating electrical machine MG1 is electrically connected to a power storage device (not shown). In this example, the first rotating electrical machine MG1 generates power by the torque of the input shaft I (internal combustion engine E) that is mainly input via the planetary gear mechanism PG, and charges the power storage device, or the second rotating electrical machine MG2. It functions as a generator that supplies electric power for driving. However, the first rotating electrical machine MG1 may function as a motor that powers and outputs driving force when the vehicle is traveling at high speed or when the internal combustion engine E is started.

  The second rotating electrical machine MG2 includes a second stator St2 fixed to the case 5 and a second rotor Ro2 that is rotatably supported on the radially inner side of the second stator St2. The second rotor Ro <b> 2 is drivingly connected so as to rotate integrally with the electric machine output gear 87 via the second rotating shaft 86. The second rotating electrical machine MG2 can perform a function as a motor (electric motor) that generates power by receiving power supply and a function as a generator (generator) that generates power by receiving power supply. It is said that. Therefore, the second rotating electrical machine MG2 is also electrically connected to the power storage device. In this example, the second rotating electrical machine MG2 mainly functions as a motor that assists the driving force for running the vehicle. However, when the vehicle is decelerated, the second rotating electrical machine MG2 may function as a generator that regenerates the inertial force of the vehicle as electric energy.

In the present embodiment, the planetary gear mechanism PG is a single pinion type planetary gear mechanism disposed coaxially with the input shaft I. In other words, the planetary gear mechanism PG has three rotating elements: a carrier CA that supports a plurality of pinion gears P, and a sun gear S and a ring gear R that mesh with the pinion gears P, respectively.
The sun gear S is drivingly connected to the first rotating shaft 47 without passing through the carrier CA and the ring gear R. The ring gear R is drivingly connected to the output gear O without passing through the sun gear S and the carrier CA. The carrier CA is drivingly connected to the input shaft I without passing through the sun gear S and the ring gear R.
These three rotating elements included in the planetary gear mechanism PG 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 the order of rotational speed in the rotational state of each rotating element. The rotational speed of each rotating element varies depending on the rotational state of the planetary gear mechanism PG, but the order in which the rotational speeds of the rotating elements are arranged is fixed because it is determined by the structure of the planetary gear mechanism PG. Note that “the order of the rotational speed of each rotating element” is equal to the order of arrangement in the speed diagram (collinear diagram) of each rotating element. Here, “arrangement order in the velocity diagram of each rotating element” means the order in which the axis corresponding to each rotating element in the velocity diagram (collinear diagram) is arranged along the direction orthogonal to the axis. That is.

  In the present embodiment, the sun gear S is drivingly connected so as to rotate integrally with the first rotating shaft 47, and the first rotating shaft 47 is drive connected so as to rotate integrally with the first rotor Ro1 of the first rotating electrical machine MG1. ing. The carrier CA is drivingly connected to rotate integrally with the input shaft I, and the input shaft I is drivingly connected to rotate integrally with the internal combustion engine E. The ring gear R is coupled to rotate integrally with the output gear O, and the output gear O is drivingly coupled to the wheels W.

  The counter gear mechanism Ct reverses the rotation direction of the output gear O and transmits the torque transmitted from the output gear O to the wheel W side. The counter gear mechanism Ct includes a counter shaft 91, a first gear 92, and a second gear 93. The first gear 92 meshes with the output gear O that rotates integrally with the ring gear R. The first gear 92 also meshes with the electric output gear 87 of the second rotating electric machine MG2 at a position different from the output gear O in the circumferential direction. The second gear 93 meshes with a differential input gear 96 included in an output differential gear device DF described later. Therefore, the counter gear mechanism Ct reverses the rotation direction of the output gear O and the electric output gear 87 of the second rotary electric machine MG2, and at the same time outputs the torque transmitted to the output gear O and the torque of the second rotary electric machine MG2 to the output differential. It is transmitted to the dynamic gear device DF.

  The output differential gear device DF has a differential input gear 96, and distributes and transmits torque transmitted to the differential input gear 96 to the plurality of wheels W. In this example, the output differential gear device DF is a differential gear mechanism using a plurality of bevel gears that mesh with each other, and is transmitted to the differential input gear 96 via the second gear 93 of the counter gear mechanism Ct. Is distributed to the two left and right wheels W via the axles 88 respectively.

  In the vehicle drive device 2 according to the present embodiment, the planetary gear mechanism PG, the first rotary shaft 47, the input shaft I, the first rotary electric machine MG1, and the internal combustion engine E are arranged on the same axis, and the second rotary electric machine MG2 is The first rotary electric machine MG1 and the like are arranged on a different axis. Further, on the same axis, the first rotating electrical machine MG1, the planetary gear mechanism PG, and the internal combustion engine E are arranged in this order from the first axial direction X1 side.

1-2. Next, the main configuration of the power transmission device 1 and the vehicle drive device 2 according to the present embodiment will be described.
<Case 5>
As shown in FIG. 2, each component of the power transmission device 1 such as the planetary gear mechanism PG and the output gear O is housed in a gear housing chamber 75 of the case 5.
The case 5 includes a peripheral wall 60 formed so as to cover the outer periphery of the planetary gear mechanism PG and the output gear O. In addition, the case 5 has a second radially extending wall 54 that extends in the radial direction on the second axial direction X2 side of the planetary gear mechanism PG so as to close the end opening of the peripheral wall 60 on the second axial direction X2 side. It has. The case 5 extends in the first radial direction extending in the radial direction on the first axial direction X1 side of the planetary gear mechanism PG and the output gear O so as to close the end opening of the peripheral wall 60 on the first axial direction X1 side. A wall 57 is provided. A gear housing chamber 75 is formed so as to be surrounded by the peripheral wall 60, the second radially extending wall 54, and the first radially extending wall 57.
In the present embodiment, the case 5 related to the gear housing chamber 75 is configured by connecting a first case 5a and a second case 5b by a fastening member. The first case 5a constitutes a first radially extending wall 57 and a portion of the peripheral wall 60 on the axial first direction X1 side. The second case 5b constitutes a second radially extending wall 54 and a portion of the peripheral wall 60 on the second axial direction X2 side.

An axial through hole is formed on the radially inner side (center portion) of the second radially extending wall 54, and the input shaft I inserted through the through hole passes through the second radially extending wall 54. It penetrates and extends in the axial direction X. The radially inner end of the second radially extending wall 54 supports the input shaft I so as to be rotatable from the radially outer side via the second input bearing 64.
The second radially extending wall 54 includes a second output projecting portion 56 that projects in the axial first direction X1 to a position overlapping the tubular member 30 on the radially inner side of the tubular member 30 of the ring gear R. Yes. The outer peripheral surface 56a of the second output protrusion 56 supports the tubular member 30 of the ring gear R through the second ring gear bearing 41 so as to be rotatable from the radially inner side.

An axial through hole is formed on the radially inner side (center portion) of the first radially extending wall 57, and the first rotary shaft 47 inserted through the through hole is a first radially extending wall. 57 is inserted into the gear housing chamber 75. The radially inner end of the first radially extending wall 57 supports the first rotating shaft 47 via the first rotating electrical machine bearing 63 so as to be rotatable from the radially outer side.
The first radially extending wall 57 includes a first output projecting portion 58 that projects in the axial second direction X2 up to the radially inner side of the tubular member 30 of the ring gear R. The outer peripheral surface 58a of the first output protrusion 58 supports the tubular member 30 of the ring gear R via the first ring gear bearing 40 so as to be rotatable from the radially inner side.

<Sungear S>
The sun gear S is formed in a cylindrical shape and includes a connecting portion 11 for connecting to the first rotating electrical machine MG1 on the first axial direction X1 side of the sun gear engaging portion 10.
In the present embodiment, the sun gear S is formed in a cylindrical shape, and the connecting portion 11 is a cylindrical member that extends from the sun gear meshing portion 10 toward the first axial direction X1 side. An input shaft I is disposed inside the sun gear S in the radial direction.
The connecting portion 11 is a spline connecting portion that is spline-fitted to the shaft tubular portion 48 of the first rotating shaft 47 from the second axial direction X2 side. In the present embodiment, spline grooves extending in the axial direction X are formed on the outer peripheral surface of the connecting portion 11, and are spline-fitted to the spline grooves formed on the inner peripheral surface of the shaft tubular portion 48.

<First rotating shaft 47>
The first rotating shaft 47 is drivingly connected to the first rotor Ro1 of the first rotating electrical machine MG1. The first rotating shaft 47 includes a cylindrical shaft cylindrical portion 48 that opens at least toward the second axial direction X2. In the present embodiment, the first rotation shaft 47 is a rotor shaft that rotates integrally with the first rotor Ro1. The first rotating shaft 47 is formed in a cylindrical shape over the entire axial direction X, and the pump drive shaft 46 is disposed radially inward.
The first rotating shaft 47 is supported on the radially inner end of the first radially extending wall 57 in a rotatable state via a first rotating electrical machine bearing 63.
The first rotating shaft 47 corresponds to the “rotating member” in the present invention.

The shaft tubular portion 48 includes a sun gear connecting portion 50 that is connected to the sun gear S. In the present embodiment, the sun gear connecting portion 50 is provided at the end portion on the side in the second axial direction X2 on the inner peripheral surface of the shaft tubular portion 48. The sun gear connecting portion 50 is formed with a spline groove extending in the axial direction X.
An input support portion 51 that supports the input shaft I via the first input bearing 20 is formed on the inner peripheral surface of the shaft tubular portion 48. In the present embodiment, the input support portion 51 is disposed on the inner circumferential surface of the shaft tubular portion 48 on the first shaft direction X1 side with respect to the sun gear connecting portion 50.
The inner diameter of the sun gear connecting portion 50 is larger than the inner diameter of the input support portion 51. The connecting portion 11 of the sun gear S is disposed on the radially inner side of the sun gear connecting portion 50, and the through portion 15 of the input shaft I is disposed on the radially inner side of the connecting portion 11. The first input bearing 20 is disposed on the radially inner side of the input support portion 51, and the inserted portion 17 of the input shaft I is disposed on the radially inner side of the first input bearing 20.

<Input shaft I>
The input shaft I is drivingly connected to the internal combustion engine E and rotates integrally with the carrier CA.
The input shaft I includes a radially enlarged portion 16 that is larger in the radial direction than the penetrating portion 15 on the shaft second direction X2 side with respect to the sun gear S. The radially expanded portion 16 is connected to rotate integrally with the carrier CA.
In the present embodiment, the radially expanded portion 16 is a flange that extends between the sun gear S and the second radially extending wall 54 in the axial direction X and extends radially outward from the shaft body portion of the input shaft I. It is formed in a shape. The radially outer end of the radially expanded portion 16 is connected to the radially inner end of the annular plate-shaped portion 90 of the carrier CA disposed on the second axial direction X2 side of the pinion gear P. In this embodiment, they are connected by welding, and the carrier CA and the input shaft I move integrally.

  The surface of the radially enlarged portion 16 on the second axial direction X2 side is disposed so as to contact the second radially extending wall 54 via the second axial load bearing 67. The surface on the first axial direction X1 side of the radially enlarged portion 16 is disposed so as to contact the surface on the second axial direction X2 side of the sun gear S via the first axial load bearing 68. That is, the first axial load bearing 68 is disposed between the sun gear S and the radially enlarged portion 16 in the axial direction X. The first shaft load bearing 68 corresponds to the “shaft load bearing” in the present invention.

  In the present embodiment, the first shaft load bearing 68 includes a roller portion including a plurality of cylindrical rollers extending in the radial direction and a cage that holds the plurality of rollers, and a first axial direction of the roller portion. It is composed of an annular plate-shaped first washer 69 disposed on the X1 side, and an annular plate-shaped second washer 70 disposed on the second axial direction X2 side of the roller portion. The first washer 69 includes a cylindrical fitting portion that extends from the radially inner end of the annular plate-shaped portion toward the first axial direction X1, and the fitting portion is included in the sun gear S. It is fitted to the peripheral surface.

  In the present embodiment, the input shaft I is drivingly connected to the internal combustion engine E via the damper DP. Specifically, a spline groove extending in the axial direction is formed on the outer peripheral surface of the end portion of the input shaft I in the second axial direction X2, and the output member of the damper DP is spline-fitted into the spline groove. (Illustrated). On the other hand, the input member of the damper DP is connected to the internal combustion engine output shaft Eo (see FIG. 1). Note that a spring that attenuates rotational vibration of the shaft is provided between the output member and the input member of the damper DP.

The input shaft I includes a penetrating portion 15 that penetrates the sun gear S in the axial direction X while being rotatable relative to the sun gear S. Further, the input shaft I includes an insertion portion 17 that is inserted from the axial second direction X2 side inside the cylindrical member 30 in the radial direction.
In the present embodiment, the penetrating portion 15 is a cylindrical member that extends in the axial first direction X1 more than the radially expanded portion 16, and the inserted portion 17 is further in the axial first direction X1 than the penetrating portion 15. It is the shaft part which extended to. The penetrating part 15 and the inserted part 17 extend in the axial first direction X1 from the radially enlarged part 16 and the end part of the sun gear S in the second axial direction X2 side to the vicinity of the radially inner side of the first radially extending wall 57. ing. The penetrating portion 15 and the inserted portion 17 are smaller in diameter than the portion on the axial second direction X2 side with respect to the radial direction enlarged portion 16. This is because the transmitted driving force of the internal combustion engine E is about the driving force for driving the oil pump OP and becomes smaller on the first axial direction X1 side than the radially enlarged portion 16 connected to the carrier CA. .

  The outer peripheral surface of the inserted portion 17 is supported by the inner peripheral surface of the shaft cylindrical portion 14 of the first rotating shaft 47 in a state that it can rotate via the first input bearing 20. In the present embodiment, a cylindrical concave portion 18 that is recessed radially inward is formed on the outer peripheral surface of the insertion portion 17, and the first input bearing 20 is fitted in the concave portion 18, so The relative movement of the first input bearing 20 in the axial direction X is restricted.

  In addition, the input shaft I is on the radially inner end portion of the second radially extending wall 54 in a state that it can rotate via the second input bearing 64 on the axial second direction X2 side of the radially expanded portion 16. It is supported. Between the second radially extending wall 54 and the input shaft I, oil leaks from the inside of the gear housing chamber 75 to the second axial direction X2 side on the second axial direction X2 side of the second input bearing 64. An oil seal 59 for restraining is arranged.

  Inside the input shaft I, an internal oil passage L1 extending from the end portion on the first axial direction X1 side in the second axial direction X2 to the second axial direction X2 side of the radially expanding portion 16 is formed. The input shaft I includes a first supply hole H1 that extends radially outward from the internal oil passage L1 in the through portion 15 and opens to the outer peripheral surface. The input shaft I includes a second supply hole H2 that extends radially outward from the internal oil passage L1 and opens to the outer peripheral surface on the axial second direction X2 side of the radial expansion portion 16.

  In the present embodiment, the oil pump OP is disposed on the first axial direction X1 side of the first rotating shaft 47, and is driven by the rotation of the pump driving shaft 46 that is coupled to rotate integrally with the input shaft I. (See FIG. 1). The pump drive shaft 46 is disposed so as to extend in the axial direction from the oil pump OP to the axial first direction X1 side end portion of the input shaft I in a space radially inward of the first rotary shaft 47 formed in a cylindrical shape. ing.

  The inserted portion 17 of the input shaft I includes a shaft coupling cylindrical portion 19 in which an end of the inserted portion 17 on the first axial direction X1 side is open. The inner peripheral surface of the shaft connecting tubular portion 19 is spline fitted to the pump drive shaft 46 from the second axial direction X2 side. Spline grooves extending in the axial direction X are formed on the inner peripheral surface of the shaft coupling tubular portion 19 and the end portion on the axial second direction X2 side of the outer peripheral surface of the pump drive shaft 46.

  Inside the pump drive shaft 46, a drive shaft oil passage L <b> 2 is formed that communicates between both axial ends in the axial direction. The oil discharged from the oil pump OP is sent to the supply hole H1 and the second supply hole H2 through the drive shaft oil passage L2 of the pump drive shaft 46 and the internal oil passage L1 of the input shaft I. Then, the oil supplied from the supply hole H1 and the second supply hole H2 is supplied to the planetary gear mechanism PG and each bearing constituting the power transmission device 1, the first rotating electrical machine MG1, and the like for lubrication and cooling. Do.

<First input bearing 20>
The first input bearing 20 is a bearing that rotatably supports the input shaft I. In the present embodiment, the first input bearing 20 supports the inserted portion 17 of the input shaft I in the radial direction so as to be rotatable with respect to the shaft tubular portion 48 of the first rotating shaft 47.
In the present embodiment, the first input bearing 20 includes a first fitting portion that is fitted to the shaft cylindrical portion 48 from the second axial direction X2 side. The first input bearing 20 is a gauge and roller type bearing including a plurality of rollers 23 and a cage 24 that holds the plurality of rollers 23. The roller 23 is formed in a cylindrical shape. The cage 24 is a cylindrical member in which slits (grooves) extending in the axial direction for holding the roller 23 are formed at a plurality of locations in the circumferential direction.
In the present embodiment, the retainer 24 has a cylindrical roller holding portion 25 that holds the roller 23, and extends in the axial second direction X <b> 2 from the roller holding portion and extends in the axial direction with a larger diameter than the roller holding portion 25. A special shape including the portion 26 is provided. More specifically, the axially extending portion 26 extends in an annular shape radially outward from the end of the cylindrical roller holding portion 25 on the axial second direction X2 side, and then on the axial second direction X2 side. It extends in a cylindrical shape.

  The first input bearing 20 is fitted into a recess 18 formed in the inserted portion 17, and relative movement in the axial direction X of the first input bearing 20 with respect to the input shaft I is restricted. In the present embodiment, the roller 23 and the roller holding portion 25 are fitted into the recess 18 to restrict relative movement, and the axially extending portion 26 is not fitted into the recess 18.

  The cage 24 includes a split portion having a cut extending in the axial direction X at one place or two or more in the circumferential direction. The diameter of the cage 24 is widened or the cage 24 is divided. It is configured so that it can be fitted into the recess 18. A resin cage 24 is preferably used.

  The axially extending portion 26 is radially outside the inserted portion 17 on the axial second direction X2 side with respect to the concave portion 18 and has a sun gear coupling portion having a larger diameter than the input support portion 51 into which the first input bearing 20 is fitted. It is arranged in a space radially inside 50. The axially extending portion 26 is disposed on the first axial direction X1 side of the connecting portion 11 of the sun gear S, and the end portion of the axially extending portion 26 on the second axial direction X2 side is connected to the connecting portion 11. It arrange | positions so that it may overlap with the edge part of the axial 1st direction X1 side seeing in the axial direction X. FIG.

  In the present embodiment, the locking member 7 is constituted by a cage 24. That is, the cage 24 is attached to the outer peripheral surface (recessed portion 18) of the input shaft I in a state in which relative movement in the axial direction X is restricted on the first axial direction X1 side with respect to the sun gear S. The axial extension part 26 which is a part which overlaps with the sun gear S (connecting part 11) seeing is seen.

The first rotating shaft 47 includes a contact portion 49 that contacts the sun gear S from the first axial direction X1 side. In the present embodiment, the end surface on the shaft second direction X2 side of the shaft tubular portion 48 is a contact portion 49 that contacts the end surface on the shaft first direction X1 side of the sun gear meshing portion 10 of the sun gear S.
The locking member 7 is disposed such that an axial gap is formed between the locking member 7 and the sun gear S in a state where the contact portion 49 is in contact with the sun gear S. In the present embodiment, an axial gap is formed between the end of the axially extending portion 26 on the second axial direction X2 side and the end of the connecting portion 11 on the first axial direction X1 side. Is arranged.

<Cylindrical member 30>
A meshing portion 31 (hereinafter referred to as a ring gear meshing portion 31) of the ring gear R with the pinion gear P is provided on the inner peripheral surface 76b of the cylindrical member 30 formed in a cylindrical shape. An output gear O is provided on the outer peripheral surface 76 a of the cylindrical member 30.
In this embodiment, the cylindrical member 30 is formed in a cylindrical shape over the entire axial direction. A planetary gear mechanism PG is arranged inside the cylindrical member 30 in the radial direction. The ring gear meshing portion 31 and the output gear O are formed integrally with the cylindrical member 30. The ring gear meshing portion 31 is formed near the center in the axial direction of the inner peripheral surface 76 b of the tubular member 30. Components of the planetary gear mechanism PG such as the pinion gear P, the carrier CA, and the sun gear S are arranged on the radially inner side of the cylindrical member 30. That is, the entire planetary gear mechanism PG is disposed at a position radially inward of the cylindrical member 30 and overlaps with the cylindrical member 30 in the radial direction. The output gear O is formed at the end of the outer peripheral surface 76a of the cylindrical member 30 on the side in the second axial direction X2. The output gear O meshes with the first gear 92 of the counter gear mechanism Ct.

An inner peripheral surface 76b of the cylindrical member 30 is rotatably supported with respect to the case 5 via the first ring gear bearing 40 on the axial first direction X1 side with respect to the ring gear meshing portion 31, and the ring gear meshing portion. 31 is supported so as to be rotatable with respect to the case 5 via a second ring gear bearing 41 on the axial second direction X2 side.
In the present embodiment, the inner peripheral surface 76b of the cylindrical member 30 is rotated from the radially inner side by the outer peripheral surface 58a of the first output protrusion 58 via the first ring gear bearing 40 in the vicinity of the end in the first axial direction X1. In the vicinity of the end portion in the second axial direction X2 of the shaft, the outer peripheral surface 56a of the second output projecting portion 56 is rotatably supported from the radially inner side via the second ring gear bearing 41.

  A cylindrical first bearing fitting surface 77 into which the first ring gear bearing 40 is fitted is formed on the inner peripheral surface 76b of the cylindrical member 30 in the vicinity of the end portion on the first axial direction X1 side. A cylindrical second bearing fitting surface 78 into which the second ring gear bearing 41 is fitted is formed near the end on the two-direction X2 side. The inner diameter of the first bearing fitting surface 77 is larger than the inner diameter of the inner peripheral surface 76b on the second axial direction X2 side of the first bearing fitting surface 77, and the inner diameter of the inner peripheral surface 76b is a step. A first stepped portion 79 that changes in a shape is formed. The inner diameter of the second bearing fitting surface 78 is larger than the inner diameter of the inner peripheral surface 76b on the first axial direction X1 side of the second bearing fitting surface 78. The inner diameter of the inner peripheral surface 76b is a step. A second stepped portion 80 that changes in a shape is formed.

  The first bearing fitting surface 77 is fitted to the first ring gear bearing 40 from the second axial direction X2 side, and the first stepped portion 79 is in contact with the first ring gear bearing 40 from the second axial direction X2 side. Be placed. The second bearing fitting surface 78 is fitted to the second ring gear bearing 41 from the axial first direction X1 side, and the second stepped portion 80 is in contact with the second ring gear bearing 41 from the axial first direction X1 side. Be placed.

<Ring gear bearing>
The first ring gear bearing 40 supports the ring gear R so as to be rotatable with respect to the case 5 on the axial first direction X1 side with respect to the ring gear meshing portion 31. The first ring gear bearing 40 includes a first fitting surface 40a that is fitted from the ring first direction X1 side with respect to the ring gear R or a member that rotates integrally with the ring gear R, and a second axial direction X2 with respect to the case 5. And a second fitting surface 40b fitted from the side.
In the present embodiment, the first ring gear bearing 40 is formed in a cylindrical shape. The first fitting surface 40a is a cylindrical outer peripheral surface of the first ring gear bearing 40, and is fitted to the cylindrical first bearing fitting surface 77 of the cylindrical member 30 from the first axial direction X1 side. The The second fitting surface 40b is a cylindrical inner peripheral surface of the first ring gear bearing 40, and is fitted to the cylindrical outer peripheral surface 58a of the first output protrusion 58 from the second axial direction X2 side. .

The second ring gear bearing 41 supports the ring gear R so as to be rotatable with respect to the case 5 on the second axial direction X2 side with respect to the ring gear meshing portion 31.
The second ring gear bearing 41 includes a first fitting surface 41 a that is fitted from the ring second direction X2 side to the ring gear R or a member that rotates integrally with the ring gear R, and a first shaft to the case 5. And a second fitting surface 41b fitted from the direction X1 side.
In the present embodiment, the second ring gear bearing 41 is formed in a cylindrical shape. The first fitting surface 41a is a cylindrical outer peripheral surface of the second ring gear bearing 41, and is fitted to the cylindrical second bearing fitting surface 78 of the tubular member 30 from the second axial direction X2 side. The The second fitting surface 41b is a cylindrical inner peripheral surface of the second ring gear bearing 41, and is fitted to the cylindrical outer peripheral surface 56a of the second output protrusion 56 from the first axial direction X1 side. .

  The first ring gear bearing 40 is arranged so as to have a portion overlapping with the carrier CA when viewed in the axial direction X, and the second ring gear bearing 41 has a portion overlapping with the carrier CA when viewed in the axial direction X. Is arranged. That is, the first ring gear bearing 40 is disposed on the first axial direction X1 side with respect to the carrier CA, and the second ring gear bearing 41 is disposed on the second axial direction X2 side with respect to the carrier CA. For this reason, when the power transmission device 1 to be described later is assembled, the ring gear R is connected to the input shaft I by fitting the first ring gear bearing 40 and the second ring gear bearing 41 to the cylindrical member 30. And can be moved together with the pinion gear P (see FIG. 3).

The periphery of the planetary gear mechanism PG is a storage chamber surrounded by the cylindrical member 30, the ring gear bearings 40 and 41, and the radially extending walls 54 and 57, and the oil supplied to the planetary gear mechanism PG is stored. It has a structure that tends to accumulate in the room.
An oil seal 59 is disposed between the radially inner end of the second radially extending wall 54 and the outer peripheral surface of the input shaft I, and the radially inner end of the first radially extending wall 57. The first rotating electrical machine bearing 63 is disposed between the first rotating shaft 47 and the outer peripheral surface of the first rotating shaft 47, and the vicinity of the inner side in the radial direction of the accommodation chamber is also covered with these.

1-3. Next, assembly of the power transmission device 1 will be described.
1-3-1. Problems when the locking member 7 is not provided First, unlike the present embodiment, problems when the locking member 7 is not provided will be described.
As shown in FIG. 7 according to the comparative example, when the locking member 7 is not provided, when the power transmission device 1 is assembled to the vehicle drive device 2, the sun gear S is in the axial direction X with respect to the input shaft I. Can be moved to. For this reason, after attaching the first shaft load bearing 68 disposed between the sun gear S in the axial direction X and the radially enlarged portion 16, the sun gear S is coupled to the shaft tubular portion 48 of the first rotating shaft 47. In some cases, the first shaft load bearing 68 may move from an appropriate mounting position. The first shaft load bearing 68 is sandwiched between the sun gear S and the radially enlarged portion 16 of the input shaft I in the assembled state. It is also difficult to confirm.

  When assembled to the vehicle drive device 2, the axial direction X is usually arranged along the vertical direction as shown in FIG. 7 in order to suppress the eccentricity of each rotating part due to gravity. Since the vehicle drive device 2 is assembled in order from the first axial direction X1 side, the first axial direction X1 is arranged downward in the vertical direction. For this reason, as shown in FIG. 7, the power transmission device 1 is assembled to the vehicle drive device 2 from the upper side in a state where the first axial direction X1 is directed downward.

For this reason, the sun gear S and the first shaft load bearing 68 fall off in the first axial direction X1 side with respect to the input shaft I due to gravity. In this case, only the sun gear S is first connected to the shaft cylindrical portion 48 of the first rotating shaft 47, and after the first shaft load bearing 68 is placed on the upper side of the sun gear S, the input shaft I is connected to the first shaft load. It is necessary to insert the radially inner side of the bearing 68 and the sun gear S in the first axial direction X1. During this insertion, the input shaft I and the pinion gear P may come into contact with the first shaft load bearing 68 and the first shaft load bearing 68 may be displaced. Further, since the sun gear S is a helical gear, when the pinion gear P is inserted into the sun gear S, there is a high possibility that each rotating portion rotates and the first shaft load bearing 68 is displaced. .
In particular, when the input shaft I is inserted, the other members of the power transmission device 1 must be moved at the same time, which increases the weight of the movement. For this reason, it is difficult for an operator to detect the displacement of the first shaft load bearing 68.

  The first axial load bearing 68 according to the present embodiment needs to fit the fitting portion of the first washer 69 to the inner peripheral surface of the sun gear S. However, during assembly, the input shaft I and the pinion gear P may come into contact with the first washer 69 and change to a non-fitted state. In this state, the first shaft load bearing 68 may not perform a predetermined function.

  At this time, it is necessary to insert the inserted portion 17 of the input shaft I into the radially inner side of the shaft tubular portion 48 of the first rotating shaft 47 and to fit the first input bearing 20. Further, it is necessary to fit the inner peripheral surface of the shaft coupling cylindrical portion 19 of the input shaft I to the pump drive shaft 46. Furthermore, it is necessary to fit the second fitting surface 40b of the first ring gear bearing 40 to the outer peripheral surface 58a of the first output protrusion 58, and the fitting is performed in the first shaft direction X1 while the input shaft I is inserted. It is necessary to apply power for the match. A high level of skill is required to simultaneously perform these operations while preventing the displacement of the first shaft load bearing 68 and the like, and the possibility that the displacement of the first shaft load bearing 68 will occur increases.

1-3-2. Next, a case where the locking member 7 is attached as in the present embodiment will be described.
In this case, the sun gear S is held and moved in the second shaft direction X2, and the first shaft load bearing 68 is disposed between the sun gear S and the radially enlarged portion 16, and then functions as the locking member 7. By attaching the input bearing 20, the arrangement and attachment of the first shaft load bearing 68 can be ensured. For example, in a state where the first shaft load bearing 68 is mounted at an appropriate position with respect to the radially enlarged portion 16 of the input shaft I, the sun gear S is engaged with the pinion gear P and is assembled at a position in contact with the first shaft load bearing 68. . At this time, since the sun gear S is moved and assembled as a single unit, the operation is easy and the first shaft load bearing 68 is not easily displaced. Further, the operator can operate only the sun gear S to check the arrangement and mounting state of the internal first shaft load bearing 68. And after arrangement | positioning of the sun gear S, by attaching the 1st input bearing 20 to the input shaft I, it is controlled that the sun gear S moves to the shaft first direction X1 side. Thereby, the state by which arrangement | positioning and attachment of the 1st axial load bearing 68 were ensured can be maintained.

As shown in FIG. 3, when the power transmission device 1 is assembled to the vehicle drive device 2 after the first input bearing 20 is mounted, even if the first shaft direction X1 is arranged vertically downward, the first input bearing 20, the sun gear S and the first shaft load bearing 68 can be prevented from falling off toward the first shaft direction X1 with respect to the input shaft I due to gravity, and the arrangement and attachment of the first shaft load bearing 68 are ensured. The state can be maintained.
In the present embodiment, the end portion on the axial second direction X2 side of the axially extending portion 26 supports the end portion on the axial first direction X1 side of the connecting portion 11 from below, so that the sun gear S and the first axial load are supported. The bearing 68 is restricted from moving downward with respect to the input shaft I. At this time, although the space between the sun gear S and the radially enlarged portion 16 is somewhat widened, it is unlikely that the input shaft I contacts the first washer 69 and changes to a non-fitted state.
Therefore, in this state, the connecting portion 11 of the sun gear S is connected to the shaft cylindrical portion 48 of the first rotating shaft 47, or the inserted portion 17 of the input shaft I is connected to the diameter of the shaft cylindrical portion 48 of the first rotating shaft 47. Inserted in the direction and fitted to the first input bearing 20, or the inner peripheral surface of the shaft connecting tubular portion 19 of the input shaft I is fitted to the pump drive shaft 46, or the second ring gear bearing 40 Even when the fitting surface 40b is fitted to the case 5, the state in which the arrangement and attachment of the first shaft load bearing 68 are ensured can be maintained. Therefore, the arrangement and attachment of the first shaft load bearing 68 can be ensured.

  Further, as shown in FIG. 3, when the power transmission device 1 is assembled, the first ring gear bearing 40 and the second ring gear bearing 41 are fitted in the cylindrical member 30 in advance, so that the cylindrical shape of the ring gear R is obtained. The bearings 40 and 41 on both sides fitted to the member 30 are in a state of sandwiching the carrier CA in a state overlapping with the carrier CA when viewed in the axial direction X. Therefore, the first ring gear bearing 40 and the second ring gear bearing 41 can function as a regulating member that regulates the separation of the ring gear R from the carrier CA and the pinion gear P. Further, the first input bearing 20 restricts the sun gear S from being separated from the input shaft I, the carrier CA, and the pinion gear P. Therefore, the entire planetary gear mechanism PG and the input shaft I constituting the power transmission device 1 can be modularized, and the power transmission device 1 can be efficiently assembled.

  As shown in FIG. 4, when the connecting portion 11 of the sun gear S is connected to the shaft tubular portion 48 of the first rotating shaft 47, the end surface (contact portion 49) of the shaft tubular portion 48 on the second axial direction X2 side. ) Supports the end surface of the sun gear meshing portion 10 of the sun gear S on the first axial direction X1 side from below. Then, the end surface of the sun gear meshing portion 10 of the sun gear S on the side in the second axial direction X2 is located below the end surface on the first axial direction X1 side of the radially expanding portion 16 of the input shaft I via the first shaft load bearing 68. Support from the side. For this reason, the space | interval of the axial direction X of the sun gear S and the radial direction expansion part 16 becomes narrow, the axial direction 2nd X2 side edge part of the axial direction extension part 26, and the axial direction 1 direction X1 side of the connection part 11 are. Increases the distance from the edge.

  In this state, as shown in FIG. 2, the second shaft load bearing 67 is placed on the upper side of the radially enlarged portion 16, and the second fitting surface 41 b of the second ring gear bearing 41 is placed on the second fitting surface 41 b from the second axial direction X2 side. When the outer peripheral surface 56a of the two-output protrusion 56 is fitted and the second case 5b is fastened to the first case 5a, the axial position of the radially expanded portion 16 is fixed. Therefore, it fixes in the state which the space | interval of the edge part by the side of the axial 2nd direction X2 of the axial direction extension part 26 and the edge part by the side of the axial 1st direction X1 of the connection part 11 spreads. Thereby, after the assembly of the power transmission device 1 is completed, it is possible to suppress the occurrence of torque loss due to frictional resistance due to the axially extending portion 26 contacting the connecting portion 11.

2. Second Embodiment A second embodiment of the power transmission device 1 according to the present invention will be described with reference to FIGS. 5 and 6.
The power transmission device 1 of the present embodiment is different from the first embodiment in the form and arrangement of the first input bearing 20, the locking member 7, and the recess 18.
In the present embodiment, unlike the first embodiment, the first input bearing 20 is not provided with the function of the locking member 7, and the locking member 7 is provided separately from the first input bearing 20. Yes. And the 1st input bearing 20 is not fitted by the recessed part 18, but the latching member 7 is fitted.

As shown in FIG. 6, the first input bearing 20 includes a second fitting portion that is fitted to the inserted portion 17 from the first axial direction X1 side.
The first input bearing 20 is a shell-type needle bearing that includes a plurality of rollers 23, a cage 24 that holds the plurality of rollers 23, and a shell 27 that covers the outer side in the radial direction and both axial sides of the rollers 23 and the cage 24. Bearings. The outer peripheral surface of the shell 27 is fitted to the inner peripheral surface of the input support portion 51. The inserted portion 17 of the input shaft I is fitted inside the first input bearing 20 in the radial direction.

In this embodiment, the recessed part 18 is formed in the outer peripheral surface of the to-be-inserted part 17 of the 2nd axial direction X2 side from the 1st input bearing 20, as shown in FIG.
In the present embodiment, the locking member 7 is a cylindrical snap ring and is fitted in the recess 18 to restrict relative movement of the locking member 7 in the axial direction X with respect to the input shaft I.

  As shown in FIG. 6, the locking member 7 is radially outside the inserted portion 17 on the second axial direction X2 side of the first input bearing 20, and the input support portion into which the first input bearing 20 is fitted. The sun gear connecting portion 50 having a diameter larger than 51 is disposed in the radially inner space. The locking member 7 is arranged on the first axial direction X1 side of the connecting portion 11 of the sun gear S, and the end of the locking member 7 on the second axial direction X2 side is the first axial direction of the connecting portion 11. It is arranged so as to overlap with the end portion on the X1 side when viewed in the axial direction X. That is, the locking member 7 is attached to the outer peripheral surface (recessed portion 18) of the input shaft I in a state where relative movement in the axial direction X is restricted on the first axial direction X1 side with respect to the sun gear S. As shown in FIG.

  The locking member 7 is disposed such that an axial gap is formed between the locking member 7 and the sun gear S in a state where the contact portion 49 is in contact with the sun gear S. In this embodiment, it arrange | positions so that the clearance gap of the axial direction X may be formed between the edge part by the side of the axial 2nd direction X2 of the latching member 7, and the edge part by the side of the axial 1st direction X1 of the connection part 11. Has been.

2-1. Assembling the power transmission device 1 In this embodiment, as shown in FIG. 5, the end of the locking member 7 on the second axial direction X2 side is lower than the end of the connecting portion 11 on the first axial direction X1 side. The sun gear S and the first shaft load bearing 68 are restricted from moving downward relative to the input shaft I. Therefore, it is possible to maintain a state in which the first shaft load bearing 68 is securely arranged and attached.
In the present embodiment, the outer peripheral surface of the shell 27 is fitted and fixed to the inner peripheral surface of the input support portion 51 by press fitting. The inserted portion 17 of the input shaft I is inserted inside the first input bearing 20 in the radial direction.

  Then, as shown in FIG. 5, when the connecting portion 11 of the sun gear S is connected to the shaft tubular portion 48 of the first rotating shaft 47, the second axial direction of the locking member 7 is the same as in the first embodiment. The distance between the end portion on the X2 side and the end portion on the first axial direction X1 side of the connecting portion 11 is widened, and when the second case 5b, the second shaft load bearing 67 and the like are assembled in this state, the distance is widened. Fixed in state.

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

(1) In the above embodiment, the case where the vehicle drive device 2 includes the second rotating electrical machine MG2 has been described as an example. However, the embodiment of the present invention is not limited to this. That is, it may be configured not to include the second rotating electrical machine MG2.

(2) In the above embodiment, the case where the first rotating shaft 47 is configured integrally with the rotor shaft of the first rotating electrical machine MG1 has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the first rotating shaft 47 may be formed of a separate member from the rotor shaft of the first rotating electrical machine MG1. In this case, the first rotating shaft 47 may be configured to be connected to the rotor shaft of the first rotating electrical machine MG1 and rotate integrally. Alternatively, the first rotating shaft 47 may be configured to be drivingly connected to the rotor shaft of the first rotating electrical machine MG1 via a gear mechanism or the like.

(3) In the above embodiment, the case where the cylindrical member 30 is formed as an integral member, and the ring gear meshing portion 31 and the output gear O are formed integrally with the cylindrical member 30 has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the cylindrical member 30 may be configured by connecting a plurality of members, and the ring gear meshing portion 31 or the output gear O may be configured by a member different from the cylindrical member 30.

  The present invention relates to an input member that is drivingly connected to an internal combustion engine, an output member that is drivingly connected to wheels, and a planetary gear mechanism that distributes and transmits torque transmitted from the input member to the output member and the rotating electrical machine. And it can utilize suitably for the power transmission device provided with these.

DESCRIPTION OF SYMBOLS 1: Power transmission device 2: Vehicle drive device 5: Case 5a: First case 5b: Second case 7: Locking member 10: Engagement part (sun gear engagement part) of the sun gear with the pinion gear
11: Connection part (spline connection part)
14: Shaft cylindrical portion 15: Through portion 16: Radially expanded portion 17: Inserted portion 18: Recessed portion 19: Shaft coupling tubular portion 20: First input bearing (input bearing)
23: Roller 24: Cage (locking member)
25: Roller holding part 26: Axial extension part 27: Shell 30: Cylindrical member 31: Engagement part with ring gear pinion gear (ring gear engagement part)
40: First ring gear bearing (ring gear bearing)
40a: first fitting surface 40b: second fitting surface 41: second ring gear bearing 41a: first fitting surface 41b: second fitting surface 46: pump drive shaft 47: first rotating shaft (rotating member)
48: Shaft cylindrical portion 49: Contact portion 50: Sun gear connecting portion 51: Input support portion 54: Second radial extending wall 56: Second output projecting portion 56a: Outer peripheral surface 57: First radial extending wall 58: first output protrusion 58a: outer peripheral surface 59: oil seal 60: peripheral wall 63: first rotating electrical machine bearing 64: second input bearing 67: second shaft load bearing 68: first shaft load bearing (shaft load bearing)
69: first washer 70: second washer 75: gear housing chamber 76a: outer peripheral surface 76b of cylindrical member: inner peripheral surface 77 of cylindrical member: first bearing fitting surface 78: second bearing fitting surface 79: First step portion 80: Second step portion 86: Second rotating shaft 87: Electric machine output gear 88: Axle 90: Annular plate portion 91: Counter shaft 92: First gear 93: Second gear 96: Differential input Gear AX: Rotational axis CA: Carrier Ct: Counter gear mechanism DF: Output differential gear device DP: Damper E: Internal combustion engine Eo: Internal combustion engine output shaft I: Input shaft (input member)
MG1: First rotating electrical machine (rotating electrical machine)
MG2: Second rotating electrical machine O: Output gear (output member)
OP: Oil pump P: Pinion gear PG: Planetary gear mechanism R: Ring gear Ro1: First rotor (rotor)
Ro2: second rotor S: sun gear W: wheel X: axial direction X1: axial first direction X2: axial second direction

Claims (5)

An input member drivingly connected to the internal combustion engine, an output member drivingly connected to the wheel, and a planetary gear mechanism that distributes and transmits torque transmitted from the input member to the output member and the rotating electrical machine. A power transmission device,
An axial load bearing that receives an axial load; and
The planetary gear mechanism includes a carrier that supports a pinion gear, a sun gear and a ring gear that mesh with the pinion gear, and the sun gear does not pass through the carrier and the ring gear. The ring gear is drivingly connected to the output member without going through the sun gear and the carrier, the carrier is drivingly connected to the input member without going through the sun gear and the ring gear,
The sun gear is formed in a cylindrical shape, and includes a connecting portion with the rotating electrical machine on the first axial direction side that is one side in the axial direction from the meshing portion with the pinion gear,
The input member is configured to be rotatable relative to the sun gear, and has a penetrating portion that penetrates the inner side in the radial direction of the sun gear in the axial direction, and an axial direction opposite to the first axis direction with respect to the sun gear. On the two-direction side, provided with a radially enlarged portion formed larger in the radial direction than the penetrating portion,
The axial load bearing is disposed between the sun gear in the axial direction and the radially enlarged portion,
The locking member is attached to the outer peripheral surface of the input member in a state in which relative movement in the axial direction is restricted on the first axial direction side with respect to the sun gear, and the sun gear is viewed in the axial direction. A power transmission device having an overlapping part. A ring gear bearing that rotatably supports the ring gear;
An input bearing that rotatably supports the input member;
The rotating member that is drivingly connected to the rotor of the rotating electrical machine includes a cylindrical shaft cylindrical portion that opens at least in the second axial direction side,
The connecting portion is a spline connecting portion that is spline-fitted from the shaft second direction side to the shaft tubular portion,
The ring gear bearing supports the ring gear so as to be rotatable with respect to the case on the first axial direction side with respect to the meshing portion with the pinion gear, and the shaft with respect to the ring gear or a member that rotates integrally with the ring gear. A fitting surface fitted from the first direction side, and a fitting surface fitted from the second axial direction side to the case;
The input member includes a portion to be inserted that is inserted from the axial second direction side into the radial inner side of the axial cylindrical portion,
The input bearing supports the insertion portion in a radial direction so as to be rotatable with respect to the shaft tubular portion, and is fitted to the shaft tubular portion from the second shaft direction side. The power transmission device according to claim 1, further comprising one or both of a fitting portion fitted to the inserted portion from the first axial direction side. An input bearing that rotatably supports the input member;
The rotating member that is drivingly connected to the rotor of the rotating electrical machine includes a cylindrical shaft cylindrical portion that opens at least in the second axial direction side,
The input member includes a portion to be inserted that is inserted from the axial second direction side into the radial inner side of the axial cylindrical portion,
The input bearing includes a plurality of rollers and a cage that holds the plurality of rollers, and is configured to support the inserted portion in a radial direction so as to be rotatable with respect to the shaft tubular portion,
The power transmission device according to claim 1, wherein the locking member is configured by the retainer attached to the inserted portion in a state where relative movement in the axial direction is restricted. The rotating member that is drivingly connected to the rotor of the rotating electrical machine includes a contact portion that contacts the sun gear from the first axial direction side,
The said locking member is arrange | positioned so that the said axial clearance may be formed between the said locking member and the said sun gear in the state which the said contact part contact | abutted to the said sun gear. 4. The power transmission device according to claim 3. The meshing portion of the ring gear with the pinion gear is formed on the inner peripheral surface of a cylindrical member disposed radially outside the sun gear and the carrier,
The carrier is coupled to rotate integrally with the radially enlarged portion;
An inner peripheral surface of the cylindrical member is supported rotatably with respect to the case via a first ring gear bearing on the first axial direction side with respect to the meshing portion of the ring gear, and the ring gear It is rotatably supported with respect to the case via a second ring gear bearing on the second axial direction side with respect to the meshing portion,
An output gear as the output member is provided on the outer peripheral surface of the cylindrical member,
The first ring gear bearing is arranged to have a portion overlapping with the carrier when viewed in the axial direction, and the second ring gear bearing has a portion overlapping with the carrier when viewed in the axial direction. The power transmission device according to any one of claims 1 to 4, wherein the power transmission device is arranged.

Images