JP2015155292A - vehicle drive device - Google Patents

vehicle drive device Download PDF

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Publication number
JP2015155292A
JP2015155292A JP2014202280A JP2014202280A JP2015155292A JP 2015155292 A JP2015155292 A JP 2015155292A JP 2014202280 A JP2014202280 A JP 2014202280A JP 2014202280 A JP2014202280 A JP 2014202280A JP 2015155292 A JP2015155292 A JP 2015155292A
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Japan
Prior art keywords
portion
member
cylindrical
rotor
input
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Pending
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JP2014202280A
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Japanese (ja)
Inventor
糟谷 悟
Satoru Kasuya
悟 糟谷
昌士 鬼頭
Masashi Kito
昌士 鬼頭
祐一 関
Yuichi Seki
祐一 関
浩樹 新谷
Hiroki Shintani
浩樹 新谷
亮介 近藤
Ryosuke Kondo
亮介 近藤
Original Assignee
アイシン・エィ・ダブリュ株式会社
Aisin Aw Co Ltd
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Priority to JP2014006067 priority Critical
Priority to JP2014006067 priority
Application filed by アイシン・エィ・ダブリュ株式会社, Aisin Aw Co Ltd filed Critical アイシン・エィ・ダブリュ株式会社
Priority to JP2014202280A priority patent/JP2015155292A/en
Publication of JP2015155292A publication Critical patent/JP2015155292A/en
Pending legal-status Critical Current

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    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/60Other road transportation technologies with climate change mitigation effect
    • Y02T10/62Hybrid vehicles
    • Y02T10/6213Hybrid vehicles using ICE and electric energy storage, i.e. battery, capacitor
    • Y02T10/6221Hybrid vehicles using ICE and electric energy storage, i.e. battery, capacitor of the parallel type

Abstract

PROBLEM TO BE SOLVED: To realize a vehicle drive device that can achieve miniaturization while having a structure which can supply a proper amount of oil with more traveling states, and supporting a rotor fixing part properly in a radial direction.
SOLUTION: A vehicle drive device comprises a pump drive member (60), a rotor fixing member (40), and two one-way clutches (F1, F2) for restricting the relative rotation of an input member (10) and the pump drive member (60) respectively. The rotor fixing member (40) rotating integrally with a rotor (Ro) is supported to an output member (50) by a contact part (A2) in contact with the output member (50). The contact part (A2) is disposed so as to have a portion which overlaps with at least one of the two one-way clutches (F1, F2) as viewed in a radial direction.
COPYRIGHT: (C)2015,JPO&INPIT

Description

  The present invention includes an input member connected to an internal combustion engine, a rotating electrical machine, a rotor fixing member fixed to a rotor of the rotating electrical machine, an output member that rotates integrally with the rotor fixing member and is drivingly connected to a wheel, and oil And a pump for a vehicle.

  In a vehicle drive device, the support structure of each rotating member is an important matter that can affect the device characteristics. In general, the device structure is determined in consideration of appropriately supporting each rotating element in the radial direction. For example, in an apparatus described in US Patent Application Publication No. 2013/0291374 (Patent Document 1), a rotor fixing member (rotor drive element 23) is substantially transmitted to a casing (transmission casing 2) only through a bearing. Directly supported. An output member [transmission input shaft 3] is supported radially on the inner peripheral surface of the case independently of the rotor fixing member.

  In addition, in a vehicle drive device, in order to appropriately perform cooling, lubrication, control, and the like, it may be required to secure an oil supply amount from an oil pump in more traveling states. In this regard, in the device of Patent Document 1, two one-way clutches [flywheel 30, 31] are used to drive the oil pump drive power source and output member [internal combustion engine-drive element 22] and output according to the running state. It is understood that a structure that can be automatically switched between members is adopted.

  However, in the apparatus of Patent Document 1, two one-way clutches are arranged at different positions in the axial direction, and a bearing that supports the rotor fixing member is arranged at an axial position different from both of the two one-way clutches. For this reason, the axial length of the apparatus is enlarged, and the entire apparatus cannot be increased in size.

US Patent Application Publication No. 2013/0291374

  Therefore, realization of a vehicle drive device that can reduce the size of the entire device while appropriately supporting the rotor fixing member in the radial direction while having a configuration capable of supplying an appropriate amount of oil in a larger number of traveling states. Is desired.

A vehicle drive device according to the present disclosure includes:
An input member drivingly connected to the internal combustion engine;
A rotating electrical machine having a rotor and a stator;
A rotor fixing member fixed to the rotor and rotating integrally with the rotor;
An output member that is supported in a radial direction so as to be relatively rotatable with respect to a case to which the stator is fixed, and that rotates integrally with the rotor fixing member and is drivingly connected to a wheel;
A pump drive member that is drivingly connected to the oil pump;
A first one-way clutch that regulates relative rotation between the rotor fixing member and the pump drive member when the rotation speed of the rotor fixing member is equal to or higher than the rotation speed of the input member;
A second one-way clutch that regulates relative rotation between the input member and the pump drive member when the rotational speed of the input member is equal to or higher than the rotational speed of the rotor fixing member;
The rotor fixing member includes a contact portion that contacts the output member, and is supported by the contact portion in a radial direction with respect to the output member, and the rotor fixing member is interposed between the contact portion and the support bearing. Supported relative to the case,
The contact portion is disposed so as to have a portion overlapping at least one of the first one-way clutch and the second one-way clutch when viewed in the radial direction.

According to this configuration, the pump driving member can be driven by the input member and the rotor fixing member having the higher rotational speed. Therefore, if either the rotor fixing member or the input member is rotating, the pump driving member can be driven, and an appropriate amount of oil can be supplied in a relatively large number of running states.
In addition, since the rotor fixing member is directly supported in the radial direction in a state where the rotor fixing member is in contact with the output member, the rotor fixing member is arranged in the radial direction as compared with the configuration in which the rotor fixing member is supported in the radial direction via the bearing. It is possible to achieve radial compactness while supporting appropriately. Furthermore, since the contact portion of the rotor fixing member with the output member overlaps with at least one of the first one-way clutch and the second one-way clutch when viewed in the radial direction, it is possible to reduce the size by shortening the shaft length. Therefore, it is possible to reduce the size of the entire apparatus while appropriately supporting the rotor fixing member in the radial direction.

  Further features and advantages of the technology according to the present disclosure will become clearer from the following description.

Schematic diagram showing the schematic configuration of a vehicle drive device Partial cross-sectional view of a vehicle drive device Partial enlarged view of FIG. Sectional drawing of the principal part in the 1st position of FIG. Sectional drawing of the principal part in the 2nd position of FIG. Partial enlarged view of FIG. Partial sectional view showing another aspect of the vehicle drive device Cross-sectional view of the main part in FIG. The schematic diagram which shows another aspect of the drive device for vehicles

  Hereinafter, embodiments of the present invention will be described. However, the scope of the present invention is not limited by the embodiments described below.

  The vehicle drive device 1 according to the present embodiment is a vehicle drive device (hybrid vehicle) for driving a vehicle (hybrid vehicle) provided with both the internal combustion engine E and the rotating electrical machine MG as a drive force source for the wheels W of the vehicle. Drive device). Specifically, the vehicle drive device 1 is configured as a drive device for a 1-motor parallel type hybrid vehicle.

  In the following description, unless otherwise specified, the “axial direction L”, “radial direction”, and “circumferential direction” are defined based on the rotational axis of the input shaft 10. In addition, the direction about each member represents the direction in the state in which they were assembled | attached to the vehicle drive device 1. FIG. Moreover, the term regarding the direction, position, etc. about each member is a concept including the state which has the difference by the error which can be accept | permitted on manufacture.

  In the following description, “drive connection” means a state in which two rotating elements are connected so as to be able to transmit a driving force (synonymous with torque). This concept includes a state in which the two rotating elements are connected so as to rotate integrally, and a state in which the driving force is transmitted through one or more transmission members. Such transmission members include various members (shafts, gear mechanisms, belts, etc.) that transmit rotation at the same speed or at different speeds, and engaging devices (frictions) that selectively transmit rotation and driving force. Engagement devices, meshing engagement devices, etc.).

  The “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that performs both functions of the motor and the generator as necessary.

  Further, regarding the arrangement of two members, “overlapping when viewed in a certain direction” means that the virtual straight line is 2 when the virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line. It means that a region that intersects both members is present at least in part. In this case, when the virtual straight line intersects both of the two members in the entire region of the member of interest, regarding the arrangement of the member of interest (arrangement with respect to the counterpart member), “they overlap completely as seen in a certain direction” " On the other hand, when the imaginary straight line intersects both of the two members only in a partial region of the member of interest, regarding the arrangement of the member of interest (arrangement with respect to the counterpart member), "Duplicate". In addition, when mentioning about arrangement | positioning of three or more members, it means that the area | region where the said virtual straight line crosses all three or more members exists in at least one part.

  As shown in FIG. 1, a vehicle drive device 1 includes an input shaft 10 that is drivingly connected to an internal combustion engine E, a rotating electrical machine MG, an output shaft 50 that is drivingly connected to wheels W, a transmission TM, and an axle. AX. In the present embodiment, the vehicle drive device 1 further includes an engagement device CL and an oil pump OP. The engagement device CL, the rotating electrical machine MG, the output shaft 50, and the transmission device TM are provided in the order of description from the input shaft 10 side in the power transmission path connecting the input shaft 10 and the axle AX. These are accommodated in a case (drive device case) 2 (see FIG. 2). In the present embodiment, the input shaft 10 corresponds to an “input member”.

  The internal combustion engine E is a prime mover (such as a gasoline engine or a diesel engine) that is driven by combustion of fuel inside the engine to extract power. In the present embodiment, an internal combustion engine output shaft (crankshaft or the like) that is an output shaft of the internal combustion engine E is drivingly connected to the input shaft 10. In the present embodiment, the output shaft of the internal combustion engine is connected to the input shaft 10 via the damper D. The internal combustion engine output shaft and the input shaft 10 may be directly connected.

  An engaging device CL is interposed between the input shaft 10 and the rotating electrical machine MG. The engagement device CL selectively connects the internal combustion engine E and the input shaft 10 to the rotating electrical machine MG and the output shaft 50. In other words, the engagement device CL can select a state in which the input shaft 10 and the output shaft 50 are connected and a state in which the input shaft 10 and the output shaft 50 are released. In other words, the engagement device CL connects or releases the input shaft 10 and the output shaft 50. In the present embodiment, the engaging device CL is configured to be hydraulically driven. Further, the engagement device CL functions as an internal combustion engine disconnecting device that disconnects the internal combustion engine E from the wheel W in a state where the engagement is released.

  The rotating electrical machine MG can perform a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. . The rotating electrical machine MG is electrically connected to a power storage device (battery, capacitor, etc.). The rotating electrical machine MG is powered by receiving power from the power storage device, or supplies the power storage device with power generated by the torque of the internal combustion engine E or the inertial force of the vehicle. The rotating electrical machine MG is drivingly connected so as to rotate integrally with the output shaft 50. In the present embodiment, the output shaft 50 corresponds to an “output member”.

  The output shaft 50 is connected to the transmission apparatus TM. The output shaft 50 functions as a shift input shaft (an example of a shift input member) that inputs rotation to the transmission apparatus TM. In the present embodiment, the transmission apparatus TM is configured to include an automatic or manual transmission mechanism provided with a changeable gear ratio, a counter gear mechanism, and a differential gear mechanism. The transmission TM transmits the rotation and torque input to the output shaft 50 according to the gear ratio at that time, converts the torque, and transmits the torque and torque to the pair of left and right axles AX and wheels W. Accordingly, the vehicle drive device 1 can cause the vehicle to travel by transmitting the torque of at least one of the internal combustion engine E and the rotating electrical machine MG to the wheels W.

  In the vehicle drive device 1 according to the present embodiment, the input shaft 10 and the output shaft 50 are arranged coaxially, and the axle AX is parallel to the input shaft 10 and the output shaft 50 and is arranged on a separate axis. It has a configuration. Such a configuration is suitable as a configuration of the vehicle drive device 1 mounted on, for example, an FF (Front Engine Front Drive) vehicle.

  As shown in FIG. 2, the case 2 includes a first divided case portion 21 that is divided in the axial direction L, a second divided case portion 22, and a third divided case portion 24. The first split case portion 21 mainly accommodates the transmission device TM. The second split case portion 22 is provided on the input shaft 10 side with respect to the first split case portion 21 in the axial direction L, and mainly accommodates the engagement device CL and the rotating electrical machine MG. The third divided case portion 24 is provided further on the internal combustion engine E side in the axial direction L than the second divided case portion 22, and closes the opening of the second divided case portion 22 on the internal combustion engine E side.

  A shaft support member 28 constituting an annular plate-like wall portion extending in the radial direction is fixed to the first split case portion 21 from the rotating electrical machine MG side. The shaft support member 28 is one of the members constituting the case 2 and is disposed on the opposite side (transmission device TM side) from the engagement device CL side in the axial direction L with respect to the rotor fixing member 40 described later. Yes. The shaft support member 28 also serves as a component member (at least one of the pump body and the pump case) of the pump case that houses a pump main body constituting the oil pump OP, for example. In this case, the shaft support member 28 may be formed with an oil passage through which oil discharged from the oil pump OP flows. The shaft support member 28 has a cylindrical shaft support portion 29 extending from the plate-like portion of the shaft support member 28 toward the side opposite to the rotating electrical machine MG side (transmission device TM side) at the radially inner end thereof. . The cylindrical shaft support portion 29 may include, for example, a cylindrical member for constituting an oil passage. In the present embodiment, the first divided case portion 21 is one case portion constituting the case 2 and can be referred to as a “first case portion”. Further, the shaft support member 28 corresponds to a “case wall”.

  The second divided case portion 22 joined to the first divided case portion 21 has an annular plate-shaped intermediate wall 23 extending in the radial direction. The intermediate wall 23 is disposed between the shaft support member 28 and the rotating electrical machine MG in the axial direction L. The third divided case portion 24 joined to the second divided case portion 22 has an annular plate-like end wall 25 extending in the radial direction. The end wall 25 is disposed on the internal combustion engine E side in the axial direction L with respect to the rotating electrical machine MG. The end wall 25 is complementary to the outer shape of the stator St, the rotor Ro, and the engagement device CL of the rotating electrical machine MG, and is closer to the shaft support member 28 side (internal combustion engine E side) from the radially outer side toward the radially inner side. It is formed in a stepped plate shape so as to be located on the opposite side. The end wall 25 has a stepped portion 26 toward the shaft support member 28 at its radially inner end (see FIG. 3). The first bearing B <b> 1 is fixed to the step portion 26. A normal ball bearing is used as the first bearing B1. In the present embodiment, the third divided case portion 24 is another case portion constituting the case 2 (different from the first divided case portion 21), and can be referred to as a “second case portion”.

  As shown in FIG. 3, the input shaft 10 is disposed so as to penetrate the third divided case portion 24 in the axial direction L. The input shaft 10 connects the input main body part 11, the input cylindrical part 12 formed in a cylindrical shape larger in diameter than the input main body part 11, and the input main body part 11 and the input cylindrical part 12. And an annular plate-like input connecting portion 13 extending in the radial direction. The input main body 11 includes a solid part 11A serving as a connecting part to the damper D and a hollow part 11B integrally formed on the output shaft 50 side with respect to the solid part 11A. The end of the output shaft 50 is accommodated in the space inside the hollow portion 11B in the radial direction. The input cylindrical portion 12 extends from the position of the open end (the end opposite to the solid portion 11A side) in the hollow portion 11B toward the shaft support member 28 side. The input connecting portion 13 connects the open-side end portion of the hollow portion 11B and the end portion on the end wall 25 side of the input cylindrical portion 12 on the shaft support member 28 side (in the case 2) from the end wall 25. doing.

  The input shaft 10 is supported so as to be rotatable relative to the case 2. In the present embodiment, the input shaft 10 is fixed to the step portion 26 of the end wall 25 constituting the third divided case portion 24 and is in contact with the outer peripheral surface of the input main body portion 11 (hollow portion 11B in this example). Is supported in the axial direction L and in the radial direction with respect to the third divided case portion 24 via the first bearing B1 disposed in the inner space. In the present embodiment, the first bearing B1 is a bearing that supports the input shaft 10 in the axial direction L and the radial direction so as to be relatively rotatable with respect to the case 2, and can be referred to as an “input bearing”. The first bearing B1 is fixed to the end wall 25 in a state where the first bearing B1 is in contact with a surface (contact surface 26a) facing the shaft support member 28 side in the stepped portion 26. A seal member is also disposed between the input main body 11 and the end wall 25.

  In the present embodiment, the engagement device CL is configured as a friction engagement device. The engagement device CL includes a friction plate 31, an inner support member 32, an outer support member 33, and a pressing member 34. These are arranged coaxially with the input shaft 10 and the output shaft 50. The friction plate 31 has a pair of an inner plate and an outer plate. A plurality of inner plates and outer plates are provided, and these are alternately arranged along the axial direction L. The plurality of inner plates are supported in the radial direction from the inner side in the radial direction by the inner support member 32 connected so as to rotate integrally with the input cylindrical portion 12. The plurality of outer plates are supported in the radial direction from the radially outer side by the outer support member 33. The outer support member 33 is connected so as to rotate integrally with a rotor fixing member 40 described later. The pressing member 34 moves along the axial direction L according to the supplied hydraulic pressure and presses the plurality of friction plates 31 together. The engagement device CL also includes a biasing member 35 for biasing the pressing member 34 toward the counter-pressing direction.

  The engaging device CL is disposed so as to have a portion that is radially inward of the rotating electrical machine MG and overlaps the rotating electrical machine MG when viewed in the radial direction. The engaging device CL is arranged so as to have a portion overlapping the stator St and the rotor Ro when viewed in the radial direction inside the rotor Ro of the rotating electrical machine MG. The engagement device CL is disposed so as to completely overlap with the stator St as viewed in the radial direction and partially overlap with the rotor Ro. In this example, approximately half of the friction plates 31 located on the internal combustion engine E side and approximately half of the stator St and the rotor Ro on the shaft support member 28 side are arranged so as to overlap each other when viewed in the radial direction. Further, the pressing member 34 is disposed so as to completely overlap the stator St and the rotor Ro as viewed in the radial direction.

  The rotating electrical machine MG includes a stator St fixed to the case 2 (in this example, the second divided case portion 22), and a rotor Ro that is rotatably supported in the radial direction on the radially inner side of the stator St. The stator St and the rotor Ro each include laminated steel plates laminated in the axial direction L. The rotor Ro is configured to have an axial dimension slightly longer than the stator St. That is, both end portions in the axial direction L of the laminated steel plates constituting the rotor Ro are located slightly outside the both ends in the axial direction L of the laminated steel plates constituting the stator St. The rotor Ro rotates integrally with a rotor fixing member that is fixed to the rotor Ro. The rotor Ro is supported in the radial direction by a rotor fixing member 40 extending radially inward from the rotor Ro. In this sense, the rotor fixing member 40 can also be referred to as a “rotor support member” that supports the rotor Ro in the radial direction.

  The rotor fixing member 40 includes a cylindrical fixing part 41, a radial connecting part 44, and a cylindrical support part 48. The cylindrical fixing portion 41 and the cylindrical support portion 48 are each formed in a cylindrical shape extending in the axial direction L. Thus, the rotor fixing member 40 has two cylindrical portions, and in this embodiment, the cylindrical fixing portion 41 which is one of them can be referred to as a “first cylindrical portion”. The other cylindrical support portion 48 can be referred to as a “second cylindrical portion”. The cylindrical fixing portion 41 (first cylindrical portion) holds the rotor Ro from the radially inner side in a state where the outer peripheral surface is in contact with the rotor Ro. The cylindrical fixing portion 41 is connected to rotate integrally with the outer support member 33 of the engagement device CL.

  The radial direction connecting portion 44 is formed in an annular plate shape that extends radially inward from the end portion on the shaft support member 28 side in the axial direction L of the cylindrical fixing portion 41. The radial direction connection part 44 is arrange | positioned so that the axial support member 28 side in the axial direction L may be extended along radial direction with respect to the engagement apparatus CL. The radially inner portion of the radially connecting portion 44 is disposed offset from the radially outer portion toward the shaft support member 28. The radial connecting portion 44 has a stepped portion 45 toward the shaft support member 28 at the central portion in the radial direction serving as an offset boundary portion. A rotation sensor 90 is arranged using this stepped portion 45. That is, the sensor rotor 92 is disposed at the stepped portion 45, and the sensor stator 91 that is disposed to face the outer side in the radial direction is fixed to the intermediate wall 23 of the second divided case portion 22. Each of the sensor stator 91 and the sensor rotor 92 includes a laminated steel plate laminated in the axial direction L. The sensor rotor 92 is configured to have an axial dimension slightly longer than that of the sensor stator 91.

  The radial direction connecting portion 44 has a through hole 46 that is formed to penetrate in the axial direction L at a position radially inward of the stepped portion 45. A plurality of through-holes 46 are provided, and these are distributed and arranged substantially evenly in the circumferential direction. A connecting shaft 75 of a transmission gear mechanism 70 described later is disposed in the through hole 46.

  The cylindrical support portion 48 (second cylindrical portion) is formed to have a smaller diameter than the cylindrical fixing portion 41 and is disposed radially inward of the cylindrical fixing portion 41. In the present embodiment, the cylindrical support portion 48 is provided so as to extend from the radially inner end of the radial coupling portion 44 toward the internal combustion engine E side. In the present embodiment, the cylindrical support portion 48 has an outer diameter and an inner diameter that are approximately the same as the hollow portion 11B of the input main body portion 11 constituting the input shaft 10. The cylindrical support portion 48 and the hollow portion 11B are arranged side by side with a predetermined gap in the axial direction L. The cylindrical fixing part 41 and the cylindrical support part 48 constituting the rotor fixing member 40 are arranged on the same side in the axial direction L (internal combustion engine E side) with respect to the radial connection part 44. The tubular fixing portion 41, the radial connecting portion 44, and the tubular support portion 48 are formed in a bowl shape with a central tubular portion that opens toward the internal combustion engine E as a whole. The input cylindrical portion 12 of the input shaft 10 is disposed in the internal space of the rotor fixing member 40 (the space surrounded by the cylindrical fixing portion 41, the radial connecting portion 44, and the cylindrical support portion 48) and the input thereof. The engaging device CL is accommodated in the radially outer side than the cylindrical portion 12. The input cylindrical portion 12 and the engagement device CL are located between the cylindrical fixing portion 41 and the cylindrical support portion 48 in the radial direction in a state where the engagement device CL is located radially outside the input cylindrical portion 12. Is arranged.

  As shown in FIG. 3, the cylindrical support portion 48 is attached to the output shaft 50. The cylindrical support portion 48 is attached to the output shaft 50 so as to be in contact with the output shaft 50. The cylindrical support portion 48 is attached so that its inner peripheral surface is in contact with the outer peripheral surface of the output shaft 50. In the present embodiment, the cylindrical support portion 48 is attached to the output shaft 50 in a state where relative movement in the radial direction and the circumferential direction is restricted with respect to the output shaft 50. In the present embodiment, the attachment portion A between the cylindrical support portion 48 and the output shaft 50 is configured by a combination of a spline engagement portion A1 and a spigot fitting portion A2. A spline engagement portion A1 is provided at the first position P1 in the attachment portion A between the cylindrical support portion 48 and the output shaft 50, and the spline engagement portion A1 is in the second position P2 on the internal combustion engine E side in the axial direction L from the first position P1. A fitting portion A2 is provided.

  The spline engagement portion A1 is an engagement portion configured by engagement of spline teeth and spline grooves. The spline engagement portion A1 includes an involute spline engagement portion, an arc-shaped spline engagement portion, a square spline engagement portion, and the like. In this embodiment, a serration engagement portion having a similar configuration is also included. To do. FIG. 4 shows an example of a cross section of the cylindrical support portion 48 and the output shaft 50 at the first position P1. As shown in this figure, in the present embodiment, the inner peripheral surface of the cylindrical support portion 48 that is the radially inner portion of the rotor fixing member 40 is formed in a spline shape at the first position P1. The inner peripheral surface of the cylindrical support portion 48 is formed to have radial unevenness, and constitutes an inner peripheral uneven surface 48a. Moreover, the outer peripheral surface which is a radially outer portion of the output shaft 50 is also formed in a spline shape. The outer peripheral surface of the output shaft 50 is also formed to have radial irregularities, and constitutes an outer circumferential uneven surface 50a.

  The inner circumferential side irregular surface 48a of the cylindrical support portion 48 and the outer circumferential side irregular surface 50a of the output shaft 50 are arranged complementarily. In the present embodiment, the tooth tip 48c constituting the inner circumferential uneven surface 48a of the cylindrical support portion 48 and the tooth bottom 50d constituting the outer circumferential uneven surface 50a of the output shaft 50 are opposed to each other, and the cylindrical support portion. The tooth bottom 48d constituting the inner circumferential uneven surface 48a of 48 and the tooth tip 50c constituting the outer circumferential uneven surface 50a of the output shaft 50 face each other. Further, the tooth side surface 48e on one side in the circumferential direction constituting the inner circumferential side irregular surface 48a of the cylindrical support portion 48 and the tooth side surface 50e on the other circumferential side constituting the outer circumferential side irregular surface 50a of the output shaft 50 are opposed to each other. ing. When the cylindrical support portion 48 and the output shaft 50 are rotated, the tooth side surface on the rotation direction side of the driving side member of the cylindrical support portion 48 and the output shaft 50 and the anti-rotation direction of the driven side member are included. The side tooth side comes into contact. Thereby, the spline engaging portion A1 mainly restricts the relative movement of the cylindrical support portion 48 and the output shaft 50 in the circumferential direction. This spline engaging portion A1 enables transmission of driving force between the rotor fixing member 40 and the output shaft 50.

  When the attachment portion A is configured by the spline engagement portion A1 and the spigot fitting portion A2 as in the present embodiment, the tooth tip 48c of the cylindrical support portion 48, the tooth bottom 50d of the output shaft 50, and The tooth bottom 48d of the cylindrical support portion 48 and the tooth tip 50c of the output shaft 50 do not contact each other. That is, if the spigot fitting portion A2 is provided, the tooth tip 48c of the cylindrical support portion 48 and the tooth bottom 50d of the output shaft 50 are arranged with a gap in the radial direction, and the cylindrical support is provided. The tooth bottom 48d of the part 48 and the tooth tip 50c of the output shaft 50 are arranged with a gap in the radial direction. When the radial fixing of the rotor fixing member 40 is performed by the spigot fitting portion A2, the spigot fitting portion A2 comes into contact first when the shaft center of the rotor fixing member 40 and the shaft center of the output shaft 50 are displaced. The tooth bottom 48d of the cylindrical support 48 and the tooth tip 50c of the output shaft 50 are not in contact with the tooth tip 48c of the cylindrical support 48 and the tooth bottom 50d of the output shaft 50. Further, the clearance between the spigot fitting portion A2 so as not to contact, the tooth bottom 48d of the cylindrical support portion 48 and the tooth tip 50c of the output shaft 50, and the tooth tip 48c of the cylindrical support portion 48 and the output shaft 50 are provided. A gap with the tooth bottom 50d is set.

  The inlay fitting portion A2 is an engaging portion configured by fitting an inner peripheral surface and an outer peripheral surface that are in contact with each other. FIG. 5 shows a cross section of the cylindrical support portion 48 and the output shaft 50 at the second position P2. As shown in this figure, in this embodiment, the inner peripheral surface of the cylindrical support portion 48 that is the radially inner portion of the rotor fixing member 40 is formed in a cylindrical shape at the second position P2. Moreover, the outer peripheral surface which is a radial direction outer side part in the output shaft 50 is also formed in the cylindrical shape. The inlay fitting portion A2 is configured such that the cylindrical support portion 48 and the output shaft 50 are in contact with each other over the entire circumference (over the entire area in the circumferential direction). That is, at the second position P2, the cylindrical inner peripheral surface 48b of the cylindrical support portion 48 and the cylindrical outer peripheral surface 50b of the output shaft 50 are in contact with each other over the entire circumference, thereby forming the spigot fitting portion A2. Yes. The inlay fitting portion A <b> 2 restricts the relative movement in the radial direction between the cylindrical support portion 48 and the output shaft 50. By this inlay fitting part A2, the rotor fixing member 40 can be directly supported in the radial direction with respect to the output shaft 50 without passing through another member (bearing or the like).

  Strictly speaking, in the present embodiment, the portion on the cylindrical support portion 48 side (the cylindrical inner peripheral surface 48b of the cylindrical support portion 48) in the spigot fitting portion A2 corresponds to the “contact portion”. Further, a portion of the spline engaging portion A1 on the cylindrical support portion 48 side (the inner peripheral uneven surface 48a of the cylindrical support portion 48) corresponds to a “connecting portion”, and more specifically, a “spline connecting portion”. It corresponds to. However, in understanding the features of the technology according to the present disclosure, it is particularly problematic to consider the whole spigot fitting portion A2 as a “contact portion” and the whole spline engagement portion A1 as a “connecting portion”. Absent. Further, in the present embodiment, the spline engaging portion A1 (strictly speaking, the inner circumferential uneven surface 48a of the cylindrical support portion 48) that constitutes the “connecting portion” provides driving force to the output shaft 50 of the rotor fixing member 40. It also serves as a “transmission unit” for transmission.

  In the present embodiment, the cylindrical surfaces (cylindrical inner peripheral surface 48b and cylindrical outer peripheral surface 50b) forming the spigot fitting portion A2 are the uneven surfaces (inner peripheral side uneven surface 48a and outer periphery) forming the spline engaging portion A1. It has a smaller diameter than the side uneven surface 50a). The cylindrical surface forming the spigot fitting portion A2 is located further radially inward than the radially inner end surface (the tooth tip 48c or the tooth bottom 50d) of the uneven surface forming the spline engaging portion A1. Further, the spline engaging portion A1 and the spigot fitting portion A2 have the same width in the axial direction L. The spline engaging portion A1 and the spigot fitting portion A2 are disposed adjacent to each other in the axial direction L. “Adjacent” means that the two parts of interest are adjacent to each other without interposing another part therebetween. In this embodiment, the spigot fitting part A2 is provided adjacent to the input main body part 11 side of the input shaft 10 in the axial direction L with respect to the spline engaging part A1. The inlay fitting portion A2 is disposed so that the entirety thereof overlaps with the input cylindrical portion 12 of the input shaft 10 when viewed in the radial direction.

  The output shaft 50 is supported in a state where it can rotate relative to the case 2. In the present embodiment, the output shaft 50 is supported in the radial direction by a shaft support member 28 (case wall) fixed to the first divided case portion 21 constituting the case 2. The output shaft 50 is supported in the radial direction on the transmission device TM side with respect to the attachment portion A in the axial direction L (particularly, the spigot fitting portion A2 here). Further, the output shaft 50 is supported in the radial direction on the opposite side to the first one-way clutch F1 and the second one-way clutch F2 described later in the axial direction L with respect to the radial coupling portion 44.

  A second bearing B2 and a third bearing B3 are disposed between the shaft support member 28 (case wall) constituting the case 2 and the radial direction of the output shaft 50 (see FIG. 2). The second bearing B2 and the third bearing B3 are disposed closer to the transmission device TM than the mounting portion A in the axial direction L (in particular, the spigot fitting portion A2 here). Further, the second bearing B2 and the third bearing B3 are disposed on the opposite side to the first one-way clutch F1 and the second one-way clutch F2 described later in the axial direction L with respect to the radial direction connecting portion 44. In the present embodiment, the paired second bearing B2 and third bearing B3 correspond to “support bearings”.

  The output shaft 50 is supported in the radial direction via the second bearing B2 and the third bearing B3 at both ends of the cylindrical shaft support portion 29 of the shaft support member 28. The output shaft 50 is supported with respect to the shaft support member 28 only in the radial direction by the second bearing B2 and the third bearing B3. The output shaft 50 is supported only in the radial direction without being supported in the axial direction L by the second bearing B2 and the third bearing B3. Needle bearings are used as the second bearing B2 and the third bearing B3. That is, as the second bearing B2 and the third bearing B3, needle bearings generally having a smaller radial size than the ball bearing are used. In the present embodiment, since the output shaft 50 is supported in the radial direction with respect to the case 2 (shaft support member 28) at two relatively spaced points in the axial direction L, the output shaft 50 can be moved in the radial direction with high axial accuracy. Can support. Further, by using needle bearings as the second bearing B2 and the third bearing B3, it is possible to minimize the increase in the radial size.

  The rotor fixing member 40 is supported in the radial direction with respect to the output shaft 50 by a spigot fitting portion A <b> 2 that contacts the output shaft 50. The rotor fixing member 40 is supported in the radial direction with respect to the output shaft 50 only by the spigot fitting portion A2. The rotor fixing member 40 is supported in the radial direction with respect to the output shaft 50 only by the spigot fitting portion A2 without being supported in the radial direction by a portion other than the spigot fitting portion A2. The rotor fixing member 40 is supported in the radial direction with respect to the output shaft 50 by the spigot fitting portion A2 contacting the output shaft 50, and the spigot fitting portion A2, the output shaft 50, the second bearing B2, and the like. It is supported in the radial direction so as to be rotatable relative to the case 2 via the third bearing B3. The rotor fixing member 40 is centered with respect to the case 2 via the spigot fitting portion A2 that contacts the output shaft 50, the output shaft 50, the second bearing B2, and the third bearing B3. For this reason, in the structure of the present embodiment, the rotor fixing member 40 and the rotor Ro can be supported in the radial direction with high axial accuracy. The output shaft 50 that penetrates the shaft support member 28 in the axial direction L is disposed so as to also penetrate the rotor fixing member 40 in the axial direction L, and the end on the internal combustion engine E side is a hollow portion of the input main body 11. 11B is inserted into the radially inner space.

  As shown in FIGS. 2 and 3, the vehicle drive device 1 according to the present embodiment includes a pump drive member 60, a transmission gear mechanism 70, and a drive transmission mechanism 80 as pump drive mechanisms for driving the oil pump OP. Is further provided. These are provided in the order described in the power transmission path connecting the pump drive member 60 and the oil pump OP, and are connected to each other.

  The pump driving member 60 includes a cylindrical pump driving cylindrical portion 61 and a flange-shaped pump driving plate extending radially outward from an end of the pump driving cylindrical portion 61 on the shaft support member 28 side. And a shaped portion 62. The pump drive tubular portion 61 is radially outside the tubular support portion 48 of the rotor fixing member 40 and radially inward of the input tubular portion 12 of the input shaft 10 and coaxially therewith. Are arranged with a predetermined gap therebetween.

  The first one-way clutch F1 is disposed in contact with the outer peripheral surface of the cylindrical support portion 48 and the inner peripheral surface of the pump drive cylindrical portion 61. That is, the outer peripheral surface of the cylindrical support portion 48 and the first one-way clutch F1 are in contact with each other, and the first one-way clutch F1 and the inner peripheral surface of the pump drive cylindrical portion 61 are in contact with each other. The outer peripheral surface of the cylindrical support portion 48 and the first one-way clutch F1 are press-fitted. The second one-way clutch F <b> 2 is disposed in contact with the outer peripheral surface of the pump drive tubular portion 61 and the inner peripheral surface of the input tubular portion 12. That is, the outer peripheral surface of the pump drive cylindrical portion 61 and the second one-way clutch F2 are in contact with each other, and the second one-way clutch F2 and the inner peripheral surface of the input cylindrical portion 12 are in contact with each other. The outer peripheral surface of the pump drive cylindrical part 61 and the second one-way clutch F2 are press-fitted.

  The output shaft 50, the cylindrical support portion 48, the first one-way clutch F1, the pump drive cylindrical portion 61, the second one-way clutch F2, and the input cylindrical portion 12 are arranged coaxially. These are arranged in the order of description from the radially inner side to the radially outer side.

  The cylindrical support portion 48, the rotating electrical machine MG, and the engagement device CL are arranged so as to have overlapping portions when viewed in the radial direction. The cylindrical support portion 48, the rotor Ro, and the engagement device CL are arranged so as to have overlapping portions when viewed in the radial direction. In the present embodiment, the spigot fitting portion A2 between the output shaft 50 and the cylindrical support portion 48 (the contact portion of the cylindrical support portion 48 with the output shaft 50) is the rotor Ro and the engagement when viewed in the radial direction. It arrange | positions so that it may have a part which overlaps with the compound apparatus CL. The inlay fitting portion A <b> 2 is disposed so as to have a portion overlapping the rotor Ro and the friction plate 31 when viewed in the radial direction. The inlay fitting portion A2 is disposed so as to completely overlap with the friction plate 31 (including the pressure plate disposed in contact with the inner support member 32) and partially overlap with the rotor Ro when viewed in the radial direction. ing.

  Note that the spline engaging portion A1 between the output shaft 50 and the cylindrical support portion 48 is disposed at a position in the axial direction L different from the rotor Ro and the friction plate 31, and in this example, the rotor Ro and the friction plate. 31 is disposed on the transmission device TM side in the axial direction L. The spline engaging portion A1 is disposed so as to have a portion overlapping the radial connecting portion 44 when viewed in the radial direction. Further, the spline engaging portion A1 is disposed so as to have a portion overlapping with the coil end portion on the transmission device TM side in the axial direction L when viewed in the radial direction. Further, the spline engaging portion A1 is disposed so as to have a portion overlapping the rotation sensor 90 disposed between the radial connecting portion 44 and the intermediate wall 23 when viewed in the radial direction.

  Further, the cylindrical support portion 48 and at least one of the first one-way clutch F1 and the second one-way clutch F2 are arranged so as to have overlapping portions when viewed in the radial direction. In this embodiment, the cylindrical support part 48 is arrange | positioned so that it may have a part which overlaps with both the 1st one-way clutch F1 and the 2nd one-way clutch F2 seeing in radial direction. The cylindrical support portion 48, the first one-way clutch F1, and the second one-way clutch F2 are such that the output shaft 50, the pump drive cylindrical portion 61, and the input cylindrical portion 12 have overlapping portions when viewed in the radial direction. Is arranged. In this embodiment, the spigot fitting portion A2 between the output shaft 50 and the cylindrical support portion 48 (the contact portion of the cylindrical support portion 48 with the output shaft 50) is a pump drive cylindrical shape when viewed in the radial direction. It arrange | positions so that it may overlap with the part 61 and the 1st one-way clutch F1 completely. The inlay fitting portion A2 is disposed so as to completely overlap with the second one-way clutch F2 and the input cylindrical portion 12 when viewed in the radial direction.

  Note that the spline engagement portion A1 between the output shaft 50 and the cylindrical support portion 48 is disposed so as to partially overlap the first one-way clutch F1 and the second one-way clutch F2. In this example, a part on the internal combustion engine E side in the spline engagement portion A1 and a part on the transmission device TM side in the first one-way clutch F1 and the second one-way clutch F2 are overlapped when viewed in the radial direction. Has been placed.

  The first one-way clutch F1 and the second one-way clutch F2 include an inner ring and an outer ring that are arranged coaxially, and a driving force transmission member (such as a roller or a sprag) that selectively transmits a driving force therebetween. Can be used.

  The first one-way clutch F1 restricts relative rotation between the rotor fixing member 40 and the pump driving member 60 in one direction. The first one-way clutch F1 allows relative rotation of the rotor fixing member 40 and the pump driving member 60 only in one direction. The first one-way clutch F1 allows relative rotation when the rotational speed of the rotor fixing member 40 (the rotating electrical machine MG) is lower than the rotational speed of the pump driving member 60, and the rotational speed of the rotor fixing member 40 increases to increase the pump. When the rotational speed of the drive member 60 becomes equal, the relative rotation is restricted. When the relative rotation between the rotor fixing member 40 and the pump driving member 60 is restricted, they are locked and rotate integrally.

  The second one-way clutch F2 restricts relative rotation between the input shaft 10 and the pump driving member 60 in one direction. The second one-way clutch F2 allows relative rotation between the input shaft 10 and the pump drive member 60 only in one direction. The second one-way clutch F2 allows relative rotation when the rotational speed of the input shaft 10 (internal combustion engine E) is lower than the rotational speed of the pump drive member 60, and the rotational speed of the input shaft 10 increases to increase the pump drive member. When the rotational speed is equal to 60, the relative rotation is restricted. When the relative rotation between the input shaft 10 and the pump driving member 60 is restricted, they are locked and rotate integrally.

  In these two one-way clutches F1 and F2, the relative rotation restriction direction of the rotor fixing member 40 with respect to the pump drive member 60 and the relative rotation restriction direction of the input shaft 10 with respect to the pump drive member 60 are in the same direction. It is configured. These function in cooperation with each other. When the rotational speed of the rotor fixing member 40 is equal to or higher than the rotational speed of the input shaft 10, the relative rotation between the input shaft 10 and the pump drive member 60 is allowed. Relative rotation between the rotor fixing member 40 and the pump drive member 60 is restricted by the first one-way clutch F1. When the rotational speed of the input shaft 10 is equal to or higher than the rotational speed of the rotor fixing member 40, the input shaft is driven by the second one-way clutch F2 while the relative rotation between the rotor fixing member 40 and the pump driving member 60 is allowed. The relative rotation between 10 and the pump drive member 60 is restricted. For this reason, the pump drive member 60 rotates at the same speed as the higher one of the input shaft 10 (internal combustion engine E) and the rotor fixing member 40 (rotating electrical machine MG).

  The pump drive plate-like portion 62 is disposed between the inner portion of the radial connecting portion 44 of the rotor fixing member 40 in the axial direction L and the input cylindrical portion 12 with a predetermined gap in the axial direction L therebetween. ing. A first drive gear 64 is formed on the outer periphery of the pump drive plate 62. The first drive gear 64 meshes with a first driven gear 72 formed on the outer periphery of the first transmission plate-like portion 71 constituting the transmission gear mechanism 70. The pump drive plate-like portion 62 and the first transmission plate-like portion 71 overlap the inner portion of the radial connection portion 44 when viewed in the axial direction L, and the outer portion of the radial connection portion 44 when viewed in the radial direction. It arrange | positions so that it may have an overlapping part.

  The transmission gear mechanism 70 includes a first driven gear 72 formed on the first transmission plate-like portion 71, a second drive gear 74 formed on the outer peripheral portion of the second transmission plate-like portion 73, and a first transmission plate. And a connecting shaft 75 that connects the second portion 71 and the second transmission plate-like portion 73. The second transmission plate-like portion 73 and the second drive gear 74 are opposite to the first transmission plate-like portion 71 and the first driven gear 72 side with respect to the radial coupling portion 44 of the rotor fixing member 40 (shaft support). It is arranged on the member 28 side). That is, the first transmission plate-like portion 71 and the first driven gear 72 and the second transmission plate-like portion 73 and the second drive gear 74 are arranged separately on both sides in the axial direction L with the radial connecting portion 44 interposed therebetween. Has been.

  The connecting shaft 75 is disposed at a position corresponding to the through hole 46 formed in the radial connecting portion 44 of the rotor fixing member 40 when viewed in the axial direction L. Thereby, the transmission gear mechanism 70 is arranged in a state where the connecting shaft 75 penetrates the radial connecting portion 44 in the axial direction L. In the present embodiment, the transmission gear mechanism 70 functions as an “intermediate transmission mechanism”. A fourth bearing B <b> 4 is disposed between the inner peripheral surface of the through hole 46 and the outer peripheral surface of the connecting shaft 75 so as to be in contact therewith. A needle bearing is used as the fourth bearing B4. The second drive gear 74 meshes with a second driven gear 82 formed on the outer periphery of the drive transmission cylindrical portion 81 that constitutes the drive transmission mechanism 80.

The drive transmission mechanism 80 transmits the rotation of the pump drive member 60 transmitted through the transmission gear mechanism 70 to the oil pump OP. A first sprocket 83 is fixed to the drive transmission cylindrical portion 81 where the second driven gear 82 is formed. As a result, the second driven gear 82 and the first sprocket 83 rotate together. The first sprocket 83 is disposed on the opposite side (the shaft support member 28 side) from the pump drive member 60 and the transmission gear mechanism 70 side in the axial direction L with respect to the second driven gear 82. A chain 85 is wound around the first sprocket 83.
In the present embodiment, a drive transmission mechanism 80 is configured including a drive transmission cylindrical portion 81 having a second driven gear 82 and a first sprocket 83, and a chain 85. Although not shown in FIGS. 2 and 3, the drive transmission mechanism 80 also includes a second sprocket that is wound around a chain 85 that is fixed to a pump shaft that is arranged on a separate shaft from the output shaft 50. It is.

  Thus, in this embodiment, the pump drive member 60 and the drive transmission mechanism 80 are drivingly connected via the transmission gear mechanism 70 arranged in a state of passing through the radial direction connecting portion 44 in the axial direction L. . For this reason, even when the radial connecting portion 44 of the rotor fixing member 40 exists between the pump drive member 60 and the drive transmission mechanism 80 in the axial direction L, the rotation of the pump drive member 60 is appropriately drive-transmitted. The mechanism 80 can be transmitted to the oil pump OP. Then, in cooperation with the two one-way clutches F1 and F2, the oil pump OP can be driven by the torque having the higher rotational speed of the internal combustion engine E and the rotating electrical machine MG. Oil discharged by driving the oil pump OP is supplied via a hydraulic control device (not shown) for controlling the engagement state of the engagement device CL and the like, and for lubricating and cooling each part of the device. The

  In the vehicle drive device 1 according to the present embodiment, the input shaft 10, the engagement device CL, the rotor Ro and the rotor fixing member 40, the output shaft 50, the pump drive member 60, the transmission gear mechanism 70, and the drive transmission mechanism 80 are It is assembled as follows.

  First, the shaft support member 28 is assembled to the first divided case portion 21 in which the transmission TM is accommodated. The shaft support member 28 is fixed to the first split case portion 21 in a state of being extrapolated to the output shaft 50. Thus, the output shaft 50 is supported in the radial direction via the shaft support member 28 so as to be rotatable relative to the case 2 (first divided case portion 21). Specifically, at both ends of the cylindrical shaft support portion 29 extending along the axial direction L at the radially inner end of the shaft support member 28, the output shaft 50 is pivoted by the second bearing B2 and the third bearing B3. It is supported by the case 2 in the radial direction via the support member 28.

  Next, the drive transmission mechanism 80 is assembled to the shaft support member 28 fixed to the first divided case portion 21. The drive transmission cylindrical portion 81 constituting the drive transmission mechanism 80 is supported by the shaft support member 28 including the cylindrical shaft support portion 29 so as to be relatively rotatable in a state where the chain 85 is wound around the first sprocket 83. . Specifically, the drive transmission cylindrical portion 81 is provided by the fifth bearing B5 that is disposed so as to contact the outer peripheral surface of the cylindrical shaft support portion 29 and to contact the side surface of the cylindrical shaft support portion 29 on the input shaft 10 side. Is positioned in the axial direction L and the radial direction. A ball bearing is used as the fifth bearing B5. Thereafter, the second divided case portion 22 is joined to the first divided case portion 21 from the internal combustion engine E side.

  Next, with respect to the shaft support member 28 fixed to the first divided case portion 21 and the output shaft 50 supported in the radial direction with respect to the shaft support member 28, the rotor Ro, the rotor fixing member 40, and the transmission gear The mechanism 70 is assembled. In the present embodiment, the rotor Ro and the rotor fixing member 40, the transmission gear mechanism 70 that is disposed through the rotor fixing member 40 in the axial direction L, and the first one-way clutch F1 are assembled in advance to constitute an intermediate unit. The The first one-way clutch F1 is press-fitted along the axial direction L from the end opposite to the radial connecting portion 44 side to the outer peripheral surface of the cylindrical support portion 48 of the rotor fixing member 40. The intermediate unit is attached to the output shaft 50 by the cylindrical support portion 48 and positioned in the axial direction L with respect to the shaft support member 28. At this time, the sixth bearing B6 (thrust bearing) is disposed between the shaft support member 28 in the axial direction L and the radial connecting portion 44 of the rotor fixing member 40 so as to be in contact with both of them. The intermediate unit is assembled from the side opposite to the shaft support member 28 side in the axial direction L (internal combustion engine E side). The rotor fixing member 40 is positioned in the radial direction with respect to the output shaft 50 at the attachment portion A.

  Next, the pump drive member 60 is assembled to the rotor fixing member 40 and the first one-way clutch F1 positioned with respect to the shaft support member 28 and the output shaft 50. Before the pump drive member 60 is assembled, the second one-way clutch F2 is press-fitted into the outer peripheral surface of the pump drive cylindrical portion 61. The pump drive member 60 is positioned in the axial direction L with respect to the radial connection portion 44 and is positioned in the radial direction with respect to the cylindrical support portion 48. At this time, the pump drive member 60 is disposed such that the inner peripheral surface of the pump drive cylindrical portion 61 is in contact with the outer peripheral surface of the first one-way clutch F1. A seventh bearing B7 (thrust bearing) is disposed between the pump drive plate-like portion 62 of the pump drive member 60 in the axial direction L and the radial connecting portion 44 so as to contact both of them.

  Next, the engaging device CL and the input shaft 10 are assembled to the rotor fixing member 40, the pump drive member 60 positioned relative to the rotor fixing member 40, and the second one-way clutch F2. The input shaft 10 is axially oriented with respect to the pump drive member 60 in a state where the engagement device CL is disposed between the input cylindrical portion 12 of the input shaft 10 and the cylindrical fixing portion 41 of the rotor fixing member 40. L and radial positioning. At this time, an eighth bearing B8 (thrust bearing) is disposed between the input coupling portion 13 of the input shaft 10 in the axial direction L and the pump drive cylindrical portion 61 of the pump drive member 60 so as to contact both of them. Is done. Further, the input cylindrical portion 12 is disposed such that the inner peripheral surface thereof is in contact with the outer peripheral surface of the second one-way clutch F2 press-fitted into the outer peripheral surface of the pump drive cylindrical portion 61. In the present embodiment, each of the bearings B6 to B8 corresponds to a “thrust bearing”.

  Next, the third divided case portion 24 is joined to the second divided case portion 22 from the internal combustion engine E side so as to close the opening of the second divided case portion 22 on the internal combustion engine E side. In the state where the stepped portion 26 formed on the end wall 25 of the third divided case portion 24 is in contact with the inner peripheral surface and the contact surface 26a facing the inner side of the case 2 (the shaft support member 28 side), The first bearing B1 is press-fitted and fixed. When the third divided case portion 24 is assembled so as to be extrapolated from the internal combustion engine E side with respect to the input shaft 10, the first bearing B <b> 1 is disposed so as to contact the outer peripheral surface of the input main body portion 11 of the input shaft 10. Is done. Thus, the input shaft 10 is supported in the axial direction L and the radial direction so as to be relatively rotatable with respect to the case 2 through only the first bearing B1, and is positioned in the radial direction. At this time, a gap adjusting member 95 is disposed between the input connecting portion 13 and the first bearing B1.

  Thus, in the present embodiment, the shaft support member 28 is fixed to the first divided case portion 21, and the shaft support member 28, the radial connection portion 44, the pump drive member 60, and the input connection portion 13 are mutually connected. It arrange | positions along with the axial direction L via a thrust bearing in between. As a result, the output shaft 50, the drive transmission mechanism 80, the transmission gear mechanism 70, the rotor fixing member 40, the pump drive member 60, and the input shaft 10 with respect to the shaft support member 28 fixed to the first divided case portion 21. Properly positioned. Further, when the third split case portion 24 to which the first bearing B1 is fixed is extrapolated from the internal combustion engine E side with respect to the input main body portion 11 of the input shaft 10, the input connecting portion 13 and the first connecting portion 13 in the axial direction L are inserted. A gap adjusting member 95 is disposed between the bearing B1. For this reason, according to the thickness of the clearance adjustment member 95, the clearance in the axial direction L between the component parts can be adjusted to an appropriate amount.

  In the present embodiment, the thickness of the gap adjustment member 95 (“α” shown in FIG. 6) is determined based on the clearance in the axial direction L between the components and the sizes of the stator St and the rotor Ro constituting the rotating electrical machine MG. Is set. More specifically, the sum of the clearances in the axial direction L from the shaft support member 28 to the first bearing B1 (the gap represented by “β” in FIG. 6) is the axial length of the rotor Ro and the axial length of the stator St. The thickness (α) of the gap adjusting member 95 is set so as to be equal to or less than half the difference. FIG. 6 shows a state in which all components from the shaft support member 28 to the gap adjustment member 95 are arranged close to the shaft support member 28 side.

  The sum of the clearances in the axial direction L from the shaft support member 28 to the first bearing B1 when there is no gap adjusting member 95 (the gap represented by “γ” in FIG. 6) It can be obtained on the basis of the joint surface with the divided case portion 24 (referred to as “reference surface Ps”; see FIG. 2). That is, the total clearance (γ) when there is no gap adjusting member 95 is the input connecting portion 13 from the reference plane Ps in a state where each component is directly or indirectly supported by the shaft support member 28 in the axial direction L. The difference between the separation length to the surface on the internal combustion engine E side and the separation length from the reference surface Ps to the surface on the shaft support member 28 side of the first bearing B1 can be obtained. Therefore, the total clearance (γ) when there is no gap adjusting member 95 can be easily measured at the final stage in the procedure of assembling each component as described above.

  On the other hand, since the difference between the axial length of the rotor Ro and the axial length of the stator St can be easily obtained from the sizes of the stator St and the rotor Ro of the rotating electrical machine MG to be used, the limit clearance (δ) is set based on the difference. The In this example, the limit clearance (δ) is set to a value that is half the difference between the axial length of the rotor Ro and the axial length of the stator St. The thickness (α) of the gap adjusting member 95 is the actual total clearance (β) obtained by subtracting the thickness (α) of the gap adjusting member 95 from the total clearance (γ) when there is no gap adjusting member 95. It is set to be equal to or less than the limit clearance (δ).

  In the present embodiment, since the gap adjusting member 95 is disposed between the input connecting portion 13 and the first bearing B1, the thickness (α) of the gap adjusting member 95 can be determined easily and appropriately. Then, by selecting and using a gap adjusting member 95 having an appropriate thickness (α) required for each individual vehicle drive device 1, the clearance in the axial direction L between each component can be easily adjusted to an appropriate amount. be able to. Even if the rotor fixing member 40 and the rotor Ro are moved to the maximum in the axial direction L, the entire rotor Ro can always be accommodated in the region occupied by the stator St in the axial direction L.

  Further, in the present embodiment, the rotor fixing member 40 is attached to the output shaft 50 by the cylindrical support portion 48 formed at the radially inner end thereof, so that the rotor fixing member 40 is placed in the case via the output shaft 50. 2 can be supported in the radial direction. Therefore, the rotor Ro and the rotor fixing member 40 can be supported in the radial direction on the case 2 with relatively high support accuracy. Further, as compared with the configuration in which the rotor fixing member 40 is supported in the radial direction via the bearing, the radial fixing can be achieved while appropriately supporting the rotor fixing member 40 in the radial direction. Further, the output shaft 50, the cylindrical support portion 48, the first one-way clutch F1, the pump drive cylindrical portion 61, the second one-way clutch F2, and the input cylindrical portion 12 are arranged coaxially and overlap when viewed in the radial direction. Therefore, the enlargement of the apparatus can be suppressed. At this time, since the components are coaxially and densely arranged in the region occupied by the pump drive cylindrical portion 61 in the axial direction L, the apparatus shaft length can be shortened more actively.

  Further, in the present embodiment, the cylindrical support portion 48 and the rotor Ro are arranged so as to have an overlapping portion when viewed in the radial direction, and the engaging device CL also has a portion overlapping with these when viewed in the radial direction. Are arranged as follows. Thereby, the enlargement of the apparatus can be suppressed, and the rotor Ro can be supported on the output shaft 50 in the radial direction via the rotor fixing member 40 in a region near the axial center (center of gravity) of the rotor Ro. . In addition, by using the engagement device CL having a relatively heavy weight, it is possible to stabilize the fixed state of the cylindrical support portion 48 with respect to the output shaft 50 in a region close to the axial center of the rotor Ro. Accordingly, the rotor Ro and the rotor fixing member 40 can be supported in the radial direction on the case 2 with higher support accuracy.

  Further, as described above, the rotor fixing member 40 is supported only in the radial direction with respect to the output shaft 50 by the spigot fitting portion A2, and the spigot fitting portion A2, the output shaft 50, the second bearing B2, and the second bearing B2. It is supported in the radial direction so as to be rotatable relative to the case 2 via the three bearings B3. Further, the rotor fixing member 40 is supported in the axial direction L by the shaft support member 28 (case wall) constituting the case 2 via the sixth bearing B6 on one side in the axial direction L (transmission device TM side). Yes. The rotor fixing member 40 has, on the other side in the axial direction L (internal combustion engine E side), a seventh bearing B7, a pump drive member 60, an eighth bearing B8, an input connecting portion 13, a gap adjusting member 95, and a first bearing B1. Is supported in the axial direction L on the end wall 25 constituting the case 2. Thus, in this embodiment, the support structure in the radial direction of the rotor fixing member 40 (mainly realized by the spigot fitting portion A2, the second bearing B2, and the third bearing B3) and the support structure in the axial direction L (main To the bearings B1, B6 to B8). For this reason, unlike the structure performed in one place without separating the support in the radial direction and the support in the axial direction L, needle bearings instead of ball bearings can be used as the second bearing B2 and the third bearing B3. Therefore, the size in the radial direction can be reduced as compared with the structure in which the rotor fixing member 40 is supported in one place in the axial direction L and the radial direction.

[Other Embodiments]
Finally, other embodiments of the vehicle drive device will be described. Note that the configurations disclosed in the following embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction arises.

(1) In the above-described embodiment, the configuration in which the gap adjusting member 95 is disposed between the input coupling portion 13 of the input shaft 10 and the first bearing B1 in the axial direction L has been described as an example. However, the embodiment of the present invention is not limited to this. If the sum total (β) of the clearance in the axial direction L from the shaft support member 28 to the first bearing B1 is adjusted to an appropriate amount, the clearance adjustment member 95 includes the shaft support member 28, the radial coupling portion 44, the pump The driving member 60 and the input connecting portion 13 may be disposed between each other.

(2) In the above embodiment, the thickness (α) of the gap adjusting member 95 is set based on the clearance in the axial direction L between the components and the sizes of the stator St and the rotor Ro constituting the rotating electrical machine MG. The configuration is described as an example. However, the embodiment of the present invention is not limited to this. For example, in addition to these, the thickness (α) of the gap adjusting member 95 may be set based on the sizes of the sensor stator 91 and the sensor rotor 92 that constitute the rotation sensor 90. In this case, for example, half of the smaller value of the difference between the axial length of the rotor Ro and the axial length of the stator St and the axial length of the sensor rotor 92 and the axial length of the sensor stator 91 is set as the limit clearance. As (δ), the thickness (α) of the gap adjusting member 95 may be set.

(3) In the above embodiment, the spline engaging portion A1 and the spigot fitting portion A2 constituting the attachment portion A between the cylindrical support portion 48 and the output shaft 50 have the same width in the axial direction L. The above configuration has been described as an example. However, the embodiment of the present invention is not limited to this. The ratio between the width in the axial direction L of the spline engaging portion A1 and the width in the axial direction L of the spigot fitting portion A2 may be arbitrary. From the viewpoint of ensuring a large transmittable torque, it is preferable that the width in the axial direction L of the spline engaging portion A1 is set larger than the width in the axial direction L of the spigot fitting portion A2. In this case, the ratio of the spigot fitting portion A2 may be “0%”. For example, as shown in FIG. 7, the attachment portion A is configured by the spline engagement portion A1 over the entire region in the axial direction L. Also good. When the attachment portion A is configured only by the spline engaging portion A1, the cylindrical support portion 48 is formed by the uneven surfaces (the inner peripheral uneven surface 48a and the outer peripheral uneven surface 50a) that constitute the spline engaging portion A1. And the relative movement of the output shaft 50 in the radial direction and the circumferential direction are restricted. In this case, a portion of the spline engagement portion A1 on the cylindrical support portion 48 side (inner peripheral side uneven surface 48a of the cylindrical support portion 48) includes a “contact portion”, a “connecting portion”, and a “transmission portion”. I will also serve.

  When the attachment portion A is configured only by the spline engaging portion A1, the tooth tip 48c of the cylindrical support portion 48 and the tooth bottom 50d of the output shaft 50 come into contact with each other, or the tooth bottom of the cylindrical support portion 48 48d is preferably in contact with the tooth tip 50c of the output shaft 50 (see FIG. 8). More specifically, in the case where the rotor fixing member 40 is supported in the radial direction only by the spline engaging portion A1, if the axis center of the rotor fixing member 40 and the axis center of the output shaft 50 are shifted, the cylindrical support portion 48 is used. One of the tooth bottom 48d and the tooth tip 50c of the output shaft 50, and the tooth tip 48c of the cylindrical support portion 48 and the tooth bottom 50d of the output shaft 50 come into contact first, and the other does not contact. Further, one of the tooth bottom 48d of the cylindrical support portion 48 and the tooth tip 50c of the output shaft 50, and the tooth tip 48c of the cylindrical support portion 48 and the tooth bottom 50d of the output shaft 50 are in contact, and the other is not in contact. As described above, a gap is set between them.

(4) In the above embodiment, the example in which the attachment portion A between the cylindrical support portion 48 and the output shaft 50 is configured by the combination of the spline engagement portion A1 and the spigot fitting portion A2 has been described. However, the embodiment of the present invention is not limited to this. If the cylindrical support portion 48 and the output shaft 50 are attached in a state where relative movement in the radial direction and the circumferential direction is restricted, for example, an engagement portion using a key and a key groove that are engaged with each other, The attachment portion A may be configured by a combination with the spigot fitting portion A2. Further, the mounting portion A may be configured by an engaging portion using a key and a key groove over the entire region in the axial direction L, an inlay fitting portion A2 fixed by welding or the like, and the like. In these cases, the “contact portion”, “connecting portion”, and “transmission portion” are determined according to the configuration of the attachment portion A in each case.

(5) In the above embodiment, the cylindrical surfaces (cylindrical inner peripheral surface 48b and cylindrical outer peripheral surface 50b) forming the spigot fitting portion A2 are the concave / convex surfaces (inner peripheral side unevenness) forming the spline engaging portion A1. An example in which the diameter is smaller than the surface 48a and the outer circumferential uneven surface 50a) has been described. However, the embodiment of the present invention is not limited to this. The cylindrical surface forming the spigot fitting portion A2 may be configured to have the same diameter or larger diameter than the uneven surface forming the spline engaging portion A1. Further, the spline engagement portion A1 and the spigot fitting portion A2 do not necessarily have to be adjacent to each other in the axial direction L, and are arranged close to each other in a state of being separated in the axial direction L with another portion interposed therebetween. Also good.

(6) In the above embodiment, the inner peripheral surface of the cylindrical support portion 48 and the outer peripheral surface of the output shaft 50 are configured to contact each other, and the outer peripheral surface of the output shaft 50 in the inner peripheral surface of the cylindrical support portion 48. The example in which the “contact portion” is formed by the portion (cylindrical inner peripheral surface 48 b) that contacts the head has been described. However, the embodiment of the present invention is not limited to this. For example, the inner peripheral surface of the cylindrical output cylindrical portion connected to the output shaft 50 is configured to abut on the outer peripheral surface of the cylindrical support portion 48, and the output cylindrical portion on the outer peripheral surface of the cylindrical support portion 48 is configured. The “contact portion” may be formed by a portion that is in contact with the inner peripheral surface. In this case, the cylindrical support portion 48, the output cylindrical portion, and the first one-way clutch F1 may be arranged in the order described from the radially inner side to the radially outer side.

(7) In the above embodiment, the configuration in which the outer peripheral surface of the cylindrical support portion 48 is in contact with the first one-way clutch F1 has been described as an example. However, the embodiment of the present invention is not limited to this. The cylindrical support portion 48 and the first one-way clutch F1 may be provided with another member interposed therebetween. Similarly, with respect to each set of the first one-way clutch F1 and the pump driving cylindrical portion 61, the pump driving cylindrical portion 61 and the second one-way clutch F2, and the second one-way clutch F2 and the input cylindrical portion 12, the respective members. Other members may be interposed therebetween.

(8) In the above embodiment, the cylindrical support portion 48, the first one-way clutch F1, the pump drive cylindrical portion 61, the second one-way clutch F2, and the input cylindrical portion 12 are moved from the radially inner side to the radially outer side. The configuration arranged in the order of description has been described as an example. However, the embodiment of the present invention is not limited to this. Even if the input cylindrical part 12, the second one-way clutch F2, the pump drive cylindrical part 61, the first one-way clutch F1, and the cylindrical support part 48 are arranged in the order described from the radially inner side to the radially outer side. good.

(9) In the above embodiment, as an example, the cylindrical support portion 48 is disposed so as to have a portion overlapping with both the first one-way clutch F1 and the second one-way clutch F2 when viewed in the radial direction. explained. However, the embodiment of the present invention is not limited to this. For example, as schematically shown in FIG. 8, the cylindrical support portion 48 is arranged so as to have a portion overlapping only with the first one-way clutch F <b> 1 without overlapping with the second one-way clutch F <b> 2 when viewed in the radial direction. Also good. In this case, the first one-way clutch F <b> 1 and the second one-way clutch F <b> 2 may be arranged side by side in the axial direction L and may be arranged so as to have overlapping portions when viewed in the axial direction L. Moreover, the cylindrical support part 48 may be formed in the stepped cylinder shape which has a large diameter part inscribed in the 1st one-way clutch F1, and a small diameter part circumscribed in the 2nd one way clutch F2. Further, the cylindrical support portion 48 may be arranged so as to have a portion overlapping only with the second one-way clutch F2 without overlapping with the first one-way clutch F1 when viewed in the radial direction (not shown).

(10) In the above embodiment, the second bearing B2 and the third bearing B3 are arranged on the transmission device TM side with respect to the mounting portion A in the axial direction L (two one-way clutches in the axial direction L with respect to the radial connecting portion 44). The configuration arranged on the side opposite to the F1 and F2 side) has been described as an example. However, the embodiment of the present invention is not limited to this. The second bearing B2 and the third bearing B3 are arranged closer to the internal combustion engine E than the mounting portion A in the axial direction L (two one-way clutches F1 and F2 in the axial direction L with respect to the radial connecting portion 44). Also good.

(11) In the above-described embodiment, a pair of needle bearings (second bearing B2 and third bearing B3) support the output shaft 50 in the radial direction so as to be relatively rotatable with respect to the case 2. ”Has been described as an example. However, the embodiment of the present invention is not limited to this. For example, a single bearing may be provided as a “support bearing”. Further, it is not necessarily a needle bearing, and a ball bearing may be provided as a “support bearing” in some cases.

(12) In the above-described embodiment, the configuration in which the shaft support member 28 (case wall) fixed to the first divided case portion 21 also serves as a constituent member of the pump case has been described as an example. However, the embodiment of the present invention is not limited to this. For example, the shaft support member 28 may be a dedicated support wall or the like for supporting the output shaft 50 in the radial direction regardless of the oil pump OP.

(13) In the above embodiment, the example in which the drive transmission mechanism 80 is configured by a chain mechanism has been described. However, the embodiment of the present invention is not limited to this. The drive transmission mechanism 80 may be configured by, for example, a belt mechanism or a gear mechanism.

(14) In the above embodiment, the drive transmission mechanism 80 is disposed closer to the shaft support member 28 than the rotating electrical machine MG, and the transmission gear mechanism 70 moves the radial connecting portion 44 of the rotor fixing member 40 in the axial direction L. The configuration arranged in a penetrating state has been described as an example. However, the embodiment of the present invention is not limited to this. For example, the drive transmission mechanism 80 may be disposed closer to the end wall 25 than the rotating electrical machine MG. In this case, the transmission gear mechanism 70 may be disposed, for example, in a state of penetrating the input connecting portion 13 in the axial direction L.

(15) In the above embodiment, the configuration in which the hydraulically driven friction engagement device is provided as the engagement device CL has been described as an example. However, the embodiment of the present invention is not limited to this. The engagement device CL may be, for example, an electromagnetic friction engagement device, a meshing engagement device, or the like.

(16) In the above-described embodiment, the configuration in which the cylindrical support portion 48 (the spigot fitting portion A2) and the rotor Ro are disposed so as to overlap when viewed in the radial direction has been described as an example. However, the embodiment of the present invention is not limited to this. The cylindrical support portion 48 and the rotor Ro may be arranged at different positions in the axial direction L so that they do not overlap when viewed in the radial direction.

(17) In the above-described embodiment, the configuration in which the cylindrical support portion 48 (the spigot fitting portion A2) and the engagement device CL are disposed so as to overlap when viewed in the radial direction has been described as an example. However, the embodiment of the present invention is not limited to this. The cylindrical support portion 48 and the engagement device CL may be arranged at different positions in the axial direction L so that they do not overlap when viewed in the radial direction.

(18) In the above embodiment, the configuration in which the rotor Ro and the engagement device CL are arranged so as to overlap each other when viewed in the radial direction has been described as an example. However, the embodiment of the present invention is not limited to this. The rotor Ro and the engagement device CL may be arranged at different positions in the axial direction L so that they do not overlap when viewed in the radial direction. Moreover, the structure by which the input shaft 10 and the rotor fixing member 40 were always connected without providing the engaging device CL may be sufficient.

(19) In the above embodiment, an example in which the present invention is applied to a vehicle drive device mounted on an FF (Front Engine Front Drive) vehicle has been described. However, the embodiment of the present invention is not limited to this. For example, the present invention can be similarly applied to a vehicle drive device mounted on an FR (Front Engine Rear Drive) vehicle or a 4WD (Four-Wheel Drive) vehicle.

(20) Regarding other configurations, it should be understood that the embodiments disclosed herein are merely examples in all respects. Accordingly, those skilled in the art can make various modifications as appropriate without departing from the spirit of the present disclosure.

[Outline of Embodiment]
In summary, the vehicle drive device according to the present disclosure preferably includes the following configurations.

[1]
An input member (10) drivingly connected to the internal combustion engine (E);
A rotating electrical machine (MG) having a rotor (Ro) and a stator (St);
A rotor fixing member (40) fixed to the rotor (Ro) and rotating integrally with the rotor (Ro);
The stator (St) is supported in a radial direction so as to be relatively rotatable via support bearings (B2, B3) with respect to the case (2) to which the stator (St) is fixed, and rotates integrally with the rotor fixing member (40); An output member (50) drivingly connected to the wheel (W);
A pump drive member (60) that is drivingly connected to the oil pump (OP);
A first one-way clutch that restricts relative rotation between the rotor fixing member (40) and the pump driving member (60) when the rotation speed of the rotor fixing member (40) is equal to or higher than the rotation speed of the input member (10). (F1),
A second one-way clutch that restricts relative rotation between the input member (10) and the pump drive member (60) when the rotational speed of the input member (10) is equal to or higher than the rotational speed of the rotor fixing member (40). F2), and
The rotor fixing member (40) includes a contact portion (A2) that comes into contact with the output member (50), and is supported in the radial direction with respect to the output member (50) by the contact portion (A2). And supported so as to be relatively rotatable with respect to the case (2) via the contact portion (A2) and the support bearings (B2, B3),
The contact portion (A2) is arranged so as to have a portion that overlaps at least one of the first one-way clutch (F1) and the second one-way clutch (F2) when viewed in the radial direction.

According to this configuration, the pump driving member can be driven by the input member and the rotor fixing member having the higher rotational speed. Therefore, if either the rotor fixing member or the input member is rotating, the pump driving member can be driven, and an appropriate amount of oil can be supplied in a relatively large number of running states.
In addition, since the rotor fixing member is directly supported in the radial direction in a state where the rotor fixing member is in contact with the output member, the rotor fixing member is arranged in the radial direction as compared with the configuration in which the rotor fixing member is supported in the radial direction via the bearing. It is possible to achieve radial compactness while supporting appropriately. Furthermore, since the contact portion of the rotor fixing member with the output member overlaps with at least one of the first one-way clutch and the second one-way clutch when viewed in the radial direction, it is possible to reduce the size by shortening the shaft length. Therefore, it is possible to reduce the size of the entire apparatus while appropriately supporting the rotor fixing member in the radial direction.

[2]
The rotor fixing member (40) has a cylindrical support portion (48) formed in a cylindrical shape,
The contact portion (A2) is formed on the inner peripheral surface of the cylindrical support portion (48) and is in contact with the outer peripheral surface of the output member (50).

  According to this configuration, the rotor fixing member is supported in the radial direction with respect to the output member by the contact portion formed on the inner peripheral surface of the cylindrical support portion and the outer peripheral surface of the output member in contact with the contact portion. The structure can be realized properly.

[3]
The output member (50), the cylindrical support portion (48), and the first one-way clutch (F1) are arranged in the order described from the radially inner side to the radially outer side.

  According to this configuration, the structure in which the rotor fixing member is supported in the radial direction by the contact portion with respect to the output member and the first one-way clutch can regulate the relative rotation between the rotor fixing member and the pump driving member is rational. Can be realized easily and easily.

[4]
The outer peripheral surface of the said cylindrical support part (48) and said 1st one-way clutch (F1) are contact | abutting.

  According to this configuration, the first one-way clutch can achieve a structure in which the relative rotation between the rotor fixing member and the pump driving member can be restricted, and the radial direction can be reduced.

[5]
The rotor fixing member (40) has a cylindrical fixing portion (41) in contact with the rotor (Ro), a diameter that connects the cylindrical fixing portion (41) and the cylindrical support portion (48) in the radial direction. A direction connecting portion (44),
The first one-way clutch (F1) is disposed on one side in the axial direction (L) with respect to the radial direction connecting portion (44), and the first one-way clutch (F1) side in the axial direction (L) A case wall (28) constituting the case (2) is disposed on the opposite side to
The support bearings (B2, B3) are opposite to the first one-way clutch (F1) side in the axial direction (L) with respect to the radial connection portion (44), and the case wall (28) and the It arrange | positions between output members (50).

  According to this configuration, the output member is substantially provided to the case wall via the support bearing using the case wall provided on the side opposite to the first one-way clutch side with respect to the radial direction connecting portion in the axial direction. Can be directly supported. Accordingly, the axial accuracy of the output member can be maintained high, and the axial accuracy of the rotor fixing member that is in contact with the output member and supported in the radial direction can also be maintained high.

[6]
A spline connecting portion (A1) connected to the output member (50) so as to rotate integrally with the output member (50) is further formed on the inner peripheral surface of the cylindrical support portion (48),
The contact portion (A2) is formed by a cylindrical surface having a smaller diameter than the spline connecting portion (A1) on the inner peripheral surface of the cylindrical support portion (48).
The spline connecting portion (A1) and the contact portion (A2) are disposed adjacent to each other in the axial direction (L).

  According to this configuration, the rotor, the rotor fixing member, and the output member can be connected so as to rotate integrally at the spline connecting portion of the cylindrical support portion. In addition, the rotor, the rotor fixing member, and the output member can be easily aligned with each other at the contact portion formed by the cylindrical surface of the cylindrical support portion. Further, by forming the cylindrical surface forming the contact portion to be smaller in diameter than the spline connecting portion, the contact portion can be made thicker than the spline connecting portion, and the strength can be increased. And by arrange | positioning such an abutting part adjacent to an axial direction with respect to a spline connection part, sufficient intensity | strength with respect to the press fit along the axial direction of the member arrange | positioned on the radial direction outer side of a cylindrical support part Can be easily secured.

[7]
The first one-way clutch (F1), the pump driving member (60), the second one-way clutch (F2), and the input member (10) are arranged in the order described from the radially inner side to the radially outer side,
The contact portion (A2) is disposed so as to have a portion overlapping both the first one-way clutch (F1) and the second one-way clutch (F2) when viewed in the radial direction.

  According to this configuration, the first one-way clutch can regulate the relative rotation between the rotor fixing member and the pump driving member, and the second one-way clutch can regulate the relative rotation between the input member and the pump driving member. Can be realized reasonably and easily. In addition, since the contact portion of the rotor fixing member with the output member overlaps with both the first one-way clutch and the second one-way clutch when viewed in the radial direction, the device shaft length is further shortened to further reduce the size of the entire device. Can be achieved.

[8]
An engagement device (CL) for selectively driving and connecting the input member (10) and the output member (50);
The rotor fixing member (40) includes a cylindrical fixing portion (41) whose outer peripheral surface is in contact with the rotor (Ro), a cylindrical support portion (48) that forms the contact portion (A2), and the cylindrical shape. A radial connecting portion (44) for connecting the fixing portion (41) and the cylindrical support portion (48) in the radial direction;
The engagement device (CL) is disposed in a space surrounded by the cylindrical fixing portion (41), the radial connecting portion (44), and the cylindrical support portion (48),
The contact portion (A2) is arranged so as to further have a portion overlapping the rotor (Ro) and the engagement device (CL) when viewed in the radial direction.

  According to this configuration, by providing the engagement device, for example, the connection between the input member and the rotating electrical machine can be released while the combustion of the internal combustion engine is stopped, and the vehicle is running while the combustion of the internal combustion engine is stopped. Energy efficiency can be increased. Further, even when such an engagement device is additionally provided, the engagement device is disposed in a space surrounded by the cylindrical fixing portion, the radial connection portion, and the cylindrical support portion. The combined device and the rotor can be overlapped when viewed in the radial direction, and a reduction in the axial length can be achieved.

[9]
A shaft support member (28) fixed to the case (2) and supporting the output member (50) in a radial direction;
The rotor fixing member (40) includes a cylindrical fixing portion (41) whose outer peripheral surface is in contact with the rotor (Ro), a cylindrical support portion (48) that forms the contact portion (A2), and the cylindrical shape. A radial connecting portion (44) for connecting the fixing portion (41) and the cylindrical support portion (48) in the radial direction;
The input member (10) includes an input cylindrical portion (12) formed in a cylindrical shape, an input main body portion (11) having a smaller diameter than the input cylindrical portion (12), and the input cylindrical portion (12 ) And the input body portion (11), and an input connection portion (13) extending in the radial direction so as to connect,
The case (2) includes a first case part (21) to which the shaft support member (28) is fixed, and a second case provided closer to the input member (10) than the first case part (21). Part (24),
An input bearing (B1) that supports the input body portion (11) in the radial direction so as to be relatively rotatable with respect to the case (2) is fixed to the second case portion (24),
The shaft support member (28), the radial connecting portion (44), the pump driving member (60), and the input connecting portion (13) are interposed through thrust bearings (B6, B7, B8). Arranged side by side in the axial direction (L),
The input bearing (B1) is disposed in a state of being in contact with a contact surface (26a) facing the shaft support member (28) side in the second case portion (24),
A gap adjusting member (95) is disposed between the input connecting portion (13) and the input bearing (B1) in the axial direction (L).

  According to this configuration, since the input member is fixed to the case via the input bearing fixed to the second case portion, the input member can be rotatably supported in a radial direction with high support accuracy. Further, with respect to the shaft support member, the radial direction connection portion, the pump drive member, the input connection portion, and the input bearing that are arranged side by side in the axial direction, a clearance adjustment member is disposed between the input connection portion and the input bearing. Therefore, the axial clearance between the components can be adjusted to an appropriate amount. Therefore, it is possible to minimize the backlash in the axial direction of each component. Further, such a gap adjustment member is fixed to the second case portion, the radial connection portion, the pump drive member, and the input connection portion that are positioned relative to the shaft support member fixed to the first case portion. Therefore, the thickness of the gap adjustment member can be determined easily and appropriately.

[10]
The rotor (Ro) has a longer axial dimension than the stator (St);
The sum (β) of the clearance in the axial direction (L) from the shaft support member (28) to the input bearing (B1) is the difference between the shaft length of the rotor (Ro) and the shaft length of the stator (St). The thickness of the gap adjusting member (95) is set so as to be equal to or less than half of the thickness.

  According to this configuration, even if the rotor support member and the rotor move to the maximum in the axial direction, the entire rotor can always be accommodated in the region occupied by the stator in the axial direction. Therefore, it is possible to suppress a decrease in performance of the rotating electrical machine.

[11]
A shaft support member (28) fixed to the case (2) and supporting the output member (50) in a radial direction;
A drive transmission mechanism (80) disposed on the pump drive member (60) side with respect to the shaft support member (28), and transmitting the rotation of the pump drive member (60) to the oil pump (OP); In addition,
The rotor fixing member (40) has a radial coupling portion (44) extending in the radial direction between the pump drive member (60) and the drive transmission mechanism (80) in the axial direction (L),
The output member (50) is disposed in a state of passing through the shaft support member (28) and the rotor fixing member (40) in the axial direction (L),
The pump drive member (60) and the drive transmission mechanism (80) pass through the radial connecting portion (44) in the axial direction (L) on the radially outer side with respect to the output member (50). Are coupled to each other via an intermediate transmission mechanism (70) arranged in

  According to this configuration, even when the radial coupling portion of the rotor fixing member is interposed between the pump driving member and the drive transmission mechanism in the axial direction, the intermediate transmission mechanism that is disposed through the radial coupling portion is provided. Thus, the rotation of the pump drive member can be appropriately transmitted to the drive transmission mechanism. Further, since the rotation of the pump drive member is transmitted to the oil pump via the intermediate transmission mechanism and the drive transmission mechanism, the degree of freedom in arrangement of the oil pump can be increased.

  The vehicle drive device according to the present disclosure only needs to exhibit at least one of the effects described above.

  The present invention can be used for a drive device for a hybrid vehicle, for example.

DESCRIPTION OF SYMBOLS 1 Vehicle drive device 2 Case 10 Input shaft 11 Input main-body part 12 Input cylindrical part 21 1st division | segmentation case part (1st case part)
24 Third division case part (second case part)
26a Contact surface 28 Shaft support member (case wall)
40 Rotor fixing member 41 Cylindrical fixing part (first cylindrical part)
44 radial direction connection part 48 cylindrical support part (2nd cylindrical part)
48a Inner peripheral uneven surface 48b Cylindrical inner peripheral surface 48c Tooth tip 48d Tooth base 48e Tooth side surface 50 Output shaft (output member)
50a Peripheral surface 50b of outer peripheral side Cylindrical outer peripheral surface 50c Tooth tip 50d Tooth bottom 50e Tooth side surface 60 Pump drive member 61 Pump drive cylindrical part 70 Transmission gear mechanism (intermediate transmission mechanism)
80 Drive transmission mechanism 95 Gap adjusting member E Internal combustion engine D Damper CL Engaging device MG Rotating electrical machine St Stator Ro Rotor TM Transmission device W Wheel OP Oil pump F1 First one-way clutch F2 Second one-way clutch A Mounting portion A1 Spline engaging portion (Connecting part, transmission part)
A2 Inlay fitting part (contact part)
B1 First bearing (input bearing)
B2 Second bearing (support bearing)
B3 Third bearing (support bearing)
B6 Sixth bearing (thrust bearing)
B7 7th bearing (thrust bearing)
B8 Eighth bearing (thrust bearing)
L axis direction

Claims (10)

  1. An input member drivingly connected to the internal combustion engine;
    A rotating electrical machine having a rotor and a stator;
    A rotor fixing member fixed to the rotor and rotating integrally with the rotor;
    An output member that is supported in a radial direction so as to be relatively rotatable with respect to a case to which the stator is fixed, and that rotates integrally with the rotor fixing member and is drivingly connected to a wheel;
    A pump drive member that is drivingly connected to the oil pump;
    A first one-way clutch that regulates relative rotation between the rotor fixing member and the pump drive member when the rotation speed of the rotor fixing member is equal to or higher than the rotation speed of the input member;
    A second one-way clutch that regulates relative rotation between the input member and the pump drive member when the rotational speed of the input member is equal to or higher than the rotational speed of the rotor fixing member;
    The rotor fixing member includes a contact portion that contacts the output member, and is supported by the contact portion in a radial direction with respect to the output member, and the rotor fixing member is interposed between the contact portion and the support bearing. Supported relative to the case,
    The vehicle drive device, wherein the contact portion is disposed so as to have a portion overlapping at least one of the first one-way clutch and the second one-way clutch when viewed in the radial direction.
  2. The rotor fixing member has a cylindrical support portion formed in a cylindrical shape,
    The vehicle drive device according to claim 1, wherein the contact portion is formed on an inner peripheral surface of the cylindrical support portion and is in contact with an outer peripheral surface of the output member.
  3.   3. The vehicle drive device according to claim 2, wherein the output member, the cylindrical support portion, and the first one-way clutch are arranged in an order from a radially inner side toward a radially outer side.
  4.   The vehicle drive device according to claim 3, wherein an outer peripheral surface of the cylindrical support portion and the first one-way clutch are press-fitted.
  5. The rotor fixing member further includes a cylindrical fixing portion in contact with the rotor, and a radial connecting portion that connects the cylindrical fixing portion and the cylindrical support portion in a radial direction,
    The first one-way clutch is arranged on one side in the axial direction with respect to the radial connecting portion, and a case wall constituting the case is arranged on the opposite side to the first one-way clutch side in the axial direction. ,
    The said support bearing is either the said 1st one-way clutch side in an axial direction with respect to the said radial direction connection part, and is arrange | positioned between the said case wall and the said output member. The vehicle drive device according to claim 1.
  6. A spline connecting portion that is connected to the output member so as to rotate integrally with the output member is further formed on the inner peripheral surface of the cylindrical support portion,
    The contact portion is formed by a cylindrical surface having a smaller diameter than the spline connecting portion on the inner peripheral surface of the cylindrical support portion,
    The vehicle drive device according to any one of claims 2 to 5, wherein the spline connecting portion and the contact portion are disposed adjacent to each other in the axial direction.
  7. The first one-way clutch, the pump driving member, the second one-way clutch, and the input member are arranged in the order described from the radially inner side to the radially outer side,
    The vehicle according to any one of claims 1 to 6, wherein the contact portion is disposed so as to have a portion overlapping with both the first one-way clutch and the second one-way clutch when viewed in the radial direction. Drive device.
  8. An engagement device for selectively connecting the input member and the output member;
    The rotor fixing member connects a cylindrical fixing portion whose outer peripheral surface is in contact with the rotor, a cylindrical support portion forming the contact portion, and the cylindrical fixing portion and the cylindrical support portion in a radial direction. A radial connecting portion,
    The engagement device is disposed in a space surrounded by the cylindrical fixing portion, the radial connecting portion, and the cylindrical support portion;
    The vehicle drive device according to claim 7, wherein the contact portion is disposed so as to further have a portion overlapping with the rotor and the engagement device when viewed in a radial direction.
  9. A shaft support member fixed to the case and supporting the output member in a radial direction;
    The rotor fixing member connects a cylindrical fixing portion whose outer peripheral surface is in contact with the rotor, a cylindrical support portion forming the contact portion, and the cylindrical fixing portion and the cylindrical support portion in a radial direction. A radial connecting portion,
    The input member is formed in a radial direction so as to connect the input cylindrical portion formed in a cylindrical shape, an input main body portion having a smaller diameter than the input cylindrical portion, and the input cylindrical portion and the input main body portion. An input coupling portion extending,
    The case has a first case portion to which the shaft support member is fixed, and a second case portion provided on the input member side with respect to the first case portion,
    An input bearing that supports the input body portion in the radial direction so as to be relatively rotatable with respect to the case is fixed to the second case portion,
    The shaft support member, the radial connection portion, the pump drive member, and the input connection portion are arranged side by side in the axial direction between each other via a thrust bearing,
    The input bearing is disposed in a state of being in contact with a contact surface facing the shaft support member side in the second case portion,
    The vehicle drive device according to any one of claims 1 to 8, wherein a gap adjusting member is disposed between the input connecting portion and the input bearing in the axial direction.
  10. The rotor has a longer axial dimension than the stator;
    The thickness of the gap adjustment member is set so that the sum of the axial clearances from the shaft support member to the input bearing is less than half of the difference between the shaft length of the rotor and the shaft length of the stator. The vehicle drive device according to claim 9.
JP2014202280A 2014-01-16 2014-09-30 vehicle drive device Pending JP2015155292A (en)

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JP2014006067 2014-01-16
JP2014202280A JP2015155292A (en) 2014-01-16 2014-09-30 vehicle drive device

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017106582A (en) * 2015-12-10 2017-06-15 トヨタ自動車株式会社 Power transmission device for vehicle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017106582A (en) * 2015-12-10 2017-06-15 トヨタ自動車株式会社 Power transmission device for vehicle
US10001206B2 (en) 2015-12-10 2018-06-19 Toyota Jidosha Kabushiki Kaisha Power transmission system for vehicle

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