JP2019094930A - Driving device for vehicle - Google Patents

Driving device for vehicle Download PDF

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JP2019094930A
JP2019094930A JP2017222307A JP2017222307A JP2019094930A JP 2019094930 A JP2019094930 A JP 2019094930A JP 2017222307 A JP2017222307 A JP 2017222307A JP 2017222307 A JP2017222307 A JP 2017222307A JP 2019094930 A JP2019094930 A JP 2019094930A
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output
gear
case
rotating
bearing
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JP6848824B2 (en
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大樹 須山
Daiki Suyama
大樹 須山
夏木 佐田
Natsuki Sada
夏木 佐田
知沙美 松本
Chisami Matsumoto
知沙美 松本
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Aisin AW Co Ltd
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Aisin AW Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
    • B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • B60K17/165—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing provided between independent half axles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/104—Differential gearings with gears having orbital motion with orbital spur gears characterised by two ring gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • F16H2048/364—Differential gearings characterised by intentionally generating speed difference between outputs using electric or hydraulic motors

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)

Abstract

To realize a driving device for a vehicle capable of miniaturizing a planetary gear device constituting a transmission device.SOLUTION: A first output member 81 includes a first output gear 81a engaged with a first driven gear 51a of a first connection member 51, and a second output member 82 includes a second output gear 82a engaged with a second driven gear 52a of a second connection member 52. Each of the first output member 81 and the second output member 82 is rotatably supported at two places in an axial direction L by a case 3 or a supporting member 40 fixed to the case 3.SELECTED DRAWING: Figure 1

Description

本発明は、車両用駆動装置に関する。   The present invention relates to a drive system for a vehicle.

第１回転電機と、第２回転電機と、第１車輪に駆動連結される第１連結部材と、第２車輪に駆動連結される第２連結部材と、第１回転電機のトルクを第１連結部材及び第２連結部材のうちの少なくとも第１連結部材に伝達すると共に、第２回転電機のトルクを第１連結部材及び第２連結部材のうちの少なくとも第２連結部材に伝達する伝達装置と、を備えた車両用駆動装置が知られている。このような構成の車両用駆動装置の一例が、特開２０１７−１４１８８９号公報（特許文献１）に開示されている。以下、背景技術の説明において括弧内に示す符号は特許文献１のものである。   The torque of the first rotating electrical machine is connected to the first rotating electric machine, the second connecting member that is drivingly connected to the second wheel, and the first connecting member that is drivingly connected to the first wheel. A transmission device that transmits the torque of the second rotating electric machine to at least a second connection member of the first connection member and the second connection member while transmitting the torque to at least the first connection member of the member and the second connection member; A vehicle drive device is known. An example of a vehicle drive device having such a configuration is disclosed in JP-A-2017-141889 (Patent Document 1). Hereinafter, reference numerals in parentheses in the description of the background art are those of Patent Document 1.

特許文献１の図１及び図７に示されるように、特許文献１の車両駆動装置（１）は、２つの電動モータ（２Ｌ，２Ｒ）と、左右の駆動輪（６１Ｌ，６１Ｒ）に駆動連結される２つの出力歯車軸（１４Ｌ，１４Ｒ）と、２つの遊星歯車機構（３０Ｌ，３０Ｒ）を用いて構成される歯車装置（３０）と、歯車装置（３０）を収容する減速装置ハウジング（９）と、を備えている。この歯車装置（３０）は、電動モータ（２Ｌ，２Ｒ）から動力が伝達される入力歯車（１２ａ）に噛み合う入力側外歯車（１３ａ）と、出力歯車軸（１４Ｌ，１４Ｒ）が有する出力歯車（１４ａ）に噛み合う出力側小径歯車（１３ｂ）とを備えている。そして、この歯車機構（３０）は、特許文献１の段落０１１０に記載のように構成されることで、電動モータ（２Ｌ，２Ｒ）の側から入力側外歯車（１３ａ）に入力されたトルクを出力側小径歯車（１３ｂ）から駆動輪（６１Ｌ，６１Ｒ）の側に出力する際に、２つの電動モータ（２Ｌ，２Ｒ）のトルク差を増幅して左右の駆動輪（６１Ｌ，６１Ｒ）に分配することが可能に構成されている（段落０１０８，０１６６）。   As shown in FIGS. 1 and 7 of Patent Document 1, the vehicle drive device (1) of Patent Document 1 is drivingly connected to two electric motors (2L, 2R) and left and right drive wheels (61L, 61R). Gear unit (30) configured by using two output gear shafts (14L, 14R) and two planetary gear mechanisms (30L, 30R), and a reduction gear housing (9) that accommodates the gear unit (30) ) And. This gear device (30) has an input gear (13a) meshing with an input gear (12a) to which power is transmitted from the electric motor (2L, 2R), and an output gear (14L, 14R). And an output-side small-diameter gear (13b) meshing with 14a). Then, the gear mechanism (30) is configured as described in paragraph 0110 of Patent Document 1 to transmit the torque input to the input-side external gear (13a) from the side of the electric motor (2L, 2R). When outputting from the output-side small-diameter gear (13b) to the drive wheels (61L, 61R), the torque difference between the two electric motors (2L, 2R) is amplified and distributed to the left and right drive wheels (61L, 61R) It is configured to be possible (paragraphs 0108 and 0166).

ところで、特許文献１の車両駆動装置（１）では、特許文献１の段落０１１８及び図２に記載のように、出力歯車（１４ａ）に噛み合う出力側小径歯車（１３ｂ）は、キャリヤフランジ（３４ａ）から軸方向に突出するように形成された中空軸部（３５）の外周面に形成されている。そして、特許文献１の段落０１１６に記載のように、中空軸部（３５）は、軸方向一方側の端部においてのみ減速装置ハウジング（９）により支持されている。そのため、歯車装置（３０）がトルクを伝達している状態において、出力側小径歯車（１３ｂ）が出力歯車（１４ａ）から受ける荷重（噛み合い力による荷重）が遊星キャリヤ（ＣＬ，ＣＲ）に伝達されやすい。また、特許文献１の車両駆動装置（１）では、特許文献１の段落０１２１及び図２に記載のように、入力歯車（１２ａ）に噛み合う入力側外歯車（１３ａ）は、内歯車（ＲＬ，ＲＲ）の外周面に形成されており、内歯車（ＲＬ，ＲＲ）は、キャリヤフランジ（３４ａ，３４ｂ）により径方向内側から支持されている。そのため、歯車装置（３０）がトルクを伝達している状態において、入力側外歯車（１３ａ）が入力歯車（１２ａ）から受ける荷重が遊星キャリヤ（ＣＬ，ＣＲ）に伝達されやすい。このように、特許文献１の車両駆動装置（１）では、出力側小径歯車（１３ｂ）や入力側外歯車（１３ａ）が受ける荷重が遊星キャリヤ（ＣＬ，ＣＲ）に伝達されやすいため、遊星キャリヤ（ＣＬ，ＣＲ）に要求される剛性がその分高くなり、歯車装置（３０）を構成する遊星歯車機構（３０Ｌ，３０Ｒ）が大型化しやすい。 By the way, in the vehicle drive device (1) of Patent Document 1, as described in paragraph 0118 and FIG. 2 of Patent Document 1, the output-side small diameter gear (13b) meshing with the output gear (14a) is a carrier flange (34a) And an outer peripheral surface of a hollow shaft portion (35) formed to project in the axial direction. Then, as described in paragraph 0116 of Patent Document 1, the hollow shaft portion (35) is supported by the reduction gear device housing (9) only at the end portion on one side in the axial direction. Therefore, when the gear unit (30) is transmitting torque, the load (load by meshing force) that the output small-diameter gear (13b) receives from the output gear (14a) is applied to the planet carrier (C L , C R ) It is easy to be transmitted. In the vehicle drive system (1) of Patent Document 1, as described in paragraph 0121 of Patent Document 1 and FIG. 2, the input-side external gear (13a) meshing with the input gear (12a) is an internal gear (R L) are formed on the outer peripheral surface of the R R), the internal gear (R L, R R) is supported from the radially inner side by the carrier flange (34a, 34b). Therefore, in a state where the gear device (30) is transmitting torque, the load which the input-side external gear (13a) receives from the input gear (12a) is easily transmitted to the planet carriers (C L , C R ). Thus, in the vehicle drive device of Patent Document 1 (1), since the output-side small-diameter gear (13b) and the input-side external gear (13a) is load undergoes easily transmitted planet carrier (C L, C R), the The rigidity required of the planet carrier (C L , C R ) is correspondingly increased, and the planetary gear mechanism (30 L, 30 R) constituting the gear device (30) is easily enlarged.

特開２０１７−１４１８８９号公報JP, 2017-141889, A

そこで、伝達装置を構成する遊星歯車装置の小型化を図ることが可能な車両用駆動装置の実現が望まれる。   Therefore, it is desired to realize a vehicle drive device capable of downsizing the planetary gear device that constitutes the transmission device.

上記に鑑みた車両用駆動装置の第１の特徴構成は、第１回転電機と、第２回転電機と、第１車輪に駆動連結される第１連結部材と、第２車輪に駆動連結される第２連結部材と、前記第１回転電機のトルクを前記第１連結部材及び前記第２連結部材のうちの少なくとも前記第１連結部材に伝達すると共に、前記第２回転電機のトルクを前記第１連結部材及び前記第２連結部材のうちの少なくとも前記第２連結部材に伝達する伝達装置と、前記第１回転電機、前記第２回転電機、前記第１連結部材、前記第２連結部材、及び前記伝達装置を収容するケースと、を備え、前記伝達装置は、第１軸上に配置され、前記第１連結部材及び前記第２連結部材は、前記第１軸に平行な第２軸上に配置され、前記伝達装置は、前記第１回転電機に駆動連結される第１回転要素、前記第１連結部材に駆動連結される第２回転要素、前記第２連結部材に駆動連結される第３回転要素、及び、前記第２回転電機に駆動連結される第４回転要素を少なくとも有する遊星歯車装置と、前記第１回転要素に連結される第１入力部材と、前記第２回転要素に連結される第１出力部材と、前記第３回転要素に連結される第２出力部材と、前記第４回転要素に連結される第２入力部材と、を備え、前記第１出力部材は、前記第１連結部材が備える第１従動ギヤに噛み合う第１出力ギヤを備え、前記第２出力部材は、前記第２連結部材が備える第２従動ギヤに噛み合う第２出力ギヤを備え、前記１出力部材及び前記第２出力部材のそれぞれが、前記ケース又は前記ケースに固定された支持部材により、軸方向の２ヶ所で回転自在に支持されている点にある。   A first characteristic configuration of the vehicle drive device in view of the above is that the first rotating electric machine, the second rotating electric machine, the first connecting member that is drivingly connected to the first wheel, and the driving connection to the second wheel The torque of the second rotating electric machine is transmitted to the second connecting member, and the torque of the first rotating electric machine is transmitted to at least the first connecting member of the first connecting member and the second connecting member. A transmission device for transmitting to at least the second connection member of the connection member and the second connection member, the first rotary electric machine, the second rotary electric machine, the first connection member, the second connection member, and A case for containing a transmission device, wherein the transmission device is disposed on a first axis, and the first connection member and the second connection member are disposed on a second axis parallel to the first axis And the transmission device is drivingly connected to the first rotating electric machine First rotation element, second rotation element drivingly connected to the first connecting member, third rotation element drivingly connected to the second connecting member, and fourth rotation drivingly connected to the second rotating electric machine A planetary gear set having at least an element, a first input member connected to the first rotating element, a first output member connected to the second rotating element, and a second connected to the third rotating element An output member, and a second input member connected to the fourth rotating element, wherein the first output member includes a first output gear engaged with a first driven gear provided in the first connecting member; The second output member includes a second output gear meshing with a second driven gear provided in the second connection member, and the support in which each of the one output member and the second output member is fixed to the case or the case Depending on the member, it is turned at two places in the axial direction In that it is rotatably supported.

上記第１の特徴構成によれば、遊星歯車装置の第２回転要素に連結される第１出力部材が、ケース又はケースに固定された支持部材により、軸方向の２ヶ所で回転自在に支持される。すなわち、第１出力部材を、軸方向の２ヶ所のそれぞれで非回転部材により支持することができるため、第１出力部材が軸方向の１ヶ所でのみ非回転部材により支持される場合や、第１出力部材が非回転部材により支持されない場合に比べて、第１出力部材の支持剛性を高めることができる。従って、第１出力ギヤが第１従動ギヤから受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置に与える影響を低減することができる。同様に、遊星歯車装置の第３回転要素に連結される第２出力部材が、ケース又はケースに固定された支持部材により、軸方向の２ヶ所で回転自在に支持されるため、第２出力ギヤが第２従動ギヤから受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置に与える影響を低減することができる。
以上のように、上記第１の特徴構成によれば、第１出力ギヤや第２出力ギヤが受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置に与える影響を低減することができる。そのため、遊星歯車装置に要求される剛性を確保することが容易となり、遊星歯車装置の小型化を図ることができる。 According to the first aspect, the first output member connected to the second rotation element of the planetary gear device is rotatably supported at two places in the axial direction by the case or the support member fixed to the case. Ru. That is, since the first output member can be supported by the non-rotational member at each of two locations in the axial direction, the first output member may be supported by the non-rotational member at only one location in the axial direction, or The support rigidity of the first output member can be enhanced as compared with the case where the one output member is not supported by the non-rotating member. Therefore, the load which the first output gear receives from the first driven gear can be properly supported, and the influence of the load on the planetary gear device can be reduced. Similarly, since the second output member connected to the third rotation element of the planetary gear set is rotatably supported at two places in the axial direction by the case or the support member fixed to the case, the second output gear Can appropriately support the load received from the second driven gear, and the influence of the load on the planetary gear device can be reduced.
As described above, according to the first characteristic configuration, the load received by the first output gear and the second output gear can be appropriately supported, and the influence of the load on the planetary gear device can be reduced. it can. Therefore, it is easy to ensure the rigidity required for the planetary gear device, and the planetary gear device can be miniaturized.

上記に鑑みた車両用駆動装置の第２の特徴構成は、第１回転電機と、第２回転電機と、第１車輪に駆動連結される第１連結部材と、第２車輪に駆動連結される第２連結部材と、前記第１回転電機のトルクを前記第１連結部材及び前記第２連結部材のうちの少なくとも前記第１連結部材に伝達すると共に、前記第２回転電機のトルクを前記第１連結部材及び前記第２連結部材のうちの少なくとも前記第２連結部材に伝達する伝達装置と、前記第１回転電機、前記第２回転電機、前記第１連結部材、前記第２連結部材、及び前記伝達装置を収容するケースと、を備え、前記伝達装置は、第１軸上に配置され、前記第１回転電機及び前記第２回転電機は、前記第１軸に平行な第３軸上に配置され、前記伝達装置は、前記第１回転電機に駆動連結される第１回転要素、前記第１連結部材に駆動連結される第２回転要素、前記第２連結部材に駆動連結される第３回転要素、及び、前記第２回転電機に駆動連結される第４回転要素を少なくとも有する遊星歯車装置と、前記第１回転要素に連結される第１入力部材と、前記第２回転要素に連結される第１出力部材と、前記第３回転要素に連結される第２出力部材と、前記第４回転要素に連結される第２入力部材と、を備え、前記第１入力部材は、前記第１回転電機に駆動連結される第１駆動ギヤに噛み合う第１入力ギヤを備え、前記第２入力部材は、前記第２回転電機に駆動連結される第２駆動ギヤに噛み合う第２入力ギヤを備え、前記１入力部材及び前記第２入力部材のそれぞれが、前記ケース又は前記ケースに固定された支持部材により、軸方向の２ヶ所で回転自在に支持されている点にある。   A second characteristic configuration of the vehicle drive device in view of the above is that the first rotating electric machine, the second rotating electric machine, the first connecting member that is drivingly connected to the first wheel, and the driving connection to the second wheel The torque of the second rotating electric machine is transmitted to the second connecting member, and the torque of the first rotating electric machine is transmitted to at least the first connecting member of the first connecting member and the second connecting member. A transmission device for transmitting to at least the second connection member of the connection member and the second connection member, the first rotary electric machine, the second rotary electric machine, the first connection member, the second connection member, and And a case for accommodating a transmission device, wherein the transmission device is disposed on a first axis, and the first rotating electric machine and the second rotating electric machine are disposed on a third axis parallel to the first axis. And the transmission device is drivingly connected to the first rotating electric machine First rotation element, second rotation element drivingly connected to the first connecting member, third rotation element drivingly connected to the second connecting member, and fourth rotation drivingly connected to the second rotating electric machine A planetary gear set having at least an element, a first input member connected to the first rotating element, a first output member connected to the second rotating element, and a second connected to the third rotating element An output member, and a second input member connected to the fourth rotating element, wherein the first input member is engaged with a first drive gear that is drivingly connected to the first rotating electric machine The second input member includes a second input gear that meshes with a second drive gear that is drivingly connected to the second rotating electric machine, and each of the one input member and the second input member corresponds to the case or the case. The shaft is fixed by the support member fixed to the case In that it is rotatably supported at two points of the direction.

上記第２の特徴構成によれば、遊星歯車装置の第１回転要素に連結される第１入力部材が、ケース又はケースに固定された支持部材により、軸方向の２ヶ所で回転自在に支持される。すなわち、第１入力部材を、軸方向の２ヶ所のそれぞれで非回転部材により支持することができるため、第１入力部材が軸方向の１ヶ所でのみ非回転部材により支持される場合や、第１入力部材が非回転部材により支持されない場合に比べて、第１入力部材の支持剛性を高めることができる。従って、第１入力ギヤが第１駆動ギヤから受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置に与える影響を低減することができる。同様に、遊星歯車装置の第４回転要素に連結される第２入力部材が、ケース又はケースに固定された支持部材により、軸方向の２ヶ所で回転自在に支持されるため、第２入力ギヤが第２駆動ギヤから受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置に与える影響を低減することができる。
以上のように、上記第２の特徴構成によれば、第１入力ギヤや第２入力ギヤが受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置に与える影響を低減することができる。そのため、遊星歯車装置に要求される剛性を確保することが容易となり、遊星歯車装置の小型化を図ることができる。 According to the second characteristic configuration, the first input member connected to the first rotation element of the planetary gear device is rotatably supported at two places in the axial direction by the case or the support member fixed to the case. Ru. That is, since the first input member can be supported by the non-rotational member at each of two locations in the axial direction, the first input member may be supported by the non-rotational member at only one location in the axial direction, or The support rigidity of the first input member can be enhanced as compared with the case where the one input member is not supported by the non-rotating member. Therefore, the load received by the first input gear from the first drive gear can be properly supported, and the influence of the load on the planetary gear device can be reduced. Similarly, since the second input member connected to the fourth rotation element of the planetary gear set is rotatably supported at two places in the axial direction by the case or the support member fixed to the case, the second input gear Can appropriately support the load received from the second drive gear, and the influence of the load on the planetary gear device can be reduced.
As described above, according to the second characteristic configuration, the load received by the first input gear and the second input gear can be appropriately supported, and the influence of the load on the planetary gear device can be reduced. it can. Therefore, it is easy to ensure the rigidity required for the planetary gear device, and the planetary gear device can be miniaturized.

車両用駆動装置の更なる特徴と利点は、図面を参照して説明する実施形態についての以下の記載から明確となる。   Further features and advantages of the vehicle drive are evident from the following description of the embodiments described with reference to the drawings.

実施形態に係る車両用駆動装置の断面図Sectional view of a vehicle drive device according to an embodiment 図１の一部拡大図Partially enlarged view of Figure 1 実施形態に係る車両用駆動装置のスケルトン図Skeleton view of a drive device for a vehicle according to an embodiment 実施形態に係る遊星歯車装置の速度線図Velocity diagram of the planetary gear device according to the embodiment

車両用駆動装置の実施形態について、図面を参照して説明する。本実施形態では、第６軸受Ｂ６が「第１支持部材と第１出力部材との間に配置される軸受」及び「第１出力軸受」に相当し、第７軸受Ｂ７が「第２支持部材と第２出力部材との間に配置される軸受」及び「第２出力軸受」に相当し、第９軸受Ｂ９が「第１支持部材と第１入力部材との間に配置される軸受」に相当し、第１２軸受Ｂ１２が「第２支持部材と第２入力部材との間に配置される軸受」に相当し、第１３軸受Ｂ１３が「第１ピニオン軸受」に相当し、第１４軸受Ｂ１４が「第２ピニオン軸受」に相当する。また、本実施形態では、第７支持部４１ｂが「第１出力部材の支持部」に相当し、第８支持部４２ｂが「第２出力部材の支持部」に相当し、第９支持部４１ｃが「第１入力部材の支持部」に相当し、第１０支持部４２ｃが「第２入力部材の支持部」に相当する。そして、本実施形態では、第１油路９１が「第１ピニオン軸受に油を供給するための油路」に相当し、第２油路９２が「第１出力軸受に油を供給するための油路」に相当し、第３油路９３が「第２ピニオン軸受に油を供給するための油路」に相当し、第４油路９４が「第２出力軸受に油を供給するための油路」に相当する。   Embodiments of a vehicle drive system will be described with reference to the drawings. In the present embodiment, the sixth bearing B6 corresponds to "a bearing disposed between the first support member and the first output member" and "a first output bearing", and a seventh bearing B7 corresponds to "a second support member. And a “second output bearing”, and the ninth bearing B9 corresponds to “a bearing disposed between the first support member and the first input member”. The twelfth bearing B12 corresponds to "the bearing disposed between the second support member and the second input member", the thirteenth bearing B13 corresponds to the "first pinion bearing", and the fourteenth bearing B14. Corresponds to the “second pinion bearing”. Further, in the present embodiment, the seventh support portion 41 b corresponds to the “support portion of the first output member”, the eighth support portion 42 b corresponds to the “support portion of the second output member”, and the ninth support portion 41 c. Corresponds to the “support portion of the first input member”, and the tenth support portion 42c corresponds to the “support portion of the second input member”. Further, in the present embodiment, the first oil passage 91 corresponds to “an oil passage for supplying oil to the first pinion bearing”, and the second oil passage 92 “for supplying oil to the first output bearing”. The third oil passage 93 corresponds to an "oil passage for supplying oil to the second pinion bearing", and the fourth oil passage 94 corresponds to "oil for supplying a second output bearing". It corresponds to "the oil passage".

本明細書では、「駆動連結」とは、２つの回転要素が駆動力を伝達可能に連結された状態を意味する。この概念には、２つの回転要素が一体的に回転するように連結された状態や、２つの回転要素が１つ以上の伝動部材を介して駆動力を伝達可能に連結された状態が含まれる。このような伝動部材には、回転を同速で又は変速して伝達する各種の部材（軸、歯車機構、ベルト、チェーン等）が含まれ、回転及び駆動力を選択的に伝達する係合装置（摩擦係合装置や噛み合い式係合装置等）が含まれてもよい。但し、差動歯車装置又は差動歯車機構の各回転要素について「駆動連結」という場合には、当該差動歯車装置又は当該差動歯車機構が備える３つ以上の回転要素に関して互いに他の回転要素を介することなく駆動連結されている状態を指すものとする。   As used herein, “drive connection” means a state in which two rotating elements are connected to transmit driving force. This concept includes the state in which two rotating elements are connected to rotate integrally, and the state in which two rotating elements are connected to be able to transmit a driving force via one or more transmission members. . Such transmission members include various members (shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at different speeds, and an engagement device that selectively transmits rotation and driving force. (A frictional engagement device, a meshing engagement device, etc.) may be included. However, when each rotary element of the differential gear device or the differential gear mechanism is referred to as “drive connection”, other rotary elements are mutually different with respect to the differential gear device or three or more rotary elements provided in the differential gear mechanism. It refers to the state of being driven and connected without intervention.

また、本明細書では、「回転電機」は、モータ（電動機）、ジェネレータ（発電機）、及び必要に応じてモータ及びジェネレータの双方の機能を果たすモータ・ジェネレータのいずれをも含む概念として用いている。また、本明細書では、２つの部材の配置に関して、「特定方向視で重複する」とは、その視線方向に平行な仮想直線を当該仮想直線に直交する各方向に移動させた場合に、当該仮想直線が２つの部材の双方に交わる領域が少なくとも一部に存在することを指す。例えば、「径方向視で重複する」とは、当該仮想直線が２つの部材の双方に交わる領域が、周方向の少なくとも一部の領域に存在することを指す。なお、以下の説明における各部材についての方向は、それらが車両用駆動装置に組み付けられた状態での方向を表す。また、各部材についての方向や位置等に関する用語は、誤差（製造上許容され得る程度の誤差）による差異を有する状態を含む概念である。   Furthermore, in this specification, “rotary electric machine” is used as a concept including any of a motor (motor), a generator (generator), and a motor generator that fulfills both functions of the motor and the generator as required. There is. Further, in the present specification, with regard to the arrangement of two members, “overlap in a specific direction view” refers to the case where a virtual straight line parallel to the viewing direction is moved in each direction orthogonal to the virtual straight line. It means that there is a region where at least a portion of the virtual straight line intersects both of the two members. For example, “overlap in radial direction” means that a region where the virtual straight line intersects both of the two members is present in at least a partial region in the circumferential direction. In addition, the direction about each member in the following description represents the direction in the state assembled | attached to the drive device for vehicles. Moreover, the term regarding the direction, the position, etc. about each member is a concept including the state which has a difference by an error (error in the degree which can be permitted in manufacture).

図１及び図３に示すように、車両用駆動装置１は、第１回転電機１１と、第２回転電機１２と、第１車輪Ｗ１に駆動連結される第１連結部材５１と、第２車輪Ｗ２に駆動連結される第２連結部材５２と、伝達装置２と、を備えている。また、図１に示すように、車両用駆動装置１は、第１回転電機１１、第２回転電機１２、第１連結部材５１、第２連結部材５２、及び伝達装置２を収容するケース３を備えている。ここで、「収容する」とは、収容対象物の少なくとも一部を収容することを意味する。例えば、図１に示すように、本実施形態では、第１連結部材５１の全体がケース３に収容される（すなわち、ケース３の内部に配置される）が、第１連結部材５１の一部のみがケース３に収容される構成とすることもできる。   As shown in FIGS. 1 and 3, the vehicle drive device 1 includes a first rotating electric machine 11, a second rotating electric machine 12, a first connecting member 51 drivingly connected to the first wheel W 1, and a second wheel A second connection member 52 drivingly connected to W2 and the transmission device 2 are provided. Further, as shown in FIG. 1, the vehicle drive device 1 has a case 3 for housing the first rotating electric machine 11, the second rotating electric machine 12, the first connecting member 51, the second connecting member 52, and the transmission device 2. Have. Here, "to contain" means to accommodate at least a part of the contained object. For example, as shown in FIG. 1, in the present embodiment, the entire first connecting member 51 is accommodated in the case 3 (ie, disposed inside the case 3), but a part of the first connecting member 51 is Only in the case 3 can be accommodated.

伝達装置２は、第１回転電機１１のトルクを第１連結部材５１及び第２連結部材５２のうちの少なくとも第１連結部材５１に伝達すると共に、第２回転電機１２のトルクを第１連結部材５１及び第２連結部材５２のうちの少なくとも第２連結部材５２に伝達する装置である。第１連結部材５１に伝達されたトルクにより第１車輪Ｗ１が回転駆動されると共に、第２連結部材５２に伝達されたトルクにより第２車輪Ｗ２が回転駆動されることで、車両（車両用駆動装置１が搭載された車両、以下同様。）が走行する。図３に示すように、車両には、第１車輪Ｗ１と一体的に回転する第１軸部材５３と、第２車輪Ｗ２と一体的に回転する第２軸部材５４とが設けられている。第１軸部材５３は、第１車輪Ｗ１に連結されるドライブシャフトの少なくとも一部（第１車輪Ｗ１とは反対側の端部）を構成し、第２軸部材５４は、第２車輪Ｗ２に連結されるドライブシャフトの少なくとも一部（第２車輪Ｗ２とは反対側の端部）を構成する。本実施形態では、第１連結部材５１は、第１軸部材５３と同軸に配置され、第２連結部材５２は、第２軸部材５４と同軸に配置されている。なお、第１車輪Ｗ１が第１軸部材５３と同軸に配置される場合には、第１連結部材５１は第１車輪Ｗ１と同軸に配置され、第２車輪Ｗ２が第２軸部材５４と同軸に配置される場合には、第２連結部材５２は第２車輪Ｗ２と同軸に配置される。そして、本実施形態では、第１連結部材５１は、第１車輪Ｗ１と一体的に回転するように連結され、第２連結部材５２は、第２車輪Ｗ２と一体的に回転するように連結されている。具体的には、図３に示すように、本実施形態では、第１連結部材５１は、第１軸部材５３を介して第１車輪Ｗ１と一体的に回転するように連結され、第２連結部材５２は、第２軸部材５４を介して第２車輪Ｗ２と一体的に回転するように連結されている。第１車輪Ｗ１及び第２車輪Ｗ２は、互いに同軸（本実施形態では後述する第２軸Ａ２上）に配置される左右一対の車輪である。   The transmission device 2 transmits the torque of the first rotating electrical machine 11 to at least the first connecting member 51 of the first connecting member 51 and the second connecting member 52, and the torque of the second rotating electrical machine 12 as the first connecting member It is a device for transmitting to at least the second connecting member 52 of the connecting members 51 and 52. The first wheel W1 is rotationally driven by the torque transmitted to the first connecting member 51, and the second wheel W2 is rotationally driven by the torque transmitted to the second connecting member 52. The vehicle on which the device 1 is mounted (the same applies hereinafter) travels. As shown in FIG. 3, the vehicle is provided with a first shaft member 53 that rotates integrally with the first wheel W1 and a second shaft member 54 that rotates integrally with the second wheel W2. The first shaft member 53 constitutes at least a part of the drive shaft connected to the first wheel W1 (the end opposite to the first wheel W1), and the second shaft member 54 is provided to the second wheel W2 At least a part (the end opposite to the second wheel W2) of the drive shaft to be connected is configured. In the present embodiment, the first connection member 51 is disposed coaxially with the first shaft member 53, and the second connection member 52 is disposed coaxially with the second shaft member 54. When the first wheel W1 is disposed coaxially with the first shaft member 53, the first connecting member 51 is disposed coaxially with the first wheel W1, and the second wheel W2 is coaxial with the second shaft member 54. The second connection member 52 is disposed coaxially with the second wheel W2. And in this embodiment, the 1st connecting member 51 is connected so that it may rotate in one with the 1st wheel W1, and the 2nd connecting member 52 is connected so that it may rotate in one with the 2nd wheel W2. ing. Specifically, as shown in FIG. 3, in the present embodiment, the first connection member 51 is connected to rotate integrally with the first wheel W1 via the first shaft member 53, and the second connection is performed. The member 52 is connected to rotate integrally with the second wheel W2 via the second shaft member 54. The first wheel W1 and the second wheel W2 are a pair of left and right wheels which are disposed coaxially with each other (on the second axis A2 described later in the present embodiment).

このように、車両用駆動装置１は、左右一対の車輪を駆動するように車両に設けられる。例えば、車両が左右一対の前輪及び左右一対の後輪を備える場合には、車両用駆動装置１を、左右一対の前輪を駆動するように設け、或いは左右一対の後輪を駆動するように設けることができる。前者の場合、左右一対の前輪が第１車輪Ｗ１及び第２車輪Ｗ２となり、後者の場合、左右一対の後輪が第１車輪Ｗ１及び第２車輪Ｗ２となる。このように車両が左右一対の前輪及び左右一対の後輪を備える場合、左右一対の前輪及び左右一対の後輪のうちの車両用駆動装置１による駆動対象ではない左右一対の車輪が、別の駆動装置（車両用駆動装置１と同じ構成の駆動装置であっても良い。）により駆動される構成とすることもできる。   Thus, the vehicle drive device 1 is provided in the vehicle so as to drive the pair of left and right wheels. For example, when the vehicle includes a pair of left and right front wheels and a pair of left and right rear wheels, the vehicle drive device 1 is provided to drive the pair of left and right front wheels, or provided to drive the pair of left and right rear wheels be able to. In the former case, the pair of left and right front wheels is the first wheel W1 and the second wheel W2, and in the case of the latter, the pair of left and right rear wheels is the first wheel W1 and the second wheel W2. Thus, when the vehicle includes a pair of left and right front wheels and a pair of left and right rear wheels, the pair of left and right wheels that are not to be driven by the vehicle drive device 1 among the pair of left and right front wheels and the pair of left and right rear wheels is another The drive unit may be driven by a drive unit (which may be a drive unit having the same configuration as the vehicle drive unit 1).

図１及び図３に示すように、伝達装置２は、第１軸Ａ１上に配置され、第１連結部材５１及び第２連結部材５２は、第１軸Ａ１に平行な第２軸Ａ２上に配置されている。また、第１回転電機１１及び第２回転電機１２は、第１軸Ａ１及び第２軸Ａ２に平行な第３軸Ａ３上に配置されている。すなわち、第３軸Ａ３は、第１軸Ａ１に平行な軸であり、第２軸Ａ２は、第１軸Ａ１及び第３軸Ａ３に平行な軸である。これらの第１軸Ａ１、第２軸Ａ２、及び第３軸Ａ３は、互いに異なる軸（仮想軸）である。以下では、これらの各軸（第１軸Ａ１、第２軸Ａ２、及び第３軸Ａ３）に平行な方向（各軸の間で共通した軸方向）を「軸方向Ｌ」とする。そして、軸方向Ｌの一方側を「軸方向第１側Ｌ１」とし、軸方向Ｌの他方側（軸方向Ｌにおける軸方向第１側Ｌ１とは反対側）を「軸方向第２側Ｌ２」とする。本実施形態では、軸方向Ｌにおける第２回転電機１２に対して第１回転電機１１が配置される側が、軸方向第１側Ｌ１である。また、以下では、特に明記している場合を除き、「径方向Ｒ」は、第１軸Ａ１を基準とする径方向を表す（図２参照）。   As shown in FIGS. 1 and 3, the transmission device 2 is disposed on the first axis A1, and the first connecting member 51 and the second connecting member 52 are on the second axis A2 parallel to the first axis A1. It is arranged. The first rotating electrical machine 11 and the second rotating electrical machine 12 are disposed on a third axis A3 parallel to the first axis A1 and the second axis A2. That is, the third axis A3 is an axis parallel to the first axis A1, and the second axis A2 is an axis parallel to the first axis A1 and the third axis A3. The first axis A1, the second axis A2, and the third axis A3 are axes (virtual axes) different from one another. In the following, a direction parallel to the respective axes (first axis A1, second axis A2, and third axis A3) (axial direction common to the respective axes) is referred to as “axial direction L”. And one side of the axial direction L is made "the axial first side L1", and the other side of the axial direction L (the side opposite to the axial first side L1 in the axial direction L) "axial second side L2" I assume. In the present embodiment, the side on which the first rotary electric machine 11 is disposed with respect to the second rotary electric machine 12 in the axial direction L is the axial first side L1. Also, in the following, “radial direction R” represents a radial direction based on the first axis A1 unless otherwise specified (see FIG. 2).

第１回転電機１１は、ケース３等の非回転部材に固定される第１ステータ１１ａと、第１ステータ１１ａに対して回転自在に支持される第１ロータ１１ｂと、を備えている。第１ロータ１１ｂは、第１ロータ軸１１ｃと一体的に回転するように連結されている。第２回転電機１２は、ケース３等の非回転部材に固定される第２ステータ１２ａと、第２ステータ１２ａに対して回転自在に支持される第２ロータ１２ｂと、を備えている。第２ロータ１２ｂは、第２ロータ軸１２ｃと一体的に回転するように連結されている。第１回転電機１１及び第２回転電機１２のそれぞれは、バッテリやキャパシタ等の蓄電装置に電気的に接続されており、蓄電装置から電力の供給を受けて力行し、或いは、車両の慣性力等により発電した電力を蓄電装置に供給して蓄電させる。   The first rotating electrical machine 11 includes a first stator 11 a fixed to a non-rotating member such as the case 3 and a first rotor 11 b rotatably supported with respect to the first stator 11 a. The first rotor 11b is connected to rotate integrally with the first rotor shaft 11c. The second rotating electrical machine 12 includes a second stator 12 a fixed to a non-rotating member such as the case 3 and a second rotor 12 b rotatably supported with respect to the second stator 12 a. The second rotor 12 b is connected to rotate integrally with the second rotor shaft 12 c. Each of the first rotating electrical machine 11 and the second rotating electrical machine 12 is electrically connected to a storage device such as a battery or a capacitor, receives power supply from the storage device and performs powering, or inertial force of a vehicle, etc. The generated power is supplied to the storage device for storage.

本実施形態では、第１回転電機１１はインナロータ型の回転電機であり、第１ロータ１１ｂは、第１ステータ１１ａよりも径方向の内側であって径方向視で第１ステータ１１ａと重複する位置に配置されている。また、本実施形態では、第２回転電機１２はインナロータ型の回転電機であり、第２ロータ１２ｂは、第２ステータ１２ａよりも径方向の内側であって径方向視で第２ステータ１２ａと重複する位置に配置されている。なお、ここでの径方向は、第３軸Ａ３を基準とする径方向である。   In the present embodiment, the first rotary electric machine 11 is an inner rotor type rotary electric machine, and the first rotor 11b is a position radially inward of the first stator 11a and overlapping the first stator 11a in the radial direction. Is located in Further, in the present embodiment, the second rotating electrical machine 12 is an inner rotor type rotating electrical machine, and the second rotor 12b is located radially inward of the second stator 12a and overlaps the second stator 12a in a radial direction. Are placed in the In addition, the radial direction here is a radial direction on the basis of 3rd axis A3.

図２及び図３に示すように、車両用駆動装置１は、第１回転電機１１に駆動連結される第１駆動ギヤ２１ａと、第２回転電機１２に駆動連結される第２駆動ギヤ２２ａとを備えている。第１駆動ギヤ２１ａは、第１回転電機１１のトルクを出力するためのギヤであり、伝達装置２が備える入力ギヤ（第１入力ギヤ７１ａ）に噛み合っている。第１回転電機１１のトルクは、第１駆動ギヤ２１ａと第１入力ギヤ７１ａとの噛み合い部から伝達装置２に入力される。第２駆動ギヤ２２ａは、第２回転電機１２のトルクを出力するためのギヤであり、伝達装置２が備える入力ギヤ（第２入力ギヤ７２ａ）に噛み合っている。第２回転電機１２のトルクは、第２駆動ギヤ２２ａと第２入力ギヤ７２ａとの噛み合い部から伝達装置２に入力される。なお、伝達装置２は、第１入力部材７１及び第２入力部材７２を備えており、第１入力部材７１が、第１駆動ギヤ２１ａに噛み合う第１入力ギヤ７１ａを備え、第２入力部材７２が、第２駆動ギヤ２２ａに噛み合う第２入力ギヤ７２ａを備えている。   As shown in FIGS. 2 and 3, the vehicle drive device 1 includes a first drive gear 21 a drivingly connected to the first rotary electric machine 11 and a second drive gear 22 a drivingly connected to the second rotary electric machine 12. Is equipped. The first drive gear 21a is a gear for outputting the torque of the first rotating electrical machine 11, and is in mesh with an input gear (first input gear 71a) included in the transmission device 2. The torque of the first rotating electrical machine 11 is input to the transmission device 2 from the meshing portion of the first drive gear 21a and the first input gear 71a. The second drive gear 22a is a gear for outputting the torque of the second rotating electrical machine 12, and is engaged with the input gear (second input gear 72a) provided in the transmission device 2. The torque of the second rotating electrical machine 12 is input to the transmission device 2 from the meshing portion of the second drive gear 22a and the second input gear 72a. The transmission device 2 includes a first input member 71 and a second input member 72. The first input member 71 includes a first input gear 71a engaged with the first drive gear 21a. The second input member 72 Is provided with a second input gear 72a that meshes with the second drive gear 22a.

本実施形態では、第１駆動ギヤ２１ａは、第１回転電機１１（第１ロータ１１ｂ）と一体的に回転するように連結されている。具体的には、車両用駆動装置１は、第１ロータ軸１１ｃと一体的に回転するように連結される第１駆動部材２１（ここでは、軸部材）を、第１回転電機１１に対して軸方向第２側Ｌ２に備えており、第１駆動部材２１の外周面に第１駆動ギヤ２１ａが形成されている。また、本実施形態では、第２駆動ギヤ２２ａは、第２回転電機１２（第２ロータ１２ｂ）と一体的に回転するように連結されている。具体的には、車両用駆動装置１は、第２ロータ軸１２ｃと一体的に回転するように連結される第２駆動部材２２（ここでは、軸部材）を、第２回転電機１２に対して軸方向第１側Ｌ１に備えており、第２駆動部材２２の外周面に第２駆動ギヤ２２ａが形成されている。   In the present embodiment, the first drive gear 21a is connected to rotate integrally with the first rotating electrical machine 11 (first rotor 11b). Specifically, the vehicle drive device 1 is configured to rotate the first drive member 21 (here, the shaft member) connected to rotate integrally with the first rotor shaft 11c with respect to the first rotating electrical machine 11. The first drive gear 21 a is formed on the outer peripheral surface of the first drive member 21. Further, in the present embodiment, the second drive gear 22a is connected to rotate integrally with the second rotary electric machine 12 (second rotor 12b). Specifically, the vehicle drive device 1 is configured such that a second drive member 22 (here, a shaft member) connected to rotate integrally with the second rotor shaft 12c with respect to the second rotating electrical machine 12 A second drive gear 22 a is formed on the outer peripheral surface of the second drive member 22, provided on the first axial side L 1.

図１及び図３に示すように、第１連結部材５１及び第２連結部材５２のそれぞれは、伝達装置２が備える出力ギヤに噛み合う従動ギヤを備えている。具体的には、第１連結部材５１は、伝達装置２が備える第１出力ギヤ８１ａに噛み合う第１従動ギヤ５１ａを備え、第２連結部材５２は、伝達装置２が備える第２出力ギヤ８２ａに噛み合う第２従動ギヤ５２ａを備えている。第１車輪Ｗ１を回転駆動するためのトルクは、第１出力ギヤ８１ａと第１従動ギヤ５１ａとの噛み合い部から第１連結部材５１に出力され、第２車輪Ｗ２を回転駆動するためのトルクは、第２出力ギヤ８２ａと第２従動ギヤ５２ａとの噛み合い部から第２連結部材５２に出力される。なお、伝達装置２は、第１出力部材８１及び第２出力部材８２を備えており、第１出力部材８１が、第１従動ギヤ５１ａに噛み合う第１出力ギヤ８１ａを備え、第２出力部材８２が、第２従動ギヤ５２ａに噛み合う第２出力ギヤ８２ａを備えている。   As shown in FIGS. 1 and 3, each of the first connection member 51 and the second connection member 52 includes a driven gear that meshes with an output gear provided in the transmission device 2. Specifically, the first connection member 51 includes a first driven gear 51a engaged with the first output gear 81a of the transmission device 2. The second connection member 52 is connected to the second output gear 82a of the transmission device 2. It has a second driven gear 52a that engages. A torque for rotationally driving the first wheel W1 is output from the meshing portion of the first output gear 81a and the first driven gear 51a to the first connecting member 51, and a torque for rotationally driving the second wheel W2 is The meshing portion between the second output gear 82a and the second driven gear 52a is outputted to the second connecting member 52. The transmission device 2 includes a first output member 81 and a second output member 82. The first output member 81 includes a first output gear 81a engaged with the first driven gear 51a. The second output member 82 The second output gear 82a meshes with the second driven gear 52a.

本実施形態では、伝達装置２は、差動歯車装置６を備えている。ここで、差動歯車装置は、差動回転可能な複数の回転要素を有する歯車装置である。すなわち、差動歯車装置は、差動回転可能な複数の回転要素を有する差動歯車機構を用いて構成される。差動歯車装置は、例えば、遊星歯車式の差動歯車装置（すなわち、遊星歯車装置）とされ、この場合、差動歯車装置は、遊星歯車式の差動歯車機構（すなわち、遊星歯車機構）を用いて構成される。また、差動歯車装置は、例えば、傘歯車式の差動歯車装置とされ、この場合、差動歯車装置は、傘歯車式の差動歯車機構を用いて構成される。なお、差動歯車装置６が備える複数の回転要素の中に、ケース３等の非回転部材に固定される非回転要素が含まれる場合があるが、本明細書では、非回転要素も含めて「回転要素」という。   In the present embodiment, the transmission device 2 includes a differential gear device 6. Here, the differential gear device is a gear device having a plurality of differentially rotatable rotating elements. That is, the differential gear device is configured using a differential gear mechanism having a plurality of differentially rotatable rotating elements. The differential gear unit is, for example, a planetary gear type differential gear unit (that is, a planetary gear unit), and in this case, the differential gear unit is a planetary gear type differential gear mechanism (that is, a planetary gear mechanism) Constructed using The differential gear device is, for example, a bevel gear differential gear device, and in this case, the differential gear device is configured using a bevel gear differential gear mechanism. In addition, although the non-rotating element fixed to non-rotating members, such as case 3 etc., may be contained in several rotating elements with which differential gear apparatus 6 is equipped, in this specification, a non-rotating element is also included. It is called "rotational element".

差動歯車装置６は、第１回転要素Ｅ１、第２回転要素Ｅ２、第３回転要素Ｅ３、及び第４回転要素Ｅ４を有している（図４参照）。第１回転要素Ｅ１に上述した第１入力部材７１が連結されることで、第１回転電機１１が第１回転要素Ｅ１に駆動連結され、第２回転要素Ｅ２に上述した第１出力部材８１が連結されることで、第１連結部材５１が第２回転要素Ｅ２に駆動連結され、第３回転要素Ｅ３に上述した第２出力部材８２が連結されることで、第２連結部材５２が第３回転要素Ｅ３に駆動連結され、第４回転要素Ｅ４に上述した第２入力部材７２が連結されることで、第２回転電機１２が第４回転要素Ｅ４に駆動連結されている。本実施形態では、差動歯車装置６は遊星歯車装置６０である。すなわち、伝達装置２は、第１回転電機１１に駆動連結される第１回転要素Ｅ１、第１連結部材５１に駆動連結される第２回転要素Ｅ２、第２連結部材５２に駆動連結される第３回転要素Ｅ３、及び、第２回転電機１２に駆動連結される第４回転要素Ｅ４を少なくとも有する遊星歯車装置６０を備えている。本実施形態では、遊星歯車装置６０は、回転要素として、第１回転要素Ｅ１、第２回転要素Ｅ２、第３回転要素Ｅ３、及び第４回転要素Ｅ４のみを有している。   The differential gear device 6 includes a first rotation element E1, a second rotation element E2, a third rotation element E3, and a fourth rotation element E4 (see FIG. 4). By connecting the first input member 71 described above to the first rotating element E1, the first rotating electric machine 11 is drivably connected to the first rotating element E1, and the first output member 81 described above is connected to the second rotating element E2. By being coupled, the first coupling member 51 is drivingly coupled to the second rotation element E2, and the second output member 82 described above is coupled to the third rotation element E3, whereby the second coupling member 52 is coupled to the third rotation element E3. The second rotary electric machine 12 is drivingly connected to the fourth rotating element E4 by drivingly connected to the rotating element E3 and by connecting the second input member 72 described above to the fourth rotating element E4. In the present embodiment, the differential gear device 6 is a planetary gear device 60. That is, the transmission device 2 includes a first rotating element E1 drivingly connected to the first rotary electric machine 11, a second rotating element E2 drivingly connected to the first connecting member 51, and a second connecting member 52 The planetary gear device 60 is provided with at least a three-rotation element E3 and a fourth rotation element E4 drivingly connected to the second electric rotating machine 12. In the present embodiment, the planetary gear device 60 has only the first rotation element E1, the second rotation element E2, the third rotation element E3, and the fourth rotation element E4 as the rotation elements.

図２及び図３に示すように、遊星歯車装置６０は、第１サンギヤＳ１、第１キャリヤＣ１、及び第１リングギヤＲ１を有する第１遊星歯車機構６１と、第２サンギヤＳ２、第２キャリヤＣ２、及び第２リングギヤＲ２を有する第２遊星歯車機構６２と、を備えている。第１キャリヤＣ１は、第１３軸受Ｂ１３を介して第１ピニオンギヤＰ１を回転自在に支持し、第２キャリヤＣ２は、第１４軸受Ｂ１４を介して第２ピニオンギヤＰ２を回転自在に支持している。そして、遊星歯車装置６０は、第１遊星歯車機構６１と第２遊星歯車機構６２とを連結して構成されている。具体的には、本実施形態では、第１遊星歯車機構６１及び第２遊星歯車機構６２の双方が、シングルピニオン型の遊星歯車機構である。そして、第１キャリヤＣ１と第２サンギヤＳ２とが一体的に回転するように連結されていると共に、第１サンギヤＳ１と第２キャリヤＣ２とが一体的に回転するように連結されている。このように、第１遊星歯車機構６１と第２遊星歯車機構６２とは、それぞれが有する３つの回転要素のうちの２つずつが互いに連結されることで、全体として４つの回転要素を備えて一体的に差動動作を行うように構成されている。なお、第１遊星歯車機構６１は、第２遊星歯車機構６２に対して軸方向第１側Ｌ１に配置されている。また、本実施形態では、第１遊星歯車機構６１は、第１回転電機１１に対して軸方向第２側Ｌ２に配置され、第２遊星歯車機構６２は、第２回転電機１２に対して軸方向第１側Ｌ１に配置されている。   As shown in FIGS. 2 and 3, the planetary gear device 60 includes a first planetary gear mechanism 61 having a first sun gear S1, a first carrier C1, and a first ring gear R1, a second sun gear S2, and a second carrier C2. And a second planetary gear mechanism 62 having a second ring gear R2. The first carrier C1 rotatably supports the first pinion gear P1 via a thirteenth bearing B13, and the second carrier C2 rotatably supports the second pinion gear P2 via a fourteenth bearing B14. The planetary gear device 60 is configured by connecting a first planetary gear mechanism 61 and a second planetary gear mechanism 62. Specifically, in the present embodiment, both of the first planetary gear mechanism 61 and the second planetary gear mechanism 62 are single pinion type planetary gear mechanisms. The first carrier C1 and the second sun gear S2 are connected to rotate integrally with each other, and the first sun gear S1 and the second carrier C2 are connected to rotate integrally with each other. As described above, the first planetary gear mechanism 61 and the second planetary gear mechanism 62 include four rotating elements as a whole by connecting two of the three rotating elements that each has to each other. It is configured to perform differential operation integrally. The first planetary gear mechanism 61 is disposed on the first axial side L1 with respect to the second planetary gear mechanism 62. Further, in the present embodiment, the first planetary gear mechanism 61 is disposed on the second axial side L2 with respect to the first rotary electric machine 11, and the second planetary gear mechanism 62 is an axis relative to the second rotary electric machine 12. It is disposed on the direction first side L1.

図３に示すように、本実施形態では、第１回転電機１１は第１リングギヤＲ１に駆動連結され、第２回転電機１２は第２リングギヤＲ２に駆動連結され、第１連結部材５１は第１キャリヤＣ１に駆動連結され、第２連結部材５２は第２キャリヤＣ２に駆動連結されている。よって、本実施形態では、第１回転電機１１が駆動連結される第１回転要素Ｅ１は、第１リングギヤＲ１であり、第１連結部材５１が駆動連結される第２回転要素Ｅ２は、一体的に回転する第１キャリヤＣ１と第２サンギヤＳ２であり、第２連結部材５２が駆動連結される第３回転要素Ｅ３は、一体的に回転する第１サンギヤＳ１と第２キャリヤＣ２であり、第２回転電機１２が駆動連結される第４回転要素Ｅ４は、第２リングギヤＲ２である。そして、本実施形態では、回転速度の順が、第１回転要素Ｅ１、第２回転要素Ｅ２、第３回転要素Ｅ３、及び第４回転要素Ｅ４の順となっている。   As shown in FIG. 3, in the present embodiment, the first rotating electrical machine 11 is drivably connected to the first ring gear R1, the second rotating electrical machine 12 is drivably connected to the second ring gear R2, and the first connecting member 51 is the first The second coupling member 52 is drivingly connected to the second carrier C2. Therefore, in the present embodiment, the first rotating element E1 to which the first rotating electrical machine 11 is drivingly connected is the first ring gear R1, and the second rotating element E2 to which the first connecting member 51 is drivingly connected is integrally formed. The third rotating element E3 that rotates the first carrier C1 and the second sun gear S2 and the second connection member 52 is drivingly connected is the first sun gear S1 and the second carrier C2 that rotate integrally. The fourth rotating element E4 to which the two-rotating electric machine 12 is drivingly connected is the second ring gear R2. And in this embodiment, the order of rotation speed is the order of the 1st rotation element E1, the 2nd rotation element E2, the 3rd rotation element E3, and the 4th rotation element E4.

なお、「回転速度の順」とは、各回転要素の回転状態における回転速度の順番のことである。各回転要素の回転速度は、差動歯車装置６（遊星歯車装置６０）の回転状態によって変化するが、各回転要素の回転速度の高低の並び順は、差動歯車装置６の構造によって定まるものであるため一定となる。なお、「各回転要素の回転速度の順」は、各回転要素の速度線図（共線図、図４参照）における配置順に等しい。ここで、「各回転要素の速度線図における配置順」とは、速度線図（共線図）における各回転要素に対応する軸が、当該軸に直交する方向に沿って配置される順番のことである。速度線図（共線図）における各回転要素に対応する軸の配置方向は、速度線図の描き方によって異なるが、その配置順は差動歯車装置６の構造によって定まるものであるため一定となる。なお、図４において、縦軸の「０」は回転速度がゼロであることを示し、上側が正、下側が負となっている。   Note that "the order of the rotational speed" is the order of the rotational speed in the rotational state of each rotary element. The rotational speed of each rotary element changes according to the rotational state of the differential gear 6 (planet gear 60), but the arrangement order of the rotational speeds of the rotary elements is determined by the structure of the differential 6 Therefore, it becomes constant. Note that “the order of the rotational speeds of the respective rotating elements” is equal to the arrangement order in the velocity diagram (see the alignment chart, FIG. 4) of each of the rotating elements. Here, "the order of arrangement of the rotational elements in the velocity diagram" is the order of arrangement of the axes corresponding to the respective rotational elements in the velocity diagram (collinear diagram) along the direction orthogonal to the axes. It is. The arrangement direction of the axis corresponding to each rotation element in the velocity diagram (collinear diagram) varies depending on how the velocity diagram is drawn, but the arrangement order is determined by the structure of the differential gear 6, and Become. In FIG. 4, “0” on the vertical axis indicates that the rotational speed is zero, the upper side is positive, and the lower side is negative.

図４において、「Ｔｉ１」は、第１回転要素Ｅ１に第１回転電機１１の側から入力されるトルク（第１入力トルクＴｉ１）を表し、「Ｔｉ２」は、第４回転要素Ｅ４に第２回転電機１２の側から入力されるトルク（第２入力トルクＴｉ２）を表している。第１入力トルクＴｉ１の大きさは、第１回転電機１１の出力トルクの大きさと、第１回転電機１１から第１回転要素Ｅ１までの変速比（第１変速比）とに応じて定まり、第２入力トルクＴｉ２の大きさは、第２回転電機１２の出力トルクの大きさと、第２回転電機１２から第４回転要素Ｅ４までの変速比（第２変速比）とに応じて定まる。本実施形態では、第１駆動ギヤ２１ａと第２駆動ギヤ２２ａとが互いに同径に形成されていると共に、第１入力ギヤ７１ａと第２入力ギヤ７２ａとが互いに同径に形成されており、第１変速比と第２変速比とは互いに等しい。ここでは、第１変速比及び第２変速比は１より大きく、第１回転電機１１の回転は減速されて第１回転要素Ｅ１に伝達され、第２回転電機１２の回転は減速されて第４回転要素Ｅ４に伝達される。   In FIG. 4, “Ti1” represents torque (first input torque Ti1) input to the first rotary element E1 from the side of the first rotary electric machine 11, and “Ti2” represents the second torque of the fourth rotary element E4. The torque (2nd input torque Ti2) input from the side of the rotary electric machine 12 is represented. The magnitude of the first input torque Ti1 is determined according to the magnitude of the output torque of the first rotating electrical machine 11 and the gear ratio (first gear ratio) from the first rotating electrical machine 11 to the first rotating element E1. The magnitude of the 2 input torque Ti2 is determined according to the magnitude of the output torque of the second rotating electrical machine 12 and the gear ratio (second gear ratio) from the second rotating electrical machine 12 to the fourth rotating element E4. In the present embodiment, the first drive gear 21a and the second drive gear 22a are formed to have the same diameter, and the first input gear 71a and the second input gear 72a are formed to have the same diameter. The first gear ratio and the second gear ratio are equal to each other. Here, the first gear ratio and the second gear ratio are larger than 1 and the rotation of the first rotary electric machine 11 is decelerated and transmitted to the first rotary element E1, and the rotation of the second rotary electric machine 12 is decelerated and the fourth It is transmitted to the rotating element E4.

また、図４において、「Ｔｏ１」は、第２回転要素Ｅ２から第１車輪Ｗ１の側に出力されるトルク（第１出力トルクＴｏ１）を表し、「Ｔｏ２」は、第３回転要素Ｅ３から第２車輪Ｗ２の側に出力されるトルク（第２出力トルクＴｏ２）を表している。第１車輪Ｗ１の駆動力の大きさは、第１出力トルクＴｏ１の大きさと、第２回転要素Ｅ２から第１車輪Ｗ１までの変速比（第３変速比）とに応じて定まり、第２車輪Ｗ２の駆動力の大きさは、第２出力トルクＴｏ２の大きさと、第３回転要素Ｅ３から第２車輪Ｗ２までの変速比（第４変速比）とに応じて定まる。本実施形態では、第１出力ギヤ８１ａと第２出力ギヤ８２ａとが互いに同径に形成されていると共に、第１従動ギヤ５１ａと第２従動ギヤ５２ａとが互いに同径に形成されており、第３変速比と第４変速比とは互いに等しい。ここでは、第３変速比及び第４変速比は１より大きく、第２回転要素Ｅ２の回転は減速されて第１車輪Ｗ１に伝達され、第３回転要素Ｅ３の回転は減速されて第２車輪Ｗ２に伝達される。   Further, in FIG. 4, “To1” represents torque (first output torque To1) output from the second rotating element E2 to the side of the first wheel W1, and “To2” represents the third torque from the third rotating element E3. The torque (2nd output torque To2) output to the 2 wheel W2 side is represented. The magnitude of the driving force of the first wheel W1 is determined according to the magnitude of the first output torque To1 and the gear ratio (third gear ratio) from the second rotating element E2 to the first wheel W1, and the second wheel The magnitude of the driving force of W2 is determined according to the magnitude of the second output torque To2 and the gear ratio (fourth gear ratio) from the third rotating element E3 to the second wheel W2. In the present embodiment, the first output gear 81a and the second output gear 82a are formed to have the same diameter, and the first driven gear 51a and the second driven gear 52a are formed to the same diameter. The third gear ratio and the fourth gear ratio are equal to each other. Here, the third gear ratio and the fourth gear ratio are larger than 1 and the rotation of the second rotating element E2 is decelerated and transmitted to the first wheel W1, and the rotation of the third rotating element E3 is decelerated and the second wheel It is transmitted to W2.

上記のように第３変速比と第４変速比とが互いに等しいため、車両の直進時には、第２回転要素Ｅ２の回転速度と第３回転要素Ｅ３の回転速度とが等しくなり、遊星歯車装置６０の全ての回転要素が同速で回転する状態となる。一方、車両の旋回時には、第１車輪Ｗ１及び第２車輪Ｗ２のうちの外側の車輪（旋回中心から遠い方の車輪）が駆動連結された回転要素の回転速度が、第１車輪Ｗ１及び第２車輪Ｗ２のうちの内側の車輪（旋回中心に近い方の車輪）が駆動連結された回転要素の回転速度よりも高い状態となる。図４は、第１車輪Ｗ１が外側の車輪となる方向に車両が旋回している状態での遊星歯車装置６０の各回転要素の状態を表している。   As described above, since the third gear ratio and the fourth gear ratio are equal to each other, when the vehicle travels straight, the rotational speed of the second rotary element E2 and the rotational speed of the third rotary element E3 become equal. All the rotating elements of are rotating at the same speed. On the other hand, at the time of turning of the vehicle, the rotational speed of the rotating element to which the outer wheel (the wheel farther from the turning center) of the first wheel W1 and the second wheel W2 is drive connected is the first wheel W1 and the second wheel W1. The inner wheel (the wheel closer to the turning center) of the wheels W2 is higher than the rotational speed of the drivingly connected rotating element. FIG. 4 shows the state of each of the rotating elements of the planetary gear device 60 in a state where the vehicle is turning in the direction in which the first wheel W1 becomes the outer wheel.

トルクの釣り合いから、第１出力トルクＴｏ１及び第２出力トルクＴｏ２のそれぞれは、以下の式（１），（２）に示すように、第１入力トルクＴｉ１、第２入力トルクＴｉ２、第１遊星歯車機構６１のギヤ比（第１ギヤ比λ１）、及び第２遊星歯車機構６２のギヤ比（第２ギヤ比λ２）に応じて定まる。ここで、第１ギヤ比λ１は、第１リングギヤＲ１の歯数に対する第１サンギヤＳ１の歯数の比であり、第２ギヤ比λ２は、第２リングギヤＲ２の歯数に対する第２サンギヤＳ２の歯数の比である。
Ｔｏ１＝（１＋λ１）・Ｔｉ１−λ２・Ｔｉ２ ・・・（１）
Ｔｏ２＝（１＋λ２）・Ｔｉ２−λ１・Ｔｉ１ ・・・（２） From the balance of torques, each of the first output torque To1 and the second output torque To2 is represented by the following equations (1) and (2), the first input torque Ti1, the second input torque Ti2, the first planet It becomes settled according to the gear ratio (1st gear ratio λ1) of the gear mechanism 61 and the gear ratio (2nd gear ratio λ2) of the second planetary gear mechanism 62. Here, the first gear ratio λ1 is a ratio of the number of teeth of the first sun gear S1 to the number of teeth of the first ring gear R1, and the second gear ratio λ2 is a ratio of the number of teeth of the second ring gear R2 to the number of teeth of the second ring gear R2. It is a ratio of the number of teeth.
To1 = (1 + λ1) · Ti1-λ2 · Ti2 (1)
To2 = (1 + λ2) · Ti2-λ1 · Ti1 (2)

このように、第１出力トルクＴｏ１及び第２出力トルクＴｏ２のそれぞれは、第１入力トルクＴｉ１及び第２入力トルクＴｉ２の双方に応じて定まる。すなわち、本実施形態では、伝達装置２は、第１回転電機１１のトルクを第１連結部材５１及び第２連結部材５２の双方に伝達すると共に、第２回転電機１２のトルクを第１連結部材５１及び第２連結部材５２の双方に伝達するように構成されている。言い換えれば、伝達装置２は、第１回転電機１１及び第２回転電機１２のトルクを、第１連結部材５１及び第２連結部材５２に分配して伝達するように構成されている。車両用駆動装置１をこのように構成することで、第１回転電機１１と第１連結部材５１との間の動力伝達経路と第２回転電機１２と第２連結部材５２との間の動力伝達経路とが分離されている場合に比べて、第１車輪Ｗ１と第２車輪Ｗ２との間で駆動力に差を設ける際に、第１車輪Ｗ１と第２車輪Ｗ２との合計駆動力を大きく確保して、車両の旋回時の走行性能の向上を図ることが可能となっている。   Thus, each of the first output torque To1 and the second output torque To2 is determined according to both the first input torque Ti1 and the second input torque Ti2. That is, in the present embodiment, the transmission device 2 transmits the torque of the first rotating electrical machine 11 to both the first connecting member 51 and the second connecting member 52, and the torque of the second rotating electrical machine 12 as the first connecting member It is comprised so that it may transmit to both 51 and the 2nd connection member 52. As shown in FIG. In other words, the transmission device 2 is configured to distribute and transmit the torque of the first rotating electrical machine 11 and the second rotating electrical machine 12 to the first connecting member 51 and the second connecting member 52. By configuring the vehicle drive device 1 in this manner, power transmission between the first rotary electric machine 11 and the first connection member 51 and power transmission between the second rotary electric machine 12 and the second connection member 52 When making a difference in driving force between the first wheel W1 and the second wheel W2 compared to the case where the path is separated, the total driving force of the first wheel W1 and the second wheel W2 is large. By securing it, it is possible to improve the running performance at the time of turning of the vehicle.

補足説明すると、一例として、第１入力トルクＴｉ１の大きさが２００［Ｎ・ｍ］である状況において、第１出力トルクＴｏ１と第２出力トルクＴｏ２との差を１６０［Ｎ・ｍ］とする場合を想定する。この場合、本実施形態に係る車両用駆動装置１とは異なりＴｏ１＝Ｔｉ１，Ｔｏ２＝Ｔｉ２となる比較例の構成では、第１出力トルクＴｏ１と第２出力トルクＴｏ２との差を１６０［Ｎ・ｍ］とするための第２入力トルクＴｉ２の大きさは４０［Ｎ・ｍ］となる。よって、この比較例の場合には、第１入力トルクＴｉ１と第２入力トルクＴｉ２との和（第１出力トルクＴｏ１と第２出力トルクＴｏ２との和に等しい）は、２４０［Ｎ・ｍ］となる。これに対して、本実施形態に係る車両用駆動装置１では、第１入力トルクＴｉ１の大きさが２００［Ｎ・ｍ］である状況において、第１出力トルクＴｏ１と第２出力トルクＴｏ２との差を１６０［Ｎ・ｍ］とするための第２入力トルクＴｉ２の大きさは、第１ギヤ比λ１及び第２ギヤ比λ２の双方が“０．４”である場合には、上記の式（１），（２）より１１１［Ｎ・ｍ］となる。よって、この場合には、第１入力トルクＴｉ１と第２入力トルクＴｉ２との和（第１出力トルクＴｏ１と第２出力トルクＴｏ２との和）は３１１［Ｎ・ｍ］となり、上記の比較例の場合に比べて、７１［Ｎ・ｍ］（＝３１１［Ｎ・ｍ］−２４０［Ｎ・ｍ］）のトルク差に相当する分、第１車輪Ｗ１と第２車輪Ｗ２との合計駆動力を大きく確保することができる。   As a supplementary explanation, as an example, in a situation where the magnitude of the first input torque Ti1 is 200 [N · m], the difference between the first output torque To1 and the second output torque To2 is 160 [N · m]. Assume the case. In this case, in the configuration of the comparative example in which To1 = Ti1 and To2 = Ti2 unlike the vehicle drive device 1 according to the present embodiment, the difference between the first output torque To1 and the second output torque To2 is 160 [N ··· The magnitude of the second input torque Ti2 for setting m] is 40 [N · m]. Therefore, in the case of this comparative example, the sum of the first input torque Ti1 and the second input torque Ti2 (equal to the sum of the first output torque To1 and the second output torque To2) is 240 [N · m]. It becomes. On the other hand, in the vehicle drive device 1 according to the present embodiment, in a situation where the magnitude of the first input torque Ti1 is 200 [N · m], the first output torque To1 and the second output torque To2 The magnitude of the second input torque Ti2 for setting the difference to 160 [N · m] is the above equation when both the first gear ratio λ1 and the second gear ratio λ2 are “0.4”. From (1) and (2), it is 111 [N · m]. Therefore, in this case, the sum of the first input torque Ti1 and the second input torque Ti2 (the sum of the first output torque To1 and the second output torque To2) is 311 [N · m], and the above comparative example The total driving force of the first wheel W1 and the second wheel W2 corresponds to a torque difference of 71 [N · m] (= 311 [N · m] −240 [N · m]) compared to the case of Can be secured large.

次に、本実施形態の車両用駆動装置１におけるケース３の構成について説明する。ケース３は、シール部材４を介して接合される複数のケース部３０を備えている。ケース部３０のそれぞれは、ケース３の外面に露出する部分を有する。すなわち、ケース部３０同士の接合部は、ケース３の外面に露出するように形成される。なお、ケース部３０同士は、例えばボルトを用いて接合される。   Next, the configuration of the case 3 in the vehicle drive device 1 of the present embodiment will be described. The case 3 includes a plurality of case portions 30 joined via the seal member 4. Each of the case portions 30 has a portion exposed to the outer surface of the case 3. That is, the joint between the case portions 30 is formed to be exposed to the outer surface of the case 3. In addition, case part 30 comrades are joined, for example using a bolt.

図１に示すように、複数のケース部３０には、第１ケース部３１と第２ケース部３２とが含まれる。第１ケース部３１は、第２ケース部３２に対して軸方向第１側Ｌ１から接合されている。第１ケース部３１は、軸方向Ｌに延びる筒状に形成された第１周壁部３１ｃを備えており、軸方向Ｌ視で第１周壁部３１ｃにより囲まれた空間（第１収容空間Ｈ１）に、第１回転電機１１、第１駆動部材２１、第１連結部材５１、及び伝達装置２の一部（具体的には、第１入力部材７１、第１出力部材８１、及び第１遊星歯車機構６１）が配置されている。また、第２ケース部３２は、軸方向Ｌに延びる筒状に形成された第２周壁部３２ｃを備えており、軸方向Ｌ視で第２周壁部３２ｃにより囲まれた空間（第２収容空間Ｈ２）に、第２回転電機１２、第２駆動部材２２、第２連結部材５２、及び伝達装置２の一部（具体的には、第２入力部材７２、第２出力部材８２、及び第２遊星歯車機構６２）が配置されている。本実施形態では、第１収容空間Ｈ１と第２収容空間Ｈ２とは、後述する第５ケース部３５によって軸方向Ｌに区画されている。   As shown in FIG. 1, the plurality of case portions 30 include a first case portion 31 and a second case portion 32. The first case portion 31 is joined to the second case portion 32 from the first axial direction L1. The first case portion 31 includes a first peripheral wall 31c formed in a tubular shape extending in the axial direction L, and a space (first accommodation space H1) surrounded by the first peripheral wall 31c in the axial direction L view. The first rotary electric machine 11, the first drive member 21, the first connection member 51, and part of the transmission device 2 (specifically, the first input member 71, the first output member 81, and the first planetary gear A mechanism 61) is arranged. In addition, the second case portion 32 includes a second peripheral wall portion 32c formed in a tubular shape extending in the axial direction L, and a space surrounded by the second peripheral wall portion 32c in the axial direction L (a second accommodation space H2) the second rotary electric machine 12, the second drive member 22, the second connection member 52, and part of the transmission device 2 (specifically, the second input member 72, the second output member 82, and the second A planetary gear mechanism 62) is arranged. In the present embodiment, the first accommodation space H1 and the second accommodation space H2 are divided in the axial direction L by a fifth case portion 35 described later.

複数のケース部３０には、更に、第３ケース部３３と第４ケース部３４とが含まれる。第１収容空間Ｈ１における第１回転電機１１が配置される部分は、第１ケース部３１によって軸方向第１側Ｌ１を区画されずに開口部が形成されており、当該開口部を閉じるように第３ケース部３３が第１ケース部３１に対して軸方向第１側Ｌ１から接合されている。また、第２収容空間Ｈ２における第２回転電機１２が配置される部分は、第２ケース部３２によって軸方向第２側Ｌ２を区画されずに開口部が形成されており、当該開口部を閉じるように第４ケース部３４が第２ケース部３２に対して軸方向第２側Ｌ２から接合されている。   The plurality of case portions 30 further include a third case portion 33 and a fourth case portion 34. In a portion of the first accommodation space H1 where the first rotary electric machine 11 is disposed, an opening is formed without the first case portion 31 defining the first side L1 in the axial direction, and the opening is closed. The third case portion 33 is joined to the first case portion 31 from the axial first side L1. Further, in the portion of the second accommodation space H2 where the second rotary electric machine 12 is disposed, an opening is formed without the second case portion 32 defining the second side L2 in the axial direction, and the opening is closed. Thus, the fourth case portion 34 is joined to the second case portion 32 from the axial second side L2.

複数のケース部３０には、更に、第５ケース部３５が含まれる。第５ケース部３５は、ケース３の内部空間（第１回転電機１１、第２回転電機１２、第１連結部材５１、第２連結部材５２、及び伝達装置２を収容するための収容空間Ｈ）を軸方向Ｌに区画する中間壁として機能する。具体的には、第５ケース部３５は、径方向Ｒに延びる形状（例えば、板状）に形成されており、第１ケース部３１と第２ケース部３２との接合部３６が形成される軸方向Ｌの位置に配置されている。そして、第５ケース部３５は、第１ケース部３１（第１周壁部３１ｃ）と第２ケース部３２（第２周壁部３２ｃ）とにより軸方向Ｌの両側から挟まれた状態で、第１ケース部３１及び第２ケース部３２のそれぞれに接合されている。すなわち、本実施形態では、第１ケース部３１と第２ケース部３２とは、接合部３６において、第５ケース部３５を介して接合されている。よって、接合部３６には、第１ケース部３１と第５ケース部３５との接合部と、第２ケース部３２と第５ケース部３５との接合部とが形成されている。   The plurality of case portions 30 further include a fifth case portion 35. The fifth case portion 35 is an internal space of the case 3 (a housing space H for housing the first rotary electric machine 11, the second rotary electric machine 12, the first connection member 51, the second connection member 52, and the transmission device 2). Function as an intermediate wall that divides the in the axial direction L. Specifically, the fifth case portion 35 is formed in a shape (for example, a plate shape) extending in the radial direction R, and the joint portion 36 between the first case portion 31 and the second case portion 32 is formed It is disposed at a position in the axial direction L. Then, the fifth case portion 35 is configured such that the first case portion 31 (the first peripheral wall portion 31c) and the second case portion 32 (the second peripheral wall portion 32c) are sandwiched from both sides in the axial direction L. It is joined to each of the case portion 31 and the second case portion 32. That is, in the present embodiment, the first case portion 31 and the second case portion 32 are joined at the joining portion 36 via the fifth case portion 35. Thus, the joint portion 36 is formed with the joint portion of the first case portion 31 and the fifth case portion 35 and the joint portion of the second case portion 32 and the fifth case portion 35.

第１ケース部３１と第２ケース部３２との接合部３６における異なるケース部同士の接合面には、ケース３内の油のケース３外への漏れを防止するためのシール部材４が設けられている。すなわち、第１ケース部３１と第２ケース部３２とは、シール部材４を介して接合されている。ここで、「シール部材４を介して」とは、第１ケース部３１と第２ケース部３２との間に少なくともシール部材４が介在していることを意味し、シール部材４に加えてシール部材４以外の部材が介在している場合も含む概念である。上記のように、本実施形態では、第１ケース部３１と第２ケース部３２とは、接合部３６において、第５ケース部３５を介して接合されている。そして、接合部３６においては、第１ケース部３１と第５ケース部３５との接合面（第１接合面３６ａ）にシール部材４が設けられていると共に、第２ケース部３２と第５ケース部３５との接合面（第２接合面３６ｂ）にシール部材４が設けられている。すなわち、第１ケース部３１と第２ケース部３２とは、シール部材４を介して接合されるが、本実施形態では、第１ケース部３１と第２ケース部３２とは、第１接合面３６ａに設けられたシール部材４と、第２接合面３６ｂに設けられたシール部材４と、第５ケース部３５とを介して、接合されている。シール部材４として、例えば、液状ガスケットを用いることができる。なお、図１では、シール部材４を簡略化して太線で示している。   A seal member 4 for preventing leakage of the oil in the case 3 to the outside of the case 3 is provided on the joint surface of the different case parts in the joint portion 36 between the first case portion 31 and the second case portion 32. ing. That is, the first case portion 31 and the second case portion 32 are joined via the seal member 4. Here, "via the seal member 4" means that at least the seal member 4 is interposed between the first case portion 31 and the second case portion 32, and in addition to the seal member 4, the seal The concept also includes the case where a member other than the member 4 intervenes. As described above, in the present embodiment, the first case portion 31 and the second case portion 32 are joined at the joining portion 36 via the fifth case portion 35. In the joint portion 36, the seal member 4 is provided on the joint surface (first joint surface 36a) between the first case portion 31 and the fifth case portion 35, and the second case portion 32 and the fifth case 35 are provided. The seal member 4 is provided on the joint surface (second joint surface 36 b) with the portion 35. That is, although the first case portion 31 and the second case portion 32 are joined via the seal member 4, in the present embodiment, the first case portion 31 and the second case portion 32 have a first joint surface. They are joined via the seal member 4 provided at 36 a, the seal member 4 provided at the second joint surface 36 b, and the fifth case portion 35. For example, a liquid gasket can be used as the seal member 4. In FIG. 1, the seal member 4 is simplified and shown by a thick line.

次に、本実施形態の車両用駆動装置１における第１連結部材５１及び第２連結部材５２の支持構造について説明する。なお、以下の第１連結部材５１及び第２連結部材５２の支持構造の説明における径方向は、特に明記している場合を除き、第２軸Ａ２を基準とする径方向である。   Next, a support structure of the first connecting member 51 and the second connecting member 52 in the vehicle drive device 1 of the present embodiment will be described. In addition, the radial direction in the description of the support structure of the following 1st connection member 51 and the 2nd connection member 52 is a radial direction on the basis of 2nd axis | shaft A2, unless otherwise specified.

図１に示すように、車両用駆動装置１は、ケース３に固定される支持部材４０を備えている。支持部材４０は、ケース３の内部に配置される。そのため、支持部材４０とケース３との固定部（本実施形態では、後述する第１固定部３７ａ及び第２固定部３７ｂ）は、異なるケース部３０同士の接合部とは異なり、ケース３の外面には露出しない。本実施形態では、車両用駆動装置１は、ケース３の内部にそれぞれ配置された支持部材４０である第１支持部材４１及び第２支持部材４２を備えている。すなわち、車両用駆動装置１は、ケース３の内部に配置される第１支持部材４１と、ケース３の内部に配置される第２支持部材４２と、を備えている。第１支持部材４１は、第５ケース部３５に対して軸方向第１側Ｌ１に配置されて（すなわち、第１収容空間Ｈ１に配置されて）第１ケース部３１に固定されており、第１収容空間Ｈ１に配置される部材を支持するために用いられる。すなわち、第１支持部材４１は、複数のケース部３０の１つである第１ケース部３１の内部に固定されている。また、第２支持部材４２は、第５ケース部３５に対して軸方向第２側Ｌ２に配置されて（すなわち、第２収容空間Ｈ２に配置されて）第２ケース部３２に固定されており、第２収容空間Ｈ２に配置される部材を支持するために用いられる。すなわち、第２支持部材４２は、複数のケース部３０の１つであって第１ケース部３１とは異なる第２ケース部３２の内部に固定されている。第１支持部材４１や第２支持部材４２は、例えばボルトを用いてケース３に固定される。   As shown in FIG. 1, the vehicle drive device 1 includes a support member 40 fixed to the case 3. The support member 40 is disposed inside the case 3. Therefore, the fixing portion between the support member 40 and the case 3 (in the present embodiment, the first fixing portion 37a and the second fixing portion 37b described later) is different from the joint portion between different case portions 30. Not exposed to In the present embodiment, the vehicle drive device 1 includes a first support member 41 and a second support member 42 which are support members 40 disposed in the inside of the case 3 respectively. That is, the vehicle drive device 1 includes a first support member 41 disposed inside the case 3 and a second support member 42 disposed inside the case 3. The first support member 41 is disposed on the first side L1 in the axial direction with respect to the fifth case portion 35 (that is, disposed in the first accommodation space H1), and is fixed to the first case portion 31. It is used in order to support the component which is arranged in 1 accommodation space H1. That is, the first support member 41 is fixed inside the first case portion 31 which is one of the plurality of case portions 30. Further, the second support member 42 is disposed on the second direction L2 in the axial direction with respect to the fifth case portion 35 (that is, disposed in the second accommodation space H2) and fixed to the second case portion 32. , And is used to support members disposed in the second accommodation space H2. That is, the second support member 42 is fixed to the inside of the second case portion 32 which is one of the plurality of case portions 30 and different from the first case portion 31. The first support member 41 and the second support member 42 are fixed to the case 3 using, for example, bolts.

第１連結部材５１は、第１ケース部３１に形成された第１支持部３１ａと、第１支持部材４１（具体的には、第１支持部材４１に形成された第５支持部４１ａ）とにより、軸方向Ｌの２ヶ所で回転自在に支持されている。本実施形態では、第５支持部４１ａは、第１支持部３１ａよりも軸方向第２側Ｌ２に配置されている。   The first connection member 51 includes a first support portion 31a formed in the first case portion 31 and a first support member 41 (specifically, a fifth support portion 41a formed in the first support member 41). Thus, it is rotatably supported at two places in the axial direction L. In the present embodiment, the fifth support portion 41a is disposed on the second side L2 in the axial direction than the first support portion 31a.

第１連結部材５１は、第１支持部３１ａにより径方向外側から支持されている。具体的には、第１支持部３１ａの内周面と第１連結部材５１の外周面との間に第１軸受Ｂ１（ここでは、ラジアル型の玉軸受）が配置されており、第１連結部材５１は、第１軸受Ｂ１を介して第１支持部３１ａにより径方向外側から支持されている。また、第１連結部材５１は、第５支持部４１ａにより径方向内側から支持されている。具体的には、第５支持部４１ａの外周面と第１連結部材５１の内周面との間に第２軸受Ｂ２（ここでは、ラジアル型の玉軸受）が配置されており、第１連結部材５１は、第２軸受Ｂ２を介して第５支持部４１ａにより径方向内側から支持されている。第１従動ギヤ５１ａは、第１連結部材５１における、第２軸受Ｂ２よりも径方向外側であって径方向視で第２軸受Ｂ２と重複するように配置される部分の外周面に形成されている。すなわち、第２軸受Ｂ２は、径方向視で第１従動ギヤ５１ａと重複するように配置されている。   The first connection member 51 is supported by the first support portion 31 a from the outer side in the radial direction. Specifically, the first bearing B1 (here, a radial type ball bearing) is disposed between the inner peripheral surface of the first support portion 31a and the outer peripheral surface of the first connecting member 51, and the first connection is made. The member 51 is supported from outside in the radial direction by the first support portion 31a via the first bearing B1. Further, the first connection member 51 is supported from the inside in the radial direction by the fifth support portion 41a. Specifically, the second bearing B2 (here, a radial type ball bearing) is disposed between the outer peripheral surface of the fifth support portion 41a and the inner peripheral surface of the first connecting member 51, and the first connection is established. The member 51 is supported from the inside in the radial direction by the fifth support portion 41a via the second bearing B2. The first driven gear 51a is formed on the outer peripheral surface of a portion of the first connecting member 51 which is disposed radially outward of the second bearing B2 and overlaps the second bearing B2 in the radial direction. There is. That is, the second bearing B2 is disposed so as to overlap the first driven gear 51a in the radial direction.

第２連結部材５２は、第２ケース部３２に形成された第２支持部３２ａと、第２支持部材４２（具体的には、第２支持部材４２に形成された第６支持部４２ａ）とにより、軸方向Ｌの２ヶ所で回転自在に支持されている。本実施形態では、第６支持部４２ａは、第２支持部３２ａよりも軸方向第１側Ｌ１に配置されている。   The second connection member 52 includes a second support portion 32a formed in the second case portion 32, and a second support member 42 (specifically, a sixth support portion 42a formed in the second support member 42) Thus, it is rotatably supported at two places in the axial direction L. In the present embodiment, the sixth support portion 42a is disposed closer to the first axial side L1 than the second support portion 32a.

第２連結部材５２は、第２支持部３２ａにより径方向外側から支持されている。具体的には、第２支持部３２ａの内周面と第２連結部材５２の外周面との間に第４軸受Ｂ４（ここでは、ラジアル型の玉軸受）が配置されており、第２連結部材５２は、第４軸受Ｂ４を介して第２支持部３２ａにより径方向外側から支持されている。また、第２連結部材５２は、第６支持部４２ａにより径方向内側から支持されている。具体的には、第６支持部４２ａの外周面と第２連結部材５２の内周面との間に第３軸受Ｂ３（ここでは、ラジアル型の玉軸受）が配置されており、第２連結部材５２は、第３軸受Ｂ３を介して第６支持部４２ａにより径方向内側から支持されている。第２従動ギヤ５２ａは、第２連結部材５２における、第３軸受Ｂ３よりも径方向外側であって径方向視で第３軸受Ｂ３と重複するように配置される部分の外周面に形成されている。すなわち、第３軸受Ｂ３は、径方向視で第２従動ギヤ５２ａと重複するように配置されている。   The second connection member 52 is supported from the radially outer side by the second support portion 32a. Specifically, the fourth bearing B4 (here, a radial type ball bearing) is disposed between the inner peripheral surface of the second support portion 32a and the outer peripheral surface of the second connecting member 52, and the second connection is established. The member 52 is supported from outside in the radial direction by the second support portion 32a via the fourth bearing B4. Further, the second connection member 52 is supported from the inside in the radial direction by the sixth support portion 42a. Specifically, the third bearing B3 (here, a radial type ball bearing) is disposed between the outer peripheral surface of the sixth support portion 42a and the inner peripheral surface of the second connecting member 52, and the second connection is established. The member 52 is supported from the inside in the radial direction by the sixth support portion 42a via the third bearing B3. The second driven gear 52a is formed on the outer peripheral surface of a portion of the second connecting member 52 which is disposed radially outward of the third bearing B3 so as to overlap with the third bearing B3 in the radial direction. There is. That is, the third bearing B3 is disposed so as to overlap the second driven gear 52a in the radial direction.

以上のように、第１連結部材５１及び第２連結部材５２は、ケース３と支持部材４０とにより、軸方向Ｌの２ヶ所で回転自在に径方向に支持されている。よって、第１連結部材５１及び第２連結部材５２の双方を、軸方向Ｌの２ヶ所のそれぞれで非回転部材により支持することができ、第１連結部材５１及び第２連結部材５２のそれぞれを適切に支持することが可能となっている。その上で、上記のような第１連結部材５１及び第２連結部材５２の支持構造を採用することで、以下に述べるようにケース部３０間のシール性能を適切に維持することが可能となっている。   As described above, the first connection member 51 and the second connection member 52 are rotatably supported at two places in the axial direction L by the case 3 and the support member 40 in the radial direction. Therefore, both the first connecting member 51 and the second connecting member 52 can be supported by the non-rotating members at two locations in the axial direction L, respectively, and each of the first connecting member 51 and the second connecting member 52 can be It is possible to support appropriately. Furthermore, by adopting the support structure of the first connection member 51 and the second connection member 52 as described above, it becomes possible to appropriately maintain the sealing performance between the case portions 30 as described below. ing.

上述したように、第１支持部３１ａとは軸方向Ｌの異なる位置で第１連結部材５１を回転自在に支持する第１支持部材４１は、第１支持部３１ａが形成された第１ケース部３１の内部に固定されるため、１つのケース部３０とその内部に固定される支持部材４０とにより第１連結部材５１を支持することができる。このような構成とは異なり、シール部材４を介して接合される第１ケース部３１と他のケース部３０（例えば、第５ケース部３５）とにより第１連結部材５１を支持する場合には、第１従動ギヤ５１ａが第１出力ギヤ８１ａから受ける荷重（噛み合い力による荷重）に起因して、第１ケース部３１と当該他のケース部３０との接合部にこれら２つのケース部３０を互いに離間させる方向の力（離間力）が作用し得る。これに対して、この車両用駆動装置１では、１つのケース部３０（第１ケース部３１）とその内部に固定される支持部材４０（第１支持部材４１）とにより第１連結部材５１を支持することができる。そのため、ケース部３０間の接合部に上記のような離間力が作用することを抑制し、或いは、当該離間力の大きさを小さく抑えることができ、この結果、ケース部３０間のシール性能を適切に維持すること可能となっている。   As described above, the first support member 41 rotatably supporting the first connecting member 51 at a position different from the first support portion 31a in the axial direction L is the first case portion in which the first support portion 31a is formed. The first connection member 51 can be supported by one case portion 30 and the support member 40 fixed to the inside thereof because the case 31 is fixed to the inside of the housing 31. Unlike such a configuration, in the case of supporting the first connection member 51 by the first case portion 31 and the other case portion 30 (for example, the fifth case portion 35) joined via the seal member 4 Due to the load (load due to meshing force) that the first driven gear 51a receives from the first output gear 81a, these two case portions 30 are joined to the joint portion between the first case portion 31 and the other case portion 30. A force (separation force) in the direction of separating the two may act. On the other hand, in the vehicle drive device 1, the first connecting member 51 is formed by one case portion 30 (first case portion 31) and the support member 40 (first support member 41) fixed to the inside thereof. It can be supported. Therefore, it is possible to suppress the effect of the separation force as described above on the joint between the case portions 30 or to suppress the magnitude of the separation force to be small, and as a result, the sealing performance between the case portions 30 can be reduced. It is possible to maintain it properly.

同様に、この車両用駆動装置１では、１つのケース部３０（第２ケース部３２）とその内部に固定される支持部材４０（第２支持部材４２）とにより第２連結部材５２を支持することができる。そのため、第２従動ギヤ５２ａが第２出力ギヤ８２ａから受ける荷重（噛み合い力による荷重）に起因して、ケース部３０間の接合部に上記のような離間力が作用することを抑制し、或いは、当該離間力の大きさを小さく抑えることができ、この結果、ケース部３０間のシール性能を適切に維持することが可能となっている。なお、噛み合い力による荷重には、歯の圧力角に起因するラジアル荷重と、歯のねじれに起因するスラスト荷重とが含まれる。はすば歯車を用いる場合には、ラジアル荷重よりもスラスト荷重が支配的となる。   Similarly, in the vehicle drive device 1, the second connecting member 52 is supported by one case portion 30 (second case portion 32) and the support member 40 (second support member 42) fixed to the inside thereof. be able to. Therefore, due to the load (load due to meshing force) that the second driven gear 52a receives from the second output gear 82a, the above-described separation force is prevented from acting on the joint between the case portions 30, or The magnitude of the separation force can be reduced, and as a result, the sealing performance between the case portions 30 can be maintained properly. The load due to the meshing force includes a radial load due to the pressure angle of the teeth and a thrust load due to the twisting of the teeth. When a helical gear is used, the thrust load is more dominant than the radial load.

なお、第１従動ギヤ５１ａが第１出力ギヤ８１ａから受ける荷重に起因して、第１支持部材４１と第１ケース部３１との固定部（第１固定部３７ａ）に、第１支持部材４１と第１ケース部３１とを互いに離間させる方向の力が作用し得る。同様に、第２従動ギヤ５２ａが第２出力ギヤ８２ａから受ける荷重に起因して、第２支持部材４２と第２ケース部３２との固定部（第２固定部３７ｂ）に、第２支持部材４２と第２ケース部３２とを互いに離間させる方向の力が作用し得る。しかしながら、上述したように、第１固定部３７ａや第２固定部３７ｂは、異なるケース部３０同士の接合部とは異なり、ケース３の外面には露出しないため、第１固定部３７ａや第２固定部３７ｂに作用し得る上記のような力がケース部（３０）間のシール性能に与える影響は限定的である。   The first support member 41 is fixed to the fixing portion (first fixing portion 37a) of the first support member 41 and the first case portion 31 due to the load that the first driven gear 51a receives from the first output gear 81a. A force in the direction of separating the first case portion 31 and the first case portion 31 may act. Similarly, due to the load that the second driven gear 52a receives from the second output gear 82a, the second support member 42 is fixed to the fixing portion (second fixing portion 37b) of the second support member 42 and the second case portion 32. A force can be exerted to move the second case portion 32 and the second case portion 32 away from each other. However, as described above, since the first fixing portion 37 a and the second fixing portion 37 b are not exposed to the outer surface of the case 3 unlike the bonding portion between different case portions 30, the first fixing portion 37 a and the second fixing portion 37 b are different. The influence of the above-described force that can act on the fixing portion 37b on the sealing performance between the case portions (30) is limited.

上述したように、本実施形態では、第１連結部材５１が第１車輪Ｗ１と一体的に回転するように連結され、第２連結部材５２が第２車輪Ｗ２と一体的に回転するように連結される。そのため、第１連結部材５１が、第１車輪Ｗ１の駆動トルクと同等の比較的大きなトルク（減速された後の回転電機（１１，１２）のトルク）の伝達を担い、第２連結部材５２が、第２車輪Ｗ２の駆動トルクと同等の比較的大きなトルク（減速された後の回転電機（１１，１２）のトルク）の伝達を担う構成となり、第１従動ギヤ５１ａが第１出力ギヤ８１ａから受ける荷重や第２従動ギヤ５２ａが第２出力ギヤ８２ａから受ける荷重が大きくなりやすい。この点に関して、上記のように、この車両用駆動装置１では、第１従動ギヤ５１ａが第１出力ギヤ８１ａから受ける荷重がケース部３０間のシール性能に与える影響や、第２従動ギヤ５２ａが第２出力ギヤ８２ａから受ける荷重がケース部３０間のシール性能に与える影響を小さく抑えることができる。そのため、第１連結部材５１が第１車輪Ｗ１と一体的に回転するように連結され、第２連結部材５２が第２車輪Ｗ２と一体的に回転するように連結される構成においても、ケース部３０間のシール性能を適切に維持することが可能である。   As described above, in the present embodiment, the first connecting member 51 is connected to rotate integrally with the first wheel W1, and the second connecting member 52 is connected to rotate integrally with the second wheel W2. Be done. Therefore, the first connection member 51 carries transmission of a relatively large torque (torque of the rotating electrical machine (11, 12) after being decelerated) equivalent to the drive torque of the first wheel W1, and the second connection member 52 The transmission of a relatively large torque (the torque of the rotating electrical machine (11, 12) after being decelerated) equal to the driving torque of the second wheel W2 is configured to transmit the first driven gear 51a from the first output gear 81a. The load received and the load received by the second driven gear 52a from the second output gear 82a tend to be large. Regarding this point, as described above, in the vehicle drive device 1, the load that the first driven gear 51a receives from the first output gear 81a affects the seal performance between the case portions 30, and the second driven gear 52a The influence of the load received from the second output gear 82 a on the sealing performance between the case portions 30 can be reduced. Therefore, even in a configuration in which the first connecting member 51 is connected to rotate integrally with the first wheel W1, and the second connecting member 52 is connected to rotate integrally with the second wheel W2, the case portion is also provided. It is possible to properly maintain the sealing performance between 30.

次に、本実施形態の車両用駆動装置１における第１出力部材８１及び第２出力部材８２の支持構造について説明する。   Next, the support structure of the first output member 81 and the second output member 82 in the vehicle drive device 1 of the present embodiment will be described.

第１出力部材８１及び第２出力部材８２は、ケース３又は支持部材４０により回転自在に支持されている。具体的には、第１出力部材８１及び第２出力部材８２のそれぞれは、ケース３又は支持部材４０により、軸方向Ｌの２ヶ所で回転自在に支持されている。ここで、「ケース３又は支持部材４０により、軸方向Ｌの２ヶ所で回転自在に支持される」とは、軸方向Ｌの２ヶ所の双方でケース３により回転自在に支持されること、軸方向Ｌの２ヶ所の双方で支持部材４０により回転自在に支持されること、軸方向Ｌの１ヶ所でケース３により回転自在に支持され軸方向Ｌの別の１ヶ所で支持部材４０により回転自在に支持されることの、いずれをも含む概念である。   The first output member 81 and the second output member 82 are rotatably supported by the case 3 or the support member 40. Specifically, each of the first output member 81 and the second output member 82 is rotatably supported at two places in the axial direction L by the case 3 or the support member 40. Here, “the case 3 or the support member 40 rotatably supported at two places in the axial direction L” means that the case 3 is rotatably supported at both two places in the axial direction L, the shaft It is rotatably supported by the support member 40 at both of two locations in the direction L, rotatably supported by the case 3 at one location in the axial direction L, and rotatable by the support member 40 at another location in the axial direction L It is a concept that includes all of what is supported by

図１に示すように、本実施形態では、第１出力部材８１は、ケース３と第１支持部材４１とにより、軸方向Ｌの２ヶ所で回転自在に支持されている。具体的には、第１出力部材８１は、第１ケース部３１に形成された第３支持部３１ｂと、第１支持部材４１に形成された第７支持部４１ｂとにより、軸方向Ｌの２ヶ所で回転自在に支持されている。第７支持部４１ｂは、第３支持部３１ｂよりも軸方向第２側Ｌ２に配置されている。   As shown in FIG. 1, in the present embodiment, the first output member 81 is rotatably supported at two places in the axial direction L by the case 3 and the first support member 41. Specifically, the first output member 81 is formed by the third support portion 31 b formed in the first case portion 31 and the seventh support portion 41 b formed in the first support member 41. It is rotatably supported at a location. The seventh support portion 41 b is disposed on the second axial side L2 in the axial direction than the third support portion 31 b.

第１出力部材８１は、第３支持部３１ｂにより径方向Ｒの外側から支持されている。具体的には、第３支持部３１ｂの内周面と第１出力部材８１の外周面との間に第５軸受Ｂ５（ここでは、ラジアル型の円錐ころ軸受）が配置されており、第１出力部材８１は、第５軸受Ｂ５を介して第３支持部３１ｂにより径方向Ｒの外側から支持されている。また、第１出力部材８１は、第７支持部４１ｂにより径方向Ｒの外側から支持されている。具体的には、第７支持部４１ｂの内周面と第１出力部材８１の外周面との間に第６軸受Ｂ６（ここでは、ラジアル型の円錐ころ軸受）が配置されており、第１出力部材８１は、第６軸受Ｂ６を介して第７支持部４１ｂにより径方向Ｒの外側から支持されている。第１出力ギヤ８１ａは、第１出力部材８１における、軸方向Ｌにおける第５軸受Ｂ５と第６軸受Ｂ６との間に配置される部分の外周面に形成されている。   The first output member 81 is supported from the outer side in the radial direction R by the third support portion 31 b. Specifically, a fifth bearing B5 (here, a radial type conical roller bearing) is disposed between the inner peripheral surface of the third support portion 31b and the outer peripheral surface of the first output member 81. The output member 81 is supported from the outer side in the radial direction R by the third support portion 31 b via the fifth bearing B5. The first output member 81 is supported by the seventh support portion 41 b from the outside in the radial direction R. Specifically, a sixth bearing B6 (here, a radial type conical roller bearing) is disposed between the inner peripheral surface of the seventh support portion 41b and the outer peripheral surface of the first output member 81. The output member 81 is supported from the outer side in the radial direction R by the seventh support portion 41 b via the sixth bearing B6. The first output gear 81a is formed on the outer peripheral surface of a portion of the first output member 81, which is disposed between the fifth bearing B5 and the sixth bearing B6 in the axial direction L.

図１に示すように、本実施形態では、第２出力部材８２は、ケース３と第２支持部材４２とにより、軸方向Ｌの２ヶ所で回転自在に支持されている。具体的には、第２出力部材８２は、第２ケース部３２に形成された第４支持部３２ｂと、第２支持部材４２に形成された第８支持部４２ｂとにより、軸方向Ｌの２ヶ所で回転自在に支持されている。第８支持部４２ｂは、第４支持部３２ｂよりも軸方向第１側Ｌ１に配置されている。   As shown in FIG. 1, in the present embodiment, the second output member 82 is rotatably supported at two places in the axial direction L by the case 3 and the second support member 42. Specifically, the second output member 82 is provided in the axial direction L by the fourth support portion 32 b formed in the second case portion 32 and the eighth support portion 42 b formed in the second support member 42. It is rotatably supported at a location. The eighth support portion 42b is disposed closer to the first axial side L1 than the fourth support portion 32b.

第２出力部材８２は、第４支持部３２ｂにより径方向Ｒの外側から支持されている。具体的には、第４支持部３２ｂの内周面と第２出力部材８２の外周面との間に第８軸受Ｂ８（ここでは、ラジアル型の円錐ころ軸受）が配置されており、第２出力部材８２は、第８軸受Ｂ８を介して第４支持部３２ｂにより径方向Ｒの外側から支持されている。また、第２出力部材８２は、第８支持部４２ｂにより径方向Ｒの外側から支持されている。具体的には、第８支持部４２ｂの内周面と第２出力部材８２の外周面との間に第７軸受Ｂ７（ここでは、ラジアル型の円錐ころ軸受）が配置されており、第２出力部材８２は、第７軸受Ｂ７を介して第８支持部４２ｂにより径方向Ｒの外側から支持されている。第２出力ギヤ８２ａは、第２出力部材８２における、軸方向Ｌにおける第７軸受Ｂ７と第８軸受Ｂ８との間に配置される部分の外周面に形成されている。   The second output member 82 is supported from the outer side in the radial direction R by the fourth support portion 32 b. Specifically, an eighth bearing B8 (here, a radial type conical roller bearing) is disposed between the inner peripheral surface of the fourth support portion 32b and the outer peripheral surface of the second output member 82. The output member 82 is supported from the outer side in the radial direction R by the fourth support portion 32 b via the eighth bearing B8. The second output member 82 is supported by the eighth support portion 42 b from the outside in the radial direction R. Specifically, a seventh bearing B7 (here, a radial type tapered roller bearing) is disposed between the inner peripheral surface of the eighth support portion 42b and the outer peripheral surface of the second output member 82. The output member 82 is supported from the outside in the radial direction R by the eighth support portion 42 b via the seventh bearing B 7. The second output gear 82 a is formed on the outer peripheral surface of a portion of the second output member 82 disposed between the seventh bearing B 7 and the eighth bearing B 8 in the axial direction L.

以上のように、第１出力部材８１及び第２出力部材８２は、ケース３又は支持部材４０により、軸方向Ｌの２ヶ所で回転自在に径方向Ｒに支持されている。よって、第１出力部材８１及び第２出力部材８２の双方を、軸方向Ｌの２ヶ所のそれぞれで非回転部材により支持することができ、第１出力部材８１や第２出力部材８２が軸方向Ｌの１ヶ所でのみ非回転部材により支持される場合や、第１出力部材８１や第２出力部材８２が非回転部材により支持されない場合（すなわち、回転部材にのみ支持される場合）に比べて、第１出力部材８１や第２出力部材８２の支持剛性を高めることが可能となっている。すなわち、第１出力ギヤ８１ａが第１従動ギヤ５１ａから受ける荷重（噛み合い力による荷重）や第２出力ギヤ８２ａが第２従動ギヤ５２ａから受ける荷重（噛み合い力による荷重）を適切に支持することができるため、当該荷重が遊星歯車装置６０に与える影響を低減することで、遊星歯車装置６０に要求される剛性を確保することが容易となり、この結果、遊星歯車装置６０の小型化を図ることが可能となっている。   As described above, the first output member 81 and the second output member 82 are rotatably supported at two places in the axial direction L by the case 3 or the support member 40 in the radial direction R. Therefore, both the first output member 81 and the second output member 82 can be supported by the non-rotating members at each of two places in the axial direction L, and the first output member 81 and the second output member 82 are in the axial direction Compared with the case where the first output member 81 or the second output member 82 is not supported by the non-rotational member (that is, when it is supported by only the rotation member), The support rigidity of the first output member 81 and the second output member 82 can be enhanced. That is, the load (load by meshing force) that the first output gear 81a receives from the first driven gear 51a and the load (load by meshing force) that the second output gear 82a receives from the second driven gear 52a can be properly supported. Since it is possible to reduce the influence of the load on the planetary gear device 60, it is easy to ensure the rigidity required for the planetary gear device 60. As a result, the planetary gear device 60 can be miniaturized. It is possible.

具体的に説明すると、本実施形態では、図２及び図３に示すように、第１出力部材８１は第１キャリヤＣ１に連結されており、第２出力部材８２は第２キャリヤＣ２に連結されている。そのため、第１出力部材８１の支持剛性が十分でない場合には、第１出力ギヤ８１ａが第１従動ギヤ５１ａから受ける荷重に起因して第１出力部材８１から第１キャリヤＣ１に荷重が伝達されやすく、第１キャリヤＣ１に要求される剛性が高くなりやすい。また、第２出力部材８２の支持剛性が十分でない場合には、第２出力ギヤ８２ａが第２従動ギヤ５２ａから受ける荷重に起因して第２出力部材８２から第２キャリヤＣ２に荷重が伝達されやすく、第２キャリヤＣ２に要求される剛性が高くなりやすい。これに対して、本実施形態の車両用駆動装置１では、上記のように第１出力部材８１や第２出力部材８２の支持剛性を高めることができるため、第１出力ギヤ８１ａが受ける荷重に起因して第１出力部材８１から第１キャリヤＣ１に伝達される荷重を低減することや、第２出力ギヤ８２ａが受ける荷重に起因して第２出力部材８２から第２キャリヤＣ２に伝達される荷重を低減することができる。この結果、第１キャリヤＣ１や第２キャリヤＣ２に要求される剛性を確保することが容易となり、第１遊星歯車機構６１や第２遊星歯車機構６２の小型化を図ることが可能となっている。   Specifically, in the present embodiment, as shown in FIGS. 2 and 3, the first output member 81 is connected to the first carrier C1, and the second output member 82 is connected to the second carrier C2. ing. Therefore, when the support rigidity of the first output member 81 is not sufficient, the load is transmitted from the first output member 81 to the first carrier C1 due to the load that the first output gear 81a receives from the first driven gear 51a. The rigidity required for the first carrier C1 tends to be high. Further, when the support rigidity of the second output member 82 is not sufficient, the load is transmitted from the second output member 82 to the second carrier C2 due to the load that the second output gear 82a receives from the second driven gear 52a. And the rigidity required for the second carrier C2 tends to be high. On the other hand, in the vehicle drive device 1 of the present embodiment, since the support rigidity of the first output member 81 and the second output member 82 can be enhanced as described above, the load received by the first output gear 81a is As a result, the load transmitted from the first output member 81 to the first carrier C1 is reduced, and the load received by the second output gear 82a is transmitted from the second output member 82 to the second carrier C2. The load can be reduced. As a result, the rigidity required for the first carrier C1 and the second carrier C2 can be easily ensured, and the first planetary gear mechanism 61 and the second planetary gear mechanism 62 can be miniaturized. .

本実施形態では、更に、第１出力部材８１は、第１キャリヤＣ１に対して軸方向Ｌに相対移動可能に連結され、第２出力部材８２は、第２キャリヤＣ２に対して軸方向Ｌに相対移動可能に連結されている。具体的には、図２に示すように、第１キャリヤＣ１は、第１ピニオンギヤＰ１に対して軸方向第１側Ｌ１に配置されて第１ピニオンギヤＰ１を回転自在に支持する第１円環板状部６８ａを備えている。第１円環板状部６８ａは、第１３軸受Ｂ１３を介して第１ピニオンギヤＰ１を径方向Ｒの内側から支持する第１ピニオン軸６４ａの、軸方向第１側Ｌ１の端部を保持している。そして、円筒状の外周面を有して軸方向Ｌに延びるように形成された第１軸方向延在部６５ａが、第１円環板状部６８ａに対して軸方向第１側Ｌ１に突出するように第１円環板状部６８ａに連結されている。本実施形態では、第１軸方向延在部６５ａは、第１円環板状部６８ａと一体的に形成されている。第１出力部材８１は、軸方向Ｌに延びる円筒状に形成されており、第１軸方向延在部６５ａよりも径方向Ｒの外側であって径方向Ｒ視で第１軸方向延在部６５ａと重複するように配置されている。すなわち、本実施形態では、第１出力部材８１は、第１遊星歯車機構６１（第１遊星歯車機構６１の噛み合い部）に対して軸方向第１側Ｌ１に配置されている。そして、第１軸方向延在部６５ａと第１出力部材８１との周方向（第１軸Ａ１を基準とする周方向）の相対回転が規制され、軸方向Ｌの相対移動が許容されるように、第１軸方向延在部６５ａの外周面に形成された係合部と第１出力部材８１の内周面に形成された係合部とが、第３連結部６６ａにおいて係合（本実施形態では、スプライン係合）している。これにより、第１出力部材８１は、第１キャリヤＣ１に対して軸方向Ｌに相対移動可能に連結されている。   Further, in the present embodiment, the first output member 81 is connected so as to be movable relative to the first carrier C1 in the axial direction L, and the second output member 82 is connected in the axial direction L to the second carrier C2. Relatively movably linked. Specifically, as shown in FIG. 2, the first carrier C1 is disposed on the first axial side L1 with respect to the first pinion gear P1 to support the first pinion gear P1 rotatably. It has a portion 68a. The first annular plate portion 68a holds an end portion of the first pinion shaft 64a that supports the first pinion gear P1 from the inside in the radial direction R via the thirteenth bearing B13, on the first axial side L1. There is. Then, a first axially extending portion 65a having a cylindrical outer peripheral surface and formed to extend in the axial direction L projects on the first axial side L1 with respect to the first annular plate portion 68a. Is connected to the first annular plate 68a. In the present embodiment, the first axially extending portion 65a is integrally formed with the first annular plate portion 68a. The first output member 81 is formed in a cylindrical shape extending in the axial direction L, and is an outer side of the first axial extending portion 65 a in the radial direction R and the first axial extending portion in the radial direction R It is arranged to overlap with 65a. That is, in the present embodiment, the first output member 81 is disposed on the first axial side L1 with respect to the first planetary gear mechanism 61 (the meshing portion of the first planetary gear mechanism 61). Then, relative rotation of the first axially extending portion 65a and the first output member 81 in the circumferential direction (peripheral direction based on the first axis A1) is restricted, and relative movement in the axial direction L is permitted. In the third connecting portion 66a, the engaging portion formed on the outer peripheral surface of the first axially extending portion 65a and the engaging portion formed on the inner peripheral surface of the first output member 81 In the embodiment, spline engagement is performed. Thus, the first output member 81 is coupled to the first carrier C1 so as to be relatively movable in the axial direction L.

また、第２キャリヤＣ２は、第２ピニオンギヤＰ２に対して軸方向第２側Ｌ２に配置されて第２ピニオンギヤＰ２を回転自在に支持する第２円環板状部６８ｂを備えている。第２円環板状部６８ｂは、第１４軸受Ｂ１４を介して第２ピニオンギヤＰ２を径方向Ｒの内側から支持する第２ピニオン軸６４ｂの、軸方向第２側Ｌ２の端部を保持している。そして、円筒状の外周面を有して軸方向Ｌに延びるように形成された第２軸方向延在部６５ｂが、第２円環板状部６８ｂに対して軸方向第２側Ｌ２に突出するように第２円環板状部６８ｂに連結されている。本実施形態では、第２軸方向延在部６５ｂは、第２円環板状部６８ｂと一体的に形成されている。第２出力部材８２は、軸方向Ｌに延びる円筒状に形成されており、第２軸方向延在部６５ｂよりも径方向Ｒの外側であって径方向Ｒ視で第２軸方向延在部６５ｂと重複するように配置されている。すなわち、本実施形態では、第２出力部材８２は、第２遊星歯車機構６２（第２遊星歯車機構６２の噛み合い部）に対して軸方向第２側Ｌ２に配置されている。そして、第２軸方向延在部６５ｂと第２出力部材８２との周方向（第１軸Ａ１を基準とする周方向）の相対回転が規制され、軸方向Ｌの相対移動が許容されるように、第２軸方向延在部６５ｂの外周面に形成された係合部と第２出力部材８２の内周面に形成された係合部とが、第４連結部６６ｂにおいて係合（本実施形態では、スプライン係合）している。これにより、第２出力部材８２は、第２キャリヤＣ２に対して軸方向Ｌに相対移動可能に連結されている。   Further, the second carrier C2 is provided with a second annular plate portion 68b disposed on the second axial side L2 with respect to the second pinion gear P2 and rotatably supporting the second pinion gear P2. The second annular plate portion 68b holds an end portion of the second pinion shaft 64b, which supports the second pinion gear P2 from the inside in the radial direction R via the fourteenth bearing B14, on the second axial side L2. There is. A second axially extending portion 65b having a cylindrical outer peripheral surface and formed to extend in the axial direction L protrudes on the second side L2 in the axial direction with respect to the second annular plate portion 68b. Is connected to the second annular plate portion 68b. In the present embodiment, the second axially extending portion 65b is integrally formed with the second annular plate portion 68b. The second output member 82 is formed in a cylindrical shape extending in the axial direction L, and is the outer side of the second axial direction extending portion 65 b in the radial direction R and the second axial direction extending portion in the radial direction R It is arranged to overlap with 65b. That is, in the present embodiment, the second output member 82 is disposed on the second axial side L2 with respect to the second planetary gear mechanism 62 (the meshing portion of the second planetary gear mechanism 62). Then, relative rotation of the second axially extending portion 65b and the second output member 82 in the circumferential direction (peripheral direction based on the first axis A1) is restricted, and relative movement in the axial direction L is permitted. In the fourth connecting portion 66b, the engaging portion formed on the outer peripheral surface of the second axially extending portion 65b and the engaging portion formed on the inner peripheral surface of the second output member 82 In the embodiment, spline engagement is performed. Thus, the second output member 82 is coupled to the second carrier C2 so as to be relatively movable in the axial direction L.

このように、本実施形態では、第１出力部材８１は、第１キャリヤＣ１に対して軸方向Ｌに相対移動可能に連結され、第２出力部材８２は、第２キャリヤＣ２に対して軸方向Ｌに相対移動可能に連結されている。そのため、第１出力部材８１と第１キャリヤＣ１とが軸方向Ｌに相対移動不能な場合に比べて、第１出力部材８１と第１キャリヤＣ１との連結部（第３連結部６６ａ）における荷重の伝達を低減することができると共に、第２出力部材８２と第２キャリヤＣ２とが軸方向Ｌに相対移動不能な場合に比べて、第２出力部材８２と第２キャリヤＣ２との連結部（第４連結部６６ｂ）における荷重の伝達を低減することができる。この結果、第１出力ギヤ８１ａが第１従動ギヤ５１ａから噛み合い力による荷重を受けることに起因して第１出力部材８１から第１キャリヤＣ１に伝達される荷重の低減や、第２出力ギヤ８２ａが第２従動ギヤ５２ａから噛み合い力による荷重を受けることに起因して第２出力部材８２から第２キャリヤＣ２に伝達される荷重の低減を、より一層図ることが可能となっている。   Thus, in the present embodiment, the first output member 81 is movably coupled relative to the first carrier C1 in the axial direction L, and the second output member 82 is axially relative to the second carrier C2. Relatively movably connected to L. Therefore, compared with the case where the first output member 81 and the first carrier C1 can not move relative to each other in the axial direction L, the load at the connecting portion (third connecting portion 66a) between the first output member 81 and the first carrier C1 As compared with the case where the second output member 82 and the second carrier C2 can not move relative to each other in the axial direction L, the connection portion between the second output member 82 and the second carrier C2 can be reduced. The transmission of the load in the fourth connecting portion 66b) can be reduced. As a result, the load transmitted from the first output member 81 to the first carrier C1 due to the first output gear 81a receiving the load by the meshing force from the first driven gear 51a is reduced, and the second output gear 82a It is possible to further reduce the load transmitted from the second output member 82 to the second carrier C2 due to receiving the load by the meshing force from the second driven gear 52a.

ところで、上述したように、第１出力部材８１は、第６軸受Ｂ６を介して回転自在に支持され、第２出力部材８２は、第７軸受Ｂ７を介して回転自在に支持されている。そして、以下に述べるように、本実施形態では、第１キャリヤＣ１に、第１３軸受Ｂ１３に油を供給するための第１油路９１と、第６軸受Ｂ６に油を供給するための第２油路９２とが形成され、第２キャリヤＣ２に、第１４軸受Ｂ１４に油を供給するための第３油路９３と、第７軸受Ｂ７に油を供給するための第４油路９４とが形成されている。   As described above, the first output member 81 is rotatably supported via the sixth bearing B6, and the second output member 82 is rotatably supported via the seventh bearing B7. As described below, in the present embodiment, the first oil passage 91 for supplying oil to the first bearing C13 and the second oil passage for supplying oil to the sixth bearing B6 in the present embodiment. An oil passage 92 is formed, and a third oil passage 93 for supplying oil to the fourteenth bearing B14 in the second carrier C2, and a fourth oil passage 94 for supplying oil to the seventh bearing B7 are formed. It is formed.

図２に示すように、本実施形態では、第１油路９１及び第２油路９２が、第１円環板状部６８ａに形成されている。第１油路９１は、径方向Ｒに延びるように形成されており、第１油路９１における径方向Ｒの外側の端部は、第１ピニオン軸６４ａに形成された第１３軸受Ｂ１３に油を供給するため油路に接続されている。これにより、第１油路９１に供給された油を第１３軸受Ｂ１３に供給して、第１３軸受Ｂ１３を潤滑することができる。第２油路９２は、径方向Ｒに延びるように形成されており、第２油路９２における径方向Ｒの外側の端部は、第１円環板状部６８ａにおける第６軸受Ｂ６に対して軸方向第２側Ｌ２に隣接する部分において開口している。これにより、第２油路９２に供給された油を第６軸受Ｂ６に供給して、第６軸受Ｂ６を潤滑することができる。   As shown in FIG. 2, in the present embodiment, the first oil passage 91 and the second oil passage 92 are formed in the first annular plate portion 68 a. The first oil passage 91 is formed to extend in the radial direction R, and the outer end of the first oil passage 91 in the radial direction R is oiled to a thirteenth bearing B13 formed on the first pinion shaft 64a. It is connected to the oil passage to supply Thus, the oil supplied to the first oil passage 91 can be supplied to the thirteenth bearing B13 to lubricate the thirteenth bearing B13. The second oil passage 92 is formed to extend in the radial direction R, and the outer end of the second oil passage 92 in the radial direction R is to the sixth bearing B6 in the first annular plate portion 68a. It is open at a portion adjacent to the axial second side L2. Thus, the oil supplied to the second oil passage 92 can be supplied to the sixth bearing B6 to lubricate the sixth bearing B6.

また、本実施形態では、第３油路９３及び第４油路９４が、第２円環板状部６８ｂに形成されている。第３油路９３は、径方向Ｒに延びるように形成されており、第３油路９３における径方向Ｒの外側の端部は、第２ピニオン軸６４ｂに形成された第１４軸受Ｂ１４に油を供給するため油路に接続されている。これにより、第３油路９３に供給された油を第１４軸受Ｂ１４に供給して、第１４軸受Ｂ１４を潤滑することができる。第４油路９４は、径方向Ｒに延びるように形成されており、第４油路９４における径方向Ｒの外側の端部は、第２円環板状部６８ｂにおける第７軸受Ｂ７に対して軸方向第１側Ｌ１に隣接する部分において開口している。これにより、第４油路９４に供給された油を第７軸受Ｂ７に供給して、第７軸受Ｂ７を潤滑することができる。   Further, in the present embodiment, the third oil passage 93 and the fourth oil passage 94 are formed in the second annular plate portion 68 b. The third oil passage 93 is formed to extend in the radial direction R, and the outer end of the third oil passage 93 in the radial direction R is oiled to the fourteenth bearing B14 formed in the second pinion shaft 64b. It is connected to the oil passage to supply Thus, the oil supplied to the third oil passage 93 can be supplied to the fourteenth bearing B14 to lubricate the fourteenth bearing B14. The fourth oil passage 94 is formed to extend in the radial direction R, and the end on the outer side in the radial direction R in the fourth oil passage 94 is for the seventh bearing B7 in the second annular plate portion 68b. It is open at a portion adjacent to the axial first side L1. Thus, the oil supplied to the fourth oil passage 94 can be supplied to the seventh bearing B7 to lubricate the seventh bearing B7.

図２に簡略化して示すように、車両用駆動装置１は油圧源５を備えており、油圧源５から吐出された油が、第１油路９１、第２油路９２、第３油路９３、及び第４油路９４のそれぞれに供給されるように構成されている。なお、油圧源５は、例えば、電動モータで駆動される電動オイルポンプ、又は、回転電機（１１，１２）と車輪（Ｗ１，Ｗ２）との間の動力伝達経路を伝わる動力によって駆動される機械式オイルポンプとすることができる。図２に示すように、第１サンギヤＳ１及び第２サンギヤＳ２よりも径方向Ｒの内側には、軸方向Ｌに延びるように形成された第３軸方向延在部６５ｃが配置されており、第３軸方向延在部６５ｃは、第２円環板状部６８ｂから軸方向第１側Ｌ１に突出するように第２円環板状部６８ｂに連結されている。本実施形態では、第３軸方向延在部６５ｃは、第２円環板状部６８ｂ及び第２軸方向延在部６５ｂと一体的に形成されている。そして、第２軸方向延在部６５ｂの径方向Ｒの中心部、第２円環板状部６８ｂの径方向Ｒの中心部、及び第３軸方向延在部６５ｃの径方向Ｒの中心部を、軸方向Ｌに連続して延びるように、軸内油路９５が形成されている。油圧源５から吐出された油は、この軸内油路９５を経由して、上述した各油路（９１〜９４）に供給される。   As simplified and shown in FIG. 2, the vehicle drive device 1 includes the hydraulic pressure source 5, and the oil discharged from the hydraulic pressure source 5 is a first oil passage 91, a second oil passage 92, and a third oil passage. It is configured to be supplied to each of 93 and the fourth oil passage 94. The hydraulic pressure source 5 is, for example, an electric oil pump driven by an electric motor or a machine driven by power transmitted through a power transmission path between the rotating electric machines (11, 12) and the wheels (W1, W2). It can be an oil pump. As shown in FIG. 2, a third axially extending portion 65 c formed to extend in the axial direction L is disposed on the inner side of the first sun gear S 1 and the second sun gear S 2 in the radial direction R, The third axially extending portion 65c is connected to the second annular plate portion 68b so as to protrude from the second annular plate portion 68b to the first axial side L1. In the present embodiment, the third axially extending portion 65c is integrally formed with the second annular plate portion 68b and the second axially extending portion 65b. The central portion in the radial direction R of the second axially extending portion 65b, the central portion in the radial direction R of the second annular plate portion 68b, and the central portion in the radial direction R of the third axially extending portion 65c. The in-shaft oil passage 95 is formed to extend continuously in the axial direction L. The oil discharged from the hydraulic pressure source 5 is supplied to the aforementioned oil passages (91 to 94) via the in-shaft oil passage 95.

具体的には、第３軸方向延在部６５ｃにおける軸方向第１側Ｌ１の端部は、第１円環板状部６８ａの径方向Ｒの中心部に形成された孔部６９に挿入されており、第３軸方向延在部６５ｃにおける孔部６９に挿入された部分に、第３軸方向延在部６５ｃの内周面（軸内油路９５の径方向Ｒの外側を区画する面）と外周面とを連通する油孔９６が形成されている。また、第１油路９１及び第２油路９２のそれぞれは、孔部６９の内周面に開口するように形成されている。これにより、油圧源５から軸内油路９５に供給された油は、遠心力等の作用により、油孔９６を経由して第１油路９１や第２油路９２に供給される。このように、第１油路９１及び第２油路９２の双方を第１キャリヤＣ１（ここでは、第１円環板状部６８ａ）に形成することで、第１油路９１及び第２油路９２に対する油の供給構造を共通化して、油路構成の簡素化を図ることが可能となっている。   Specifically, the end of the first axial side L1 of the third axially extending portion 65c is inserted into the hole 69 formed in the central portion of the first annular plate portion 68a in the radial direction R. The inner peripheral surface of the third axially extending portion 65c (a surface that divides the outer side of the in-shaft oil passage 95 in the radial direction R into the third axially extending portion 65c inserted into the hole 69) An oil hole 96 is formed to communicate the above and the outer peripheral surface. Further, each of the first oil passage 91 and the second oil passage 92 is formed to open at the inner peripheral surface of the hole 69. Thus, the oil supplied from the hydraulic pressure source 5 to the in-shaft oil passage 95 is supplied to the first oil passage 91 and the second oil passage 92 via the oil hole 96 by the action of the centrifugal force and the like. Thus, by forming both the first oil passage 91 and the second oil passage 92 in the first carrier C1 (here, the first annular plate portion 68a), the first oil passage 91 and the second oil can be obtained. It is possible to simplify the oil passage configuration by making the oil supply structure to the passage 92 common.

なお、第１油路９１及び第２油路９２は共に第１円環板状部６８ａに形成されるため、第１油路９１と第２油路９２とは、軸方向Ｌの位置及び周方向（第１軸Ａ１を基準とする周方向）の位置の少なくとも一方を互いにずらして形成すると好適である。図２に示すように、本実施形態では、第１油路９１を、径方向Ｒに平行に延びるように形成し、第２油路９２を、径方向Ｒに対して傾斜した方向（径方向Ｒの外側に向かうに従って軸方向第１側Ｌ１に向かう方向）に延びるように形成することで、第１油路９１と第２油路９２との間で軸方向Ｌの位置を互いにずらしている。図２に示す例では、第１油路９１と第２油路９２とは、軸方向Ｌの互いに同じ位置に配置される部分を一部にも有さないように、軸方向Ｌの位置が互いにずれている。また、本実施形態では、第１油路９１と第２油路９２とは、周方向（第１軸Ａ１を基準とする周方向）の位置を互いにずらして形成されているが、図２では、便宜上、第１油路９１と第２油路９２との双方を同じ断面に示している。   In addition, since the first oil passage 91 and the second oil passage 92 are both formed in the first annular plate portion 68a, the first oil passage 91 and the second oil passage 92 have a position and a circumference in the axial direction L. It is preferable that at least one of the positions in the direction (the circumferential direction with respect to the first axis A1) be offset from each other. As shown in FIG. 2, in the present embodiment, the first oil passage 91 is formed to extend in parallel to the radial direction R, and the second oil passage 92 is inclined with respect to the radial direction R (radial direction The positions in the axial direction L are mutually shifted between the first oil passage 91 and the second oil passage 92 by forming so as to extend in the direction toward the first axial direction L1 toward the outer side of R). . In the example shown in FIG. 2, the first oil passage 91 and the second oil passage 92 have a position in the axial direction L such that a portion disposed at the same position in the axial direction L is not partially included. They are offset from each other. Further, in the present embodiment, the first oil passage 91 and the second oil passage 92 are formed so as to be offset from each other in the circumferential direction (the circumferential direction with respect to the first axis A1). For convenience, both the first oil passage 91 and the second oil passage 92 are shown in the same cross section.

また、第３油路９３及び第４油路９４のそれぞれは、第２円環板状部６８ｂの内周面（軸内油路９５の径方向Ｒの外側を区画する面）に開口するように形成されている。よって、油圧源５から軸内油路９５に供給された油は、遠心力等の作用により、第３油路９３や第４油路９４に供給される。このように、第３油路９３及び第４油路９４の双方を第２キャリヤＣ２（ここでは、第２円環板状部６８ｂ）に形成することで、第３油路９３及び第４油路９４に対する油の供給構造を共通化して、油路構成の簡素化を図ることが可能となっている。   Further, each of the third oil passage 93 and the fourth oil passage 94 is opened to the inner peripheral surface of the second annular plate portion 68 b (the surface which divides the outer side of the in-shaft oil passage 95 in the radial direction R). Is formed. Therefore, the oil supplied from the hydraulic pressure source 5 to the in-shaft oil passage 95 is supplied to the third oil passage 93 and the fourth oil passage 94 by the action of the centrifugal force and the like. Thus, by forming both the third oil passage 93 and the fourth oil passage 94 in the second carrier C2 (here, the second annular plate portion 68b), the third oil passage 93 and the fourth oil are formed. It is possible to simplify the oil passage configuration by making the oil supply structure to the passage 94 common.

なお、第３油路９３及び第４油路９４は共に第２円環板状部６８ｂに形成されるため、第３油路９３と第４油路９４とは、軸方向Ｌの位置及び周方向（第１軸Ａ１を基準とする周方向）の位置の少なくとも一方を互いにずらして形成すると好適である。図２に示すように、本実施形態では、第３油路９３を、径方向Ｒに平行に延びるように形成し、第４油路９４を、径方向Ｒに対して傾斜した方向（径方向Ｒの外側に向かうに従って軸方向第２側Ｌ２に向かう方向）に延びるように形成することで、第３油路９３と第４油路９４との間で軸方向Ｌの位置を互いにずらしている。図２に示す例では、第３油路９３と第４油路９４とは、軸方向Ｌの同じ位置において第２円環板状部６８ｂの内周面に開口している。すなわち、第３油路９３と第４油路９４とは、軸方向Ｌの互いに同じ位置に配置される部分を一部有しつつ、軸方向Ｌの位置が互いにずれている。また、本実施形態では、第３油路９３と第４油路９４とは、周方向（第１軸Ａ１を基準とする周方向）の位置を互いにずらして形成されているが、図２では、便宜上、第３油路９３と第４油路９４との双方を同じ断面に示している。   In addition, since the third oil passage 93 and the fourth oil passage 94 are both formed in the second annular plate portion 68b, the third oil passage 93 and the fourth oil passage 94 have a position and a circumference in the axial direction L. It is preferable that at least one of the positions in the direction (the circumferential direction with respect to the first axis A1) be offset from each other. As shown in FIG. 2, in the present embodiment, the third oil passage 93 is formed to extend in parallel to the radial direction R, and the fourth oil passage 94 is inclined with respect to the radial direction R (radial direction The position in the axial direction L is mutually shifted between the third oil passage 93 and the fourth oil passage 94 by forming so as to extend in the direction toward the second axial direction L2 toward the outer side of R). . In the example shown in FIG. 2, the third oil passage 93 and the fourth oil passage 94 open at the same position in the axial direction L on the inner circumferential surface of the second annular plate portion 68 b. That is, while the third oil passage 93 and the fourth oil passage 94 partially include portions disposed at the same position in the axial direction L, the positions in the axial direction L are shifted from each other. Further, in the present embodiment, the third oil passage 93 and the fourth oil passage 94 are formed so as to be offset from each other in the circumferential direction (the circumferential direction with respect to the first axis A1). For convenience, both the third oil passage 93 and the fourth oil passage 94 are shown in the same cross section.

次に、本実施形態の車両用駆動装置１における第１入力部材７１及び第２入力部材７２の支持構造について説明する。   Next, the support structure of the first input member 71 and the second input member 72 in the vehicle drive device 1 of the present embodiment will be described.

第１入力部材７１及び第２入力部材７２は、ケース３又は支持部材４０により回転自在に支持されている。具体的には、第１入力部材７１及び第２入力部材７２のそれぞれは、ケース３又は支持部材４０により、軸方向Ｌの２ヶ所で回転自在に支持されている。   The first input member 71 and the second input member 72 are rotatably supported by the case 3 or the support member 40. Specifically, each of the first input member 71 and the second input member 72 is rotatably supported at two places in the axial direction L by the case 3 or the support member 40.

図２に示すように、本実施形態では、第１入力部材７１は、ケース３と第１支持部材４１とにより、軸方向Ｌの２ヶ所で回転自在に支持されている。具体的には、第１入力部材７１は、第５ケース部３５に形成された第１３支持部３５ａと、第１支持部材４１に形成された第９支持部４１ｃとにより、軸方向Ｌの２ヶ所で回転自在に支持されている。第９支持部４１ｃは、第１３支持部３５ａよりも軸方向第１側Ｌ１に配置されている。   As shown in FIG. 2, in the present embodiment, the first input member 71 is rotatably supported at two places in the axial direction L by the case 3 and the first support member 41. Specifically, the first input member 71 is formed by the thirteenth supporting portion 35 a formed in the fifth case portion 35 and the ninth supporting portion 41 c formed in the first supporting member 41. It is rotatably supported at a location. The ninth support portion 41c is disposed closer to the first axial side L1 than the thirteenth support portion 35a.

第１入力部材７１は、第１３支持部３５ａにより径方向Ｒの外側から支持されている。具体的には、第１３支持部３５ａの内周面と第１入力部材７１の外周面との間に第１０軸受Ｂ１０（ここでは、ラジアル型の玉軸受）が配置されており、第１入力部材７１は、第１０軸受Ｂ１０を介して第１３支持部３５ａにより径方向Ｒの外側から支持されている。本実施形態では、第１入力部材７１は、第１リングギヤＲ１を備えている。そして、第１リングギヤＲ１は、第１入力部材７１における、第１０軸受Ｂ１０よりも径方向Ｒの内側であって径方向Ｒ視で第１０軸受Ｂ１０と重複するように配置される部分の内周面に形成されている。すなわち、第１０軸受Ｂ１０は、径方向Ｒ視で第１リングギヤＲ１と重複するように配置されている。また、第１入力部材７１は、第９支持部４１ｃにより径方向Ｒの内側から支持されている。具体的には、第９支持部４１ｃの外周面と第１入力部材７１の内周面との間に第９軸受Ｂ９（ここでは、ラジアル型の玉軸受）が配置されており、第１入力部材７１は、第９軸受Ｂ９を介して第９支持部４１ｃにより径方向Ｒの内側から支持されている。第１入力ギヤ７１ａは、第１入力部材７１における、第９軸受Ｂ９よりも径方向Ｒの外側であって径方向Ｒ視で第９軸受Ｂ９と重複するように配置される部分の外周面に形成されている。すなわち、第９軸受Ｂ９は、径方向Ｒ視で第１入力ギヤ７１ａと重複するように配置されている。また、第９軸受Ｂ９は、径方向Ｒ視で第６軸受Ｂ６と重複するように配置されている。   The first input member 71 is supported from the outside in the radial direction R by the thirteenth support portion 35 a. Specifically, the tenth bearing B10 (here, a radial type ball bearing) is disposed between the inner peripheral surface of the thirteenth support portion 35a and the outer peripheral surface of the first input member 71, and the first input The member 71 is supported from the outside in the radial direction R by the thirteenth support portion 35a via the tenth bearing B10. In the present embodiment, the first input member 71 includes the first ring gear R1. The first ring gear R1 is an inner periphery of a portion of the first input member 71 which is disposed inward of the tenth bearing B10 in the radial direction R and overlaps the tenth bearing B10 in the radial direction R view. It is formed on the surface. That is, the tenth bearing B10 is disposed so as to overlap with the first ring gear R1 in the radial direction R. The first input member 71 is supported by the ninth support portion 41 c from the inside in the radial direction R. Specifically, a ninth bearing B9 (here, a radial type ball bearing) is disposed between the outer peripheral surface of the ninth support portion 41c and the inner peripheral surface of the first input member 71. The member 71 is supported from the inside in the radial direction R by the ninth support portion 41c via the ninth bearing B9. The first input gear 71a is on the outer peripheral surface of a portion of the first input member 71 that is located outside the ninth bearing B9 in the radial direction R and that overlaps the ninth bearing B9 in the radial direction R view. It is formed. That is, the ninth bearing B9 is disposed so as to overlap the first input gear 71a in the radial direction R. The ninth bearing B9 is disposed to overlap the sixth bearing B6 in the radial direction R.

図２に示すように、本実施形態では、第２入力部材７２は、ケース３と第２支持部材４２とにより、軸方向Ｌの２ヶ所で回転自在に支持されている。具体的には、第２入力部材７２は、第５ケース部３５に形成された第１４支持部３５ｂと、第２支持部材４２に形成された第１０支持部４２ｃとにより、軸方向Ｌの２ヶ所で回転自在に支持されている。第１０支持部４２ｃは、第１４支持部３５ｂよりも軸方向第２側Ｌ２に配置されている。   As shown in FIG. 2, in the present embodiment, the second input member 72 is rotatably supported at two places in the axial direction L by the case 3 and the second support member 42. Specifically, the second input member 72 is formed by a fourteenth supporting portion 35 b formed in the fifth case portion 35 and a tenth supporting portion 42 c formed in the second supporting member 42. It is rotatably supported at a location. The tenth support portion 42c is disposed closer to the second axial side L2 than the fourteenth support portion 35b.

第２入力部材７２は、第１４支持部３５ｂにより径方向Ｒの外側から支持されている。具体的には、第１４支持部３５ｂの内周面と第２入力部材７２の外周面との間に第１１軸受Ｂ１１（ここでは、ラジアル型の玉軸受）が配置されており、第２入力部材７２は、第１１軸受Ｂ１１を介して第１４支持部３５ｂにより径方向Ｒの外側から支持されている。本実施形態では、第２入力部材７２は、第２リングギヤＲ２を備えている。そして、第２リングギヤＲ２は、第２入力部材７２における、第１１軸受Ｂ１１よりも径方向Ｒの内側であって径方向Ｒ視で第１１軸受Ｂ１１と重複するように配置される部分の内周面に形成されている。すなわち、第１１軸受Ｂ１１は、径方向Ｒ視で第２リングギヤＲ２と重複するように配置されている。また、第２入力部材７２は、第１０支持部４２ｃにより径方向Ｒの内側から支持されている。具体的には、第１０支持部４２ｃの外周面と第２入力部材７２の内周面との間に第１２軸受Ｂ１２（ここでは、ラジアル型の玉軸受）が配置されており、第２入力部材７２は、第１２軸受Ｂ１２を介して第１０支持部４２ｃにより径方向Ｒの内側から支持されている。第２入力ギヤ７２ａは、第２入力部材７２における、第１２軸受Ｂ１２よりも径方向Ｒの外側であって径方向Ｒ視で第１２軸受Ｂ１２と重複するように配置される部分の外周面に形成されている。すなわち、第１２軸受Ｂ１２は、径方向Ｒ視で第２入力ギヤ７２ａと重複するように配置されている。また、第１２軸受Ｂ１２は、径方向Ｒ視で第７軸受Ｂ７と重複するように配置されている。   The second input member 72 is supported from the outside in the radial direction R by the fourteenth support portion 35 b. Specifically, an eleventh bearing B11 (here, a radial type ball bearing) is disposed between the inner peripheral surface of the fourteenth support portion 35b and the outer peripheral surface of the second input member 72. The member 72 is supported from the outside in the radial direction R by the fourteenth support portion 35 b via the eleventh bearing B11. In the present embodiment, the second input member 72 includes the second ring gear R2. The second ring gear R2 is an inner periphery of a portion of the second input member 72 which is disposed inward of the eleventh bearing B11 in the radial direction R and overlaps the eleventh bearing B11 in the radial direction R. It is formed on the surface. That is, the eleventh bearing B11 is arranged to overlap the second ring gear R2 in the radial direction R. The second input member 72 is supported by the tenth support portion 42c from the inside in the radial direction R. Specifically, a twelfth bearing B12 (here, a radial type ball bearing) is disposed between the outer peripheral surface of the tenth support portion 42c and the inner peripheral surface of the second input member 72. The member 72 is supported from the inside in the radial direction R by a tenth support portion 42c via a twelfth bearing B12. The second input gear 72a is on the outer peripheral surface of a portion of the second input member 72 which is located outside the twelfth bearing B12 in the radial direction R and which overlaps the twelfth bearing B12 in the radial direction R view. It is formed. That is, the twelfth bearing B12 is disposed so as to overlap with the second input gear 72a in the radial direction R. The twelfth bearing B12 is disposed to overlap with the seventh bearing B7 in the radial direction R view.

以上のように、第１入力部材７１及び第２入力部材７２は、ケース３又は支持部材４０により、軸方向Ｌの２ヶ所で回転自在に径方向Ｒに支持されている。よって、第１入力部材７１及び第２入力部材７２の双方を、軸方向Ｌの２ヶ所のそれぞれで非回転部材により支持することができ、第１入力部材７１や第２入力部材７２が軸方向Ｌの１ヶ所でのみ非回転部材により支持される場合や、第１入力部材７１や第２入力部材７２が非回転部材により支持されない場合（すなわち、回転部材にのみ支持される場合）に比べて、第１入力部材７１や第２入力部材７２の支持剛性を高めることが可能となっている。すなわち、第１入力ギヤ７１ａが第１駆動ギヤ２１ａから受ける荷重（噛み合い力による荷重）や第２入力ギヤ７２ａが第２駆動ギヤ２２ａから受ける荷重（噛み合い力による荷重）を適切に支持することができるため、当該荷重が遊星歯車装置６０に与える影響を低減することで、遊星歯車装置６０に要求される剛性を確保することが容易となり、この結果、遊星歯車装置６０の小型化を図ることが可能となっている。   As described above, the first input member 71 and the second input member 72 are rotatably supported at two places in the axial direction L by the case 3 or the support member 40 in the radial direction R. Therefore, both the first input member 71 and the second input member 72 can be supported by the non-rotating members at each of two places in the axial direction L, and the first input member 71 and the second input member 72 are in the axial direction Compared with the case where the first input member 71 or the second input member 72 is not supported by the non-rotational member (that is, when the first input member 71 or the second input member 72 is supported only by the rotation member) The support rigidity of the first input member 71 and the second input member 72 can be enhanced. That is, properly supporting the load received by the first input gear 71a from the first drive gear 21a (load by meshing force) and the load received by the second input gear 72a from the second drive gear 22a (load by meshing force). Since it is possible to reduce the influence of the load on the planetary gear device 60, it is easy to ensure the rigidity required for the planetary gear device 60. As a result, the planetary gear device 60 can be miniaturized. It is possible.

具体的に説明すると、本実施形態では、図２及び図３に示すように、第１入力部材７１は第１リングギヤＲ１を備えており、第２入力部材７２は第２リングギヤＲ２を備えている。そのため、第１入力部材７１の支持剛性が十分でない場合には、第１入力ギヤ７１ａが第１駆動ギヤ２１ａから受ける荷重に起因して第１入力部材７１から第１リングギヤＲ１を介して第１キャリヤＣ１に荷重が伝達されやすく、第１キャリヤＣ１に要求される剛性が高くなりやすい。また、第２入力部材７２の支持剛性が十分でない場合には、第２入力ギヤ７２ａが第２駆動ギヤ２２ａから受ける荷重に起因して第２入力部材７２から第２リングギヤＲ２を介して第２キャリヤＣ２に荷重が伝達されやすく、第２キャリヤＣ２に要求される剛性が高くなりやすい。これに対して、本実施形態の車両用駆動装置１では、上記のように第１入力部材７１や第２入力部材７２の支持剛性を高めることができるため、第１入力ギヤ７１ａが受ける荷重に起因して第１入力部材７１から第１キャリヤＣ１に伝達される荷重を低減することや、第２入力ギヤ７２ａが受ける荷重に起因して第２入力部材７２から第２キャリヤＣ２に伝達される荷重を低減することができる。この結果、第１キャリヤＣ１や第２キャリヤＣ２に要求される剛性を確保することが容易となり、第１遊星歯車機構６１や第２遊星歯車機構６２の小型化を図ることが可能となっている。   Specifically, in the present embodiment, as shown in FIGS. 2 and 3, the first input member 71 includes the first ring gear R1, and the second input member 72 includes the second ring gear R2. . Therefore, when the support rigidity of the first input member 71 is not sufficient, the first input member 71 receives the first ring gear R1 from the first input gear 71 due to the load received from the first drive gear 21a. The load is easily transmitted to the carrier C1, and the rigidity required for the first carrier C1 tends to be high. In addition, when the support rigidity of the second input member 72 is not sufficient, the second input member 72 receives the second ring gear R2 from the second input member 72 due to the load that the second input gear 72a receives from the second drive gear 22a. The load is easily transmitted to the carrier C2, and the rigidity required for the second carrier C2 tends to be high. On the other hand, in the vehicle drive device 1 of the present embodiment, since the support rigidity of the first input member 71 and the second input member 72 can be enhanced as described above, the load received by the first input gear 71a is As a result, the load transmitted from the first input member 71 to the first carrier C1 is reduced, and the load received by the second input gear 72a is transmitted from the second input member 72 to the second carrier C2. The load can be reduced. As a result, the rigidity required for the first carrier C1 and the second carrier C2 can be easily ensured, and the first planetary gear mechanism 61 and the second planetary gear mechanism 62 can be miniaturized. .

次に、本実施形態の車両用駆動装置１における第１駆動部材２１及び第２駆動部材２２の支持構造について説明する。なお、以下の第１駆動部材２１及び第２駆動部材２２の支持構造の説明における径方向は、特に明記している場合を除き、第３軸Ａ３を基準とする径方向である。   Next, the support structure of the first drive member 21 and the second drive member 22 in the vehicle drive device 1 of the present embodiment will be described. The radial direction in the following description of the support structure of the first drive member 21 and the second drive member 22 is a radial direction based on the third axis A3, unless otherwise specified.

第１駆動部材２１及び第２駆動部材２２は、ケース３又は支持部材４０により回転自在に支持されている。具体的には、第１駆動部材２１及び第２駆動部材２２のそれぞれは、ケース３又は支持部材４０により、軸方向Ｌの２ヶ所で回転自在に支持されている。   The first drive member 21 and the second drive member 22 are rotatably supported by the case 3 or the support member 40. Specifically, each of the first drive member 21 and the second drive member 22 is rotatably supported at two places in the axial direction L by the case 3 or the support member 40.

図１及び図２に示すように、本実施形態では、第１駆動部材２１は、ケース３と第１支持部材４１とにより、軸方向Ｌの２ヶ所で回転自在に支持されている。具体的には、第１駆動部材２１は、第５ケース部３５に形成された第１５支持部３５ｃと、第１支持部材４１に形成された第１１支持部４１ｄとにより、軸方向Ｌの２ヶ所で回転自在に支持されている。第１１支持部４１ｄは、第１５支持部３５ｃよりも軸方向第１側Ｌ１に配置されている。   As shown in FIGS. 1 and 2, in the present embodiment, the first drive member 21 is rotatably supported at two places in the axial direction L by the case 3 and the first support member 41. Specifically, the first drive member 21 is formed by the fifteenth support portion 35 c formed in the fifth case portion 35 and the eleventh support portion 41 d formed in the first support member 41. It is rotatably supported at a location. The eleventh support portion 41d is disposed closer to the first axial side L1 than the fifteenth support portion 35c.

第１駆動部材２１は、第１５支持部３５ｃにより径方向外側から支持されている。具体的には、第１５支持部３５ｃの内周面と第１駆動部材２１の外周面との間に第１６軸受Ｂ１６（ここでは、ラジアル型の玉軸受）が配置されており、第１駆動部材２１は、第１６軸受Ｂ１６を介して第１５支持部３５ｃにより径方向外側から支持されている。第１６軸受Ｂ１６は、第１軸Ａ１を基準とする径方向視（すなわち、径方向Ｒ視）で第１０軸受Ｂ１０と重複するように配置されている。また、第１駆動部材２１は、第１１支持部４１ｄにより径方向外側から支持されている。具体的には、第１１支持部４１ｄの内周面と第１駆動部材２１の外周面との間に第１５軸受Ｂ１５（ここでは、ラジアル型の玉軸受）が配置されており、第１駆動部材２１は、第１５軸受Ｂ１５を介して第１１支持部４１ｄにより径方向外側から支持されている。第１５軸受Ｂ１５は、第２軸Ａ２を基準とする径方向視で第２軸受Ｂ２と重複するように配置されている。第１駆動ギヤ２１ａは、第１駆動部材２１における、軸方向Ｌにおける第１５軸受Ｂ１５と第１６軸受Ｂ１６との間に配置される部分の外周面に形成されている。   The first drive member 21 is supported by the fifteenth support portion 35c from the outer side in the radial direction. Specifically, a sixteenth bearing B16 (here, a radial type ball bearing) is disposed between the inner peripheral surface of the fifteenth support portion 35c and the outer peripheral surface of the first drive member 21. The member 21 is supported from outside in the radial direction by a fifteenth support portion 35c via a sixteenth bearing B16. The sixteenth bearing B16 is disposed so as to overlap with the tenth bearing B10 in the radial direction (that is, in the radial direction R) with respect to the first axis A1. The first drive member 21 is supported by the eleventh support portion 41d from the outer side in the radial direction. Specifically, a fifteenth bearing B15 (here, a radial type ball bearing) is disposed between the inner peripheral surface of the eleventh support portion 41d and the outer peripheral surface of the first drive member 21. The member 21 is supported from outside in the radial direction by an eleventh support portion 41d via a fifteenth bearing B15. The fifteenth bearing B15 is disposed so as to overlap with the second bearing B2 in a radial direction based on the second axis A2. The first drive gear 21 a is formed on the outer peripheral surface of a portion of the first drive member 21 which is disposed between the fifteenth bearing B 15 and the sixteenth bearing B 16 in the axial direction L.

図１及び図２に示すように、本実施形態では、第２駆動部材２２は、ケース３と第２支持部材４２とにより、軸方向Ｌの２ヶ所で回転自在に支持されている。具体的には、第２駆動部材２２は、第５ケース部３５に形成された第１６支持部３５ｄと、第２支持部材４２に形成された第１２支持部４２ｄとにより、軸方向Ｌの２ヶ所で回転自在に支持されている。第１２支持部４２ｄは、第１６支持部３５ｄよりも軸方向第２側Ｌ２に配置されている。   As shown in FIGS. 1 and 2, in the present embodiment, the second drive member 22 is rotatably supported at two places in the axial direction L by the case 3 and the second support member 42. Specifically, the second drive member 22 is configured by the second support portion 35 d formed in the fifth case portion 35 and the twelfth support portion 42 d formed in the second support member 42. It is rotatably supported at a location. The twelfth support portion 42d is disposed closer to the second axial side L2 than the sixteenth support portion 35d.

第２駆動部材２２は、第１６支持部３５ｄにより径方向外側から支持されている。具体的には、第１６支持部３５ｄの内周面と第２駆動部材２２の外周面との間に第１７軸受Ｂ１７（ここでは、ラジアル型の玉軸受）が配置されており、第２駆動部材２２は、第１７軸受Ｂ１７を介して第１６支持部３５ｄにより径方向外側から支持されている。第１７軸受Ｂ１７は、第１軸Ａ１を基準とする径方向視（すなわち、径方向Ｒ視）で第１１軸受Ｂ１１と重複するように配置されている。また、第２駆動部材２２は、第１２支持部４２ｄにより径方向外側から支持されている。具体的には、第１２支持部４２ｄの内周面と第２駆動部材２２の外周面との間に第１８軸受Ｂ１８（ここでは、ラジアル型の玉軸受）が配置されており、第２駆動部材２２は、第１８軸受Ｂ１８を介して第１２支持部４２ｄにより径方向外側から支持されている。第１８軸受Ｂ１８は、第２軸Ａ２を基準とする径方向視で第３軸受Ｂ３と重複するように配置されている。第２駆動ギヤ２２ａは、第２駆動部材２２における、軸方向Ｌにおける第１７軸受Ｂ１７と第１８軸受Ｂ１８との間に配置される部分の外周面に形成されている。   The second drive member 22 is supported by the sixteenth support portion 35d from the outside in the radial direction. Specifically, a seventeenth bearing B17 (here, a radial type ball bearing) is disposed between the inner peripheral surface of the sixteenth support portion 35d and the outer peripheral surface of the second drive member 22. The member 22 is supported from outside in the radial direction by a sixteenth support portion 35d via a seventeenth bearing B17. The seventeenth bearing B17 is disposed so as to overlap the eleventh bearing B11 in a radial direction view (that is, in a radial direction R view) based on the first axis A1. Further, the second drive member 22 is supported by the twelfth support portion 42d from the outside in the radial direction. Specifically, an eighteenth bearing B18 (here, a radial type ball bearing) is disposed between the inner peripheral surface of the twelfth support portion 42d and the outer peripheral surface of the second drive member 22. The member 22 is supported from outside in the radial direction by a twelfth support portion 42d via an eighteenth bearing B18. The eighteenth bearing B18 is disposed so as to overlap with the third bearing B3 in the radial direction with respect to the second axis A2. The second drive gear 22 a is formed on the outer peripheral surface of a portion of the second drive member 22 which is disposed between the seventeenth bearing B 17 and the eighteenth bearing B 18 in the axial direction L.

以上のように、本実施形態では、第１支持部材４１は、第１入力部材７１及び第１出力部材８１を支持するために用いられ、更に、第１連結部材５１及び第１駆動部材２１を支持するためにも用いられている。すなわち、第１支持部材４１には、第１入力部材７１の支持部（第９支持部４１ｃ）と、第１出力部材８１の支持部（第７支持部４１ｂ）とが形成され、更に、第１連結部材５１の支持部（第５支持部４１ａ）と、第１駆動部材２１の支持部（第１１支持部４１ｄ）とが形成されている。また、本実施形態では、第２支持部材４２は、第２入力部材７２及び第２出力部材８２を支持するために用いられ、更に、第２連結部材５２及び第２駆動部材２２を支持するためにも用いられている。すなわち、第２支持部材４２には、第２入力部材７２の支持部（第１０支持部４２ｃ）と、第２出力部材８２の支持部（第８支持部４２ｂ）とが形成され、更に、第２連結部材５２の支持部（第６支持部４２ａ）と、第２駆動部材２２の支持部（第１２支持部４２ｄ）とが形成されている。このように、第１支持部材４１や第２支持部材４２を複数の回転部材を支持するために用いることで、部品点数を少なく抑えることができると共に、各回転部材の支持精度（同じ支持部材４０に支持される回転部材同士の相対位置の精度）を確保することが容易となる。   As described above, in the present embodiment, the first support member 41 is used to support the first input member 71 and the first output member 81, and further, the first connecting member 51 and the first driving member 21 are used. It is also used to support. That is, in the first support member 41, the support portion (ninth support portion 41c) of the first input member 71 and the support portion (seventh support portion 41b) of the first output member 81 are formed. A support portion (fifth support portion 41 a) of the first connection member 51 and a support portion (eleventh support portion 41 d) of the first drive member 21 are formed. Further, in the present embodiment, the second support member 42 is used to support the second input member 72 and the second output member 82, and further to support the second connection member 52 and the second drive member 22. It is also used in That is, in the second support member 42, the support portion (tenth support portion 42c) of the second input member 72 and the support portion (eighth support portion 42b) of the second output member 82 are formed. A support portion (sixth support portion 42 a) of the second connection member 52 and a support portion (sixteenth support portion 42 d) of the second drive member 22 are formed. As described above, by using the first support member 41 and the second support member 42 to support a plurality of rotating members, the number of parts can be reduced, and the supporting accuracy of each rotating member (the same supporting member 40 It is easy to ensure the accuracy of the relative position of the rotating members supported by each other.

本実施形態では、第１入力部材７１、第２入力部材７２、第１出力部材８１、及び第２出力部材８２のそれぞれが、ケース３又は支持部材４０により回転自在に支持されている。そのため、第１入力部材７１に連結される第１回転要素Ｅ１、第２入力部材７２に連結される第４回転要素Ｅ４、第１出力部材８１に連結される第２回転要素Ｅ２、及び、第２出力部材８２に連結される第３回転要素Ｅ３のそれぞれの支持精度を適切に確保することができる。その上で、本実施形態では、第１遊星歯車機構６１の回転要素と第２遊星歯車機構６２の回転要素との連結部６３を、径方向Ｒに隙間を有する連結構造としている。これにより、各部品の径方向Ｒにおける寸法誤差や組付誤差を連結部６３で吸収することを可能として、第１遊星歯車機構６１や第２遊星歯車機構６２におけるギヤの噛み合い部に過大な荷重（偏荷重等）が作用することを回避可能としている。   In the present embodiment, each of the first input member 71, the second input member 72, the first output member 81, and the second output member 82 is rotatably supported by the case 3 or the support member 40. Therefore, a first rotating element E1 connected to the first input member 71, a fourth rotating element E4 connected to the second input member 72, a second rotating element E2 connected to the first output member 81, and The support precision of each of the 3rd rotation element E3 connected with 2 output members 82 can be secured appropriately. Moreover, in the present embodiment, the connecting portion 63 between the rotating element of the first planetary gear mechanism 61 and the rotating element of the second planetary gear mechanism 62 has a connecting structure having a gap in the radial direction R. As a result, dimensional errors and assembly errors in the radial direction R of each component can be absorbed by the connecting portion 63, and excessive load is applied to the meshing portions of the gears in the first planetary gear mechanism 61 and the second planetary gear mechanism 62. It is possible to avoid the effect of (bias load etc.).

具体的には、本実施形態では、第１キャリヤＣ１と第２サンギヤＳ２とが一体的に回転するように連結されていると共に、第１サンギヤＳ１と第２キャリヤＣ２とが一体的に回転するように連結されている。そして、第１キャリヤＣ１と第２サンギヤＳ２との連結部６３である第２連結部６３ｂと、第１サンギヤＳ１と第２キャリヤＣ２との連結部６３である第１連結部６３ａとを、径方向Ｒに隙間を有する連結構造としている。   Specifically, in the present embodiment, the first carrier C1 and the second sun gear S2 are connected to rotate integrally, and the first sun gear S1 and the second carrier C2 rotate integrally. It is linked as such. The diameter of the second connecting portion 63b, which is the connecting portion 63 between the first carrier C1 and the second sun gear S2, and the first connecting portion 63a, which is the connecting portion 63 between the first sun gear S1 and the second carrier C2. The connection structure has a gap in the direction R.

図２に示すように、第１キャリヤＣ１は、第１ピニオンギヤＰ１に対して軸方向第２側Ｌ２に配置されて第１ピニオンギヤＰ１を回転自在に支持する第３円環板状部６８ｃを備えている。そして、第３円環板状部６８ｃの径方向Ｒの内側の端部には、軸方向Ｌに延びる円筒状に形成された第３筒状部６７ｃが連結されている。ここでは、第３筒状部６７ｃは、第３円環板状部６８ｃと一体的に形成されている。また、第２サンギヤＳ２には、軸方向Ｌに延びる円筒状に形成された第２筒状部６７ｂが、第２サンギヤＳ２に対して軸方向第１側Ｌ１に突出するように連結されている。ここでは、第２筒状部６７ｂは、第２サンギヤＳ２が外周面に形成された円筒状部材と一体的に形成されている。第２筒状部６７ｂの外周面は第３筒状部６７ｃの内周面よりも小径に形成されている。そして、第２筒状部６７ｂと第３筒状部６７ｃとの周方向（第１軸Ａ１を基準とする周方向）の相対回転が規制され、軸方向Ｌの相対移動が許容されるように、第２筒状部６７ｂの外周面に形成された係合部と第３筒状部６７ｃの内周面に形成された係合部とが、第２連結部６３ｂにおいて係合（本実施形態では、スプライン係合）している。第２連結部６３ｂには、少なくとも第２筒状部６７ｂと第３筒状部６７ｃとの軸方向Ｌの相対移動を可能とする程度の径方向Ｒの隙間が形成されている。   As shown in FIG. 2, the first carrier C1 includes a third annular plate portion 68c disposed on the second axial side L2 with respect to the first pinion gear P1 and rotatably supporting the first pinion gear P1. ing. A third cylindrical portion 67c formed in a cylindrical shape extending in the axial direction L is connected to an inner end of the third annular plate portion 68c in the radial direction R. Here, the third cylindrical portion 67c is integrally formed with the third annular plate portion 68c. In addition, a second cylindrical portion 67b formed in a cylindrical shape extending in the axial direction L is connected to the second sun gear S2 so as to protrude on the first sun direction S1 with respect to the second sun gear S2. . Here, the second cylindrical portion 67b is integrally formed with a cylindrical member in which the second sun gear S2 is formed on the outer peripheral surface. The outer peripheral surface of the second cylindrical portion 67b is smaller in diameter than the inner peripheral surface of the third cylindrical portion 67c. Then, relative rotation of the second cylindrical portion 67b and the third cylindrical portion 67c in the circumferential direction (peripheral direction based on the first axis A1) is restricted, and relative movement in the axial direction L is permitted. The engagement portion formed on the outer peripheral surface of the second cylindrical portion 67b and the engagement portion formed on the inner peripheral surface of the third cylindrical portion 67c are engaged at the second connection portion 63b (this embodiment) In the figure, spline engagement is performed. In the second connection portion 63b, a gap in the radial direction R is formed so as to allow relative movement of at least the second cylindrical portion 67b and the third cylindrical portion 67c in the axial direction L.

また、図２に示すように、軸方向Ｌに延びる筒状に形成された第１筒状部６７ａの外周面に、第１サンギヤＳ１が形成されている。第１筒状部６７ａの内周面は、第３軸方向延在部６５ｃの外周面よりも大径に形成されている。そして、第１筒状部６７ａと第３軸方向延在部６５ｃとの周方向（第１軸Ａ１を基準とする周方向）の相対回転が規制され、軸方向Ｌの相対移動が許容されるように、第１筒状部６７ａの内周面に形成された係合部と第３軸方向延在部６５ｃの外周面に形成された係合部とが、第１連結部６３ａにおいて係合（本実施形態では、スプライン係合）している。第１連結部６３ａには、少なくとも第１筒状部６７ａと第３軸方向延在部６５ｃとの軸方向Ｌの相対移動を可能とする程度の径方向Ｒの隙間が形成されている。   Further, as shown in FIG. 2, a first sun gear S <b> 1 is formed on the outer peripheral surface of a first cylindrical portion 67 a formed in a cylindrical shape extending in the axial direction L. The inner circumferential surface of the first tubular portion 67a is formed to have a diameter larger than the outer circumferential surface of the third axially extending portion 65c. Then, relative rotation of the first cylindrical portion 67a and the third axially extending portion 65c in the circumferential direction (peripheral direction based on the first axis A1) is restricted, and relative movement in the axial direction L is permitted. Thus, the engagement portion formed on the inner circumferential surface of the first cylindrical portion 67a and the engagement portion formed on the outer circumferential surface of the third axially extending portion 65c are engaged at the first connecting portion 63a. (In the present embodiment, spline engagement is performed). In the first connecting portion 63a, a gap in the radial direction R is formed so as to allow relative movement of at least the first cylindrical portion 67a and the third axially extending portion 65c in the axial direction L.

〔その他の実施形態〕
次に、車両用駆動装置のその他の実施形態について説明する。 Other Embodiments
Next, other embodiments of the vehicle drive device will be described.

（１）上記の実施形態では、第１キャリヤＣ１と第２サンギヤＳ２とが連結されると共に、第１サンギヤＳ１と第２キャリヤＣ２とが連結されることで、第１遊星歯車機構６１と第２遊星歯車機構６２とが全体として４つの回転要素（Ｅ１〜Ｅ４）を備えて一体的に差動動作を行う構成を例として説明した。しかし、そのような構成に限定されることなく、例えば、第１キャリヤＣ１と第２リングギヤＲ２とが連結されると共に第１リングギヤＲ１と第２キャリヤＣ２とが連結されることで、第１遊星歯車機構６１と第２遊星歯車機構６２とが全体として４つの回転要素（Ｅ１〜Ｅ４）を備えて一体的に差動動作を行う構成とすることもできる。この場合、第１回転電機１１が第１サンギヤＳ１に駆動連結され、第１連結部材５１が一体的に回転する第１キャリヤＣ１と第２リングギヤＲ２に駆動連結され、第２連結部材５２が一体的に回転する第１リングギヤＲ１と第２キャリヤＣ２に駆動連結され、第２回転電機１２が第２サンギヤＳ２に駆動連結される構成とすることで、上記の実施形態と同様に、回転速度の順が、第１回転電機１１に駆動連結される第１回転要素Ｅ１、第１連結部材５１に駆動連結される第２回転要素Ｅ２、第２連結部材５２に駆動連結される第３回転要素Ｅ３、及び、第２回転電機１２に駆動連結される第４回転要素Ｅ４の順となる構成を実現することができる。 (1) In the above embodiment, the first carrier C1 and the second sun gear S2 are connected, and the first sun gear S1 and the second carrier C2 are connected, whereby the first planetary gear mechanism 61 and the first carrier C1 are connected. The configuration has been described as an example in which the two-planet gear mechanism 62 includes four rotating elements (E1 to E4) as a whole to integrally perform differential operation. However, without being limited to such a configuration, for example, the first carrier C1 and the second ring gear R2 are connected, and the first ring gear R1 and the second carrier C2 are connected, for example. The gear mechanism 61 and the second planetary gear mechanism 62 may be configured to include four rotating elements (E1 to E4) as a whole to integrally perform differential operation. In this case, the first rotary electric machine 11 is drivably connected to the first sun gear S1, and the first connection member 51 is drivably connected to the first carrier C1 and the second ring gear R2 that rotate integrally, and the second connection member 52 is integrated. The second rotary electric machine 12 is drivingly connected to the first ring gear R1 and the second carrier C2, and the second rotating electric machine 12 is drivingly connected to the second sun gear S2. In order, the first rotating element E1 drivingly connected to the first rotating electric machine 11, the second rotating element E2 drivingly connected to the first connecting member 51, and the third rotating element E3 drivingly connected to the second connecting member 52 And the structure which becomes order of the 4th rotation element E4 drive-connected to the 2nd rotary electric machine 12 is realizable.

（２）上記の実施形態では、第１遊星歯車機構６１及び第２遊星歯車機構６２の双方が、シングルピニオン型の遊星歯車機構である構成を例として説明した。しかし、そのような構成に限定されることなく、例えば、第１遊星歯車機構６１及び第２遊星歯車機構６２の双方が、ダブルピニオン型の遊星歯車機構である構成とすることもできる。この場合、第１キャリヤＣ１と第２リングギヤＲ２とが連結されると共に第１リングギヤＲ１と第２キャリヤＣ２とが連結されることで、第１遊星歯車機構６１と第２遊星歯車機構６２とが全体として４つの回転要素（Ｅ１〜Ｅ４）を備えて一体的に差動動作を行う構成とすることができる。この場合、第１回転電機１１が第１サンギヤＳ１に駆動連結され、第１連結部材５１が一体的に回転する第１リングギヤＲ１と第２キャリヤＣ２に駆動連結され、第２連結部材５２が一体的に回転する第１キャリヤＣ１と第２リングギヤＲ２に駆動連結され、第２回転電機１２が第２サンギヤＳ２に駆動連結される構成とすることで、上記の実施形態と同様に、回転速度の順が、第１回転電機１１に駆動連結される第１回転要素Ｅ１、第１連結部材５１に駆動連結される第２回転要素Ｅ２、第２連結部材５２に駆動連結される第３回転要素Ｅ３、及び、第２回転電機１２に駆動連結される第４回転要素Ｅ４の順となる構成を実現することができる。 (2) In the above embodiment, the configuration in which both the first planetary gear mechanism 61 and the second planetary gear mechanism 62 are single pinion type planetary gear mechanisms has been described as an example. However, without being limited to such a configuration, for example, both of the first planetary gear mechanism 61 and the second planetary gear mechanism 62 may be double pinion type planetary gear mechanisms. In this case, the first carrier C1 and the second ring gear R2 are connected, and the first ring gear R1 and the second carrier C2 are connected, so that the first planetary gear mechanism 61 and the second planetary gear mechanism 62 As a whole, four rotation elements (E1 to E4) can be provided to perform differential operation integrally. In this case, the first rotary electric machine 11 is drivably connected to the first sun gear S1, and the first connection member 51 is drivably connected to the first ring gear R1 and the second carrier C2 that rotate integrally, and the second connection member 52 is integrated. In the same manner as in the above-described embodiment, the second electric rotating machine 12 is drivingly connected to the first carrier C1 and the second ring gear R2 that rotate in a rotating manner, and the second rotating electric machine 12 is drivingly connected to the second sun gear S2. In order, the first rotating element E1 drivingly connected to the first rotating electric machine 11, the second rotating element E2 drivingly connected to the first connecting member 51, and the third rotating element E3 drivingly connected to the second connecting member 52 And the structure which becomes order of the 4th rotation element E4 drive-connected to the 2nd rotary electric machine 12 is realizable.

（３）上記の実施形態では、伝達装置２が、第１回転電機１１のトルクを第１連結部材５１及び第２連結部材５２の双方に伝達すると共に、第２回転電機１２のトルクを第１連結部材５１及び第２連結部材５２の双方に伝達する構成を例として説明した。しかし、そのような構成に限定されることなく、伝達装置２が、第１回転電機１１のトルクを第１連結部材５１及び第２連結部材５２のうちの第１連結部材５１のみに伝達すると共に、第２回転電機１２のトルクを第１連結部材５１及び第２連結部材５２のうちの第２連結部材５２のみに伝達する構成とすることもできる。すなわち、第１回転電機１１と第１連結部材５１との間の動力伝達経路と第２回転電機１２と第２連結部材５２との間の動力伝達経路とが分離された構成とすることもできる。 (3) In the above embodiment, the transmission device 2 transmits the torque of the first rotating electric machine 11 to both the first connecting member 51 and the second connecting member 52, and the torque of the second rotating electric machine 12 is the first The configuration for transmitting to both the connecting member 51 and the second connecting member 52 has been described as an example. However, without being limited to such a configuration, the transmission device 2 transmits the torque of the first rotary electric machine 11 only to the first connection member 51 of the first connection member 51 and the second connection member 52. Alternatively, the torque of the second rotary electric machine 12 may be transmitted to only the second connection member 52 of the first connection member 51 and the second connection member 52. That is, the power transmission path between the first rotary electric machine 11 and the first connection member 51 and the power transmission path between the second rotary electric machine 12 and the second connection member 52 can be separated. .

例えば、上記の実施形態のように第１遊星歯車機構６１と第２遊星歯車機構６２とを連結せずに、第１遊星歯車機構６１と第２遊星歯車機構６２とが互いに独立に差動動作を行う構成とすることで、第１回転電機１１と第１連結部材５１との間の動力伝達経路と第２回転電機１２と第２連結部材５２との間の動力伝達経路とが分離された構成を実現することができる。この場合、第１遊星歯車機構６１は、第１回転電機１１に駆動連結される第１回転要素Ｅ１と、第１連結部材５１に駆動連結される第２回転要素Ｅ２と、第５回転要素と、を備え、第２遊星歯車機構６２は、第２連結部材５２に駆動連結される第３回転要素Ｅ３と、第２回転電機１２に駆動連結される第４回転要素Ｅ４と、第６回転要素と、を備える。すなわち、差動歯車装置６（遊星歯車装置６０）は、全体として６つの回転要素を有する。この場合、例えば、第５回転要素が非回転部材に固定され、第６回転要素が非回転部材に固定される構成とすることができる。   For example, without connecting the first planetary gear mechanism 61 and the second planetary gear mechanism 62 as in the above embodiment, the first planetary gear mechanism 61 and the second planetary gear mechanism 62 perform differential operation independently of each other. The power transmission path between the first rotary electric machine 11 and the first connection member 51 and the power transmission path between the second rotary electric machine 12 and the second connection member 52 are separated by The configuration can be realized. In this case, the first planetary gear mechanism 61 includes a first rotating element E1 drivingly connected to the first rotating electric machine 11, a second rotating element E2 drivingly connected to the first connecting member 51, and a fifth rotating element , And the second planetary gear mechanism 62 includes a third rotating element E3 drivingly connected to the second connection member 52, a fourth rotating element E4 drivingly connected to the second rotating electric machine 12, and a sixth rotating element And. That is, differential gear device 6 (planet gear device 60) has six rotating elements as a whole. In this case, for example, the fifth rotation element may be fixed to the non-rotation member, and the sixth rotation element may be fixed to the non-rotation member.

（４）上記の実施形態では、第１出力部材８１及び第２出力部材８２のそれぞれが、ケース３又は支持部材４０により、軸方向Ｌの２ヶ所で回転自在に支持される構成を例として説明した。しかし、そのような構成に限定されることなく、第１出力部材８１及び第２出力部材８２の一方又は双方が、軸方向Ｌの１ヶ所でのみケース３又は支持部材４０により回転自在に支持される構成や、第１出力部材８１及び第２出力部材８２の一方又は双方が、ケース３及び支持部材４０のいずれにも支持されない構成（すなわち、回転部材にのみ回転自在に支持される構成）とすることもできる。 (4) In the above embodiment, the first output member 81 and the second output member 82 are respectively supported by the case 3 or the support member 40 at two points in the axial direction L as an example. did. However, without being limited to such a configuration, one or both of the first output member 81 and the second output member 82 are rotatably supported by the case 3 or the support member 40 only at one position in the axial direction L. A configuration in which one or both of the first output member 81 and the second output member 82 are not supported by either of the case 3 and the support member 40 (that is, a configuration in which they are rotatably supported only by the rotating member) You can also

（５）上記の実施形態では、第１入力部材７１及び第２入力部材７２のそれぞれが、ケース３又は支持部材４０により、軸方向Ｌの２ヶ所で回転自在に支持される構成を例として説明した。しかし、そのような構成に限定されることなく、第１入力部材７１及び第２入力部材７２の一方又は双方が、軸方向Ｌの１ヶ所でのみケース３又は支持部材４０により回転自在に支持される構成や、第１入力部材７１及び第２入力部材７２の一方又は双方が、ケース３及び支持部材４０のいずれにも支持されない構成（すなわち、回転部材にのみ回転自在に支持される構成）とすることもできる。 (5) In the above embodiment, the configuration in which the first input member 71 and the second input member 72 are rotatably supported at two places in the axial direction L by the case 3 or the support member 40 is described as an example. did. However, without being limited to such a configuration, one or both of the first input member 71 and the second input member 72 are rotatably supported by the case 3 or the support member 40 only at one position in the axial direction L. A configuration in which one or both of the first input member 71 and the second input member 72 are not supported by any of the case 3 and the support member 40 (that is, a configuration in which the first input member 71 and the second input member 72 are rotatably supported only by the rotating member) You can also

（６）上記の実施形態では、ケース３が第５ケース部３５を備え、第１ケース部３１と第２ケース部３２とが第５ケース部３５を介して接合される構成を例として説明した。しかし、そのような構成に限定されることなく、ケース３が第５ケース部３５を備えず、第１ケース部３１と第２ケース部３２とが第５ケース部３５を介さずに接合される構成（すなわち、シール部材４のみを介して接合される構成）とすることもできる。この場合、例えば、第５ケース部３５と同様の回転部材の支持機能を有する支持部材４０を、第５ケース部３５に代えて設けてもよい。 (6) In the above embodiment, the case 3 includes the fifth case portion 35, and the first case portion 31 and the second case portion 32 are joined via the fifth case portion 35 as an example. . However, without being limited to such a configuration, the case 3 does not include the fifth case portion 35, and the first case portion 31 and the second case portion 32 are joined without interposing the fifth case portion 35. It can also be configured (i.e., configured to be joined only via the seal member 4). In this case, for example, the supporting member 40 having the same supporting function as the fifth case portion 35 may be provided instead of the fifth case portion 35.

（７）上記の実施形態では、第１キャリヤＣ１に第１油路９１と第２油路９２とが形成され、第２キャリヤＣ２に第３油路９３と第４油路９４とが形成される構成を例として説明した。しかし、そのような構成に限定されることなく、例えば、第１キャリヤＣ１に第２油路９２が形成されず、第２キャリヤＣ２に第４油路９４が形成されない構成とすることもできる。 (7) In the above embodiment, the first oil passage 91 and the second oil passage 92 are formed in the first carrier C1, and the third oil passage 93 and the fourth oil passage 94 are formed in the second carrier C2. Configuration has been described as an example. However, without being limited to such a configuration, for example, the second oil passage 92 may not be formed in the first carrier C1, and the fourth oil passage 94 may not be formed in the second carrier C2.

（８）上記の実施形態では、第９軸受Ｂ９が、径方向Ｒ視で第６軸受Ｂ６と重複するように配置され、第１２軸受Ｂ１２が、径方向Ｒ視で第７軸受Ｂ７と重複するように配置される構成を例として説明した。しかし、そのような構成に限定されることなく、第９軸受Ｂ９が、径方向Ｒ視で第６軸受Ｂ６と重複しないように、第６軸受Ｂ６に対して軸方向第１側Ｌ１又は軸方向第２側Ｌ２に配置される構成や、第１２軸受Ｂ１２が、径方向Ｒ視で第７軸受Ｂ７と重複しないように、第７軸受Ｂ７に対して軸方向第１側Ｌ１又は軸方向第２側Ｌ２に配置される構成とすることもできる。 (8) In the above embodiment, the ninth bearing B9 is disposed so as to overlap the sixth bearing B6 in the radial direction R, and the twelfth bearing B12 overlaps the seventh bearing B7 in the radial direction R. The configuration arranged as described above has been described as an example. However, without being limited to such a configuration, the axial first side L1 or the axial direction with respect to the sixth bearing B6 so that the ninth bearing B9 does not overlap the sixth bearing B6 in the radial direction R view. The first side L1 or the second axial direction with respect to the seventh bearing B7 so that the configuration disposed on the second side L2 and the twelfth bearing B12 do not overlap with the seventh bearing B7 in the radial direction R view. It can also be configured to be disposed on the side L2.

（９）上記の実施形態では、第１支持部材４１に、第５支持部４１ａと、第７支持部４１ｂと、第９支持部４１ｃと、第１１支持部４１ｄとが形成され、第２支持部材４２に、第６支持部４２ａと、第８支持部４２ｂと、第１０支持部４２ｃと、第１２支持部４２ｄとが形成される構成を例として説明した。しかし、そのような構成に限定されることなく、第５支持部４１ａ、第７支持部４１ｂ、第９支持部４１ｃ、及び第１１支持部４１ｄの一部のみが第１支持部材４１に形成され、残りの支持部が他の支持部材４０或いはケース３に形成される構成とすることもできる。また、第６支持部４２ａ、第８支持部４２ｂ、第１０支持部４２ｃ、及び第１２支持部４２ｄの一部のみが第２支持部材４２に形成され、残りの支持部が他の支持部材４０或いはケース３に形成される構成とすることもできる。 (9) In the above embodiment, the fifth support portion 41a, the seventh support portion 41b, the ninth support portion 41c, and the eleventh support portion 41d are formed in the first support member 41. The configuration in which the sixth support portion 42a, the eighth support portion 42b, the tenth support portion 42c, and the twelfth support portion 42d are formed in the member 42 has been described as an example. However, without being limited to such a configuration, only a part of the fifth support portion 41a, the seventh support portion 41b, the ninth support portion 41c, and the eleventh support portion 41d is formed in the first support member 41. Alternatively, the remaining support may be formed on another support member 40 or the case 3. In addition, only a part of the sixth support portion 42a, the eighth support portion 42b, the tenth support portion 42c, and the twelfth support portion 42d is formed on the second support member 42, and the remaining support portions are the other support members 40. Alternatively, the configuration may be formed in the case 3.

（１０）上記の実施形態では、第１出力部材８１が、第１キャリヤＣ１に対して軸方向Ｌに相対移動可能に連結され、第２出力部材８２が、第２キャリヤＣ２に対して軸方向Ｌに相対移動可能に連結される構成を例として説明した。しかし、そのような構成に限定されることなく、第１出力部材８１が、第１キャリヤＣ１と一体的に形成されること等により、第１キャリヤＣ１に対して軸方向Ｌに相対移動不能に連結される構成とすることもできる。また、第２出力部材８２が、第２キャリヤＣ２と一体的に形成されること等により、第２キャリヤＣ２に対して軸方向Ｌに相対移動不能に連結される構成とすることもできる。 (10) In the above embodiment, the first output member 81 is connected to be able to move relative to the first carrier C1 in the axial direction L, and the second output member 82 is connected to the second carrier C2 in the axial direction. The configuration in which relative movement is connected to L has been described as an example. However, the present invention is not limited to such a configuration, and the first output member 81 can not be moved relative to the first carrier C1 in the axial direction L by being integrally formed with the first carrier C1 or the like. It can also be configured to be linked. In addition, the second output member 82 may be integrally connected to the second carrier C <b> 2 so that the second output member 82 can not move relatively in the axial direction L with respect to the second carrier C <b> 2.

（１１）上記の実施形態では、第１出力部材８１が、第１遊星歯車機構６１（第１遊星歯車機構６１の噛み合い部）に対して軸方向第１側Ｌ１に配置され、第２出力部材８２が、第２遊星歯車機構６２（第２遊星歯車機構６２の噛み合い部）に対して軸方向第２側Ｌ２に配置される構成を例として説明した。しかし、そのような構成に限定されることなく、第１出力部材８１が、第１遊星歯車機構６１（第１遊星歯車機構６１の噛み合い部）に対して軸方向第２側Ｌ２に配置され、第２出力部材８２が、第２遊星歯車機構６２（第２遊星歯車機構６２の噛み合い部）に対して軸方向第１側Ｌ１に配置される構成とすることもできる。 (11) In the above embodiment, the first output member 81 is disposed on the first axial side L1 with respect to the first planetary gear mechanism 61 (the meshing portion of the first planetary gear mechanism 61), and the second output member The configuration in which the second planetary gear mechanism 82 is disposed on the second axial side L2 with respect to the second planetary gear mechanism 62 (the meshing portion of the second planetary gear mechanism 62) has been described as an example. However, without being limited to such a configuration, the first output member 81 is disposed on the second axial side L2 with respect to the first planetary gear mechanism 61 (the meshing portion of the first planetary gear mechanism 61), The second output member 82 may be disposed on the first axial side L1 with respect to the second planetary gear mechanism 62 (the meshing portion of the second planetary gear mechanism 62).

（１２）上記の実施形態では、第１駆動ギヤ２１ａが第１入力ギヤ７１ａに噛み合い、第２駆動ギヤ２２ａが第２入力ギヤ７２ａに噛み合う構成を例として説明した。しかし、そのような構成に限定されることなく、第１駆動ギヤ２１ａと第１入力ギヤ７１ａとが別のギヤ又はギヤ機構を介して連結され、第２駆動ギヤ２２ａと第２入力ギヤ７２ａとが別のギヤ又はギヤ機構を介して連結される構成とすることもできる。 (12) In the above embodiment, the first drive gear 21a meshes with the first input gear 71a, and the second drive gear 22a meshes with the second input gear 72a. However, without being limited to such a configuration, the first drive gear 21a and the first input gear 71a are connected via another gear or gear mechanism, and the second drive gear 22a and the second input gear 72a May be connected via another gear or gear mechanism.

（１３）上記の実施形態では、第１出力ギヤ８１ａが第１従動ギヤ５１ａに噛み合い、第２出力ギヤ８２ａが第２従動ギヤ５２ａに噛み合う構成を例として説明した。しかし、そのような構成に限定されることなく、第１出力ギヤ８１ａと第１従動ギヤ５１ａとが別のギヤ又はギヤ機構を介して連結され、第２出力ギヤ８２ａと第２従動ギヤ５２ａとが別のギヤ又はギヤ機構を介して連結される構成とすることもできる。 (13) In the above embodiment, the configuration in which the first output gear 81a meshes with the first driven gear 51a and the second output gear 82a meshes with the second driven gear 52a has been described as an example. However, without being limited to such a configuration, the first output gear 81a and the first driven gear 51a are connected via another gear or gear mechanism, and the second output gear 82a and the second driven gear 52a May be connected via another gear or gear mechanism.

（１４）上記の実施形態では、第１連結部材５１が第１車輪Ｗ１と一体的に回転するように連結され、第２連結部材５２が第２車輪Ｗ２と一体的に回転するように連結される構成を例として説明した。しかし、そのような構成に限定されることなく、第１連結部材５１が、第１軸部材５３と同軸に配置されると共に歯車機構（例えば、差動歯車機構）を介して第１車輪Ｗ１に連結され、第２連結部材５２が、第２軸部材５４と同軸に配置されると共に歯車機構（例えば、差動歯車機構）を介して第２車輪Ｗ２に連結される構成とすることもできる。なお、第１連結部材５１が第１軸部材５３とは別軸に配置され、第２連結部材５２が第２軸部材５４とは別軸に配置される構成とすることも可能である。 (14) In the above embodiment, the first connecting member 51 is connected to rotate integrally with the first wheel W1, and the second connecting member 52 is connected to rotate integrally with the second wheel W2. Configuration has been described as an example. However, without being limited to such a configuration, the first connection member 51 is disposed coaxially with the first shaft member 53 and is connected to the first wheel W1 via a gear mechanism (for example, a differential gear mechanism). The second connection member 52 may be connected coaxially with the second shaft member 54 and connected to the second wheel W2 via a gear mechanism (for example, a differential gear mechanism). The first connecting member 51 may be disposed on an axis different from the first shaft member 53, and the second connecting member 52 may be disposed on an axis different from the second shaft member 54.

（１５）上記の実施形態では、第１連結部材５１が、ケース３に形成された第１支持部３１ａと、第１支持部材４１とにより、軸方向Ｌの２ヶ所で回転自在に支持され、第２連結部材５２が、ケース３に形成された第２支持部３２ａと、第２支持部材４２とにより、軸方向Ｌの２ヶ所で回転自在に支持される構成を例として説明した。しかし、そのような構成に限定されることなく、例えば、第１連結部材５１が、軸方向Ｌの２ヶ所のそれぞれでケース３に回転自在に支持され、第２連結部材５２が、軸方向Ｌの２ヶ所のそれぞれでケース３に回転自在に支持される構成とすることもできる。 (15) In the above embodiment, the first connection member 51 is rotatably supported at two places in the axial direction L by the first support portion 31 a formed in the case 3 and the first support member 41, The configuration in which the second connection member 52 is rotatably supported at two places in the axial direction L by the second support portion 32 a formed in the case 3 and the second support member 42 has been described as an example. However, without being limited to such a configuration, for example, the first connection member 51 is rotatably supported by the case 3 at each of two places in the axial direction L, and the second connection member 52 is In each of the two places, the case 3 may be rotatably supported.

（１６）上記の実施形態では、第１回転電機１１及び第２回転電機１２が、第３軸Ａ３上に配置される構成を例として説明した。しかし、そのような構成に限定されることなく、第１回転電機１１及び第２回転電機１２の一方又は双方が、第１軸Ａ１上に又は第２軸Ａ２上に配置される構成とすることもできる。また、上記の実施形態では、第１連結部材５１及び第２連結部材５２が、第２軸Ａ２上に配置される構成を例として説明した。しかし、そのような構成に限定されることなく、第１連結部材５１及び第２連結部材５２が、第１軸Ａ１上に又は第３軸Ａ３上に配置される構成とすることもできる。 (16) In the above embodiment, the configuration in which the first rotating electrical machine 11 and the second rotating electrical machine 12 are disposed on the third axis A3 has been described as an example. However, without being limited to such a configuration, one or both of the first rotating electrical machine 11 and the second rotating electrical machine 12 may be disposed on the first axis A1 or on the second axis A2. You can also. Moreover, in said embodiment, the 1st connection member 51 and the 2nd connection member 52 demonstrated as an example the structure arrange | positioned on 2nd axis | shaft A2. However, without being limited to such a configuration, the first connecting member 51 and the second connecting member 52 may be arranged on the first axis A1 or on the third axis A3.

（１７）なお、上述した各実施形態で開示された構成は、矛盾が生じない限り、他の実施形態で開示された構成と組み合わせて適用すること（その他の実施形態として説明した実施形態同士の組み合わせを含む）も可能である。その他の構成に関しても、本明細書において開示された実施形態は全ての点で単なる例示に過ぎない。従って、本開示の趣旨を逸脱しない範囲内で、適宜、種々の改変を行うことが可能である。 (17) Note that the configurations disclosed in each of the above-described embodiments may be combined with the configurations disclosed in the other embodiments and applied as long as no contradiction occurs (the embodiments described as the other embodiments Combinations are also possible. As for the other configurations, the embodiments disclosed herein are merely illustrative in all respects. Therefore, various modifications can be made as appropriate without departing from the spirit of the present disclosure.

〔上記実施形態の概要〕
以下、上記において説明した車両用駆動装置の概要について説明する。 [Summary of the above embodiment]
Hereinafter, an outline of the vehicle drive device described above will be described.

第１回転電機（１１）と、第２回転電機（１２）と、第１車輪（Ｗ１）に駆動連結される第１連結部材（５１）と、第２車輪（Ｗ２）に駆動連結される第２連結部材（５２）と、前記第１回転電機（１１）のトルクを前記第１連結部材（５１）及び前記第２連結部材（５２）のうちの少なくとも前記第１連結部材（５１）に伝達すると共に、前記第２回転電機（１２）のトルクを前記第１連結部材（５１）及び前記第２連結部材（５２）のうちの少なくとも前記第２連結部材（５２）に伝達する伝達装置（２）と、前記第１回転電機（１１）、前記第２回転電機（１２）、前記第１連結部材（５１）、前記第２連結部材（５２）、及び前記伝達装置（２）を収容するケース（３）と、を備え、前記伝達装置（２）は、第１軸（Ａ１）上に配置され、前記第１連結部材（５１）及び前記第２連結部材（５２）は、前記第１軸（Ａ１）に平行な第２軸（Ａ２）上に配置され、前記伝達装置（２）は、前記第１回転電機（１１）に駆動連結される第１回転要素（Ｅ１）、前記第１連結部材（５１）に駆動連結される第２回転要素（Ｅ２）、前記第２連結部材（５２）に駆動連結される第３回転要素（Ｅ３）、及び、前記第２回転電機（１２）に駆動連結される第４回転要素（Ｅ４）を少なくとも有する遊星歯車装置（６０）と、前記第１回転要素（Ｅ１）に連結される第１入力部材（７１）と、前記第２回転要素（Ｅ２）に連結される第１出力部材（８１）と、前記第３回転要素（Ｅ３）に連結される第２出力部材（８２）と、前記第４回転要素（Ｅ４）に連結される第２入力部材（７２）と、を備え、前記第１出力部材（８１）は、前記第１連結部材（５１）が備える第１従動ギヤ（５１ａ）に噛み合う第１出力ギヤ（８１ａ）を備え、前記第２出力部材（８２）は、前記第２連結部材（５２）が備える第２従動ギヤ（５２ａ）に噛み合う第２出力ギヤ（８２ａ）を備え、前記第１出力部材（８１）及び前記第２出力部材（８２）のそれぞれが、前記ケース（３）又は前記ケース（３）に固定された支持部材（４０）により、軸方向（Ｌ）の２ヶ所で回転自在に支持されている。   The first rotating electric machine (11), the second rotating electric machine (12), the first connecting member (51) drivingly connected to the first wheel (W1), and the second driving motor connected to the second wheel (W2) The torque of the second connecting member (52) and the first rotating electric machine (11) is transmitted to at least the first connecting member (51) of the first connecting member (51) and the second connecting member (52) And a transmission device (2) for transmitting the torque of the second rotary electric machine (12) to at least the second connection member (52) of the first connection member (51) and the second connection member (52). And a case for housing the first rotating electric machine (11), the second rotating electric machine (12), the first connecting member (51), the second connecting member (52), and the transmission device (2) And the transmission device (2) is disposed on the first axis (A1). The first connection member (51) and the second connection member (52) are disposed on a second axis (A2) parallel to the first axis (A1), and the transmission device (2) is A first rotating element (E1) drivingly connected to the first rotating electric machine (11), a second rotating element (E2) drivingly connected to the first connecting member (51), the second connecting member (52) A planetary gear device (60) including at least a third rotating element (E3) drivingly connected to the second rotating electric machine (12) and a fourth rotating element (E4) drivingly connected to the second rotating electric machine (12); The first input member (71) connected to the element (E1), the first output member (81) connected to the second rotating element (E2), and the third rotating element (E3) A second output member (82) and a second input member (72) connected to the fourth rotating element (E4) And the first output member (81) includes a first output gear (81a) engaged with a first driven gear (51a) of the first connection member (51), and the second output member (81). 82) includes a second output gear (82a) meshing with a second driven gear (52a) included in the second connection member (52), and the first output member (81) and the second output member (82) Each is rotatably supported at two places in the axial direction (L) by the case (3) or a support member (40) fixed to the case (3).

この構成によれば、遊星歯車装置（６０）の第２回転要素（Ｅ２）に連結される第１出力部材（８１）が、ケース（３）又はケース（３）に固定された支持部材（４０）により、軸方向（Ｌ）の２ヶ所で回転自在に支持される。すなわち、第１出力部材（８１）を、軸方向（Ｌ）の２ヶ所のそれぞれで非回転部材により支持することができるため、第１出力部材（８１）が軸方向（Ｌ）の１ヶ所でのみ非回転部材により支持される場合や、第１出力部材（８１）が非回転部材により支持されない場合に比べて、第１出力部材（８１）の支持剛性を高めることができる。従って、第１出力ギヤ（８１ａ）が第１従動ギヤ（５１ａ）から受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置（６０）に与える影響を低減することができる。同様に、遊星歯車装置（６０）の第３回転要素（Ｅ３）に連結される第２出力部材（８２）が、ケース（３）又はケース（３）に固定された支持部材（４０）により、軸方向（Ｌ）の２ヶ所で回転自在に支持されるため、第２出力ギヤ（８２ａ）が第２従動ギヤ（５２ａ）から受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置（６０）に与える影響を低減することができる。
以上のように、上記の構成によれば、第１出力ギヤ（８１ａ）や第２出力ギヤ（８２ａ）が受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置（６０）に与える影響を低減することができる。そのため、遊星歯車装置（６０）に要求される剛性を確保することが容易となり、遊星歯車装置（６０）の小型化を図ることができる。 According to this configuration, the first output member (81) connected to the second rotating element (E2) of the planetary gear device (60) is fixed to the case (3) or the case (3). ) Is rotatably supported at two places in the axial direction (L). That is, since the first output member (81) can be supported by the non-rotational member at each of two places in the axial direction (L), the first output member (81) can be supported at one place in the axial direction (L) The support rigidity of the first output member (81) can be enhanced as compared with the case where the first output member (81) is not supported by the non-rotational member or when the first output member (81) is not supported by the non-rotational member. Therefore, the load received by the first output gear (81a) from the first driven gear (51a) can be properly supported, and the influence of the load on the planetary gear device (60) can be reduced. Similarly, the second output member (82) connected to the third rotating element (E3) of the planetary gear (60) is supported by the case (3) or the support member (40) fixed to the case (3) Since the second output gear (82a) is rotatably supported at two points in the axial direction (L), the load received from the second driven gear (52a) can be properly supported, and the load is a planetary gear device. The influence on (60) can be reduced.
As described above, according to the above configuration, the load received by the first output gear (81a) and the second output gear (82a) can be properly supported, and the load is applied to the planetary gear device (60). The impact can be reduced. Therefore, the rigidity required of the planetary gear device (60) can be easily ensured, and the planetary gear device (60) can be miniaturized.

ここで、前記第１回転電機（１１）及び前記第２回転電機（１２）は、前記第１軸（Ａ１）及び前記第２軸（Ａ２）に平行な第３軸（Ａ３）上に配置されていると好適である。   Here, the first rotating electric machine (11) and the second rotating electric machine (12) are disposed on a third axis (A3) parallel to the first axis (A1) and the second axis (A2). Is preferable.

この構成によれば、第１回転電機（１１）及び第２回転電機（１２）が第１軸（Ａ１）又は第２軸（Ａ２）に配置される場合に比べて、第１回転電機（１１）及び第２回転電機（１２）を伝達装置（２）の軸方向（Ｌ）の配置領域の中心側に寄せて配置しやすくなり、この結果、装置全体の軸方向（Ｌ）の小型化を図りやすくなる。   According to this configuration, compared to the case where the first rotating electric machine (11) and the second rotating electric machine (12) are disposed on the first axis (A1) or the second axis (A2), the first rotating electric machine (11) And the second rotating electric machine (12) can be positioned closer to the center side of the arrangement region in the axial direction (L) of the transmission device (2), and as a result, the axial direction (L) of the entire device can be reduced. It becomes easy to plan.

第１回転電機（１１）と、第２回転電機（１２）と、第１車輪（Ｗ１）に駆動連結される第１連結部材（５１）と、第２車輪（Ｗ２）に駆動連結される第２連結部材（５２）と、前記第１回転電機（１１）のトルクを前記第１連結部材（５１）及び前記第２連結部材（５２）のうちの少なくとも前記第１連結部材（５１）に伝達すると共に、前記第２回転電機（１２）のトルクを前記第１連結部材（５１）及び前記第２連結部材（５２）のうちの少なくとも前記第２連結部材（５２）に伝達する伝達装置（２）と、前記第１回転電機（１１）、前記第２回転電機（１２）、前記第１連結部材（５１）、前記第２連結部材（５２）、及び前記伝達装置（２）を収容するケース（３）と、を備え、前記伝達装置（２）は、第１軸（Ａ１）上に配置され、前記第１回転電機（１１）及び前記第２回転電機（１２）は、前記第１軸（Ａ１）に平行な第３軸（Ａ３）上に配置され、前記伝達装置（２）は、前記第１回転電機（１１）に駆動連結される第１回転要素（Ｅ１）、前記第１連結部材（５１）に駆動連結される第２回転要素（Ｅ２）、前記第２連結部材（５２）に駆動連結される第３回転要素（Ｅ３）、及び、前記第２回転電機（１２）に駆動連結される第４回転要素（Ｅ４）を少なくとも有する遊星歯車装置（６０）と、前記第１回転要素（Ｅ１）に連結される第１入力部材（７１）と、前記第２回転要素（Ｅ２）に連結される第１出力部材（８１）と、前記第３回転要素（Ｅ３）に連結される第２出力部材（８２）と、前記第４回転要素（Ｅ４）に連結される第２入力部材（７２）と、を備え、前記第１入力部材（７１）は、前記第１回転電機（１１）に駆動連結される第１駆動ギヤ（２１ａ）に噛み合う第１入力ギヤ（７１ａ）を備え、前記第２入力部材（７２）は、前記第２回転電機（１２）に駆動連結される第２駆動ギヤ（２２ａ）に噛み合う第２入力ギヤ（７２ａ）を備え、前記第１入力部材（７１）及び前記第２入力部材（７２）のそれぞれが、前記ケース（３）又は前記ケース（３）に固定された支持部材（４０）により、軸方向（Ｌ）の２ヶ所で回転自在に支持されている。   The first rotating electric machine (11), the second rotating electric machine (12), the first connecting member (51) drivingly connected to the first wheel (W1), and the second driving motor connected to the second wheel (W2) The torque of the second connecting member (52) and the first rotating electric machine (11) is transmitted to at least the first connecting member (51) of the first connecting member (51) and the second connecting member (52) And a transmission device (2) for transmitting the torque of the second rotary electric machine (12) to at least the second connection member (52) of the first connection member (51) and the second connection member (52). And a case for housing the first rotating electric machine (11), the second rotating electric machine (12), the first connecting member (51), the second connecting member (52), and the transmission device (2) And the transmission device (2) is disposed on the first axis (A1). The first rotating electric machine (11) and the second rotating electric machine (12) are disposed on a third axis (A3) parallel to the first axis (A1), and the transmission device (2) is A first rotating element (E1) drivingly connected to the first rotating electric machine (11), a second rotating element (E2) drivingly connected to the first connecting member (51), the second connecting member (52) A planetary gear device (60) including at least a third rotating element (E3) drivingly connected to the second rotating electric machine (12) and a fourth rotating element (E4) drivingly connected to the second rotating electric machine (12); The first input member (71) connected to the element (E1), the first output member (81) connected to the second rotating element (E2), and the third rotating element (E3) A second output member (82) and a second input member (72) connected to the fourth rotating element (E4) And the first input member (71) includes a first input gear (71a) engaged with a first drive gear (21a) drivingly connected to the first rotating electric machine (11), and the second input member (71). The input member (72) includes a second input gear (72a) meshing with a second drive gear (22a) drivingly connected to the second rotary electric machine (12), and the first input member (71) and the first input member (71) Each of the two input members (72) is rotatably supported at two places in the axial direction (L) by the case (3) or a support member (40) fixed to the case (3).

この構成によれば、遊星歯車装置（６０）の第１回転要素（Ｅ１）に連結される第１入力部材（７１）が、ケース（３）又はケース（３）に固定された支持部材（４０）により、軸方向（Ｌ）の２ヶ所で回転自在に支持される。すなわち、第１入力部材（７１）を、軸方向（Ｌ）の２ヶ所のそれぞれで非回転部材により支持することができるため、第１入力部材（７１）が軸方向（Ｌ）の１ヶ所でのみ非回転部材により支持される場合や、第１入力部材（７１）が非回転部材により支持されない場合に比べて、第１入力部材（７１）の支持剛性を高めることができる。従って、第１入力ギヤ（７１ａ）が第１駆動ギヤ（２１ａ）から受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置（６０）に与える影響を低減することができる。同様に、遊星歯車装置（６０）の第４回転要素（Ｅ４）に連結される第２入力部材（７２）が、ケース（３）又はケース（３）に固定された支持部材（４０）により、軸方向（Ｌ）の２ヶ所で回転自在に支持されるため、第２入力ギヤ（７２ａ）が第２駆動ギヤ（２２ａ）から受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置（６０）に与える影響を低減することができる。
以上のように、上記の構成によれば、第１入力ギヤ（７１ａ）や第２入力ギヤ（７２ａ）が受ける荷重を適切に支持することができ、当該荷重が遊星歯車装置（６０）に与える影響を低減することができる。そのため、遊星歯車装置（６０）に要求される剛性を確保することが容易となり、遊星歯車装置（６０）の小型化を図ることができる。 According to this configuration, the first input member (71) connected to the first rotation element (E1) of the planetary gear device (60) is fixed to the case (3) or the case (3). ) Is rotatably supported at two places in the axial direction (L). That is, since the first input member (71) can be supported by the non-rotational member at each of two places in the axial direction (L), the first input member (71) can be supported at one place in the axial direction (L) The support rigidity of the first input member (71) can be enhanced as compared with the case where the first input member (71) is not supported by the non-rotational member or when the first input member (71) is not supported by the non-rotational member. Therefore, the load received by the first input gear (71a) from the first drive gear (21a) can be properly supported, and the influence of the load on the planetary gear device (60) can be reduced. Similarly, a second input member (72) connected to the fourth rotating element (E4) of the planetary gear device (60) is supported by the case (3) or the support member (40) fixed to the case (3) Since the second input gear (72a) is rotatably supported at two points in the axial direction (L), the load received from the second drive gear (22a) can be appropriately supported, and the load is a planetary gear The influence on (60) can be reduced.
As described above, according to the above configuration, the load received by the first input gear (71a) and the second input gear (72a) can be appropriately supported, and the load is applied to the planetary gear device (60). The impact can be reduced. Therefore, the rigidity required of the planetary gear device (60) can be easily ensured, and the planetary gear device (60) can be miniaturized.

ここで、前記第１連結部材（５１）及び前記第２連結部材（５２）は、前記第１軸（Ａ１）及び前記第３軸（Ａ３）に平行な第２軸（Ａ２）上に配置されていると好適である。   Here, the first connection member (51) and the second connection member (52) are disposed on a second axis (A2) parallel to the first axis (A1) and the third axis (A3). Is preferable.

この構成によれば、第１連結部材（５１）及び第２連結部材（５２）が第１軸（Ａ１）又は第３軸（Ａ３）に配置される場合に比べて、第１連結部材（５１）及び第２連結部材（５２）を伝達装置（２）の軸方向（Ｌ）の配置領域の中心側に寄せて配置しやすくなり、この結果、装置全体の軸方向（Ｌ）の小型化を図りやすくなる。   According to this configuration, the first connection member (51) is compared to the case where the first connection member (51) and the second connection member (52) are disposed on the first axis (A1) or the third axis (A3). And the second connecting member (52) can be arranged closer to the center side of the arrangement region in the axial direction (L) of the transmission device (2), and as a result, the axial direction (L) of the entire device can be reduced. It becomes easy to plan.

ここで、前記遊星歯車装置（６）は、第１サンギヤ（Ｓ１）、第１キャリヤ（Ｃ１）、及び第１リングギヤ（Ｒ１）を有する第１遊星歯車機構（６１）と、第２サンギヤ（Ｓ２）、第２キャリヤ（Ｃ２）、及び第２リングギヤ（Ｒ２）を有する第２遊星歯車機構（６２）と、を備え、前記第１回転要素（Ｅ１）は、前記第１リングギヤ（Ｒ１）であり、前記第２回転要素（Ｅ２）は、一体的に回転する前記第１キャリヤ（Ｃ１）と前記第２サンギヤ（Ｓ２）であり、前記第３回転要素（Ｅ３）は、一体的に回転する前記第１サンギヤ（Ｓ１）と前記第２キャリヤ（Ｃ２）であり、前記第４回転要素（Ｅ４）は、前記第２リングギヤ（Ｒ２）であると好適である。   Here, the planetary gear unit (6) includes a first planetary gear mechanism (61) having a first sun gear (S1), a first carrier (C1), and a first ring gear (R1), and a second sun gear (S2). A second planetary gear mechanism (62) having a second carrier (C2) and a second ring gear (R2), and the first rotating element (E1) is the first ring gear (R1) The second rotating element (E2) is the first carrier (C1) and the second sun gear (S2) that rotate integrally, and the third rotating element (E3) rotates the integrally. Preferably, the first sun gear (S1) and the second carrier (C2), and the fourth rotating element (E4) is the second ring gear (R2).

この構成によれば、回転速度の順が、第１回転電機（１１）に駆動連結される第１回転要素（Ｅ１）、第１連結部材（５１）に駆動連結される第２回転要素（Ｅ２）、第２連結部材（５２）に駆動連結される第３回転要素（Ｅ３）、第２回転電機（１２）に駆動連結される第４回転要素（Ｅ４）の順となるため、第１回転電機（１１）及び第２回転電機（１２）のトルクを、伝達装置（２）により第１連結部材（５１）及び第２連結部材（５２）に分配して伝達することができる。よって、第１回転電機（１１）と第１連結部材（５１）との間の動力伝達経路と第２回転電機（１２）と第２連結部材（５２）との間の動力伝達経路とが分離されている場合に比べて、車両の旋回時の走行性能の向上を図ることができる。   According to this configuration, the first rotating element (E1) that is drivingly connected to the first rotating electric machine (11) and the second rotating element (E2) that is drivingly connected to the first connecting member (51) in order of rotational speed , The third rotation element (E3) drivingly connected to the second connecting member (52), and the fourth rotation element (E4) drivingly connected to the second rotating electric machine (12), so that the first rotation The torque of the electric machine (11) and the second rotating electric machine (12) can be distributed and transmitted to the first connecting member (51) and the second connecting member (52) by the transmission device (2). Therefore, the power transmission path between the first rotary electric machine (11) and the first connection member (51) and the power transmission path between the second rotary electric machine (12) and the second connection member (52) are separated. The traveling performance at the time of turning of the vehicle can be improved as compared with the case where the vehicle is driven.

上記のように前記遊星歯車装置（６０）が前記第１遊星歯車機構（６１）と前記第２遊星歯車機構（６２）とを備える構成において、前記第１遊星歯車機構（６１）は、前記第２遊星歯車機構（６２）に対して前記軸方向（Ｌ）の一方側である軸方向第１側（Ｌ１）に配置され、前記第１出力部材（８１）は、前記第１遊星歯車機構（６１）に対して前記軸方向第１側（Ｌ１）に配置され、前記第２出力部材（８２）は、前記第２遊星歯車機構（６２）に対して前記軸方向（Ｌ）における前記軸方向第１側（Ｌ１）とは反対側である軸方向第２側（Ｌ２）に配置され、前記第１出力部材（８１）は、前記第１キャリヤ（Ｃ１）に対して前記軸方向（Ｌ）に相対移動可能に連結され、前記第２出力部材（８２）は、前記第２キャリヤ（Ｃ２）に対して前記軸方向（Ｌ）に相対移動可能に連結されていると好適である。   As described above, in the configuration in which the planetary gear device (60) includes the first planetary gear mechanism (61) and the second planetary gear mechanism (62), the first planetary gear mechanism (61) includes the first planetary gear mechanism (61). The first planetary gear mechanism (62) is disposed on a first axial direction side (L1) which is one side of the axial direction (L) with respect to the second planetary gear mechanism (62), and the first output member (81) 61) with respect to the first axial direction (L1) and the second output member (82) is the axial direction in the axial direction (L) with respect to the second planetary gear mechanism (62) The first output member (81) is disposed on the second side (L2) in the axial direction opposite to the first side (L1), and the first output member (81) is in the axial direction (L) with respect to the first carrier (C1). And the second output member (82) is connected to the second carrier (C2). It is preferable to have a relatively movably connected in the axial direction (L) and.

この構成によれば、第１出力部材（８１）が第１キャリヤ（Ｃ１）に対して軸方向（Ｌ）に相対移動可能に連結されるため、第１出力部材（８１）と第１キャリヤ（Ｃ１）とが一体的に形成される場合等、第１出力部材（８１）と第１キャリヤ（Ｃ１）とが軸方向（Ｌ）に相対移動不能な場合に比べて、第１出力部材（８１）と第１キャリヤ（Ｃ１）との連結部（６６ａ）における荷重の伝達を低減することができる。これにより、第１出力ギヤ（８１ａ）が第１従動ギヤ（５１ａ）から荷重を受けることに起因して第１出力部材（８１）から第１キャリヤ（Ｃ１）に伝達される荷重を低減することができる。同様に、上記の構成によれば、第２出力部材（８２）が第２キャリヤ（Ｃ２）に対して軸方向（Ｌ）に相対移動可能に連結されるため、第２出力ギヤ（８２ａ）が第２従動ギヤ（５２ａ）から荷重を受けることに起因して第２出力部材（８２）から第２キャリヤ（Ｃ２）に伝達される荷重を低減することができる。この結果、第１キャリヤ（Ｃ１）や第２キャリヤ（Ｃ２）に要求される剛性を確保することが容易となり、第１遊星歯車機構（６１）や第２遊星歯車機構（６２）の小型化を図ることができる。   According to this configuration, the first output member (81) and the first carrier (C1) are connected so as to be movable relative to the first carrier (C1) in the axial direction (L). When the first output member 81 and the first carrier C1 can not move relative to each other in the axial direction L, such as when C1) is integrally formed, the first output member 81 Transfer of the load at the connecting portion (66a) of the first carrier (C1) with the first carrier (C1) can be reduced. Thereby, the load transmitted from the first output member (81) to the first carrier (C1) due to the first output gear (81a) receiving a load from the first driven gear (51a) is reduced. Can. Similarly, according to the above configuration, since the second output member (82) is coupled so as to be movable relative to the second carrier (C2) in the axial direction (L), the second output gear (82a) The load transmitted from the second output member (82) to the second carrier (C2) due to receiving the load from the second driven gear (52a) can be reduced. As a result, the rigidity required for the first carrier (C1) and the second carrier (C2) can be easily secured, and the first planetary gear mechanism (61) and the second planetary gear mechanism (62) can be miniaturized. Can be

上記の各構成の車両用駆動装置（１）において、前記ケース（３）の内部にそれぞれ配置された前記支持部材（４０）である第１支持部材（４１）及び第２支持部材（４２）を備え、前記第１支持部材（４１）に、前記第１入力部材（７１）の支持部（４１ｃ）及び前記第１出力部材（８１）の支持部（４１ｂ）が形成され、前記第２支持部材（４２）に、前記第２入力部材（７２）の支持部（４２ｃ）及び前記第２出力部材（８２）の支持部（４２ｂ）が形成されていると好適である。   In the vehicle drive device (1) of each configuration described above, the first support member (41) and the second support member (42), which are the support members (40) respectively disposed inside the case (3) A support portion (41c) of the first input member (71) and a support portion (41b) of the first output member (81) are formed on the first support member (41), and the second support member Preferably, the supporting portion (42c) of the second input member (72) and the supporting portion (42b) of the second output member (82) are formed in (42).

この構成によれば、第１支持部材（４１）に、第１入力部材（７１）の支持部（４１ｃ）及び第１出力部材（８１）の支持部（４１ｂ）の双方が形成されるため、これらの支持部（４１ｃ，４１ｂ）が互いに異なる支持部材に形成される場合に比べて、部品点数を少なく抑えることができると共に、第１入力部材（７１）と第１出力部材（８１）との相対位置の精度を確保することが容易となる。同様に、上記の構成によれば、第２支持部材（４２）に、第２入力部材（７２）の支持部（４２ｃ）及び第２出力部材（８２）の支持部（４２ｂ）の双方が形成されるため、これらの支持部（４２ｃ，４２ｂ）が互いに異なる支持部材に形成される場合に比べて、部品点数を少なく抑えることができると共に、第２入力部材（７２）と第２出力部材（８２）との相対位置の精度を確保することが容易となる。   According to this configuration, both the support portion (41c) of the first input member (71) and the support portion (41b) of the first output member (81) are formed on the first support member (41). As compared with the case where these support portions (41c, 41b) are formed on different support members, the number of parts can be reduced, and the first input member (71) and the first output member (81) It becomes easy to ensure the accuracy of the relative position. Similarly, according to the above configuration, both the support portion (42c) of the second input member (72) and the support portion (42b) of the second output member (82) are formed on the second support member (42). Therefore, the number of parts can be reduced as compared with the case where these support portions (42c, 42b) are formed on different support members, and the second input member (72) and the second output member ( This makes it easy to ensure the accuracy of the relative position with respect to the above 82).

上記のように前記車両用駆動装置（１）が前記第１支持部材（４１）及び前記第２支持部材（４２）を備える構成において、前記第１支持部材（４１）と前記第１入力部材（７１）との間に配置される軸受（Ｂ９）と、前記第１支持部材（４１）と前記第１出力部材（８１）との間に配置される軸受（Ｂ６）とが、前記第１軸（Ａ１）を基準とする径方向（Ｒ）視で互いに重複するように配置され、前記第２支持部材（４２）と前記第２入力部材（７２）との間に配置される軸受（Ｂ１２）と、前記第２支持部材（４２）と前記第２出力部材（８２）との間に配置される軸受（Ｂ７）とが、前記径方向（Ｒ）視で互いに重複するように配置されていると好適である。   As described above, in the configuration in which the vehicle drive device (1) includes the first support member (41) and the second support member (42), the first support member (41) and the first input member ( 71), and a bearing (B9) disposed between the first shaft and the first shaft, and a bearing (B6) disposed between the first support member (41) and the first output member (81) Bearings (B12) disposed so as to overlap each other in the radial direction (R) with respect to (A1) and disposed between the second support member (42) and the second input member (72) And a bearing (B7) disposed between the second support member (42) and the second output member (82) are disposed so as to overlap with each other in the radial direction (R). Is preferred.

この構成によれば、第１支持部材（４１）と第１入力部材（７１）との間に配置される軸受（Ｂ９）と、第１支持部材（４１）と第１出力部材（８１）との間に配置される軸受（Ｂ６）とが、径方向（Ｒ）視で重複する分、伝達装置（２）が占有するスペースを軸方向（Ｌ）に小さくできる。また、上記の構成によれば、第２支持部材（４２）と第２入力部材（７２）との間に配置される軸受（Ｂ１２）と、第２支持部材（４２）と第２出力部材（８２）との間に配置される軸受（Ｂ７）とが、径方向（Ｒ）視で重複する分、伝達装置（２）が占有するスペースを軸方向（Ｌ）に小さくできる。   According to this configuration, the bearing (B9) disposed between the first support member (41) and the first input member (71), the first support member (41) and the first output member (81) The space occupied by the transmission device (2) can be reduced in the axial direction (L) by the amount that the bearings (B6) arranged between the two overlap in the radial direction (R) view. Further, according to the above configuration, the bearing (B12) disposed between the second support member (42) and the second input member (72), the second support member (42) and the second output member ( The space occupied by the transmission device (2) can be made smaller in the axial direction (L) by the amount that the bearing (B7) disposed between 82 and 82 overlaps in the radial direction (R) view.

上記の各構成の車両用駆動装置（１）において、前記遊星歯車装置（６０）は、第１遊星歯車機構（６１）と第２遊星歯車機構（６２）とを連結して構成され、前記第１入力部材（７１）、前記第２入力部材（７２）、前記第１出力部材（８１）、及び前記第２出力部材（８２）のそれぞれは、前記ケース（３）又は前記支持部材（４０）により回転自在に支持され、前記第１遊星歯車機構（６１）の回転要素と前記第２遊星歯車機構（６２）の回転要素との連結部（６３）が、前記第１軸（Ａ１）を基準とする径方向（Ｒ）に隙間を有する連結構造となっていると好適である。   In the vehicle drive device (1) of each configuration described above, the planetary gear device (60) is configured by connecting a first planetary gear mechanism (61) and a second planetary gear mechanism (62), and Each of the one input member (71), the second input member (72), the first output member (81), and the second output member (82) is the case (3) or the support member (40). Is rotatably supported, and a connecting portion (63) of the rotary element of the first planetary gear mechanism (61) and the rotary element of the second planetary gear mechanism (62) is based on the first axis (A1). It is preferable that the connecting structure has a gap in the radial direction (R).

この構成によれば、第１入力部材（７１）、第２入力部材（７２）、第１出力部材（８１）、及び第２出力部材（８２）のそれぞれが、ケース（３）又は支持部材（４０）により回転自在に支持されるため、第１入力部材（７１）に連結される第１回転要素（Ｅ１）、第２入力部材（７２）に連結される第４回転要素（Ｅ４）、第１出力部材（８１）に連結される第２回転要素（Ｅ２）、及び、第２出力部材（８２）に連結される第３回転要素（Ｅ３）のそれぞれの支持精度を適切に確保することができる。その上で、上記の構成によれば、第１遊星歯車機構（６１）の回転要素と第２遊星歯車機構（６２）の回転要素との連結部（６３）が、径方向（Ｒ）に隙間を有する連結構造となっているため、各部品の径方向（Ｒ）における寸法誤差や組付誤差を連結部（６３）で吸収することができ、第１遊星歯車機構（６１）や第２遊星歯車機構（６２）におけるギヤの噛み合い部に過大な荷重（偏荷重等）が作用することを回避しやすくなる。   According to this configuration, each of the first input member (71), the second input member (72), the first output member (81), and the second output member (82) corresponds to the case (3) or the support member ( 40) to be rotatably supported, the first rotating element (E1) connected to the first input member (71), the fourth rotating element (E4) connected to the second input member (72), Properly secure the support accuracy of each of the second rotating element (E2) connected to the one output member (81) and the third rotating element (E3) connected to the second output member (82) it can. Furthermore, according to the above configuration, the connecting portion (63) of the rotary element of the first planetary gear mechanism (61) and the rotary element of the second planetary gear mechanism (62) is a gap in the radial direction (R) (1), so that dimensional errors and assembly errors in the radial direction (R) of each component can be absorbed by the connecting portion (63), and the first planetary gear mechanism (61) and the second planetary gear It becomes easy to avoid that an excessive load (bias load etc.) acts on the meshing part of the gear in the gear mechanism (62).

また、前記遊星歯車装置（６０）は、第１ピニオン軸受（Ｂ１３）を介して第１ピニオンギヤ（Ｐ１）を回転自在に支持する第１キャリヤ（Ｃ１）を有する第１遊星歯車機構（６１）と、第２ピニオン軸受（Ｂ１４）を介して第２ピニオンギヤ（Ｐ２）を回転自在に支持する第２キャリヤ（Ｃ２）を有する第２遊星歯車機構（６２）と、を備え、前記第１出力部材（８１）は、前記第１キャリヤ（Ｃ１）に連結されると共に第１出力軸受（Ｂ６）を介して回転自在に支持され、前記第２出力部材（８２）は、前記第２キャリヤ（Ｃ２）に連結されると共に第２出力軸受（Ｂ７）を介して回転自在に支持され、前記第１キャリヤ（Ｃ１）に、前記第１ピニオン軸受（Ｂ１３）に油を供給するための油路（９１）と、前記第１出力軸受（Ｂ６）に油を供給するための油路（９２）とが形成され、前記第２キャリヤ（Ｃ２）に、前記第２ピニオン軸受（Ｂ１４）に油を供給するための油路（９３）と、前記第２出力軸受（Ｂ７）に油を供給するための油路（９４）とが形成されていると好適である。   The planetary gear set (60) has a first planetary gear mechanism (61) having a first carrier (C1) rotatably supporting the first pinion gear (P1) via the first pinion bearing (B13). A second planetary gear mechanism (62) having a second carrier (C2) rotatably supporting the second pinion gear (P2) via the second pinion bearing (B14); 81) is connected to the first carrier (C1) and rotatably supported via the first output bearing (B6), and the second output member (82) is connected to the second carrier (C2) An oil passage (91), which is connected and rotatably supported via a second output bearing (B7), for supplying oil to the first pinion bearing (B13) to the first carrier (C1) The first output bearing (B6) And an oil passage (92) for supplying oil to the second carrier (C2), and an oil passage (93) for supplying oil to the second pinion bearing (B14); It is preferable that an oil passage (94) for supplying oil to the bearing (B7) is formed.

この構成によれば、第１出力軸受（Ｂ６）に油を供給するための油路（９２）が、第１ピニオン軸受（Ｂ１３）に油を供給するための油路（９１）と同様に第１キャリヤ（Ｃ１）に形成されるため、これらの油路（９１，９２）に対する油の供給構造を共通化して、油路構成の簡素化を図ることができる。同様に、上記の構成によれば、第２出力軸受（Ｂ７）に油を供給するための油路（９４）が、第２ピニオン軸受（Ｂ１４）に油を供給するための油路（９３）と同様に第２キャリヤ（Ｃ２）に形成されるため、これらの油路（９３，９４）に対する油の供給構造を共通化して、油路構成の簡素化を図ることができる。   According to this configuration, the oil passage (92) for supplying the oil to the first output bearing (B6) is the same as the oil passage (91) for supplying the oil to the first pinion bearing (B13). Since it is formed in one carrier (C1), the oil supply structure to these oil passages (91, 92) can be made common, and the oil passage configuration can be simplified. Similarly, according to the above configuration, the oil passage (94) for supplying oil to the second output bearing (B7) and the oil passage (93) for supplying oil to the second pinion bearing (B14) Similarly to the above, since the second carrier (C2) is formed, the oil supply structure to these oil passages (93, 94) can be made common, and the oil passage configuration can be simplified.

本開示に係る車両用駆動装置は、上述した各効果のうち、少なくとも１つを奏することができれば良い。   The vehicle drive device according to the present disclosure only needs to be able to exhibit at least one of the above-described effects.

１：車両用駆動装置
２：伝達装置
３：ケース
１１：第１回転電機
１２：第２回転電機
２１ａ：第１駆動ギヤ
２２ａ：第２駆動ギヤ
４０：支持部材
４１：第１支持部材
４１ｂ：第７支持部（第１出力部材の支持部）
４１ｃ：第９支持部（第１入力部材の支持部）
４２：第２支持部材
４２ｂ：第８支持部（第２出力部材の支持部）
４２ｃ：第１０支持部（第２入力部材の支持部）
５１：第１連結部材
５１ａ：第１従動ギヤ
５２：第２連結部材
５２ａ：第２従動ギヤ
６０：遊星歯車装置
６１：第１遊星歯車機構
６２：第２遊星歯車機構
６３：連結部
７１：第１入力部材
７１ａ：第１入力ギヤ
７２：第２入力部材
７２ａ：第２入力ギヤ
８１：第１出力部材
８１ａ：第１出力ギヤ
８２：第２出力部材
８２ａ：第２出力ギヤ
９１：第１油路（第１ピニオン軸受に油を供給するための油路）
９２：第２油路（第１出力軸受に油を供給するための油路）
９３：第３油路（第２ピニオン軸受に油を供給するための油路）
９４：第４油路（第２出力軸受に油を供給するための油路）
Ａ１：第１軸
Ａ２：第２軸
Ａ３：第３軸
Ｂ６：第６軸受（第１支持部材と第１出力部材との間に配置される軸受、第１出力軸受）
Ｂ７：第７軸受（第２支持部材と第２出力部材との間に配置される軸受、第２出力軸受）
Ｂ９：第９軸受（第１支持部材と第１入力部材との間に配置される軸受）
Ｂ１２：第１２軸受（第２支持部材と第２入力部材との間に配置される軸受）
Ｂ１３：第１３軸受（第１ピニオン軸受）
Ｂ１４：第１４軸受（第２ピニオン軸受）
Ｃ１：第１キャリヤ
Ｃ２：第２キャリヤ
Ｅ１：第１回転要素
Ｅ２：第２回転要素
Ｅ３：第３回転要素
Ｅ４：第４回転要素
Ｌ：軸方向
Ｌ１：軸方向第１側
Ｌ２：軸方向第２側
Ｐ１：第１ピニオンギヤ
Ｐ２：第２ピニオンギヤ
Ｒ１：第１リングギヤ
Ｒ２：第２リングギヤ
Ｓ１：第１サンギヤ
Ｓ２：第２サンギヤ
Ｗ１：第１車輪
Ｗ２：第２車輪 1: Vehicle drive device 2: Transmission device 3: Case 11: first rotary electric machine 12: second rotary electric machine 21a: first drive gear 22a: second drive gear 40: support member 41: first support member 41b: first 7 support portion (support portion of first output member)
41c: ninth support portion (support portion of first input member)
42: second support member 42b: eighth support portion (support portion of second output member)
42c: tenth support (support for second input member)
51: first connecting member 51a: first driven gear 52: second connecting member 52a: second driven gear 60: planetary gear device 61: first planetary gear mechanism 62: second planetary gear mechanism 63: connecting portion 71: first 1 input member 71a: first input gear 72: second input member 72a: second input gear 81: first output member 81a: first output gear 82: second output member 82a: second output gear 91: first oil Road (oil path for supplying oil to the first pinion bearing)
92: Second oil passage (oil passage for supplying oil to the first output bearing)
93: Third oil passage (oil passage for supplying oil to the second pinion bearing)
94: Fourth oil passage (oil passage for supplying oil to the second output bearing)
A1: first axis A2: second axis A3: third axis B6: sixth bearing (bearing disposed between first support member and first output member, first output bearing)
B7: Seventh bearing (bearing disposed between second support member and second output member, second output bearing)
B9: ninth bearing (a bearing disposed between the first support member and the first input member)
B12: Twelfth bearing (a bearing disposed between the second support member and the second input member)
B13: Thirteenth bearing (first pinion bearing)
B14: 14th bearing (2nd pinion bearing)
C1: first carrier C2: second carrier E1: first rotating element E2: second rotating element E3: third rotating element E4: fourth rotating element L: axial direction L1: axial first side L2: axial first 2 side P1: first pinion gear P2: second pinion gear R1: first ring gear R2: second ring gear S1: first sun gear S2: second sun gear W1: first wheel W2: second wheel

Claims (10)

第１回転電機と、
第２回転電機と、
第１車輪に駆動連結される第１連結部材と、
第２車輪に駆動連結される第２連結部材と、
前記第１回転電機のトルクを前記第１連結部材及び前記第２連結部材のうちの少なくとも前記第１連結部材に伝達すると共に、前記第２回転電機のトルクを前記第１連結部材及び前記第２連結部材のうちの少なくとも前記第２連結部材に伝達する伝達装置と、
前記第１回転電機、前記第２回転電機、前記第１連結部材、前記第２連結部材、及び前記伝達装置を収容するケースと、を備え、
前記伝達装置は、第１軸上に配置され、
前記第１連結部材及び前記第２連結部材は、前記第１軸に平行な第２軸上に配置され、
前記伝達装置は、前記第１回転電機に駆動連結される第１回転要素、前記第１連結部材に駆動連結される第２回転要素、前記第２連結部材に駆動連結される第３回転要素、及び、前記第２回転電機に駆動連結される第４回転要素を少なくとも有する遊星歯車装置と、前記第１回転要素に連結される第１入力部材と、前記第２回転要素に連結される第１出力部材と、前記第３回転要素に連結される第２出力部材と、前記第４回転要素に連結される第２入力部材と、を備え、
前記第１出力部材は、前記第１連結部材が備える第１従動ギヤに噛み合う第１出力ギヤを備え、
前記第２出力部材は、前記第２連結部材が備える第２従動ギヤに噛み合う第２出力ギヤを備え、
前記第１出力部材及び前記第２出力部材のそれぞれが、前記ケース又は前記ケースに固定された支持部材により、軸方向の２ヶ所で回転自在に支持されている車両用駆動装置。 First electric rotating machine,
Second rotating electric machine,
A first connecting member drivingly connected to the first wheel;
A second connecting member drivingly connected to the second wheel;
The torque of the first rotating electric machine is transmitted to at least the first connecting member of the first connecting member and the second connecting member, and the torque of the second rotating electric machine is transmitted to the first connecting member and the second A transmission device for transmitting to at least the second connection member of the connection members;
And a case for containing the first rotating electric machine, the second rotating electric machine, the first connecting member, the second connecting member, and the transmission device.
The transmission device is disposed on a first axis,
The first connection member and the second connection member are disposed on a second axis parallel to the first axis,
The transmission device includes a first rotating element drivingly connected to the first rotating electric machine, a second rotating element drivingly connected to the first connecting member, and a third rotating element drivingly connected to the second connecting member. A planetary gear set having at least a fourth rotating element drivingly connected to the second rotating electric machine, a first input member connected to the first rotating element, and a first connected to the second rotating element An output member, a second output member connected to the third rotation element, and a second input member connected to the fourth rotation element;
The first output member includes a first output gear engaged with a first driven gear provided in the first connection member,
The second output member includes a second output gear engaged with a second driven gear provided in the second connection member,
The vehicle drive device in which each of the first output member and the second output member is rotatably supported at two places in the axial direction by the case or a support member fixed to the case. 前記第１回転電機及び前記第２回転電機は、前記第１軸及び前記第２軸に平行な第３軸上に配置されている請求項１に記載の車両用駆動装置。   The vehicle drive device according to claim 1, wherein the first rotating electrical machine and the second rotating electrical machine are disposed on a third axis parallel to the first axis and the second axis. 第１回転電機と、
第２回転電機と、
第１車輪に駆動連結される第１連結部材と、
第２車輪に駆動連結される第２連結部材と、
前記第１回転電機のトルクを前記第１連結部材及び前記第２連結部材のうちの少なくとも前記第１連結部材に伝達すると共に、前記第２回転電機のトルクを前記第１連結部材及び前記第２連結部材のうちの少なくとも前記第２連結部材に伝達する伝達装置と、
前記第１回転電機、前記第２回転電機、前記第１連結部材、前記第２連結部材、及び前記伝達装置を収容するケースと、を備え、
前記伝達装置は、第１軸上に配置され、
前記第１回転電機及び前記第２回転電機は、前記第１軸に平行な第３軸上に配置され、
前記伝達装置は、前記第１回転電機に駆動連結される第１回転要素、前記第１連結部材に駆動連結される第２回転要素、前記第２連結部材に駆動連結される第３回転要素、及び、前記第２回転電機に駆動連結される第４回転要素を少なくとも有する遊星歯車装置と、前記第１回転要素に連結される第１入力部材と、前記第２回転要素に連結される第１出力部材と、前記第３回転要素に連結される第２出力部材と、前記第４回転要素に連結される第２入力部材と、を備え、
前記第１入力部材は、前記第１回転電機に駆動連結される第１駆動ギヤに噛み合う第１入力ギヤを備え、
前記第２入力部材は、前記第２回転電機に駆動連結される第２駆動ギヤに噛み合う第２入力ギヤを備え、
前記第１入力部材及び前記第２入力部材のそれぞれが、前記ケース又は前記ケースに固定された支持部材により、軸方向の２ヶ所で回転自在に支持されている車両用駆動装置。 First electric rotating machine,
Second rotating electric machine,
A first connecting member drivingly connected to the first wheel;
A second connecting member drivingly connected to the second wheel;
The torque of the first rotating electric machine is transmitted to at least the first connecting member of the first connecting member and the second connecting member, and the torque of the second rotating electric machine is transmitted to the first connecting member and the second A transmission device for transmitting to at least the second connection member of the connection members;
And a case for containing the first rotating electric machine, the second rotating electric machine, the first connecting member, the second connecting member, and the transmission device.
The transmission device is disposed on a first axis,
The first rotating electric machine and the second rotating electric machine are disposed on a third axis parallel to the first axis,
The transmission device includes a first rotating element drivingly connected to the first rotating electric machine, a second rotating element drivingly connected to the first connecting member, and a third rotating element drivingly connected to the second connecting member. A planetary gear set having at least a fourth rotating element drivingly connected to the second rotating electric machine, a first input member connected to the first rotating element, and a first connected to the second rotating element An output member, a second output member connected to the third rotation element, and a second input member connected to the fourth rotation element;
The first input member includes a first input gear that meshes with a first drive gear that is drivingly connected to the first rotating electrical machine.
The second input member includes a second input gear that meshes with a second drive gear that is drivingly connected to the second rotating electrical machine.
The vehicle drive device in which each of the first input member and the second input member is rotatably supported at two places in the axial direction by the case or a support member fixed to the case. 前記第１連結部材及び前記第２連結部材は、前記第１軸及び前記第３軸に平行な第２軸上に配置されている請求項３に記載の車両用駆動装置。   The vehicle drive device according to claim 3, wherein the first connection member and the second connection member are disposed on a second axis parallel to the first axis and the third axis. 前記遊星歯車装置は、第１サンギヤ、第１キャリヤ、及び第１リングギヤを有する第１遊星歯車機構と、第２サンギヤ、第２キャリヤ、及び第２リングギヤを有する第２遊星歯車機構と、を備え、
前記第１回転要素は、前記第１リングギヤであり、
前記第２回転要素は、一体的に回転する前記第１キャリヤと前記第２サンギヤであり、
前記第３回転要素は、一体的に回転する前記第１サンギヤと前記第２キャリヤであり、
前記第４回転要素は、前記第２リングギヤである請求項１から４のいずれか一項に記載の車両用駆動装置。 The planetary gear set includes a first planetary gear mechanism having a first sun gear, a first carrier, and a first ring gear, and a second planetary gear mechanism having a second sun gear, a second carrier, and a second ring gear. ,
The first rotating element is the first ring gear,
The second rotating element is the first carrier and the second sun gear, which rotate together.
The third rotating element is the first sun gear and the second carrier that rotate together.
The vehicle drive device according to any one of claims 1 to 4, wherein the fourth rotating element is the second ring gear. 前記第１遊星歯車機構は、前記第２遊星歯車機構に対して前記軸方向の一方側である軸方向第１側に配置され、
前記第１出力部材は、前記第１遊星歯車機構に対して前記軸方向第１側に配置され、
前記第２出力部材は、前記第２遊星歯車機構に対して前記軸方向における前記軸方向第１側とは反対側である軸方向第２側に配置され、
前記第１出力部材は、前記第１キャリヤに対して前記軸方向に相対移動可能に連結され、
前記第２出力部材は、前記第２キャリヤに対して前記軸方向に相対移動可能に連結されている請求項５に記載の車両用駆動装置。 The first planetary gear mechanism is disposed on an axial first side which is one side of the second planetary gear mechanism in the axial direction,
The first output member is disposed on the first side in the axial direction with respect to the first planetary gear mechanism,
The second output member is disposed on an axial second side opposite to the first axial side in the axial direction with respect to the second planetary gear mechanism.
The first output member is connected so as to be movable relative to the first carrier in the axial direction,
The vehicle drive device according to claim 5, wherein the second output member is coupled to the second carrier so as to be relatively movable in the axial direction. 前記ケースの内部にそれぞれ配置された前記支持部材である第１支持部材及び第２支持部材を備え、
前記第１支持部材に、前記第１入力部材の支持部及び前記第１出力部材の支持部が形成され、
前記第２支持部材に、前記第２入力部材の支持部及び前記第２出力部材の支持部が形成されている請求項１から６のいずれか一項に記載の車両用駆動装置。 And a first support member and a second support member, which are the support members respectively disposed inside the case,
A support portion of the first input member and a support portion of the first output member are formed on the first support member,
The vehicle drive device according to any one of claims 1 to 6, wherein a support portion of the second input member and a support portion of the second output member are formed on the second support member. 前記第１支持部材と前記第１入力部材との間に配置される軸受と、前記第１支持部材と前記第１出力部材との間に配置される軸受とが、前記第１軸を基準とする径方向視で互いに重複するように配置され、
前記第２支持部材と前記第２入力部材との間に配置される軸受と、前記第２支持部材と前記第２出力部材との間に配置される軸受とが、前記径方向視で互いに重複するように配置されている請求項７に記載の車両用駆動装置。 A bearing disposed between the first support member and the first input member, and a bearing disposed between the first support member and the first output member are based on the first axis. Are arranged to overlap each other in the radial direction
A bearing disposed between the second support member and the second input member, and a bearing disposed between the second support member and the second output member overlap each other in the radial direction. The vehicle drive device according to claim 7, which is arranged to 前記遊星歯車装置は、第１遊星歯車機構と第２遊星歯車機構とを連結して構成され、
前記第１入力部材、前記第２入力部材、前記第１出力部材、及び前記第２出力部材のそれぞれは、前記ケース又は前記支持部材により回転自在に支持され、
前記第１遊星歯車機構の回転要素と前記第２遊星歯車機構の回転要素との連結部が、前記第１軸を基準とする径方向に隙間を有する連結構造となっている請求項１から８のいずれか一項に記載の車両用駆動装置。 The planetary gear device is configured by connecting a first planetary gear mechanism and a second planetary gear mechanism,
Each of the first input member, the second input member, the first output member, and the second output member is rotatably supported by the case or the support member,
The connection structure between the rotating element of the first planetary gear mechanism and the rotating element of the second planetary gear mechanism has a connecting structure having a gap in the radial direction based on the first axis. The vehicle drive device according to any one of the above. 前記遊星歯車装置は、第１ピニオン軸受を介して第１ピニオンギヤを回転自在に支持する第１キャリヤを有する第１遊星歯車機構と、第２ピニオン軸受を介して第２ピニオンギヤを回転自在に支持する第２キャリヤを有する第２遊星歯車機構と、を備え、
前記第１出力部材は、前記第１キャリヤに連結されると共に第１出力軸受を介して回転自在に支持され、
前記第２出力部材は、前記第２キャリヤに連結されると共に第２出力軸受を介して回転自在に支持され、
前記第１キャリヤに、前記第１ピニオン軸受に油を供給するための油路と、前記第１出力軸受に油を供給するための油路とが形成され、
前記第２キャリヤに、前記第２ピニオン軸受に油を供給するための油路と、前記第２出力軸受に油を供給するための油路とが形成されている請求項１から９のいずれか一項に記載の車両用駆動装置。 The planetary gear set rotatably supports a second pinion gear via a first planetary gear mechanism having a first carrier rotatably supporting a first pinion gear via a first pinion bearing, and a second pinion bearing. A second planetary gear mechanism having a second carrier;
The first output member is coupled to the first carrier and rotatably supported via a first output bearing.
The second output member is coupled to the second carrier and rotatably supported via a second output bearing.
An oil passage for supplying oil to the first pinion bearing and an oil passage for supplying oil to the first output bearing are formed in the first carrier.
The oil passage for supplying oil to the second pinion bearing, and the oil passage for supplying oil to the second output bearing are formed in the second carrier. The vehicle drive device according to any one of the above.
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