JP2022072678A - Vehicular drive device - Google Patents

Vehicular drive device Download PDF

Info

Publication number
JP2022072678A
JP2022072678A JP2020182252A JP2020182252A JP2022072678A JP 2022072678 A JP2022072678 A JP 2022072678A JP 2020182252 A JP2020182252 A JP 2020182252A JP 2020182252 A JP2020182252 A JP 2020182252A JP 2022072678 A JP2022072678 A JP 2022072678A
Authority
JP
Japan
Prior art keywords
gear
axis
counter
axial direction
gear mechanism
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2020182252A
Other languages
Japanese (ja)
Other versions
JP7476761B2 (en
Inventor
大樹 須山
Daiki Suyama
崇之 奥村
Takayuki Okumura
広哲 長内
Hiroaki Osanai
年寿 水谷
Toshihisa Mizutani
健太 片岡
Kenta Kataoka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aisin Corp filed Critical Aisin Corp
Priority to JP2020182252A priority Critical patent/JP7476761B2/en
Publication of JP2022072678A publication Critical patent/JP2022072678A/en
Application granted granted Critical
Publication of JP7476761B2 publication Critical patent/JP7476761B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/72—Electric energy management in electromobility

Landscapes

  • Retarders (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)

Abstract

To realize a vehicular drive device capable of suppressing axial dimensions to be small.SOLUTION: A vehicular drive device (1) is equipped with a first drive power source (10), a second drive power source (20), a first output member (70A), a second output member (70B), a first counter gear mechanism (30), a second counter gear mechanism (40), and a differential gear mechanism (50). The first counter gear mechanism (30) and the second counter gear mechanism (40) are disposed on separated shafts, and a disposing area in an axial direction (L) of the first counter gear mechanism (30) and a disposing area in the axial direction (L) of the second counter gear mechanism (40) are overlapped.SELECTED DRAWING: Figure 2

Description

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

第１駆動力源と、第２駆動力源と、第１車輪に駆動連結される第１出力部材と、第２車輪に駆動連結される第２出力部材と、動力伝達装置とを備えた車両用駆動装置が利用されている。このような車両用駆動装置の一例が、特開２０１５－２１５９４号公報（特許文献１）に開示されている。 A vehicle including a first driving force source, a second driving force source, a first output member that is driven and connected to the first wheel, a second output member that is driven and connected to the second wheel, and a power transmission device. Drive device is used. An example of such a vehicle drive device is disclosed in Japanese Patent Application Laid-Open No. 2015-21594 (Patent Document 1).

特許文献１の車両用駆動装置は、動力伝達装置として、第１駆動力源（第一モータ２）に駆動連結される第１カウンタギヤ機構（減速ギヤ列６）と、第２駆動力源（第二モータ３）に駆動連結される第２カウンタギヤ機構（減速ギヤ列７）と、両カウンタギヤ機構に駆動連結される差動歯車機構（歯車装置５）とを備えている。差動歯車機構は、第１駆動力源から伝達される駆動力及び第２駆動力源から伝達される駆動力を、第１出力部材（リングギヤＲ２）と第２出力部材（リングギヤＲ１）とに分配して出力するように構成されている。これにより、第１駆動力源と第２駆動力源との間でのトルク移動を利用して、総トルクの減少を抑えつつ、第１車輪（右駆動輪４Ｒ）と第２車輪（左駆動輪４Ｒ）との間に大きなトルク差を設けることが可能となっている。 The vehicle drive device of Patent Document 1 has, as a power transmission device, a first counter gear mechanism (reduction gear train 6) that is driven and connected to a first drive force source (first motor 2) and a second drive force source (reduction gear train 6). It includes a second counter gear mechanism (reduction gear train 7) that is driven and connected to the second motor 3), and a differential gear mechanism (gear device 5) that is driven and connected to both counter gear mechanisms. The differential gear mechanism transfers the driving force transmitted from the first driving force source and the driving force transmitted from the second driving force source to the first output member (ring gear R2) and the second output member (ring gear R1). It is configured to be distributed and output. As a result, the torque transfer between the first driving force source and the second driving force source is utilized to suppress the decrease in the total torque, while the first wheel (right drive wheel 4R) and the second wheel (left drive). It is possible to provide a large torque difference with the wheel 4R).

しかし、特許文献１の車両用駆動装置では、第１駆動力源と第２駆動力源とが同軸に配置されているとともに、これらとは異なる位置で、第１カウンタギヤ機構と第２カウンタギヤ機構とが同軸に配置されている。このため、車両用駆動装置が軸方向に大型化しやすく、車両への搭載性が悪くなりやすいという問題があった。 However, in the vehicle drive device of Patent Document 1, the first driving force source and the second driving force source are arranged coaxially, and the first counter gear mechanism and the second counter gear are arranged at different positions. The mechanism is arranged coaxially. For this reason, there is a problem that the drive device for a vehicle tends to be large in the axial direction, and the mountability on the vehicle tends to deteriorate.

特開２０１５－２１５９４号公報Japanese Unexamined Patent Publication No. 2015-21594

そこで、軸方向寸法を小さく抑えることができる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 that can keep the axial dimension small.

本開示に係る車両用駆動装置は、
第１駆動力源と、第２駆動力源と、第１車輪に駆動連結される第１出力部材と、第２車輪に駆動連結される第２出力部材と、動力伝達装置と、を備えた車両用駆動装置であって、
前記第１駆動力源は、第１軸上に配置され、
前記第２駆動力源は、前記第１軸とは異なる第２軸上に配置され、
前記第１出力部材及び前記第２出力部材は、前記第１軸及び前記第２軸とは異なる第３軸上に配置され、
前記動力伝達装置は、前記第１駆動力源の回転体と一体的に回転する第１ギヤと、前記第２駆動力源の回転体と一体的に回転する第２ギヤと、前記第１軸、前記第２軸、及び前記第３軸とは異なる第４軸上に配置される第１カウンタギヤ機構と、前記第１軸、前記第２軸、前記第３軸、及び前記第４軸とは異なる第５軸上に配置される第２カウンタギヤ機構と、前記第３軸上に配置される差動歯車機構と、を備え、
前記第１カウンタギヤ機構は、前記第１ギヤに噛み合う第３ギヤと、前記第３ギヤと一体的に回転する第４ギヤと、を備え、
前記第２カウンタギヤ機構は、前記第２ギヤに噛み合う第５ギヤと、前記第５ギヤと一体的に回転する第６ギヤと、を備え、
前記差動歯車機構は、前記第４ギヤに噛み合う第７ギヤと、前記第６ギヤに噛み合う第８ギヤと、を備え、前記第１駆動力源から前記第７ギヤに伝達された駆動力及び前記第２駆動力源から前記第８ギヤに伝達された駆動力を、前記第１出力部材と前記第２出力部材とに分配して出力するように構成され、
前記第１軸、前記第２軸、前記第３軸、前記第４軸、及び前記第５軸は、互いに平行に配置され、
前記第１軸、前記第２軸、前記第３軸、前記第４軸、及び前記第５軸に平行な方向を軸方向とし、前記軸方向の一方側を軸方向第１側とするとともに他方側を軸方向第２側として、
前記第１駆動力源は前記第１ギヤに対して前記軸方向第１側に配置され、前記第２駆動力源は前記第２ギヤに対して前記軸方向第２側に配置され、
前記第１カウンタギヤ機構の前記軸方向の配置領域と、前記第２カウンタギヤ機構の前記軸方向の配置領域とが重複している。 The vehicle drive device according to the present disclosure is
It includes a first driving force source, a second driving force source, a first output member that is driven and connected to the first wheel, a second output member that is driven and connected to the second wheel, and a power transmission device. It is a vehicle drive device
The first driving force source is arranged on the first axis.
The second driving force source is arranged on a second axis different from the first axis.
The first output member and the second output member are arranged on a third axis different from the first axis and the second axis.
The power transmission device includes a first gear that rotates integrally with the rotating body of the first driving force source, a second gear that rotates integrally with the rotating body of the second driving force source, and the first shaft. A first counter gear mechanism arranged on a fourth axis different from the second axis and the third axis, and the first axis, the second axis, the third axis, and the fourth axis. A second counter gear mechanism arranged on a different fifth axis and a differential gear mechanism arranged on the third axis.
The first counter gear mechanism includes a third gear that meshes with the first gear and a fourth gear that rotates integrally with the third gear.
The second counter gear mechanism includes a fifth gear that meshes with the second gear and a sixth gear that rotates integrally with the fifth gear.
The differential gear mechanism includes a seventh gear that meshes with the fourth gear and an eighth gear that meshes with the sixth gear, and the driving force transmitted from the first driving force source to the seventh gear and The driving force transmitted from the second driving force source to the eighth gear is configured to be distributed and output to the first output member and the second output member.
The first axis, the second axis, the third axis, the fourth axis, and the fifth axis are arranged in parallel with each other.
The direction parallel to the first axis, the second axis, the third axis, the fourth axis, and the fifth axis is the axial direction, and one side of the axial direction is the first side in the axial direction and the other. With the side as the second side in the axial direction,
The first driving force source is arranged on the first side in the axial direction with respect to the first gear, and the second driving force source is arranged on the second side in the axial direction with respect to the second gear.
The axial arrangement area of the first counter gear mechanism and the axial arrangement area of the second counter gear mechanism overlap.

この構成によれば、第１カウンタギヤ機構を介して伝達される第１駆動力源の駆動力及び第２カウンタギヤ機構を介して伝達される第２駆動力源の駆動力を、差動歯車機構により第１出力部材と第２出力部材とに分配して出力することができる。また、この構成では、第１駆動力源と第２駆動力源とが別軸に配置されるとともに、これらとは異なる位置で、第１カウンタギヤ機構と第２カウンタギヤ機構とが別軸に配置される。そして、そのことを利用して、第１カウンタギヤ機構の軸方向の配置領域と第２カウンタギヤ機構の軸方向の配置領域とを重複させている。これにより、車両用駆動装置の軸方向寸法を小さく抑えることができる。 According to this configuration, the driving force of the first driving force source transmitted via the first counter gear mechanism and the driving force of the second driving force source transmitted via the second counter gear mechanism are set to the differential gear. By the mechanism, it is possible to distribute and output to the first output member and the second output member. Further, in this configuration, the first driving force source and the second driving force source are arranged on different axes, and the first counter gear mechanism and the second counter gear mechanism are arranged on different axes at different positions. Be placed. Then, utilizing this fact, the axially arranged area of the first counter gear mechanism and the axially arranged area of the second counter gear mechanism are overlapped. As a result, the axial dimension of the vehicle drive device can be kept small.

本開示に係る技術のさらなる特徴と利点は、図面を参照して記述する以下の例示的かつ非限定的な実施形態の説明によってより明確になるであろう。 Further features and advantages of the techniques according to the present disclosure will be further clarified by the following illustration of exemplary and non-limiting embodiments described with reference to the drawings.

実施形態の車両用駆動装置のスケルトン図Skeleton diagram of the vehicle drive device of the embodiment 車両用駆動装置の軸方向に沿う断面図Cross-sectional view along the axial direction of the vehicle drive 車両用駆動装置の各構成要素の軸方向視での位置関係を示す図The figure which shows the positional relationship in the axial direction of each component of a vehicle drive device.

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。図１及び図２に示すように、車両用駆動装置１は、第１回転電機１０と、第２回転電機２０と、第１車輪Ｗ１に駆動連結される第１出力部材７０Ａと、第２車輪Ｗ２に駆動連結される第２出力部材７０Ｂと、動力伝達装置３とを備えている。動力伝達装置３は、第１カウンタギヤ機構３０と、第２カウンタギヤ機構４０と、差動歯車機構５０とを備えている。これらはケース（駆動装置ケース）９に収容されている。なお、第１出力部材７０Ａ及び第２出力部材７０Ｂの一部は、ケース９の外部に露出している。 An embodiment of a vehicle drive device will be described with reference to the drawings. As shown in FIGS. 1 and 2, the vehicle drive device 1 includes a first rotary electric machine 10, a second rotary electric machine 20, a first output member 70A driven and connected to the first wheel W1, and a second wheel. It includes a second output member 70B that is driven and connected to W2, and a power transmission device 3. The power transmission device 3 includes a first counter gear mechanism 30, a second counter gear mechanism 40, and a differential gear mechanism 50. These are housed in a case (driving device case) 9. A part of the first output member 70A and the second output member 70B is exposed to the outside of the case 9.

本実施形態において、「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る。 In the present embodiment, the term "rotary electric machine" is used as a concept including any of a motor (motor), a generator (generator), and, if necessary, a motor / generator that functions as both a motor and a generator.

また、「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）が含まれても良い。 Further, the "driving connection" means a state in which two rotating elements are connected so as to be able to transmit a driving force. This concept includes a state in which two rotating elements are connected so as to rotate integrally, and a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. .. Such transmission members include various members (shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at different speeds, and are engaging devices that selectively transmit rotation and driving force. (Friction engagement device, meshing engagement device, etc.) may be included.

第１回転電機１０は、第１軸Ｘ１上に配置されている。すなわち、第１回転電機１０の回転体である第１ロータ１２が、第１軸Ｘ１を中心として回転する。第２回転電機２０は、第１軸Ｘ１とは異なる第２軸Ｘ２上に配置されている。すなわち、第２回転電機２０の回転体である第２ロータ２２が、第２軸Ｘ２を中心として回転する。第１出力部材７０Ａ及び第２出力部材７０Ｂは、第１軸Ｘ１及び第２軸Ｘ２とは異なる第３軸Ｘ３上に配置されている。本実施形態では、差動歯車機構５０も、第３軸Ｘ３上に配置されている。すなわち、第１出力部材７０Ａ及び第２出力部材７０Ｂ、並びに差動歯車機構５０の回転要素である第１サンギヤ５３、第２サンギヤ５４、リングギヤ５５、及びキャリヤ５６のそれぞれが、第３軸Ｘ３を中心として回転する。 The first rotary electric machine 10 is arranged on the first axis X1. That is, the first rotor 12, which is a rotating body of the first rotary electric machine 10, rotates about the first axis X1. The second rotary electric machine 20 is arranged on the second axis X2, which is different from the first axis X1. That is, the second rotor 22, which is a rotating body of the second rotary electric machine 20, rotates about the second axis X2. The first output member 70A and the second output member 70B are arranged on a third axis X3, which is different from the first axis X1 and the second axis X2. In this embodiment, the differential gear mechanism 50 is also arranged on the third axis X3. That is, each of the first output member 70A and the second output member 70B, and the first sun gear 53, the second sun gear 54, the ring gear 55, and the carrier 56, which are the rotating elements of the differential gear mechanism 50, form the third axis X3. Rotate as the center.

第１カウンタギヤ機構３０は、第１軸Ｘ１、第２軸Ｘ２、及び第３軸Ｘ３とは異なる第４軸Ｘ４上に配置されている。すなわち、第１カウンタギヤ機構３０の第１カウンタ軸３３が、第４軸Ｘ４を中心として回転する。第２カウンタギヤ機構４０は、第１軸Ｘ１、第２軸Ｘ２、第３軸Ｘ３、及び第４軸Ｘ４とは異なる第５軸Ｘ５上に配置されている。すなわち、第２カウンタギヤ機構４０の第２カウンタ軸４３が、第５軸Ｘ５を中心として回転する。 The first counter gear mechanism 30 is arranged on a fourth axis X4, which is different from the first axis X1, the second axis X2, and the third axis X3. That is, the first counter shaft 33 of the first counter gear mechanism 30 rotates about the fourth shaft X4. The second counter gear mechanism 40 is arranged on the fifth axis X5, which is different from the first axis X1, the second axis X2, the third axis X3, and the fourth axis X4. That is, the second counter shaft 43 of the second counter gear mechanism 40 rotates about the fifth shaft X5.

これらの第１軸Ｘ１、第２軸Ｘ２、第３軸Ｘ３、第４軸Ｘ４、及び第５軸Ｘ５は、互いに異なる仮想軸であり、互いに平行に配置されている。本実施形態では、これらの第１軸Ｘ１、第２軸Ｘ２、第３軸Ｘ３、第４軸Ｘ４、及び第５軸Ｘ５に平行な方向を「軸方向Ｌ」とする。そして、軸方向Ｌの一方側（本例では第２回転電機２０に対して第１回転電機１０が配置される側）を「軸方向第１側Ｌ１」とするとともに、その反対側である軸方向Ｌの他方側（第２回転電機２０が配置される側）を「軸方向第２側Ｌ２」とする。 These first axis X1, second axis X2, third axis X3, fourth axis X4, and fifth axis X5 are different virtual axes from each other and are arranged in parallel with each other. In the present embodiment, the direction parallel to these first axis X1, second axis X2, third axis X3, fourth axis X4, and fifth axis X5 is referred to as "axial direction L". Then, one side of the axial direction L (in this example, the side where the first rotary electric machine 10 is arranged with respect to the second rotary electric machine 20) is defined as the "first side L1 in the axial direction", and the shaft on the opposite side. The other side of the direction L (the side on which the second rotary electric machine 20 is arranged) is referred to as "the second side L2 in the axial direction".

第１回転電機１０は、第１ステータ１１と、第１ロータ１２とを備えている。本実施形態では、第１回転電機１０は、インナロータ型の回転電機であり、非回転部材（本例ではケース９）に第１ステータ１１が固定されているとともに、この第１ステータ１１の内側に、第１ロータ１２が回転自在に支持されている。本実施形態では、第１回転電機１０が「第１駆動力源」に相当し、第１ロータ１２が「第１駆動力源の回転体」に相当する。 The first rotary electric machine 10 includes a first stator 11 and a first rotor 12. In the present embodiment, the first rotary electric machine 10 is an inner rotor type rotary electric machine, and the first stator 11 is fixed to a non-rotating member (case 9 in this example), and inside the first stator 11. , The first rotor 12 is rotatably supported. In the present embodiment, the first rotary electric machine 10 corresponds to the "first driving force source", and the first rotor 12 corresponds to the "rotating body of the first driving force source".

第１ロータ１２には、軸方向Ｌに沿って延在する第１入力軸１５が一体的に回転するように連結されている。第１入力軸１５は、第１ロータ１２から軸方向第２側Ｌ２に向かって延出している。そして、本例では、この第１入力軸１５の外面に第１入力ギヤ１６が形成されている。これにより、第１入力ギヤ１６は、第１回転電機１０の第１ロータ１２と一体的に回転する。第１入力ギヤ１６は、第１回転電機１０に対して軸方向第２側Ｌ２に配置されており、逆に言えば、第１回転電機１０は第１入力ギヤ１６に対して軸方向第１側Ｌ１に配置されている。本実施形態では、第１入力ギヤ１６が「第１ギヤ」に相当する。第１入力ギヤ１６は、動力伝達装置３の一部を構成している。 A first input shaft 15 extending along the axial direction L is connected to the first rotor 12 so as to rotate integrally. The first input shaft 15 extends from the first rotor 12 toward the second side L2 in the axial direction. Then, in this example, the first input gear 16 is formed on the outer surface of the first input shaft 15. As a result, the first input gear 16 rotates integrally with the first rotor 12 of the first rotary electric machine 10. The first input gear 16 is arranged on the second side L2 in the axial direction with respect to the first rotary electric machine 10. Conversely, the first rotary electric machine 10 is the first in the axial direction with respect to the first input gear 16. It is arranged on the side L1. In this embodiment, the first input gear 16 corresponds to the "first gear". The first input gear 16 constitutes a part of the power transmission device 3.

第２回転電機２０は、第２ステータ２１と、第２ロータ２２とを備えている。本実施形態では、第２回転電機２０は、インナロータ型の回転電機であり、非回転部材（本例ではケース９）に第２ステータ２１が固定されているとともに、この第２ステータ２１の内側に、第２ロータ２２が回転自在に支持されている。本実施形態では、第２回転電機２０が「第２駆動力源」に相当し、第２ロータ２２が「第２駆動力源の回転体」に相当する。 The second rotary electric machine 20 includes a second stator 21 and a second rotor 22. In the present embodiment, the second rotary electric machine 20 is an inner rotor type rotary electric machine, and the second stator 21 is fixed to a non-rotating member (case 9 in this example), and inside the second stator 21. , The second rotor 22 is rotatably supported. In the present embodiment, the second rotary electric machine 20 corresponds to the "second driving force source", and the second rotor 22 corresponds to the "rotating body of the second driving force source".

第２ロータ２２には、軸方向Ｌに沿って延在する第２入力軸２５が一体的に回転するように連結されている。第２入力軸２５は、第２ロータ２２から軸方向第１側Ｌ１に向かって延出している。そして、本例では、この第２入力軸２５の外面には第２入力ギヤ２６が形成されている。これにより、第２入力ギヤ２６は、第２回転電機２０の第２ロータ２２と一体的に回転する。第２入力ギヤ２６は、第２回転電機２０に対して軸方向第１側Ｌ１に配置されており、逆に言えば、第２回転電機２０は第２入力ギヤ２６に対して軸方向第２側Ｌ２に配置されている。本実施形態では、第２入力ギヤ２６が「第２ギヤ」に相当する。第２入力ギヤ２６は、動力伝達装置３の一部を構成している。 A second input shaft 25 extending along the axial direction L is connected to the second rotor 22 so as to rotate integrally. The second input shaft 25 extends from the second rotor 22 toward the first side L1 in the axial direction. In this example, the second input gear 26 is formed on the outer surface of the second input shaft 25. As a result, the second input gear 26 rotates integrally with the second rotor 22 of the second rotary electric machine 20. The second input gear 26 is arranged on the first side L1 in the axial direction with respect to the second rotary electric machine 20. Conversely, the second rotary electric machine 20 has a second axial direction with respect to the second input gear 26. It is arranged on the side L2. In this embodiment, the second input gear 26 corresponds to the "second gear". The second input gear 26 constitutes a part of the power transmission device 3.

第２回転電機２０は、第１回転電機１０とは独立して回転可能に設けられる。すなわち、第２ロータ２２は、第１ロータ１２と一体的に回転するようには連結されておらず、第１ロータ１２の回転速度と第２ロータ２２の回転速度との比は、車両用駆動装置１の状態に応じて変化する。第１回転電機１０及び第２回転電機２０としては、互いに同じ出力特性を備える２つの回転電機を用いても良いし、互いに異なる出力特性を備える２つの回転電機を用いても良い。 The second rotary electric machine 20 is rotatably provided independently of the first rotary electric machine 10. That is, the second rotor 22 is not connected so as to rotate integrally with the first rotor 12, and the ratio of the rotation speed of the first rotor 12 to the rotation speed of the second rotor 22 is a vehicle drive. It changes according to the state of the device 1. As the first rotary electric machine 10 and the second rotary electric machine 20, two rotary electric machines having the same output characteristics may be used, or two rotary electric machines having different output characteristics may be used.

動力伝達装置３は、第１ロータ１２と一体的に回転する第１入力ギヤ１６及び第２ロータ２２と一体的に回転する第２入力ギヤ２６に加え、第１カウンタギヤ機構３０と、第２カウンタギヤ機構４０と、差動歯車機構５０とを備えている。 The power transmission device 3 includes a first counter gear mechanism 30 and a second, in addition to a first input gear 16 that rotates integrally with the first rotor 12 and a second input gear 26 that rotates integrally with the second rotor 22. It includes a counter gear mechanism 40 and a differential gear mechanism 50.

第１カウンタギヤ機構３０は、第１カウンタ入力ギヤ３１と、第１カウンタ出力ギヤ３２と、第１カウンタ軸３３とを備えている。第１カウンタ入力ギヤ３１は、第１カウンタギヤ機構３０の入力要素であり、第１入力ギヤ１６に噛み合っている。第１カウンタ軸３３は、第１カウンタ入力ギヤ３１と第１カウンタ出力ギヤ３２とを一体的に回転するように連結している。第１カウンタ出力ギヤ３２は、第１カウンタ入力ギヤ３１に対して軸方向第１側Ｌ１に配置されている。本実施形態では、第１カウンタ入力ギヤ３１が「第３ギヤ」に相当し、第１カウンタ出力ギヤ３２が「第４ギヤ」に相当する。第１カウンタ出力ギヤ３２は、第１カウンタギヤ機構３０の出力要素であり、差動歯車機構５０の第１差動入力ギヤ５１に噛み合っている。 The first counter gear mechanism 30 includes a first counter input gear 31, a first counter output gear 32, and a first counter shaft 33. The first counter input gear 31 is an input element of the first counter gear mechanism 30 and meshes with the first input gear 16. The first counter shaft 33 connects the first counter input gear 31 and the first counter output gear 32 so as to rotate integrally. The first counter output gear 32 is arranged on the first side L1 in the axial direction with respect to the first counter input gear 31. In the present embodiment, the first counter input gear 31 corresponds to the "third gear", and the first counter output gear 32 corresponds to the "fourth gear". The first counter output gear 32 is an output element of the first counter gear mechanism 30 and meshes with the first differential input gear 51 of the differential gear mechanism 50.

第１カウンタギヤ機構３０は、第１入力ギヤ１６の回転を変速し、当該変速後の回転を、第１差動入力ギヤ５１を介して差動歯車機構５０に伝達する。本実施形態では、第１カウンタ入力ギヤ３１が第１入力ギヤ１６よりも大径に形成されているとともに、第１カウンタ出力ギヤ３２が第１差動入力ギヤ５１よりも小径に形成されている。このため、第１入力ギヤ１６の回転は、第１入力ギヤ１６と第１カウンタ入力ギヤ３１との歯数比に応じて減速されるとともに、第１カウンタ出力ギヤ３２と第１差動入力ギヤ５１との歯数比に応じて更に減速されて（つまり、二段階に減速されて）、差動歯車機構５０に入力される。 The first counter gear mechanism 30 shifts the rotation of the first input gear 16 and transmits the rotation after the shift to the differential gear mechanism 50 via the first differential input gear 51. In the present embodiment, the first counter input gear 31 is formed to have a larger diameter than the first input gear 16, and the first counter output gear 32 is formed to have a smaller diameter than the first differential input gear 51. .. Therefore, the rotation of the first input gear 16 is decelerated according to the gear ratio between the first input gear 16 and the first counter input gear 31, and the first counter output gear 32 and the first differential input gear are decelerated. It is further decelerated according to the gear ratio with 51 (that is, decelerated in two steps) and input to the differential gear mechanism 50.

第２カウンタギヤ機構４０は、第２カウンタ入力ギヤ４１と、第２カウンタ出力ギヤ４２と、第２カウンタ軸４３とを備えている。第２カウンタ入力ギヤ４１は、第２カウンタギヤ機構４０の入力要素であり、第２入力ギヤ２６に噛み合っている。第２カウンタ軸４３は、第２カウンタ入力ギヤ４１と第２カウンタ出力ギヤ４２とを一体的に回転するように連結している。第２カウンタ出力ギヤ４２は、第２カウンタ入力ギヤ４１に対して軸方向第２側Ｌ２に配置されている。本実施形態では、第２カウンタ入力ギヤ４１が「第５ギヤ」に相当し、第２カウンタ出力ギヤ４２が「第６ギヤ」に相当する。第２カウンタ出力ギヤ４２は、第２カウンタギヤ機構４０の出力要素であり、差動歯車機構５０の第２差動入力ギヤ５２に噛み合っている。 The second counter gear mechanism 40 includes a second counter input gear 41, a second counter output gear 42, and a second counter shaft 43. The second counter input gear 41 is an input element of the second counter gear mechanism 40 and meshes with the second input gear 26. The second counter shaft 43 connects the second counter input gear 41 and the second counter output gear 42 so as to rotate integrally. The second counter output gear 42 is arranged on the second side L2 in the axial direction with respect to the second counter input gear 41. In the present embodiment, the second counter input gear 41 corresponds to the "fifth gear", and the second counter output gear 42 corresponds to the "sixth gear". The second counter output gear 42 is an output element of the second counter gear mechanism 40 and meshes with the second differential input gear 52 of the differential gear mechanism 50.

第２カウンタギヤ機構４０は、第２入力ギヤ２６の回転を変速し、当該変速後の回転を、第２差動入力ギヤ５２を介して差動歯車機構５０に伝達する。本実施形態では、第２カウンタ入力ギヤ４１が第２入力ギヤ２６よりも大径に形成されているとともに、第２カウンタ出力ギヤ４２が第２差動入力ギヤ５２よりも小径に形成されている。このため、第２入力ギヤ２６の回転は、第２入力ギヤ２６と第２カウンタ入力ギヤ４１との歯数比に応じて減速されるとともに、第２カウンタ出力ギヤ４２と第２差動入力ギヤ５２との歯数比に応じて更に減速されて（つまり、二段階に減速されて）、差動歯車機構５０に入力される。 The second counter gear mechanism 40 shifts the rotation of the second input gear 26, and transmits the rotation after the shift to the differential gear mechanism 50 via the second differential input gear 52. In the present embodiment, the second counter input gear 41 is formed to have a larger diameter than the second input gear 26, and the second counter output gear 42 is formed to have a smaller diameter than the second differential input gear 52. .. Therefore, the rotation of the second input gear 26 is decelerated according to the gear ratio between the second input gear 26 and the second counter input gear 41, and the second counter output gear 42 and the second differential input gear 42 are decelerated. It is further decelerated (that is, decelerated in two steps) according to the gear ratio with 52, and is input to the differential gear mechanism 50.

本実施形態では、第１カウンタ入力ギヤ３１が第１カウンタ出力ギヤ３２よりも大径に形成されているとともに、第２カウンタ入力ギヤ４１が第２カウンタ出力ギヤ４２よりも大径に形成されている。そして、軸方向Ｌにおける第１回転電機１０と第１カウンタ入力ギヤ３１との間に第１カウンタ出力ギヤ３２が配置されている。また、軸方向Ｌにおける第２回転電機２０と第２カウンタ入力ギヤ４１との間に第２カウンタ出力ギヤ４２が配置されている。 In the present embodiment, the first counter input gear 31 is formed to have a diameter larger than that of the first counter output gear 32, and the second counter input gear 41 is formed to have a diameter larger than that of the second counter output gear 42. There is. A first counter output gear 32 is arranged between the first rotary electric machine 10 and the first counter input gear 31 in the axial direction L. Further, a second counter output gear 42 is arranged between the second rotary electric machine 20 and the second counter input gear 41 in the axial direction L.

差動歯車機構５０は、第１回転電機１０から伝達される駆動力及び第２回転電機２０から伝達される駆動力を、第１出力部材７０Ａと第２出力部材７０Ｂとに分配して出力するように構成されている。差動歯車機構５０は、第１差動入力ギヤ５１と、第２差動入力ギヤ５２と、ラビニヨ型の遊星歯車機構とを備えている。ラビニヨ型の遊星歯車機構は、第１サンギヤ５３と、第２サンギヤ５４と、リングギヤ５５と、キャリヤ５６とを有する４要素の遊星歯車機構で構成されている。 The differential gear mechanism 50 distributes and outputs the driving force transmitted from the first rotary electric machine 10 and the driving force transmitted from the second rotary electric machine 20 to the first output member 70A and the second output member 70B. It is configured as follows. The differential gear mechanism 50 includes a first differential input gear 51, a second differential input gear 52, and a ravinyo-type planetary gear mechanism. The labigno-type planetary gear mechanism is composed of a four-element planetary gear mechanism having a first sun gear 53, a second sun gear 54, a ring gear 55, and a carrier 56.

第１差動入力ギヤ５１は、第１連結部材６１に形成されている。本実施形態では、第１連結部材６１の外周面に、第１差動入力ギヤ５１が形成されている。第１差動入力ギヤ５１は、第１カウンタ出力ギヤ３２に噛み合っている。本実施形態では、第１差動入力ギヤ５１が「第７ギヤ」に相当する。第１連結部材６１は、第２連結軸６４と同軸に、当該第２連結軸６４の径方向外側を覆うように配置されている。また、第１差動入力ギヤ５１が形成された第１連結部材６１は、リングギヤ５５と一体的に回転するように連結されている。 The first differential input gear 51 is formed on the first connecting member 61. In the present embodiment, the first differential input gear 51 is formed on the outer peripheral surface of the first connecting member 61. The first differential input gear 51 meshes with the first counter output gear 32. In this embodiment, the first differential input gear 51 corresponds to the "seventh gear". The first connecting member 61 is arranged coaxially with the second connecting shaft 64 so as to cover the radial outside of the second connecting shaft 64. Further, the first connecting member 61 on which the first differential input gear 51 is formed is connected so as to rotate integrally with the ring gear 55.

第２差動入力ギヤ５２は、第２連結部材６２に形成されている。本実施形態では、第２連結部材６２の外周面に、第２差動入力ギヤ５２が形成されている。第２差動入力ギヤ５２は、第２カウンタ出力ギヤ４２に噛み合っている。本実施形態では、第２差動入力ギヤ５２が「第８ギヤ」に相当する。第２連結部材６２は、第１連結部材６１に対して軸方向第２側Ｌ２において、第１連結軸６３及び第２出力部材７０Ｂの径方向外側を覆うように配置されている。また、第２差動入力ギヤ５２が形成された第２連結部材６２は、第２サンギヤ５４が形成された第２連結軸６４と一体的に回転するように連結されている。 The second differential input gear 52 is formed on the second connecting member 62. In the present embodiment, the second differential input gear 52 is formed on the outer peripheral surface of the second connecting member 62. The second differential input gear 52 meshes with the second counter output gear 42. In this embodiment, the second differential input gear 52 corresponds to the "eighth gear". The second connecting member 62 is arranged so as to cover the radial outside of the first connecting shaft 63 and the second output member 70B on the second side L2 in the axial direction with respect to the first connecting member 61. Further, the second connecting member 62 in which the second differential input gear 52 is formed is connected so as to rotate integrally with the second connecting shaft 64 in which the second sun gear 54 is formed.

第１サンギヤ５３は、第２出力部材７０Ｂと一体的に回転するように連結されている。本実施形態では、第１サンギヤ５３は、軸方向Ｌに沿って延在する第１連結軸６３を介して、第２出力部材７０Ｂと連結されている。第１連結軸６３の軸方向第１側Ｌ１の端部にスプライン係合されたサンギヤ形成部材６５の外周面に第１サンギヤ５３が形成されているとともに、第１連結軸６３の軸方向第２側Ｌ２の端部の径方向内側に第２出力部材７０Ｂが進入した状態で、第１連結軸６３と第２出力部材７０Ｂとがスプライン係合により互いに連結されている。 The first sun gear 53 is connected to the second output member 70B so as to rotate integrally. In the present embodiment, the first sun gear 53 is connected to the second output member 70B via the first connecting shaft 63 extending along the axial direction L. The first sun gear 53 is formed on the outer peripheral surface of the sun gear forming member 65 spline-engaged with the end of the first side L1 in the axial direction of the first connecting shaft 63, and the second in the axial direction of the first connecting shaft 63. The first connecting shaft 63 and the second output member 70B are connected to each other by spline engagement in a state where the second output member 70B has entered the radial inside of the end portion of the side L2.

第２サンギヤ５４は、第２カウンタ出力ギヤ４２に噛み合う第２差動入力ギヤ５２と一体的に回転するように連結されている。本実施形態では、第２サンギヤ５４は、軸方向Ｌに沿って延在する第２連結軸６４と第２連結部材６２とを介して、第２差動入力ギヤ５２と連結されている。第２連結軸６４の軸方向第１側Ｌ１の端部における外周面に第２サンギヤ５４が形成されているとともに、第２連結軸６４とスプライン係合により連結された第２連結部材６２の外周面に、第２差動入力ギヤ５２が形成されている。 The second sun gear 54 is connected so as to rotate integrally with the second differential input gear 52 that meshes with the second counter output gear 42. In the present embodiment, the second sun gear 54 is connected to the second differential input gear 52 via a second connecting shaft 64 extending along the axial direction L and a second connecting member 62. The second sun gear 54 is formed on the outer peripheral surface at the end of the first side L1 in the axial direction of the second connecting shaft 64, and the outer circumference of the second connecting member 62 connected to the second connecting shaft 64 by spline engagement. A second differential input gear 52 is formed on the surface.

なお、本実施形態では、第２サンギヤ５４は、第１サンギヤ５３に対して軸方向第２側Ｌ２に配置されており、当該第１サンギヤ５３よりも小径に形成されている。 In the present embodiment, the second sun gear 54 is arranged on the second side L2 in the axial direction with respect to the first sun gear 53, and is formed to have a smaller diameter than the first sun gear 53.

リングギヤ５５は、第１カウンタ出力ギヤ３２に噛み合う第１差動入力ギヤ５１と一体的に回転するように連結されている。本実施形態では、リングギヤ５５は、第１連結部材６１を介して第１差動入力ギヤ５１と連結されている。 The ring gear 55 is connected so as to rotate integrally with the first differential input gear 51 that meshes with the first counter output gear 32. In the present embodiment, the ring gear 55 is connected to the first differential input gear 51 via the first connecting member 61.

キャリヤ５６は、第１出力部材７０Ａと一体的に回転するように連結されている。本実施形態では、キャリヤ５６は、第１出力部材７０Ａの軸方向第２側Ｌ２の端部において一体的に形成されている。また、キャリヤ５６は、複数対の第１ピニオンギヤ５７及び第２ピニオンギヤ５８を回転自在に支持している。本実施形態では、それぞれのピニオン軸５９の外周面に、第１ピニオンギヤ５７及び第２ピニオンギヤ５８が一体的に形成されている。キャリヤ５６は、第１ピニオンギヤ５７及び第２ピニオンギヤ５８が形成された複数のピニオン軸５９の軸方向Ｌの両端部を、それぞれ回転自在に支持している。 The carrier 56 is connected to the first output member 70A so as to rotate integrally. In the present embodiment, the carrier 56 is integrally formed at the end of the second side L2 in the axial direction of the first output member 70A. Further, the carrier 56 rotatably supports a plurality of pairs of the first pinion gear 57 and the second pinion gear 58. In the present embodiment, the first pinion gear 57 and the second pinion gear 58 are integrally formed on the outer peripheral surface of each pinion shaft 59. The carrier 56 rotatably supports both ends of the plurality of pinion shafts 59 in which the first pinion gear 57 and the second pinion gear 58 are formed in the axial direction L, respectively.

なお、本実施形態では、第２ピニオンギヤ５８は、第１ピニオンギヤ５７に対して軸方向第２側Ｌ２に配置されており、当該第１ピニオンギヤ５７よりも大径に形成されている。そして、第１ピニオンギヤ５７は、第１サンギヤ５３に噛み合い、第２ピニオンギヤ５８は、第２サンギヤ５４に噛み合っている。 In the present embodiment, the second pinion gear 58 is arranged on the second side L2 in the axial direction with respect to the first pinion gear 57, and is formed to have a larger diameter than the first pinion gear 57. The first pinion gear 57 meshes with the first sun gear 53, and the second pinion gear 58 meshes with the second sun gear 54.

このように、差動歯車機構５０において、リングギヤ５５は第１カウンタ出力ギヤ３２に噛み合う第１差動入力ギヤ５１と一体的に回転するように連結されている。キャリヤ５６は、第１出力部材７０Ａと一体的に回転するように連結されている。第１サンギヤ５３は、第２出力部材７０Ｂと一体的に回転するように連結されている。第２サンギヤ５４は、第２カウンタ出力ギヤ４２に噛み合う第２差動入力ギヤ５２と一体的に回転するように連結されている。差動歯車機構５０は、第１回転電機１０から第１差動入力ギヤ５１に伝達された駆動力及び第２回転電機２０から第２差動入力ギヤ５２に伝達された駆動力を、第１出力部材７０Ａと第２出力部材７０Ｂとに分配して出力する。 As described above, in the differential gear mechanism 50, the ring gear 55 is connected so as to rotate integrally with the first differential input gear 51 that meshes with the first counter output gear 32. The carrier 56 is connected to the first output member 70A so as to rotate integrally. The first sun gear 53 is connected to the second output member 70B so as to rotate integrally. The second sun gear 54 is connected so as to rotate integrally with the second differential input gear 52 that meshes with the second counter output gear 42. The differential gear mechanism 50 first receives the driving force transmitted from the first rotary electric machine 10 to the first differential input gear 51 and the driving force transmitted from the second rotary electric machine 20 to the second differential input gear 52. The output member 70A and the second output member 70B are distributed and output.

図２に示すように、ケース９は、第１ケース部９１と、第２ケース部９２と、第１カバー部９３と、第２カバー部９４とを有している。第１カバー部９３、第１ケース部９１、第２ケース部９２、及び第２カバー部９４が、軸方向第１側Ｌ１から軸方向第２側Ｌ２に向かって記載の順に配置され、それぞれ互いに接合されている。 As shown in FIG. 2, the case 9 has a first case portion 91, a second case portion 92, a first cover portion 93, and a second cover portion 94. The first cover portion 93, the first case portion 91, the second case portion 92, and the second cover portion 94 are arranged in the order described from the axial first side L1 to the axial second side L2, respectively. It is joined.

第１ケース部９１は、第１周壁部９１Ａと第１隔壁部９１Ｂとを有している。第１周壁部９１Ａは、第１回転電機１０、第１カウンタギヤ機構３０、及び差動歯車機構５０の径方向外側を囲む異形筒状に形成されている。第１隔壁部９１Ｂは、第１回転電機１０に対して軸方向第２側Ｌ２に配置されている。第１隔壁部９１Ｂは、第１回転電機１０が収容される部分と、第１入力ギヤ１６及び第１カウンタギヤ機構３０が収容される部分とを区画している。また、第１隔壁部９１Ｂは、第２入力軸２５、第１カウンタ軸３３、及び第２カウンタ軸４３の軸方向第１側Ｌ１の端部を回転自在に支持している。 The first case portion 91 has a first peripheral wall portion 91A and a first partition wall portion 91B. The first peripheral wall portion 91A is formed in a deformed tubular shape surrounding the radial outer side of the first rotary electric machine 10, the first counter gear mechanism 30, and the differential gear mechanism 50. The first partition wall portion 91B is arranged on the second side L2 in the axial direction with respect to the first rotary electric machine 10. The first partition wall portion 91B partitions a portion in which the first rotary electric machine 10 is housed and a portion in which the first input gear 16 and the first counter gear mechanism 30 are housed. Further, the first partition wall portion 91B rotatably supports the ends of the second input shaft 25, the first counter shaft 33, and the first side L1 in the axial direction of the second counter shaft 43.

第２ケース部９２は、第２周壁部９２Ａと第２隔壁部９２Ｂとを有している。第２周壁部９２Ａは、第２回転電機２０及び第２カウンタギヤ機構４０の径方向外側を囲む異形筒状に形成されている。第２隔壁部９２Ｂは、第２回転電機２０に対して軸方向第１側Ｌ１に配置されている。第２隔壁部９２Ｂは、第２回転電機２０が収容される部分と、第２入力ギヤ２６及び第２カウンタギヤ機構４０が収容される部分とを区画している。また、第２隔壁部９２Ｂは、第１入力軸１５、第１カウンタ軸３３、及び第２カウンタ軸４３の軸方向第２側Ｌ２の端部を回転自在に支持している。 The second case portion 92 has a second peripheral wall portion 92A and a second partition wall portion 92B. The second peripheral wall portion 92A is formed in a deformed tubular shape surrounding the radial outer side of the second rotary electric machine 20 and the second counter gear mechanism 40. The second partition wall portion 92B is arranged on the first side L1 in the axial direction with respect to the second rotary electric machine 20. The second partition wall portion 92B partitions a portion in which the second rotary electric machine 20 is housed and a portion in which the second input gear 26 and the second counter gear mechanism 40 are housed. Further, the second partition wall portion 92B rotatably supports the ends of the first input shaft 15, the first counter shaft 33, and the second side L2 in the axial direction of the second counter shaft 43.

第１カバー部９３は、第３周壁部９３Ａと第１側壁部９３Ｂとを有している。第３周壁部９３Ａは、第１回転電機１０の径方向外側を囲む筒状に形成されている。第１側壁部９３Ｂは、第１回転電機１０に対して軸方向第１側Ｌ１に配置されており、第１ケース部９１の軸方向第１側Ｌ１の開口を閉塞する。また、第１カバー部９３は、第１入力軸１５及び第１出力部材７０Ａの軸方向第１側Ｌ１の端部を回転自在に支持している。 The first cover portion 93 has a third peripheral wall portion 93A and a first side wall portion 93B. The third peripheral wall portion 93A is formed in a cylindrical shape that surrounds the radial outer side of the first rotary electric machine 10. The first side wall portion 93B is arranged on the first side L1 in the axial direction with respect to the first rotary electric machine 10, and closes the opening of the first side L1 in the axial direction of the first case portion 91. Further, the first cover portion 93 rotatably supports the ends of the first input shaft 15 and the first output member 70A on the first side L1 in the axial direction.

第２カバー部９４は、第４周壁部９４Ａと第２側壁部９４Ｂとを有している。第４周壁部９４Ａは、第２回転電機２０の径方向外側を囲む筒状に形成されている。第２側壁部９４Ｂは、第２回転電機２０に対して軸方向第２側Ｌ２に配置されており、第２ケース部９２の軸方向第２側Ｌ２の開口を閉塞する。また、第２カバー部９４は、第２入力軸２５及び第２出力部材７０Ｂの軸方向第２側Ｌ２の端部を回転自在に支持している。 The second cover portion 94 has a fourth peripheral wall portion 94A and a second side wall portion 94B. The fourth peripheral wall portion 94A is formed in a cylindrical shape that surrounds the radial outer side of the second rotary electric machine 20. The second side wall portion 94B is arranged on the second side L2 in the axial direction with respect to the second rotary electric machine 20, and closes the opening of the second side L2 in the axial direction of the second case portion 92. Further, the second cover portion 94 rotatably supports the ends of the second input shaft 25 and the second output member 70B on the second side L2 in the axial direction.

上述したように、本実施形態では、第１回転電機１０が配置される第１軸Ｘ１、第２回転電機２０が配置される第２軸Ｘ２、第１カウンタギヤ機構３０が配置される第４軸Ｘ４、及び第２カウンタギヤ機構４０が配置される第５軸Ｘ５は、互いに異なる位置にある。第１回転電機１０と第２回転電機２０とが別軸に配置され、第１カウンタギヤ機構３０と第２カウンタギヤ機構４０とが別軸に配置されている。第１カウンタギヤ機構３０と第２カウンタギヤ機構４０とは、図３に示すように、軸方向視で（軸方向Ｌに沿って見て）重複していない。 As described above, in the present embodiment, the first axis X1 in which the first rotary electric machine 10 is arranged, the second axis X2 in which the second rotary electric machine 20 is arranged, and the fourth counter gear mechanism 30 are arranged. The shaft X4 and the fifth shaft X5 in which the second counter gear mechanism 40 is arranged are located at different positions from each other. The first rotary electric machine 10 and the second rotary electric machine 20 are arranged on different shafts, and the first counter gear mechanism 30 and the second counter gear mechanism 40 are arranged on different shafts. As shown in FIG. 3, the first counter gear mechanism 30 and the second counter gear mechanism 40 do not overlap each other in the axial direction (viewed along the axial direction L).

なお、２つの部材の配置に関して、「軸方向視で重複する」とは、その視線方向である軸方向Ｌ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存在することを意味する。従って、「軸方向視で重複しない」とは、軸方向Ｌ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存在しないことを意味する。 Regarding the arrangement of the two members, "overlapping in the axial direction" means that the virtual straight line parallel to the axial direction L, which is the line-of-sight direction, is moved in each direction orthogonal to the virtual straight line. It means that there is a region where the virtual straight line intersects both of the two members. Therefore, "does not overlap in axial view" means that when a virtual straight line parallel to the axial direction L is moved in each direction orthogonal to the virtual straight line, a region where the virtual straight line intersects both of the two members is formed. It means that it does not exist.

そして本実施形態では、図２に示すように、第１カウンタギヤ機構３０の軸方向Ｌの配置領域と、第２カウンタギヤ機構４０の軸方向Ｌの配置領域とが重複している。ここで、第１カウンタギヤ機構３０の軸方向Ｌの配置領域は、本実施形態では、軸方向Ｌにおける第１カウンタ軸３３の軸方向第１側Ｌ１の端部から軸方向第２側Ｌ２の端部までの領域である。同様に、第２カウンタギヤ機構４０の軸方向Ｌの配置領域は、本実施形態では、軸方向Ｌにおける第２カウンタ軸４３の軸方向第１側Ｌ１の端部から軸方向第２側Ｌ２の端部までの領域である。そして、本実施形態では、第１カウンタ軸３３の軸方向第２側Ｌ２の端部が、第２カウンタ軸４３の軸方向第１側Ｌ１の端部よりも軸方向第２側Ｌ２に位置するように配置されている。 In the present embodiment, as shown in FIG. 2, the arrangement region of the first counter gear mechanism 30 in the axial direction L and the arrangement region of the second counter gear mechanism 40 in the axial direction L overlap. Here, the arrangement region of the first counter gear mechanism 30 in the axial direction L is, in the present embodiment, from the end portion of the first side L1 in the axial direction of the first counter shaft 33 in the axial direction L to the second side L2 in the axial direction. The area to the end. Similarly, in the present embodiment, the arrangement region of the second counter gear mechanism 40 in the axial direction L is located from the end of the axial first side L1 of the second counter shaft 43 in the axial direction L to the axial second side L2. The area to the end. Then, in the present embodiment, the end of the second counter axis 33 in the axial direction L2 is located on the second side L2 in the axial direction with respect to the end of the first side L1 in the axial direction of the second counter shaft 43. It is arranged like this.

この構成によれば、第１カウンタギヤ機構３０を介して第１回転電機１０の駆動力及び第２カウンタギヤ機構４０を介して伝達される第２回転電機２０の駆動力を、差動歯車機構５０により第１出力部材７０Ａと第２出力部材７０Ｂとに分配して出力することができる。よって、第１回転電機１０と第２回転電機２０との間でのトルク移動を利用して、総トルクの減少を抑えつつ、第１車輪Ｗ１と第２車輪Ｗ２との間に大きなトルク差を設けることができる。また、この構成では、第１回転電機１０と第２回転電機２０とが別軸に配置されるとともに、これらとは異なる位置で、第１カウンタギヤ機構３０と第２カウンタギヤ機構４０とが別軸に配置される。このため、第１カウンタギヤ機構３０の軸方向Ｌの配置領域と第２カウンタギヤ機構４０の軸方向Ｌの配置領域とを重複させることができている。これにより、車両用駆動装置１の軸方向寸法を小さく抑えることができている。 According to this configuration, the driving force of the first rotary electric machine 10 via the first counter gear mechanism 30 and the driving force of the second rotary electric machine 20 transmitted via the second counter gear mechanism 40 are transferred to the differential gear mechanism. 50 can be distributed and output to the first output member 70A and the second output member 70B. Therefore, by utilizing the torque transfer between the first rotary electric machine 10 and the second rotary electric machine 20, a large torque difference between the first wheel W1 and the second wheel W2 is generated while suppressing the decrease in the total torque. Can be provided. Further, in this configuration, the first rotary electric machine 10 and the second rotary electric machine 20 are arranged on different axes, and the first counter gear mechanism 30 and the second counter gear mechanism 40 are separated at different positions. Placed on the axis. Therefore, the arrangement area of the first counter gear mechanism 30 in the axial direction L and the arrangement area of the second counter gear mechanism 40 in the axial direction L can be overlapped. As a result, the axial dimension of the vehicle drive device 1 can be kept small.

さらに本実施形態では、第１カウンタギヤ機構３０の軸方向Ｌにおける中央部よりも軸方向第２側Ｌ２の領域と、第２カウンタギヤ機構４０の軸方向Ｌにおける中央部よりもの軸方向第１側Ｌ１の配置領域とが重複している。そして、第１カウンタギヤ機構３０において軸方向第２側Ｌ２に設けられた第１カウンタ入力ギヤ３１の軸方向Ｌの配置領域と、第２カウンタギヤ機構４０において軸方向第１側Ｌ１に設けられた第２カウンタ入力ギヤ４１の軸方向Ｌの配置領域とが重複している。第１カウンタ入力ギヤ３１の軸方向第２側Ｌ２の端部が、第２カウンタ入力ギヤ４１の軸方向第１側Ｌ１の端部よりも軸方向第２側Ｌ２に位置するように配置されている。 Further, in the present embodiment, the region of the second counter gear mechanism 30 in the axial direction L2 from the central portion in the axial direction L and the first axial direction of the second counter gear mechanism 40 from the central portion in the axial direction L. The arrangement area on the side L1 overlaps. Then, in the first counter gear mechanism 30, it is provided in the arrangement region of the first counter input gear 31 provided on the second side L2 in the axial direction in the axial direction L, and in the second counter gear mechanism 40 on the first side L1 in the axial direction. The second counter input gear 41 overlaps with the arrangement area in the axial direction L. The end of the second side L2 in the axial direction of the first counter input gear 31 is arranged so as to be located at the second side L2 in the axial direction with respect to the end of the first side L1 in the axial direction of the second counter input gear 41. There is.

第２カウンタ入力ギヤ４１は、その軸方向Ｌの配置領域を第１カウンタ入力ギヤ３１の軸方向Ｌの配置領域と重複させつつ、全体としては第１カウンタ入力ギヤ３１よりも軸方向第２側Ｌ２に位置するように配置されている。このため、第２カウンタギヤ機構４０において軸方向第２側Ｌ２に設けられた第２カウンタ出力ギヤ４２の軸方向Ｌの配置領域と、第１カウンタギヤ機構３０において軸方向第１側Ｌ１に設けられた第１カウンタ出力ギヤ３２の軸方向Ｌの配置領域とは重複していない。これらは、軸方向Ｌの配置領域が互いに重複する第１カウンタ入力ギヤ３１及び第２カウンタ入力ギヤ４１に対して、軸方向Ｌの反対側に分かれて配置されている。 The second counter input gear 41 overlaps the arrangement area in the axial direction L with the arrangement area in the axial direction L of the first counter input gear 31, and as a whole, is on the second side in the axial direction with respect to the first counter input gear 31. It is arranged so as to be located at L2. Therefore, in the second counter gear mechanism 40, it is provided in the arrangement region of the second counter output gear 42 provided in the second side L2 in the axial direction in the axial direction L, and in the first counter gear mechanism 30 in the first side L1 in the axial direction. It does not overlap with the arrangement area of the first counter output gear 32 in the axial direction L. These are separately arranged on the opposite side of the axial direction L with respect to the first counter input gear 31 and the second counter input gear 41 in which the arrangement regions in the axial direction L overlap each other.

このように、本実施形態では、第１カウンタ入力ギヤ３１の軸方向Ｌの配置領域と第２カウンタ入力ギヤ４１の軸方向Ｌの配置領域とが重複し、第１カウンタ出力ギヤ３２の軸方向Ｌの配置領域と第２カウンタ出力ギヤ４２の軸方向Ｌの配置領域とが重複していない。 As described above, in the present embodiment, the arrangement area of the first counter input gear 31 in the axial direction L and the arrangement area of the second counter input gear 41 in the axial direction L overlap, and the axial direction of the first counter output gear 32 overlaps. The arrangement area of L and the arrangement area of the second counter output gear 42 in the axial direction L do not overlap.

ここで、第１カウンタ出力ギヤ３２の軸方向Ｌの配置領域と第２カウンタ出力ギヤ４２の軸方向Ｌの配置領域とを重複させると、差動歯車機構５０における第１差動入力ギヤ５１と第２差動入力ギヤ５２とを配置することが困難になる。そこで、第１カウンタ出力ギヤ３２の軸方向Ｌの配置領域と第２カウンタ出力ギヤ４２の軸方向Ｌの配置領域とを重複させずに、第１カウンタ入力ギヤ３１の軸方向Ｌの配置領域と第２カウンタ入力ギヤ４１の軸方向Ｌの配置領域とを重複させている。こうすることで、第１カウンタ出力ギヤ３２と第１差動入力ギヤ５１との噛み合い、及び、第２カウンタ出力ギヤ４２と第２差動入力ギヤ５２との噛み合いを確保しつつ、第１カウンタギヤ機構３０と第２カウンタギヤ機構４０とが互いに重複する領域の軸方向Ｌの長さを比較的長く確保して、車両用駆動装置１の軸方向寸法をより小さく抑えることができる。 Here, if the arrangement area of the first counter output gear 32 in the axial direction L and the arrangement area of the second counter output gear 42 in the axial direction L overlap, the first differential input gear 51 in the differential gear mechanism 50 and the first differential input gear 51 It becomes difficult to arrange the second differential input gear 52. Therefore, without overlapping the arrangement area of the first counter output gear 32 in the axial direction L and the arrangement area of the second counter output gear 42 in the axial direction L, the arrangement area of the first counter input gear 31 in the axial direction L is used. It overlaps with the arrangement area of the second counter input gear 41 in the axial direction L. By doing so, while ensuring the meshing of the first counter output gear 32 and the first differential input gear 51 and the meshing of the second counter output gear 42 and the second differential input gear 52, the first counter The length of the axial direction L in the region where the gear mechanism 30 and the second counter gear mechanism 40 overlap each other can be secured to be relatively long, and the axial dimension of the vehicle drive device 1 can be suppressed to be smaller.

なお、本実施形態では、第１カウンタ出力ギヤ３２の軸方向Ｌの配置領域は、第２入力軸２５の軸方向第１側Ｌ１の端部を回転自在に支持する軸受（第２入力軸受）及び第２カウンタ軸４３の軸方向第１側Ｌ１の端部を転自在に支持する軸受（第２カウンタ軸受）の軸方向Ｌの配置領域と重複している。また、第２カウンタ出力ギヤ４２の軸方向Ｌの配置領域は、第１入力軸１５の軸方向第２側Ｌ２の端部を回転自在に支持する軸受（第１入力軸受）及び第１カウンタ軸３３の軸方向第２側Ｌ２の端部を転自在に支持する軸受（第１カウンタ軸受）の軸方向Ｌの配置領域と重複している。 In the present embodiment, the arrangement region of the first counter output gear 32 in the axial direction L is a bearing (second input bearing) that rotatably supports the end portion of the first side L1 in the axial direction of the second input shaft 25. And the bearing (second counter bearing) that rotatably supports the end of the first side L1 in the axial direction of the second counter shaft 43 overlaps with the arrangement region in the axial direction L. Further, the arrangement region of the second counter output gear 42 in the axial direction L is a bearing (first input bearing) that rotatably supports the end portion of the second side L2 in the axial direction of the first input shaft 15 and the first counter shaft. It overlaps with the arrangement region in the axial direction L of the bearing (first counter bearing) that rotatably supports the end portion of the second side L2 in the axial direction of 33.

また、本実施形態では、差動歯車機構５０の軸方向Ｌの配置領域が、第１回転電機１０の軸方向Ｌの配置領域と重複している。ここで、差動歯車機構５０の軸方向Ｌの配置領域は、本実施形態では、軸方向Ｌにおけるキャリヤ５６の軸方向第１側Ｌ１の端部から、外周面に第２差動入力ギヤ５２が形成された第２連結部材６２の軸方向第２側Ｌ２の端部までの領域である。第１回転電機１０の軸方向Ｌの配置領域は、第１ステータ１１の軸方向第１側Ｌ１の端部から軸方向第２側Ｌ２の端部までの領域である。そして、本実施形態では、第１ステータ１１の軸方向第２側Ｌ２の端部が、キャリヤ５６の軸方向第１側Ｌ１の端部よりも軸方向第２側Ｌ２に位置するように配置されている。 Further, in the present embodiment, the arrangement region of the differential gear mechanism 50 in the axial direction L overlaps with the arrangement region of the first rotary electric machine 10 in the axial direction L. Here, in the present embodiment, the arrangement region of the differential gear mechanism 50 in the axial direction L is the second differential input gear 52 on the outer peripheral surface from the end portion of the carrier 56 on the first side L1 in the axial direction in the axial direction L. Is the region up to the end of the second side L2 in the axial direction of the second connecting member 62 in which the is formed. The arrangement region of the first rotary electric machine 10 in the axial direction L is a region from the end portion of the axial first side L1 of the first stator 11 to the end portion of the axial second side L2. Then, in the present embodiment, the end portion of the axial second side L2 of the first stator 11 is arranged so as to be located at the axial second side L2 of the carrier 56 with respect to the end portion of the axial first side L1. ing.

さらに本実施形態では、差動歯車機構５０のうち、ラビニヨ型の遊星歯車機構（第１サンギヤ５３、第２サンギヤ５４、リングギヤ５５、及びキャリヤ５６）の軸方向Ｌの配置領域が、第１回転電機１０の軸方向Ｌの配置領域と重複している。一方、差動歯車機構５０を構成する第１差動入力ギヤ５１及び第２差動入力ギヤ５２は、第１ステータ１１の軸方向第２側Ｌ２の端部よりもさらに軸方向第２側Ｌ２に配置されている。すなわち、第１差動入力ギヤ５１及び第２差動入力ギヤ５２の軸方向Ｌの配置領域は、第１回転電機１０の軸方向Ｌの配置領域とは重複していない。 Further, in the present embodiment, among the differential gear mechanisms 50, the axial L arrangement region of the labigno type planetary gear mechanism (first sun gear 53, second sun gear 54, ring gear 55, and carrier 56) is the first rotation. It overlaps with the arrangement area of the electric machine 10 in the axial direction L. On the other hand, the first differential input gear 51 and the second differential input gear 52 constituting the differential gear mechanism 50 are further axially second side L2 than the end portion of the first stator 11 on the axial second side L2. Is located in. That is, the arrangement area of the first differential input gear 51 and the second differential input gear 52 in the axial direction L does not overlap with the arrangement area of the first rotary electric machine 10 in the axial direction L.

また、本実施形態では、差動歯車機構５０の軸方向Ｌの配置領域は、第２回転電機２０の軸方向Ｌの配置領域とは重複していない。ここで、第２回転電機２０の軸方向Ｌの配置領域は、第２ステータ２１の軸方向第１側Ｌ１の端部から軸方向第２側Ｌ２の端部までの領域である。本実施形態では、第２ステータ２１の軸方向第１側Ｌ１の端部が、第２差動入力ギヤ５２が形成された第２連結部材６２の軸方向第２側Ｌ２の端部よりもさらに軸方向第２側Ｌ２に位置するように配置されている。 Further, in the present embodiment, the arrangement region of the differential gear mechanism 50 in the axial direction L does not overlap with the arrangement region of the second rotary electric machine 20 in the axial direction L. Here, the arrangement region of the second rotary electric machine 20 in the axial direction L is a region from the end portion of the axial first side L1 of the second stator 21 to the end portion of the axial second side L2. In the present embodiment, the end of the axial first side L1 of the second stator 21 is further than the end of the axial second side L2 of the second connecting member 62 on which the second differential input gear 52 is formed. It is arranged so as to be located on the second side L2 in the axial direction.

図３に示すように、第１回転電機１０と差動歯車機構５０とは、軸方向視でそれぞれの外縁どうしが接するような位置関係で配置されている。ここで、第１回転電機１０の外縁は、第１ステータ１１の径方向外側の端部である。差動歯車機構５０の外縁は、第１差動入力ギヤ５１及び第２差動入力ギヤ５２の径方向外側の端部である。一方、第２回転電機２０と差動歯車機構５０とは、軸方向視で互いに重複するように配置されている。第２ステータ２１の径方向外側領域と、第１差動入力ギヤ５１が形成された第１連結部材６１の径方向外側領域及び第２差動入力ギヤ５２が形成された第２連結部材６２の径方向外側領域とが軸方向視で互いに重複している。 As shown in FIG. 3, the first rotary electric machine 10 and the differential gear mechanism 50 are arranged in a positional relationship so that their outer edges are in contact with each other in the axial direction. Here, the outer edge of the first rotary electric machine 10 is a radial outer end portion of the first stator 11. The outer edge of the differential gear mechanism 50 is a radial outer end of the first differential input gear 51 and the second differential input gear 52. On the other hand, the second rotary electric machine 20 and the differential gear mechanism 50 are arranged so as to overlap each other in the axial direction. The radial outer region of the second stator 21, the radial outer region of the first connecting member 61 in which the first differential input gear 51 is formed, and the second connecting member 62 in which the second differential input gear 52 is formed. The radial outer regions overlap each other in the axial direction.

このように、本実施形態では、軸方向Ｌに沿う軸方向視で、第２回転電機２０と差動歯車機構５０とが重複するように配置されている。 As described above, in the present embodiment, the second rotary electric machine 20 and the differential gear mechanism 50 are arranged so as to overlap each other in the axial direction along the axial direction L.

これにより、第２回転電機２０を差動歯車機構５０に近づけて配置することができる。よって、車両用駆動装置１の径方向寸法を小さく抑えることができる。 As a result, the second rotary electric machine 20 can be arranged close to the differential gear mechanism 50. Therefore, the radial dimension of the vehicle drive device 1 can be kept small.

本実施形態では、第１回転電機１０及び第２回転電機２０として、同じ体格のもの（ここでは特に径方向のサイズが同じもの）が用いられている。このため、第２回転電機２０が差動歯車機構５０と軸方向視で互いに重複するように配置されることで、差動歯車機構５０が配置される第３軸Ｘ３と第２回転電機２０が配置される第２軸Ｘ２との軸間距離が、第３軸Ｘ３と第１回転電機１０が配置される第１軸Ｘ１との軸間距離よりも短くなっている。 In the present embodiment, as the first rotary electric machine 10 and the second rotary electric machine 20, those having the same physique (here, those having the same radial size in particular) are used. Therefore, the second rotary electric machine 20 is arranged so as to overlap with the differential gear mechanism 50 in the axial direction, so that the third axis X3 and the second rotary electric machine 20 in which the differential gear mechanism 50 is arranged are arranged. The distance between the axes of the second axis X2 to be arranged is shorter than the distance between the third axis X3 and the first axis X1 to which the first rotary electric machine 10 is arranged.

すなわち、本実施形態では、差動歯車機構５０の軸方向Ｌの配置領域が、第１回転電機１０の軸方向Ｌの配置領域と重複し、かつ、第２回転電機２０の軸方向Ｌの配置領域とは重複せず、第２軸Ｘ２と第３軸Ｘ３との軸間距離が、第１軸Ｘ１と第３軸Ｘ３との軸間距離よりも短い。 That is, in the present embodiment, the arrangement area of the differential gear mechanism 50 in the axial direction L overlaps with the arrangement area of the first rotary electric machine 10 in the axial direction L, and the arrangement of the second rotary electric machine 20 in the axial direction L. It does not overlap with the region, and the distance between the axes of the second axis X2 and the third axis X3 is shorter than the distance between the axes of the first axis X1 and the third axis X3.

これにより、差動歯車機構５０とは軸方向Ｌの配置領域が重複しない第２回転電機２０を差動歯車機構５０に近づけて配置することができる。よって、車両用駆動装置１の径方向寸法を小さく抑えることができる。 As a result, the second rotary electric machine 20 whose arrangement region in the axial direction L does not overlap with the differential gear mechanism 50 can be arranged close to the differential gear mechanism 50. Therefore, the radial dimension of the vehicle drive device 1 can be kept small.

また、第１カウンタギヤ機構３０と差動歯車機構５０とが軸方向視で互いに重複するように配置されているとともに、第２カウンタギヤ機構４０と差動歯車機構５０とも軸方向視で互いに重複するように配置されている。本実施形態では、第１カウンタ出力ギヤ３２及び第２カウンタ出力ギヤ４２の径方向全域と、第１差動入力ギヤ５１が形成された第１連結部材６１の径方向外側領域及び第２差動入力ギヤ５２が形成された第２連結部材６２の径方向外側領域とが軸方向視で互いに重複している。 Further, the first counter gear mechanism 30 and the differential gear mechanism 50 are arranged so as to overlap each other in the axial view, and the second counter gear mechanism 40 and the differential gear mechanism 50 also overlap each other in the axial view. Arranged to do. In the present embodiment, the entire radial direction of the first counter output gear 32 and the second counter output gear 42, the radial outer region of the first connecting member 61 in which the first differential input gear 51 is formed, and the second differential The radial outer region of the second connecting member 62 on which the input gear 52 is formed overlaps with each other in the axial direction.

このように、本実施形態では、軸方向Ｌに沿う軸方向視で、差動歯車機構５０と第１カウンタギヤ機構３０とが重複するとともに、差動歯車機構５０と第２カウンタギヤ機構４０とが重複するように配置されている。 As described above, in the present embodiment, the differential gear mechanism 50 and the first counter gear mechanism 30 overlap each other in the axial view along the axial direction L, and the differential gear mechanism 50 and the second counter gear mechanism 40 Are arranged so that they overlap.

これにより、車両用駆動装置１の径方向寸法をさらに小さく抑えることができる。 As a result, the radial dimension of the vehicle drive device 1 can be further reduced.

なお、本実施形態では、第１カウンタギヤ機構３０及び第２カウンタギヤ機構４０として、同じ体格のもの（ここでは特に径方向のサイズが同じもの）が用いられている。よって、差動歯車機構５０が配置される第３軸Ｘ３と第１カウンタギヤ機構３０が配置される第４軸Ｘ４との軸間距離は、第３軸Ｘ３と第２カウンタギヤ機構４０が配置される第５軸Ｘ５との軸間距離と等しくなっている。 In this embodiment, as the first counter gear mechanism 30 and the second counter gear mechanism 40, those having the same physique (here, those having the same radial size in particular) are used. Therefore, the distance between the third axis X3 in which the differential gear mechanism 50 is arranged and the fourth axis X4 in which the first counter gear mechanism 30 is arranged is such that the third axis X3 and the second counter gear mechanism 40 are arranged. It is equal to the distance between the axes and the fifth axis X5.

〔その他の実施形態〕
（１）上記の実施形態では、第３軸Ｘ３と第２軸Ｘ２との軸間距離が、第３軸Ｘ３と第１軸Ｘ１との軸間距離よりも短い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３軸Ｘ３と第２軸Ｘ２との軸間距離が、第３軸Ｘ３と第１軸Ｘ１との軸間距離と等しくても良いし、長くても良い。 [Other embodiments]
(1) In the above embodiment, the configuration in which the distance between the axes of the third axis X3 and the second axis X2 is shorter than the distance between the axes of the third axis X3 and the first axis X1 has been described as an example. However, without being limited to such a configuration, for example, the distance between the axes of the third axis X3 and the second axis X2 may be equal to the distance between the axes of the third axis X3 and the first axis X1. , May be long.

（２）上記の実施形態では、第２回転電機２０と差動歯車機構５０とが軸方向視で互いに重複するように配置されてい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２回転電機２０と差動歯車機構５０とが軸方向視で互いに重複していなくても良い。 (2) In the above embodiment, a configuration in which the second rotary electric machine 20 and the differential gear mechanism 50 are arranged so as to overlap each other in the axial direction has been described as an example. However, the present invention is not limited to such a configuration, and the second rotary electric machine 20 and the differential gear mechanism 50 may not overlap each other in the axial direction.

（３）上記の実施形態では、第１カウンタ入力ギヤ３１の軸方向Ｌの配置領域と第２カウンタ入力ギヤ４１の軸方向Ｌの配置領域とが重複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、第１カウンタ入力ギヤ３１と第２カウンタ入力ギヤ４１とは重複せず、例えば第１カウンタ軸３３の軸方向第２側Ｌ２の端部と第２カウンタ軸４３の軸方向第１側Ｌ１の端部だけが重複しても良い。 (3) In the above embodiment, a configuration in which the arrangement area of the first counter input gear 31 in the axial direction L and the arrangement area of the second counter input gear 41 in the axial direction L overlap has been described as an example. However, without being limited to such a configuration, the first counter input gear 31 and the second counter input gear 41 do not overlap, for example, the end of the second side L2 in the axial direction of the first counter shaft 33 and the second counter. 2 Only the end portion of the first side L1 in the axial direction of the counter shaft 43 may overlap.

（４）上記の実施形態では、第１回転電機１０の外縁と差動歯車機構５０の外縁とが、軸方向視で接するような位置関係で配置されている構成を例として説明した。しかし、そのような構成には限定されない。例えば、第１回転電機１０の外縁と差動歯車機構５０の外縁とが、軸方向視で、径方向に互いに離間した位置関係で配置されていても良い。或いは、第１回転電機１０と差動歯車機構５０とが、軸方向視で重複するように配置されていても良い。この場合、差動歯車機構５０における、第１回転電機１０の第１ステータ１１よりも軸方向第２側Ｌ２に配置された部分、具体的には、第１差動入力ギヤ５１及び第２差動入力ギヤ５２が、軸方向視で第１回転電機１０の第１ステータ１１と重複するように配置される。 (4) In the above embodiment, the configuration in which the outer edge of the first rotary electric machine 10 and the outer edge of the differential gear mechanism 50 are arranged in a positional relationship so as to be in contact with each other in the axial direction has been described as an example. However, it is not limited to such a configuration. For example, the outer edge of the first rotary electric machine 10 and the outer edge of the differential gear mechanism 50 may be arranged in a positional relationship so as to be separated from each other in the radial direction in the axial direction. Alternatively, the first rotary electric machine 10 and the differential gear mechanism 50 may be arranged so as to overlap each other in the axial direction. In this case, in the differential gear mechanism 50, a portion of the first rotary electric machine 10 arranged on the second side L2 in the axial direction with respect to the first stator 11, specifically, the first differential input gear 51 and the second difference. The dynamic input gear 52 is arranged so as to overlap the first stator 11 of the first rotary electric machine 10 in the axial direction.

（５）上記の実施形態では、第１カウンタギヤ機構３０と差動歯車機構５０とが軸方向視で互いに重複するように配置されているとともに、第２カウンタギヤ機構４０と差動歯車機構５０とも軸方向視で互いに重複するように配置されてい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カウンタギヤ機構３０及び第２カウンタギヤ機構４０が軸方向視で差動歯車機構５０と重複しなくても良い。この場合、例えば第１カウンタ出力ギヤ３２が第１カウンタ入力ギヤ３１よりも大径に形成されるとともに、第２カウンタ出力ギヤ４２が第２カウンタ入力ギヤ４１よりも大径に形成されても良い。 (5) In the above embodiment, the first counter gear mechanism 30 and the differential gear mechanism 50 are arranged so as to overlap each other in the axial direction, and the second counter gear mechanism 40 and the differential gear mechanism 50 are arranged so as to overlap each other. The configuration in which they are arranged so as to overlap each other in the axial direction is described as an example. However, the first counter gear mechanism 30 and the second counter gear mechanism 40 do not have to overlap with the differential gear mechanism 50 in the axial direction without being limited to such a configuration. In this case, for example, the first counter output gear 32 may be formed to have a larger diameter than the first counter input gear 31, and the second counter output gear 42 may be formed to have a larger diameter than the second counter input gear 41. ..

（６）上記の実施形態では、差動歯車機構５０がラビニヨ型の遊星歯車機構を含んで構成されている例について説明した。しかし、そのような構成に限定されることなく、差動歯車機構５０が、ラビニヨ型とは異なる構成の遊星歯車機構、或いは、遊星歯車機構以外の差動歯車機構を含んで構成されても良い。 (6) In the above embodiment, an example in which the differential gear mechanism 50 is configured to include a labigno-type planetary gear mechanism has been described. However, without being limited to such a configuration, the differential gear mechanism 50 may be configured to include a planetary gear mechanism having a configuration different from that of the ravinyo type, or a differential gear mechanism other than the planetary gear mechanism. ..

（７）上記の実施形態では、第１駆動力源及び第２駆動力源がいずれも回転電機（第１回転電機１０、第２回転電機２０）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、第１駆動力源及び第２駆動力源の少なくとも一方として、回転電機以外の駆動力源を用いても良い。回転電機以外の駆動力源としては、例えば内燃機関を例示することができる。なお、内燃機関とは、機関内部における燃料の燃焼により駆動されて動力を取り出す原動機（ガソリンエンジン、ディーゼルエンジン等）である。 (7) In the above embodiment, the configuration in which the first driving force source and the second driving force source are both rotary electric machines (first rotary electric machine 10 and second rotary electric machine 20) has been described as an example. However, without being limited to such a configuration, a driving force source other than the rotary electric machine may be used as at least one of the first driving force source and the second driving force source. As a driving force source other than the rotary electric machine, for example, an internal combustion engine can be exemplified. The internal combustion engine is a prime mover (gasoline engine, diesel engine, etc.) that is driven by the combustion of fuel inside the engine to extract power.

（８）上述した各実施形態（上記の実施形態及びその他の実施形態を含む；以下同様）で開示される構成は、矛盾が生じない限り、他の実施形態で開示される構成と組み合わせて適用することも可能である。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例示であって、本開示の趣旨を逸脱しない範囲内で適宜改変することが可能である。 (8) The configurations disclosed in each of the above-described embodiments (including the above-described embodiment and other embodiments; the same shall apply hereinafter) shall be applied in combination with the configurations disclosed in the other embodiments as long as there is no contradiction. It is also possible to do. As for other configurations, the embodiments disclosed in the present specification are exemplary in all respects, and can be appropriately modified without departing from the spirit of the present disclosure.

１：車両用駆動装置、３：動力伝達装置、９：ケース、１０：第１回転電機（第１駆動力源）、１１：第１ステータ、１２：第１ロータ（第１駆動力源の回転体）、１５：第１入力軸、１６：第１入力ギヤ（第１ギヤ）、２０：第２回転電機（第２駆動力源）、２１：第２ステータ、２２：第２ロータ（第２駆動力源の回転体）、２５：第２入力軸、２６：第２入力ギヤ（第２ギヤ）、３０：第１カウンタギヤ機構、３１：第１カウンタ入力ギヤ（第３ギヤ）、３２：第１カウンタ出力ギヤ（第４ギヤ）、３３：第１カウンタ軸、４０：第２カウンタギヤ機構、４１：第２カウンタ入力ギヤ（第５ギヤ）、４２：第２カウンタ出力ギヤ（第６ギヤ）、４３：第２カウンタ軸、５０：差動歯車機構、５１：第１差動入力ギヤ（第７ギヤ）、５２：第２差動入力ギヤ（第８ギヤ）、５３：第１サンギヤ、５４：第２サンギヤ、５５：リングギヤ、５６：キャリヤ、５７：第１ピニオンギヤ、５８：第２ピニオンギヤ、５９：ピニオン軸、６１：第１連結部材、６２：第２連結部材、６３：第１連結軸、６４：第２連結軸、６５：サンギヤ形成部材、７０Ａ：第１出力部材、７０Ｂ：第２出力部材、９１：第１ケース部、９１Ａ：第１周壁部、９１Ｂ：第１隔壁部、９２：第２ケース部、９２Ａ：第２周壁部、９２Ｂ：第２隔壁部、９３：第１カバー部、９３Ａ：第３周壁部、９３Ｂ：第１側壁部、９４：第２カバー部、９４Ａ：第４周壁部、９４Ｂ：第２側壁部、Ｌ：軸方向、Ｌ１：軸方向第１側、Ｌ２：軸方向第２側、Ｗ１：第１車輪、Ｗ２：第２車輪、Ｘ１：第１軸、Ｘ２：第２軸、Ｘ３：第３軸、Ｘ４：第４軸、Ｘ５：第５軸 1: Vehicle drive device, 3: Power transmission device, 9: Case, 10: First rotary electric machine (first drive force source), 11: First stator, 12: First rotor (first drive force source rotation) Body), 15: 1st input shaft, 16: 1st input gear (1st gear), 20: 2nd rotary electric machine (2nd driving force source), 21: 2nd stator, 22: 2nd rotor (2nd) (Rotating body of driving force source), 25: 2nd input shaft, 26: 2nd input gear (2nd gear), 30: 1st counter gear mechanism, 31: 1st counter input gear (3rd gear), 32: 1st counter output gear (4th gear), 33: 1st counter shaft, 40: 2nd counter gear mechanism, 41: 2nd counter input gear (5th gear), 42: 2nd counter output gear (6th gear) ), 43: 2nd counter shaft, 50: differential gear mechanism, 51: 1st differential input gear (7th gear), 52: 2nd differential input gear (8th gear), 53: 1st sun gear, 54: 2nd sun gear, 55: ring gear, 56: carrier, 57: 1st pinion gear, 58: 2nd pinion gear, 59: pinion shaft, 61: 1st connecting member, 62: 2nd connecting member, 63: 1st connecting Shaft, 64: 2nd connecting shaft, 65: Sun gear forming member, 70A: 1st output member, 70B: 2nd output member, 91: 1st case part, 91A: 1st peripheral wall part, 91B: 1st partition wall part, 92: 2nd case part, 92A: 2nd peripheral wall part, 92B: 2nd partition wall part, 93: 1st cover part, 93A: 3rd peripheral wall part, 93B: 1st side wall part, 94: 2nd cover part, 94A : 4th peripheral wall part, 94B: 2nd side wall part, L: axial direction, L1: axial 1st side, L2: axial 2nd side, W1: 1st wheel, W2: 2nd wheel, X1: 1st Axis, X2: 2nd axis, X3: 3rd axis, X4: 4th axis, X5: 5th axis

Claims (5)

第１駆動力源と、第２駆動力源と、第１車輪に駆動連結される第１出力部材と、第２車輪に駆動連結される第２出力部材と、動力伝達装置と、を備えた車両用駆動装置であって、
前記第１駆動力源は、第１軸上に配置され、
前記第２駆動力源は、前記第１軸とは異なる第２軸上に配置され、
前記第１出力部材及び前記第２出力部材は、前記第１軸及び前記第２軸とは異なる第３軸上に配置され、
前記動力伝達装置は、前記第１駆動力源の回転体と一体的に回転する第１ギヤと、前記第２駆動力源の回転体と一体的に回転する第２ギヤと、前記第１軸、前記第２軸、及び前記第３軸とは異なる第４軸上に配置される第１カウンタギヤ機構と、前記第１軸、前記第２軸、前記第３軸、及び前記第４軸とは異なる第５軸上に配置される第２カウンタギヤ機構と、前記第３軸上に配置される差動歯車機構と、を備え、
前記第１カウンタギヤ機構は、前記第１ギヤに噛み合う第３ギヤと、前記第３ギヤと一体的に回転する第４ギヤと、を備え、
前記第２カウンタギヤ機構は、前記第２ギヤに噛み合う第５ギヤと、前記第５ギヤと一体的に回転する第６ギヤと、を備え、
前記差動歯車機構は、前記第４ギヤに噛み合う第７ギヤと、前記第６ギヤに噛み合う第８ギヤと、を備え、前記第１駆動力源から前記第７ギヤに伝達された駆動力及び前記第２駆動力源から前記第８ギヤに伝達された駆動力を、前記第１出力部材と前記第２出力部材とに分配して出力するように構成され、
前記第１軸、前記第２軸、前記第３軸、前記第４軸、及び前記第５軸は、互いに平行に配置され、
前記第１軸、前記第２軸、前記第３軸、前記第４軸、及び前記第５軸に平行な方向を軸方向とし、前記軸方向の一方側を軸方向第１側とするとともに他方側を軸方向第２側として、
前記第１駆動力源は前記第１ギヤに対して前記軸方向第１側に配置され、前記第２駆動力源は前記第２ギヤに対して前記軸方向第２側に配置され、
前記第１カウンタギヤ機構の前記軸方向の配置領域と、前記第２カウンタギヤ機構の前記軸方向の配置領域とが重複している、車両用駆動装置。 It includes a first driving force source, a second driving force source, a first output member that is driven and connected to the first wheel, a second output member that is driven and connected to the second wheel, and a power transmission device. It is a vehicle drive device
The first driving force source is arranged on the first axis.
The second driving force source is arranged on a second axis different from the first axis.
The first output member and the second output member are arranged on a third axis different from the first axis and the second axis.
The power transmission device includes a first gear that rotates integrally with the rotating body of the first driving force source, a second gear that rotates integrally with the rotating body of the second driving force source, and the first shaft. A first counter gear mechanism arranged on a fourth axis different from the second axis and the third axis, and the first axis, the second axis, the third axis, and the fourth axis. A second counter gear mechanism arranged on a different fifth axis and a differential gear mechanism arranged on the third axis.
The first counter gear mechanism includes a third gear that meshes with the first gear and a fourth gear that rotates integrally with the third gear.
The second counter gear mechanism includes a fifth gear that meshes with the second gear and a sixth gear that rotates integrally with the fifth gear.
The differential gear mechanism includes a seventh gear that meshes with the fourth gear and an eighth gear that meshes with the sixth gear, and the driving force transmitted from the first driving force source to the seventh gear and The driving force transmitted from the second driving force source to the eighth gear is configured to be distributed and output to the first output member and the second output member.
The first axis, the second axis, the third axis, the fourth axis, and the fifth axis are arranged in parallel with each other.
The direction parallel to the first axis, the second axis, the third axis, the fourth axis, and the fifth axis is the axial direction, and one side of the axial direction is the first side in the axial direction and the other. With the side as the second side in the axial direction,
The first driving force source is arranged on the first side in the axial direction with respect to the first gear, and the second driving force source is arranged on the second side in the axial direction with respect to the second gear.
A vehicle drive device in which the axially arranged area of the first counter gear mechanism and the axially arranged area of the second counter gear mechanism overlap. 前記差動歯車機構の前記軸方向の配置領域が、前記第１駆動力源の前記軸方向の配置領域と重複し、かつ、前記第２駆動力源の前記軸方向の配置領域とは重複せず、
前記第２軸と前記第３軸との軸間距離が、前記第１軸と前記第３軸との軸間距離よりも短い、請求項１に記載の車両用駆動装置。 The axially arranged area of the differential gear mechanism overlaps with the axially arranged area of the first driving force source, and overlaps with the axially arranged area of the second driving force source. figure,
The vehicle drive device according to claim 1, wherein the distance between the second axis and the third axis is shorter than the distance between the first axis and the third axis. 前記軸方向に沿う軸方向視で、前記第２駆動力源と前記差動歯車機構とが重複するように配置されている、請求項２に記載の車両用駆動装置。 The vehicle drive device according to claim 2, wherein the second driving force source and the differential gear mechanism are arranged so as to overlap each other in an axial direction along the axial direction. 前記第３ギヤの前記軸方向の配置領域と前記第５ギヤの前記軸方向の配置領域とが重複し、
前記第４ギヤの前記軸方向の配置領域と前記第６ギヤの前記軸方向の配置領域とが重複していない、請求項１から３のいずれか一項に記載の車両用駆動装置。 The axially arranged area of the third gear and the axially arranged area of the fifth gear overlap with each other.
The vehicle drive device according to any one of claims 1 to 3, wherein the axially arranged area of the fourth gear and the axially arranged area of the sixth gear do not overlap. 前記軸方向に沿う軸方向視で、前記差動歯車機構と前記第１カウンタギヤ機構とが重複するとともに、前記差動歯車機構と前記第２カウンタギヤ機構とが重複するように配置されている、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 differential gear mechanism and the first counter gear mechanism overlap each other in the axial view along the axial direction, and the differential gear mechanism and the second counter gear mechanism are arranged so as to overlap each other. , The vehicle drive device according to any one of claims 1 to 4.
JP2020182252A 2020-10-30 2020-10-30 Vehicle drive device Active JP7476761B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2020182252A JP7476761B2 (en) 2020-10-30 2020-10-30 Vehicle drive device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2020182252A JP7476761B2 (en) 2020-10-30 2020-10-30 Vehicle drive device

Publications (2)

Publication Number Publication Date
JP2022072678A true JP2022072678A (en) 2022-05-17
JP7476761B2 JP7476761B2 (en) 2024-05-01

Family

ID=81603898

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2020182252A Active JP7476761B2 (en) 2020-10-30 2020-10-30 Vehicle drive device

Country Status (1)

Country Link
JP (1) JP7476761B2 (en)

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020179202A1 (en) 2019-03-06 2020-09-10 三菱自動車工業株式会社 Left-right wheel driving device
CN111332113A (en) 2020-03-16 2020-06-26 上海电气集团股份有限公司 Electric vehicle double-motor planetary gear train stepless speed change electric drive system

Also Published As

Publication number Publication date
JP7476761B2 (en) 2024-05-01

Similar Documents

Publication Publication Date Title
WO2021039966A1 (en) Vehicle driving device
US9534665B1 (en) Electrical all-wheel drive
JP6197469B2 (en) Vehicle drive device
JP7215585B2 (en) Vehicle drive transmission device
JP6849092B2 (en) Vehicle drive
JP6852800B2 (en) Vehicle drive
JP6856140B2 (en) Vehicle drive
WO2021106349A1 (en) Driving device for vehicle
JP6915197B2 (en) Vehicle drive
WO2018181557A1 (en) Vehicle drive device
WO2018079842A1 (en) Vehicle drive device
JP2022072678A (en) Vehicular drive device
JP2016222118A (en) Drive unit for vehicle
JP2022125649A (en) Vehicle drive device
CN113710527B (en) Transmission device for hybrid vehicle
WO2020230441A1 (en) Vehicle drive device
WO2020261669A1 (en) Vehicle driving device
JP2014065426A (en) Vehicular running gear
WO2018079843A1 (en) Vehicle drive transmission apparatus
WO2022138072A1 (en) Drive device for vehicle
JP6964509B2 (en) Vehicle drive
JP5747383B2 (en) Power transmission device
WO2021085611A1 (en) Vehicle drive device
JP2022152833A (en) Vehicle drive device
JP2013060161A (en) Electrically-driven device

Legal Events

Date Code Title Description
A711 Notification of change in applicant

Free format text: JAPANESE INTERMEDIATE CODE: A712

Effective date: 20210423

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20230801

TRDD Decision of grant or rejection written
A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20240314

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20240319

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20240401

R150 Certificate of patent or registration of utility model

Ref document number: 7476761

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150