JP7635604B2 - Friction engagement device and vehicle drive device - Google Patents

Friction engagement device and vehicle drive device Download PDF

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JP7635604B2
JP7635604B2 JP2021055750A JP2021055750A JP7635604B2 JP 7635604 B2 JP7635604 B2 JP 7635604B2 JP 2021055750 A JP2021055750 A JP 2021055750A JP 2021055750 A JP2021055750 A JP 2021055750A JP 7635604 B2 JP7635604 B2 JP 7635604B2
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裕紀 市川
孝之 土井
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Aisin Corp
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Description

本発明は、摩擦係合装置及び車両用駆動装置に関する。 The present invention relates to a friction engagement device and a vehicle drive device.

複数の摩擦材どうしを互いに押し付けるように押圧する押圧部材として、回転部材と一体的に回転する第１押圧部材と、非回転部材に支持されて第１押圧部材と相対回転する第２押圧部材とを備えた、静止シリンダ型の摩擦係合装置が利用されている。このような静止シリンダ型の摩擦係合装置の一例が、特開平１０－１２２２６０号公報（特許文献１）に開示されている。 A stationary cylinder type friction engagement device is used that is equipped with a first pressing member that rotates integrally with a rotating member and a second pressing member that is supported by a non-rotating member and rotates relative to the first pressing member as a pressing member that presses multiple friction materials against each other. An example of such a stationary cylinder type friction engagement device is disclosed in JP-A-10-122260 (Patent Document 1).

特許文献１の摩擦係合装置において、摩擦材（摩擦材ディスク５２及びセパレータプレート５１）を潤滑するのに、径方向内側から供給される油でその潤滑を行うことが考えられる。しかし、特許文献１の摩擦係合装置では、第１支持部材（ハブ５３）と付勢部材（リターンスプリング５８）を保持するための保持部材（スプリングリテーナ５８ａ）とに囲まれた領域に油が溜まるような構造となっている。第１支持部材は回転部材であるから、当該第１支持部材の回転中に、溜まった油に遠心油圧が生じて、付勢部材とは別に押圧部材（押圧部材３３）を押し戻すように作用する場合がある。このような遠心油圧はばらつきが大きいため、摩擦係合装置の制御性が悪くなるという問題があった。 In the friction engagement device of Patent Document 1, it is conceivable to lubricate the friction material (friction material disk 52 and separator plate 51) with oil supplied from the radial inside. However, the friction engagement device of Patent Document 1 is structured so that oil accumulates in an area surrounded by the first support member (hub 53) and a retaining member (spring retainer 58a) for retaining the biasing member (return spring 58). Because the first support member is a rotating member, centrifugal oil pressure is generated in the accumulated oil while the first support member is rotating, and this may act to push back the pressing member (pressing member 33) separately from the biasing member. Such centrifugal oil pressure varies widely, which causes a problem of poor controllability of the friction engagement device.

特開平１０－１２２２６０号公報Japanese Patent Application Publication No. 10-122260

そこで、摩擦材の潤滑を適切に行いつつ、摩擦係合装置の制御性を向上させることが望まれている。 Therefore, it is desirable to improve the controllability of the friction engagement device while properly lubricating the friction material.

本開示に係る摩擦係合装置は、
第１摩擦材を支持する第１摩擦材支持部を備え、回転可能に支持された第１支持部材と、
第２摩擦材を支持する第２摩擦材支持部を備え、前記第１支持部材とは独立して回転可能に支持された第２支持部材と、
前記第１支持部材と一体的に回転するとともに当該第１支持部材に対して軸方向に移動自在に支持され、前記第１摩擦材と前記第２摩擦材とを互いに押し付けるように前記第１摩擦材及び前記第２摩擦材を前記軸方向に押圧する第１押圧部材と、
非回転部材に対して前記軸方向に移動自在に支持され、前記第１押圧部材と相対回転自在な状態で当該第１押圧部材を前記軸方向に押圧する第２押圧部材と、
前記第２押圧部材を前記軸方向に駆動する押圧駆動部と、を備え、
前記第１摩擦材支持部は、前記軸方向に沿う筒状に形成され、
前記第２摩擦材支持部は、前記第１摩擦材支持部よりも径方向の外側に当該第１摩擦材支持部と同軸に配置され、
前記第１摩擦材は、前記第１摩擦材支持部と一体的に回転するように連結され、
前記第２摩擦材は、前記第２摩擦材支持部と一体的に回転するように連結され、
前記第１摩擦材及び前記第２摩擦材は、前記第１摩擦材支持部と前記第２摩擦材支持部との前記径方向の間において、互いに前記軸方向に対向するように配置され、
前記第１支持部材は、前記第１摩擦材支持部から前記径方向の内側へ向けて延在する径方向延在部をさらに備え、
前記第１押圧部材は、前記第１摩擦材支持部の内周面に沿って摺動する摺動部を備え、
前記第１摩擦材支持部の内周面と前記径方向延在部と前記摺動部とに囲まれた領域に油溜め部が形成され、
前記油溜め部に油を供給する油供給部が設けられ、
前記第１摩擦材支持部に、前記油溜め部と前記第１摩擦材及び前記第２摩擦材が配置された摩擦材配置領域とを連通する第１油路が設けられ、
前記第１支持部材及び前記第１押圧部材の少なくとも一方に、前記油溜め部と前記摩擦材配置領域以外の空間とを連通する第２油路が設けられ、
前記第１油路における前記油溜め部側に開口する開口部を第１開口部とし、前記第２油路における前記油溜め部側に開口する開口部を第２開口部として、前記第２開口部が前記第１開口部に対して前記径方向の内側に離間して配置されている。 The friction engagement device according to the present disclosure comprises:
a first support member including a first friction material support portion that supports a first friction material and is rotatably supported;
a second support member including a second friction material support portion that supports a second friction material, the second support member being supported rotatably independent of the first support member;
a first pressing member that rotates integrally with the first support member, is supported by the first support member so as to be movable in the axial direction, and presses the first friction material and the second friction material in the axial direction so as to press the first friction material and the second friction material against each other;
a second pressing member that is supported on the non-rotating member so as to be movable in the axial direction and presses the first pressing member in the axial direction while being rotatable relative to the first pressing member;
a pressing drive unit that drives the second pressing member in the axial direction,
The first friction material support portion is formed in a cylindrical shape along the axial direction,
the second friction material support portion is disposed radially outward of the first friction material support portion and coaxially with the first friction material support portion,
The first friction material is connected to the first friction material support portion so as to rotate integrally with the first friction material support portion,
the second friction material is connected to the second friction material support portion so as to rotate integrally with the second friction material,
the first friction material and the second friction material are disposed between the first friction material support portion and the second friction material support portion in the radial direction so as to face each other in the axial direction,
The first support member further includes a radially extending portion extending inward in the radial direction from the first friction material support portion,
the first pressing member includes a sliding portion that slides along an inner circumferential surface of the first friction material support portion,
an oil reservoir is formed in a region surrounded by an inner circumferential surface of the first friction material support portion, the radially extending portion, and the sliding portion;
an oil supply unit that supplies oil to the oil reservoir;
a first oil passage is provided in the first friction material support portion, the first oil passage communicating with the oil reservoir and a friction material arrangement area in which the first friction material and the second friction material are arranged;
At least one of the first support member and the first pressing member is provided with a second oil passage that communicates the oil reservoir with a space other than the friction material arrangement area,
An opening in the first oil passage that opens toward the oil reservoir is designated as a first opening, and an opening in the second oil passage that opens toward the oil reservoir is designated as a second opening, and the second opening is positioned radially inward and spaced apart from the first opening.

この構成によれば、油供給部から供給されて油溜め部に溜まった油を、第１油路を介して摩擦材配置領域に供給することができる。よって、第１摩擦材及び第２摩擦材の潤滑を適切に行うことができる。また、油溜め部に溜まった油のうち、第２開口部よりも径方向の内側にある油を、第２油路を介して、油溜め部の外に排出することができる。これにより、油溜め部に溜まる油の量が多くなり過ぎないように規制することができる。よって、油溜め部に溜まる油による遠心油圧によって第１押圧部材が受ける影響を少なく抑えることができ、その結果、摩擦係合装置の制御性を向上させることができる。 According to this configuration, the oil supplied from the oil supply unit and stored in the oil reservoir can be supplied to the friction material arrangement area via the first oil passage. This allows the first and second friction materials to be properly lubricated. In addition, the oil stored in the oil reservoir that is radially inward of the second opening can be discharged to the outside of the oil reservoir via the second oil passage. This makes it possible to regulate the amount of oil that accumulates in the oil reservoir so that it does not become too large. This makes it possible to minimize the effect of centrifugal oil pressure caused by the oil stored in the oil reservoir on the first pressing member, thereby improving the controllability of the friction engagement device.

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 technology disclosed herein will become more apparent from the following description of exemplary, non-limiting embodiments, which are 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1 is a skeleton diagram of a vehicle drive device according to an embodiment of the present invention; 車両用駆動装置の断面図Cross-sectional view of a vehicle drive device 車両用駆動装置の拡大断面図Enlarged cross-sectional view of a vehicle drive device 車両用駆動装置の拡大断面図Enlarged cross-sectional view of a vehicle drive device 車両用駆動装置を軸方向から見た模式図FIG. 1 is a schematic diagram of a vehicle drive device as viewed from an axial direction;

摩擦係合装置を含む変速機を備えた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、本実施形態の車両用駆動装置１００は、概略的には、変速機１と、回転電機２と、差動歯車機構３と、それぞれが車輪Ｗに駆動連結される一対の出力部材４とを備えている。また、変速機１は、第１ギヤ１２及び第２ギヤ１４を備えた第１軸部材１０と、第３ギヤ２２及び第４ギヤ２４を支持するとともに出力ギヤ２５を備えた第２軸部材２０と、噛み合い式係合装置３０と、摩擦係合装置４０とを備えている。これらは、ケース（駆動装置ケース）６内に収容されている。なお、出力部材４の一部は、ケース６の外部に露出している。 An embodiment of a vehicle drive device having a transmission including a friction engagement device will be described with reference to the drawings. As shown in Figs. 1 and 2, the vehicle drive device 100 of this embodiment generally includes a transmission 1, a rotating electric machine 2, a differential gear mechanism 3, and a pair of output members 4 each of which is drivingly connected to wheels W. The transmission 1 also includes a first shaft member 10 including a first gear 12 and a second gear 14, a second shaft member 20 supporting a third gear 22 and a fourth gear 24 and including an output gear 25, a meshing engagement device 30, and a friction engagement device 40. These are housed in a case (drive device case) 6. A portion of the output member 4 is exposed to the outside of the case 6.

ここで、「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。 Here, the term "rotating electric machine" is used as a concept that includes motors, generators, and motor-generators that function as both motors and generators as necessary.

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。 In addition, "driving connection" refers to a state in which two rotating elements are connected so that they can transmit a driving force. This concept includes a state in which two rotating elements are connected so that they rotate as a unit, and a state in which two rotating elements are connected so that they can 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 a variable speed, and may also include engagement devices (friction engagement devices, meshing engagement devices, etc.) that selectively transmit rotation and driving force.

回転電機２及び第１軸部材１０は、第１軸Ｘ１上に配置されている。第２軸部材２０、噛み合い式係合装置３０、及び摩擦係合装置４０は、第２軸Ｘ２上に配置されている。差動歯車機構３及び出力部材４は、第３軸Ｘ３上に配置されている。第１軸Ｘ１、第２軸Ｘ２、及び第３軸Ｘ３は、互いに異なる平行な軸であり、以下ではこれらに平行な方向を「軸方向Ｌ」と言う。また、軸方向Ｌの一方側（本例では図１における左側）を軸方向第１側Ｌ１と言い、その反対側である軸方向Ｌの他方側（本例では図１における右側）を軸方向第２側Ｌ２と言う。また、以下では、軸方向Ｌに沿って見た状態を「軸方向視」と言う。 The rotating electric machine 2 and the first shaft member 10 are arranged on the first axis X1. The second shaft member 20, the meshing type engagement device 30, and the friction engagement device 40 are arranged on the second axis X2. The differential gear mechanism 3 and the output member 4 are arranged on the third axis X3. The first axis X1, the second axis X2, and the third axis X3 are parallel axes different from one another, and the direction parallel to these axes will be referred to as the "axial direction L" below. In addition, one side of the axial direction L (the left side in FIG. 1 in this example) will be referred to as the first axial side L1, and the other side of the axial direction L (the right side in FIG. 1 in this example) will be referred to as the second axial side L2. In addition, the state viewed along the axial direction L will be referred to as the "axial view" below.

回転電機２は、ケース６に固定されたステータ２Ａと、このステータ２Ａの径方向内側に回転自在に支持されたロータ２Ｂとを備えている。回転電機２は、蓄電装置（図示せず）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って発電した電力を蓄電装置に供給して蓄電させる。ロータ２Ｂは、ロータ軸２Ｃと一体的に回転するように連結されている。ロータ軸２Ｃは、軸方向Ｌの２箇所で、ロータ軸受９１（図２を参照）によってケース６に対して回転自在に支持されている。ロータ軸２Ｃは、軸方向第１側Ｌ１の端部で、変速機１の第１軸部材１０と一体的に回転するように連結されている。 The rotating electric machine 2 includes a stator 2A fixed to the case 6 and a rotor 2B supported rotatably on the radial inside of the stator 2A. The rotating electric machine 2 receives power from an electric storage device (not shown) to run, or supplies electric power generated by the inertial force of the vehicle or the like to the electric storage device for storage. The rotor 2B is connected to the rotor shaft 2C so as to rotate integrally therewith. The rotor shaft 2C is supported rotatably relative to the case 6 at two points in the axial direction L by rotor bearings 91 (see FIG. 2). The rotor shaft 2C is connected to the first shaft member 10 of the transmission 1 at the end of the first axial side L1 so as to rotate integrally therewith.

変速機１は、回転電機２側からの回転を変速して車輪Ｗ側に伝達する。本実施形態の変速機１は、第１ギヤ１２及び第２ギヤ１４を備えた第１軸部材１０と、第３ギヤ２２及び第４ギヤ２４を支持するとともに出力ギヤ２５を備えた第２軸部材２０と、噛み合い式係合装置３０と、摩擦係合装置４０とを備えている。噛み合い式係合装置３０が、第３ギヤ２２及び第４ギヤ２４のいずれか一方を第２軸部材２０に対して選択的に連結することで、変速機１は、回転電機２側からの回転を２段階に変速して車輪Ｗ側に伝達することができる。摩擦係合装置４０は、噛み合い式係合装置３０が第４ギヤ２４を第２軸部材２０に対して連結する際に、係合状態となることで、第４ギヤ２４と第２軸部材２０との回転速度を同期させる。 The transmission 1 changes the speed of the rotation from the rotating electric machine 2 and transmits it to the wheels W. The transmission 1 of this embodiment includes a first shaft member 10 having a first gear 12 and a second gear 14, a second shaft member 20 supporting a third gear 22 and a fourth gear 24 and having an output gear 25, a meshing engagement device 30, and a friction engagement device 40. The meshing engagement device 30 selectively connects either the third gear 22 or the fourth gear 24 to the second shaft member 20, so that the transmission 1 can change the speed of the rotation from the rotating electric machine 2 in two stages and transmit it to the wheels W. The friction engagement device 40 is engaged when the meshing engagement device 30 connects the fourth gear 24 to the second shaft member 20, thereby synchronizing the rotational speeds of the fourth gear 24 and the second shaft member 20.

本実施形態では、噛み合い式係合装置３０は、軸方向Ｌにおいて、第３ギヤ２２と第４ギヤ２４との間に配置されている。また、摩擦係合装置４０は、第３ギヤ２２及び第４ギヤ２４に対して軸方向第１側Ｌ１に配置されている。また、出力ギヤ２５は、第３ギヤ２２及び第４ギヤ２４に対して軸方向第２側Ｌ２に配置されている。 In this embodiment, the meshing engagement device 30 is disposed between the third gear 22 and the fourth gear 24 in the axial direction L. The friction engagement device 40 is disposed on the first axial side L1 relative to the third gear 22 and the fourth gear 24. The output gear 25 is disposed on the second axial side L2 relative to the third gear 22 and the fourth gear 24.

差動歯車機構３は、差動入力ギヤ３Ａを備えており、この差動入力ギヤ３Ａに入力される変速機１側からの回転及びトルクを、一対の出力部材４に分配して伝達する。一対の出力部材４は、それぞれが車輪Ｗに駆動連結されている。このように、回転電機２の側から伝達される回転が、変速機１を介して差動歯車機構３に伝達され、さらに差動歯車機構３により一対の出力部材４に分配され、さらに一対の車輪Ｗに伝達される。これにより、車両用駆動装置１００は、回転電機２のトルクを車輪Ｗに伝達させて車両を走行させることができる。 The differential gear mechanism 3 has a differential input gear 3A, and distributes and transmits the rotation and torque from the transmission 1 side that is input to this differential input gear 3A to a pair of output members 4. Each of the pair of output members 4 is drivingly connected to the wheels W. In this way, the rotation transmitted from the rotating electric machine 2 side is transmitted to the differential gear mechanism 3 via the transmission 1, and is further distributed by the differential gear mechanism 3 to the pair of output members 4, and further transmitted to the pair of wheels W. In this way, the vehicle drive device 100 can transmit the torque of the rotating electric machine 2 to the wheels W to run the vehicle.

図２に示すように、ケース６は、第１ケース部６Ａと第２ケース部６Ｂと第３ケース部６Ｃとを備えている。第１ケース部６Ａは、第２ケース部６Ｂ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６Ａは、変速機１及び差動歯車機構３を収容している。第１ケース部６Ａは、変速機１及び差動歯車機構３の径方向外側を覆う第１周壁部６Ａａと、変速機１及び差動歯車機構３の軸方向第１側Ｌ１を覆う第１支持壁部６Ａｂとを備えている。第２ケース部６Ｂは回転電機２を収容している。第２ケース部６Ｂは、回転電機２の径方向外側を覆う第２周壁部６Ｂａと、回転電機２の軸方向第１側Ｌ１を覆う第２支持壁部６Ｂｂとを備えている。図示の例では、変速機１及び差動歯車機構３の一部も、第２ケース部６Ｂに収容されている。第３ケース部６Ｃは、第１ケース部６Ａ及び第２ケース部６Ｂの内部で、変速機１及び差動歯車機構３の収容空間と回転電機２の収容空間とを区画している。 As shown in FIG. 2, the case 6 includes a first case portion 6A, a second case portion 6B, and a third case portion 6C. The first case portion 6A is joined to the second case portion 6B from the first axial side L1. The first case portion 6A houses the transmission 1 and the differential gear mechanism 3. The first case portion 6A includes a first peripheral wall portion 6Aa that covers the radial outside of the transmission 1 and the differential gear mechanism 3, and a first support wall portion 6Ab that covers the first axial side L1 of the transmission 1 and the differential gear mechanism 3. The second case portion 6B houses the rotating electric machine 2. The second case portion 6B includes a second peripheral wall portion 6Ba that covers the radial outside of the rotating electric machine 2, and a second support wall portion 6Bb that covers the first axial side L1 of the rotating electric machine 2. In the illustrated example, the transmission 1 and a part of the differential gear mechanism 3 are also housed in the second case portion 6B. The third case portion 6C separates the space inside the first case portion 6A and the second case portion 6B into a space for accommodating the transmission 1 and the differential gear mechanism 3 and a space for accommodating the rotating electric machine 2.

図２及び図３に示すように、変速機１は、第１ギヤ１２及び第２ギヤ１４を備えた第１軸部材１０と、第３ギヤ２２及び第４ギヤ２４を支持するとともに出力ギヤ２５を備えた第２軸部材２０と、噛み合い式係合装置３０と、摩擦係合装置４０とを備えている。 As shown in Figures 2 and 3, the transmission 1 includes a first shaft member 10 having a first gear 12 and a second gear 14, a second shaft member 20 supporting a third gear 22 and a fourth gear 24 and having an output gear 25, a meshing engagement device 30, and a friction engagement device 40.

第１軸部材１０は、変速機１の入力部材（変速入力部材）として機能する。第１軸部材１０は、ロータ軸２Ｃに対して軸方向第１側Ｌ１に配置されている。第１軸部材１０は、その軸方向第２側Ｌ２の端部がロータ軸２Ｃに挿入された状態で、当該ロータ軸２Ｃと一体的に回転するように連結されている。また、第１軸部材１０は、軸方向Ｌの２箇所で、第１軸受９２によってケース６に対して回転自在に支持されている。第１軸部材１０は、軸方向第１側Ｌ１において、第１ケース部６Ａに対して回転自在に支持され、軸方向第２側Ｌ２において、第３ケース部６Ｃに対して回転自在に支持されている。 The first shaft member 10 functions as an input member (transmission input member) of the transmission 1. The first shaft member 10 is disposed on the first axial side L1 relative to the rotor shaft 2C. The first shaft member 10 is connected to the rotor shaft 2C so as to rotate integrally with the rotor shaft 2C with its end on the second axial side L2 inserted into the rotor shaft 2C. The first shaft member 10 is also rotatably supported by the first bearing 92 at two points in the axial direction L relative to the case 6. The first shaft member 10 is rotatably supported by the first case portion 6A on the first axial side L1, and rotatably supported by the third case portion 6C on the second axial side L2.

本実施形態では、第１ケース部６Ａの第１支持壁部６Ａｂには、軸方向第２側Ｌ２に突出する筒状の第１筒状支持部６１が形成されている（図３を参照）。この第１筒状支持部６１に、一対の第１軸受９２のうちの１つが内嵌されている。 In this embodiment, the first support wall 6Ab of the first case 6A is formed with a first cylindrical support portion 61 that protrudes toward the second axial side L2 (see FIG. 3). One of the pair of first bearings 92 is fitted into the first cylindrical support portion 61.

第１ギヤ１２及び第２ギヤ１４は、第１軸部材１０と一体的に回転するように当該第１軸部材１０に連結されている。本実施形態では、第１ギヤ１２は、第１軸部材１０の外周面に形成されている。第１ギヤ１２は、第３ギヤ２２に噛み合っている。また、第２ギヤ１４は、第１軸部材１０と一体的に回転するように当該第１軸部材１０に連結された第２ギヤ形成部材１３の外周面に形成されている。第２ギヤ１４は、第４ギヤ２４に噛み合っている。第２ギヤ１４は、第１ギヤ１２に対して、軸方向第１側Ｌ１に間隔を空けて配置されている。 The first gear 12 and the second gear 14 are connected to the first shaft member 10 so as to rotate integrally with the first shaft member 10. In this embodiment, the first gear 12 is formed on the outer peripheral surface of the first shaft member 10. The first gear 12 meshes with the third gear 22. The second gear 14 is formed on the outer peripheral surface of the second gear forming member 13 which is connected to the first shaft member 10 so as to rotate integrally with the first shaft member 10. The second gear 14 meshes with the fourth gear 24. The second gear 14 is disposed at a distance from the first gear 12 on the first axial side L1.

第２軸部材２０は、第１軸部材１０と平行に配置されている。第２軸部材２０の軸方向Ｌの配置領域は、第１軸部材１０の軸方向Ｌの配置領域に重複している。本実施形態では、第２軸部材２０の軸方向Ｌの配置領域は、第１軸部材１０の軸方向Ｌの配置領域に包含されている。また、第２軸部材２０は、軸方向Ｌの２箇所で、第２軸受９３によってケース６に対して回転自在に支持されている。第２軸部材２０は、軸方向第１側Ｌ１において、第１ケース部６Ａに対して回転自在に支持され、軸方向第２側Ｌ２において、第３ケース部６Ｃに対して回転自在に支持されている。 The second shaft member 20 is arranged parallel to the first shaft member 10. The arrangement area of the second shaft member 20 in the axial direction L overlaps with the arrangement area of the first shaft member 10 in the axial direction L. In this embodiment, the arrangement area of the second shaft member 20 in the axial direction L is included in the arrangement area of the first shaft member 10 in the axial direction L. The second shaft member 20 is supported rotatably relative to the case 6 by the second bearing 93 at two points in the axial direction L. The second shaft member 20 is supported rotatably relative to the first case portion 6A on the first axial side L1, and is supported rotatably relative to the third case portion 6C on the second axial side L2.

本実施形態では、第１ケース部６Ａの第１支持壁部６Ａｂには、軸方向第２側Ｌ２に突出する筒状の第２筒状支持部６２が形成されている（図３を参照）。この第２筒状支持部６２に、一対の第２軸受９３のうちの１つが内嵌されている。 In this embodiment, the first support wall 6Ab of the first case 6A is formed with a second cylindrical support portion 62 that protrudes toward the second axial side L2 (see FIG. 3). One of the pair of second bearings 93 is fitted into the second cylindrical support portion 62.

第３ギヤ２２及び第４ギヤ２４は、第２軸部材２０と相対回転可能な状態で当該第２軸部材２０に支持されている。本実施形態では、第３ギヤ２２は、第２軸部材２０に対して軸受を介して回転可能に支持された第３ギヤ形成部材２１の外周面に形成されている。第３ギヤ２２は、第１ギヤ１２に噛み合っている。また、第４ギヤ２４は、第２軸部材２０に対して軸受を介して回転可能に支持された第４ギヤ形成部材２３の外周面に形成されている。第４ギヤ２４は、第２ギヤ１４に噛み合っている。図示の例では、第３ギヤ形成部材２１及び第４ギヤ形成部材２３を支持する軸受には、針状ころ軸受が用いられている。 The third gear 22 and the fourth gear 24 are supported by the second shaft member 20 in a state in which they can rotate relative to the second shaft member 20. In this embodiment, the third gear 22 is formed on the outer peripheral surface of the third gear forming member 21, which is rotatably supported on the second shaft member 20 via a bearing. The third gear 22 meshes with the first gear 12. The fourth gear 24 is formed on the outer peripheral surface of the fourth gear forming member 23, which is rotatably supported on the second shaft member 20 via a bearing. The fourth gear 24 meshes with the second gear 14. In the illustrated example, needle roller bearings are used as the bearings that support the third gear forming member 21 and the fourth gear forming member 23.

なお、本実施形態では、第１ギヤ１２は第２ギヤ１４よりも小径であり、それに対応して、第３ギヤ２２は第４ギヤ２４よりも大径となっている。 In this embodiment, the first gear 12 has a smaller diameter than the second gear 14, and correspondingly, the third gear 22 has a larger diameter than the fourth gear 24.

出力ギヤ２５は、第２軸部材２０と一体的に回転するように当該第２軸部材２０に連結されている。本実施形態では、出力ギヤ２５は、第２軸部材２０の外周面に形成されている。出力ギヤ２５は、第３ギヤ２２が形成された第３ギヤ形成部材２１に対して軸方向第２側Ｌ２に隣接する位置に形成されている。出力ギヤ２５は、変速機１の出力部材（変速出力部材）として機能する。出力ギヤ２５は、差動歯車機構３の差動入力ギヤ３Ａに噛み合っている。 The output gear 25 is connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20. In this embodiment, the output gear 25 is formed on the outer peripheral surface of the second shaft member 20. The output gear 25 is formed at a position adjacent to the second axial side L2 of the third gear forming member 21 on which the third gear 22 is formed. The output gear 25 functions as an output member (transmission output member) of the transmission 1. The output gear 25 meshes with the differential input gear 3A of the differential gear mechanism 3.

図３に示すように、噛み合い式係合装置３０は、第１係合部３１と、第２係合部３２と、第３係合部３３と、切替部材３５とを備えている。 As shown in FIG. 3, the meshing engagement device 30 includes a first engagement portion 31, a second engagement portion 32, a third engagement portion 33, and a switching member 35.

第１係合部３１は、第２軸部材２０と一体的に回転するように当該第２軸部材２０に連結されている。本実施形態では、第１係合部３１は、第２軸部材２０と一体的に回転するように当該第２軸部材２０に連結された連結部材３１Ａの外周面に形成されている。第１係合部３１は、外歯の係合部となっている。 The first engagement portion 31 is connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20. In this embodiment, the first engagement portion 31 is formed on the outer circumferential surface of a connecting member 31A that is connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20. The first engagement portion 31 is an external tooth engagement portion.

第２係合部３２は、第３ギヤ２２と一体的に回転するように当該第３ギヤ２２に連結されている。本実施形態では、第２係合部３２は、外周面に第３ギヤ２２が形成された第３ギヤ形成部材２１に形成されている。第２係合部３２は、第１係合部３１に対して軸方向第２側Ｌ２に隣接して配置されている。第２係合部３２は、第１係合部３１と同径同ピッチの外歯の係合部となっている。 The second engagement portion 32 is connected to the third gear 22 so as to rotate integrally with the third gear 22. In this embodiment, the second engagement portion 32 is formed on a third gear forming member 21 on whose outer circumferential surface the third gear 22 is formed. The second engagement portion 32 is disposed adjacent to the first engagement portion 31 on the second axial side L2. The second engagement portion 32 is an engagement portion with external teeth of the same diameter and pitch as the first engagement portion 31.

第３係合部３３は、第４ギヤ２４と一体的に回転するように当該第４ギヤ２４に連結されている。本実施形態では、第３係合部３３は、外周面に第４ギヤ２４が形成された第４ギヤ形成部材２３に形成されている。第３係合部３３は、第１係合部３１に対して軸方向第１側Ｌ１に隣接して配置されている。第３係合部３３は、第１係合部３１及び第２係合部３２と同径同ピッチの外歯の係合部となっている。 The third engagement portion 33 is connected to the fourth gear 24 so as to rotate integrally with the fourth gear 24. In this embodiment, the third engagement portion 33 is formed on the fourth gear forming member 23 on whose outer circumferential surface the fourth gear 24 is formed. The third engagement portion 33 is disposed adjacent to the first axial side L1 of the first engagement portion 31. The third engagement portion 33 is an engagement portion with external teeth of the same diameter and pitch as the first engagement portion 31 and the second engagement portion 32.

切替部材３５は、連結部材３１Ａの径方向Ｒの外側を覆う筒状に形成されている。そして、切替部材３５の内周面には、それぞれが外歯の第１係合部３１、第２係合部３２、及び第３係合部３３に噛み合う内歯の係合部が形成されている。切替部材３５の内歯と第１係合部３１、第２係合部３２、及び第３係合部３３の外歯とは、軸方向Ｌに相対移動可能、かつ、周方向に相対回転不能に係合する。 The switching member 35 is formed in a cylindrical shape that covers the outside of the connecting member 31A in the radial direction R. The inner peripheral surface of the switching member 35 is formed with internal tooth engagement portions that mesh with the first engagement portion 31, the second engagement portion 32, and the third engagement portion 33, which are external teeth. The internal teeth of the switching member 35 and the external teeth of the first engagement portion 31, the second engagement portion 32, and the third engagement portion 33 engage with each other so as to be movable relative to each other in the axial direction L, but not rotatable relative to each other in the circumferential direction.

噛み合い式係合装置３０は、切替部材３５が第１係合部３１及び第２係合部３２の両方に係合した状態で、第３ギヤ２２と第２軸部材２０とを一体的に回転するように連結する。また、噛み合い式係合装置３０は、切替部材３５が第１係合部３１及び第３係合部３３の両方に係合した状態で、第４ギヤ２４と第２軸部材２０とを一体的に回転するように連結する。このようにして、噛み合い式係合装置３０は、第３ギヤ２２及び第４ギヤ２４のいずれか一方を第２軸部材２０に対して選択的に連結する。第３ギヤ２２と第２軸部材２０とが一体的に回転するように連結された状態で、回転電機２の駆動力は、互いに噛み合う第１ギヤ１２と第３ギヤ２２とを介して車輪Ｗ側に伝達される。一方、第４ギヤ２４と第２軸部材２０とが一体的に回転するように連結された状態で、回転電機２の駆動力は、互いに噛み合う第２ギヤ１４と第４ギヤ２４とを介して車輪Ｗ側に伝達される。 The meshing engagement device 30 connects the third gear 22 and the second shaft member 20 to rotate together when the switching member 35 is engaged with both the first engagement portion 31 and the second engagement portion 32. The meshing engagement device 30 also connects the fourth gear 24 and the second shaft member 20 to rotate together when the switching member 35 is engaged with both the first engagement portion 31 and the third engagement portion 33. In this way, the meshing engagement device 30 selectively connects either the third gear 22 or the fourth gear 24 to the second shaft member 20. When the third gear 22 and the second shaft member 20 are connected to rotate together, the driving force of the rotating electric machine 2 is transmitted to the wheel W side via the first gear 12 and the third gear 22 that mesh with each other. On the other hand, when the fourth gear 24 and the second shaft member 20 are connected so as to rotate together, the driving force of the rotating electric machine 2 is transmitted to the wheel W side via the second gear 14 and the fourth gear 24, which mesh with each other.

なお、切替部材３５が第１係合部３１に係合しているが、第２係合部３２及び第３係合部３３の両方に係合していない状態では、噛み合い式係合装置３０は非係合状態（解放状態）となる。そして、噛み合い式係合装置３０が非係合状態で、かつ、摩擦係合装置４０も非係合状態では、変速機１は駆動力を伝達しないニュートラル状態となる。 When the switching member 35 is engaged with the first engagement portion 31 but not engaged with either the second engagement portion 32 or the third engagement portion 33, the meshing engagement device 30 is in a disengaged state (disengaged state). When the meshing engagement device 30 is in a disengaged state and the friction engagement device 40 is also in a disengaged state, the transmission 1 is in a neutral state in which it does not transmit driving force.

図３及び図４に示すように、摩擦係合装置４０は、第１支持部材４１と、第２支持部材４２と、第１摩擦材４３と、第２摩擦材４４と、第１押圧部材４５と、第２押圧部材４６と、押圧駆動部４９とを備えている。 As shown in Figures 3 and 4, the friction engagement device 40 includes a first support member 41, a second support member 42, a first friction material 43, a second friction material 44, a first pressing member 45, a second pressing member 46, and a pressing drive unit 49.

第１支持部材４１は、第１摩擦材４３を支持するための部材であり、回転可能に支持されている。第１支持部材４１は、第１摩擦材支持部４１Ａと第１径方向延在部４１Ｂと軸連結部４１Ｃとを備えている。これらは、一体的に形成されている。第１摩擦材支持部４１Ａは、軸方向Ｌに沿う筒状に形成されており、第１摩擦材４３を径方向Ｒの内側から支持している。第１摩擦材支持部４１Ａの外周面には、外歯が形成されている。第１径方向延在部４１Ｂは、第１摩擦材支持部４１Ａから径方向Ｒの内側へ向けて延在している。本実施形態では、第１径方向延在部４１Ｂは、第１摩擦材支持部４１Ａの軸方向第２側Ｌ２の端部から径方向Ｒの内側へ向けて延在している。 The first support member 41 is a member for supporting the first friction material 43, and is supported rotatably. The first support member 41 includes a first friction material support portion 41A, a first radial extension portion 41B, and a shaft connection portion 41C. These are integrally formed. The first friction material support portion 41A is formed in a cylindrical shape along the axial direction L, and supports the first friction material 43 from the inside in the radial direction R. External teeth are formed on the outer peripheral surface of the first friction material support portion 41A. The first radial extension portion 41B extends from the first friction material support portion 41A toward the inside in the radial direction R. In this embodiment, the first radial extension portion 41B extends from the end of the axial second side L2 of the first friction material support portion 41A toward the inside in the radial direction R.

軸連結部４１Ｃは、第１径方向延在部４１Ｂの下端部から軸方向Ｌに延在している。軸連結部４１Ｃは、軸方向Ｌに沿う筒状に形成されており、第２軸部材２０に外挿されている。軸連結部４１Ｃは、第２軸部材２０と一体的に回転するように連結されている。これにより、第１支持部材４１の全体が、第２軸部材２０と一体的に回転するように連結されている。第１支持部材４１を構成する各部のうち、第１径方向延在部４１Ｂは、第１押圧部材４５に対して軸方向第２側Ｌ２に配置されている。 The shaft connecting portion 41C extends in the axial direction L from the lower end of the first radially extending portion 41B. The shaft connecting portion 41C is formed in a cylindrical shape along the axial direction L and is inserted onto the second shaft member 20. The shaft connecting portion 41C is connected to the second shaft member 20 so as to rotate integrally therewith. As a result, the entire first support member 41 is connected to the second shaft member 20 so as to rotate integrally therewith. Of the various portions constituting the first support member 41, the first radially extending portion 41B is disposed on the second axial side L2 relative to the first pressing member 45.

第２支持部材４２は、第２摩擦材４４を支持するための部材であり、第１支持部材４１とは独立して回転可能に支持されている。第２支持部材４２は、第２摩擦材支持部４２Ａと第２径方向延在部４２Ｂとを備えている。これらは、一体的に形成されている。第２摩擦材支持部４２Ａは、軸方向Ｌに沿う筒状に形成されており、第２摩擦材４４を径方向Ｒの外側から支持している。第２摩擦材支持部４２Ａの内周面には、内歯が形成されている。第２摩擦材支持部４２Ａは、第１摩擦材支持部４１Ａよりも径方向Ｒの外側に、第１摩擦材支持部４１Ａと同軸に配置されている。 The second support member 42 is a member for supporting the second friction material 44, and is supported rotatably independent of the first support member 41. The second support member 42 includes a second friction material support portion 42A and a second radially extending portion 42B, which are integrally formed. The second friction material support portion 42A is formed in a cylindrical shape along the axial direction L, and supports the second friction material 44 from the outside in the radial direction R. Internal teeth are formed on the inner peripheral surface of the second friction material support portion 42A. The second friction material support portion 42A is disposed coaxially with the first friction material support portion 41A, outside the radial direction R of the first friction material support portion 41A.

第２径方向延在部４２Ｂは、第２摩擦材支持部４２Ａから径方向Ｒの内側へ向けて延在している。本実施形態では、第２径方向延在部４２Ｂは、第２摩擦材支持部４２Ａの軸方向第２側Ｌ２の端部から径方向Ｒの内側へ向けて延在している。第２径方向延在部４２Ｂは、第１径方向延在部４１Ｂに対して軸方向第２側Ｌ２に隣接して配置されている。また、第２径方向延在部４２Ｂは、第４ギヤ形成部材２３に対して軸方向第１側Ｌ１に隣接して配置されている。第２径方向延在部４２Ｂは、第４ギヤ２４が形成された第４ギヤ形成部材２３と一体的に回転するように連結されている。これにより、第２支持部材４２の全体が、第４ギヤ２４と一体的に回転するように連結されている。 The second radial extension portion 42B extends from the second friction material support portion 42A toward the inside in the radial direction R. In this embodiment, the second radial extension portion 42B extends from the end of the second axial side L2 of the second friction material support portion 42A toward the inside in the radial direction R. The second radial extension portion 42B is disposed adjacent to the first radial extension portion 41B on the second axial side L2. The second radial extension portion 42B is disposed adjacent to the fourth gear forming member 23 on the first axial side L1. The second radial extension portion 42B is connected to the fourth gear forming member 23 on which the fourth gear 24 is formed so as to rotate integrally. As a result, the entire second support member 42 is connected to the fourth gear 24 so as to rotate integrally.

第１摩擦材４３は、軸方向Ｌに複数枚並んで配置されている。それぞれの第１摩擦材４３の内周面には、第１摩擦材支持部４１Ａの外歯に噛み合う内歯が形成されている。第１摩擦材４３は、第１摩擦材支持部４１Ａの外周面に、当該第１摩擦材支持部４１Ａに対して軸方向Ｌに相対移動可能、かつ、周方向に相対回転不能に支持されている。 The first friction material 43 is arranged in a row in the axial direction L. The inner circumferential surface of each first friction material 43 is formed with internal teeth that mesh with the external teeth of the first friction material support part 41A. The first friction material 43 is supported on the outer circumferential surface of the first friction material support part 41A so as to be movable relative to the first friction material support part 41A in the axial direction L, but not rotatable relative to the first friction material support part 41A in the circumferential direction.

第２摩擦材４４は、軸方向Ｌに複数枚並んで配置されている。第１摩擦材４３と第２摩擦材４４とは、軸方向Ｌに交互に配置されており、互いに軸方向Ｌに対向するように配置されている。それぞれの第２摩擦材４４の外周面には、第２摩擦材支持部４２Ａの内歯に噛み合う外歯が形成されている。第２摩擦材４４は、第２摩擦材支持部４２Ａの内周面に、当該第２摩擦材支持部４２Ａに対して軸方向Ｌに相対移動可能、かつ、周方向に相対回転不能に支持されている。 The second friction materials 44 are arranged in a row in the axial direction L. The first friction materials 43 and the second friction materials 44 are arranged alternately in the axial direction L and arranged to face each other in the axial direction L. External teeth that mesh with the internal teeth of the second friction material support part 42A are formed on the outer circumferential surface of each second friction material 44. The second friction material 44 is supported on the inner circumferential surface of the second friction material support part 42A so as to be movable relative to the second friction material support part 42A in the axial direction L and non-rotatable relative to the second friction material support part 42A in the circumferential direction.

第１押圧部材４５は、第２押圧部材４６と協働して、第１摩擦材４３と第２摩擦材４４とを互いに押し付けるように押圧する。第１押圧部材４５は、第１摩擦材４３及び第２摩擦材４４に対して軸方向第１側Ｌ１に配置されている。第１押圧部材４５は、第１摩擦材支持部４１Ａの外歯に噛み合う内歯を備えており、第１摩擦材支持部４１Ａに対して軸方向Ｌに相対移動可能、かつ、周方向に相対回転不能に支持されている。こうして、第１押圧部材４５は、第１支持部材４１と一体的に回転するとともに当該第１支持部材４１に対して軸方向Ｌに移動自在に支持されている。第１押圧部材４５は、第２押圧部材４６を介して押圧駆動部４９により軸方向Ｌに駆動された場合に、第１摩擦材４３及び第２摩擦材４４を軸方向第１側Ｌ１から押圧して第１摩擦材４３と第２摩擦材４４とを互いに圧接する。 The first pressing member 45 cooperates with the second pressing member 46 to press the first friction material 43 and the second friction material 44 against each other. The first pressing member 45 is disposed on the first axial side L1 relative to the first friction material 43 and the second friction material 44. The first pressing member 45 has internal teeth that mesh with the external teeth of the first friction material support portion 41A, and is supported so as to be movable relative to the first friction material support portion 41A in the axial direction L and non-rotatable in the circumferential direction. In this way, the first pressing member 45 rotates integrally with the first support member 41 and is supported so as to be movable relative to the first support member 41 in the axial direction L. When the first pressing member 45 is driven in the axial direction L by the pressing drive unit 49 via the second pressing member 46, it presses the first friction material 43 and the second friction material 44 from the first axial side L1, thereby pressing the first friction material 43 and the second friction material 44 against each other.

第１押圧部材４５は、摺動部４５Ａと押圧部４５Ｂとを備えている。摺動部４５Ａは、第１摩擦材支持部４１Ａよりも径方向Ｒの内側に配置されており、当該第１摩擦材支持部４１Ａの内周面に沿って摺動する。本実施形態では、摺動部４５Ａにおける第１摩擦材支持部４１Ａの内周面に対向する面（摺動対向面）と第１摩擦材支持部４１Ａの内周面との間に、シール部材５１が配置されている。摺動部４５Ａは、径方向Ｒに沿って延在するように形成されている。本例では、摺動部４５Ａは、第１摩擦材支持部４１Ａと第１支持部材４１の軸連結部４１Ｃとに亘るように径方向Ｒに沿って形成されている。また、摺動部４５Ａは、保持部材４７によって保持された付勢部材４８によって、軸方向第１側Ｌ１に向けて付勢されている。付勢部材４８は、軸方向Ｌにおける、第１摩擦材４３と第２摩擦材４４とを互いに押し付ける側とは反対側へ向けて第１押圧部材４５を付勢する。このような付勢部材４８として、本実施形態ではリターンスプリングが用いられている。 The first pressing member 45 includes a sliding portion 45A and a pressing portion 45B. The sliding portion 45A is disposed inward in the radial direction R from the first frictional material support portion 41A, and slides along the inner circumferential surface of the first frictional material support portion 41A. In this embodiment, a seal member 51 is disposed between the surface (sliding opposing surface) of the sliding portion 45A facing the inner circumferential surface of the first frictional material support portion 41A and the inner circumferential surface of the first frictional material support portion 41A. The sliding portion 45A is formed so as to extend along the radial direction R. In this example, the sliding portion 45A is formed along the radial direction R so as to span the first frictional material support portion 41A and the shaft connecting portion 41C of the first support member 41. In addition, the sliding portion 45A is biased toward the first axial side L1 by a biasing member 48 held by the holding member 47. The biasing member 48 biases the first pressing member 45 in the axial direction L in the direction opposite to the side where the first friction material 43 and the second friction material 44 are pressed against each other. In this embodiment, a return spring is used as the biasing member 48.

押圧部４５Ｂは、摺動部４５Ａから径方向Ｒの外側に延びている。押圧部４５Ｂは、第１摩擦材支持部４１Ａよりも径方向Ｒの外側に配置されている。押圧部４５Ｂは、第１摩擦材支持部４１Ａと第２摩擦材支持部４２Ａとの径方向Ｒの間に配置される部分を有するように形成されている。押圧部４５Ｂは、摺動部４５Ａと一体的に軸方向Ｌに沿って移動して、第１摩擦材４３及び第２摩擦材４４を押圧する。 The pressing portion 45B extends outward in the radial direction R from the sliding portion 45A. The pressing portion 45B is disposed outward in the radial direction R from the first frictional material support portion 41A. The pressing portion 45B is formed to have a portion disposed between the first frictional material support portion 41A and the second frictional material support portion 42A in the radial direction R. The pressing portion 45B moves along the axial direction L integrally with the sliding portion 45A to press the first frictional material 43 and the second frictional material 44.

第２押圧部材４６は、第１押圧部材４５と協働して、第１摩擦材４３と第２摩擦材４４とを互いに押し付けるように押圧する。第２押圧部材４６は、第１押圧部材４５に対してさらに軸方向第１側Ｌ１に配置されている。本実施形態では、第２押圧部材４６は、間にスラスト軸受９５を介して、第１押圧部材４５に隣接して配置されている。第２押圧部材４６は、ケース６に対して軸方向Ｌに移動自在に支持されている。第１ケース部６Ａの第１支持壁部６Ａｂには、軸方向第２側Ｌ２に突出する筒状の第３筒状支持部６３が形成されている。第３筒状支持部６３は、第２筒状支持部６２と同心に、当該第２筒状支持部６２よりも大径に形成されている。第２押圧部材４６は、径方向Ｒにおける第２筒状支持部６２と第３筒状支持部６３との間の環状空間に配置されている。 The second pressing member 46 cooperates with the first pressing member 45 to press the first friction material 43 and the second friction material 44 against each other. The second pressing member 46 is disposed on the first axial side L1 relative to the first pressing member 45. In this embodiment, the second pressing member 46 is disposed adjacent to the first pressing member 45 with a thrust bearing 95 interposed therebetween. The second pressing member 46 is supported on the case 6 so as to be movable in the axial direction L. The first support wall 6Ab of the first case portion 6A is formed with a cylindrical third cylindrical support portion 63 that protrudes to the second axial side L2. The third cylindrical support portion 63 is formed concentrically with the second cylindrical support portion 62 and has a larger diameter than the second cylindrical support portion 62. The second pressing member 46 is disposed in the annular space between the second cylindrical support portion 62 and the third cylindrical support portion 63 in the radial direction R.

第２押圧部材４６は、第３筒状支持部６３の内周面及び第２筒状支持部６２の外周面に沿って摺動する。本実施形態では、第２押圧部材４６における第３筒状支持部６３の内周面に対向する面と第３筒状支持部６３の内周面との間に、シール部材５２が配置されている。また、第２押圧部材４６における第２筒状支持部６２の外周面に対向する面と第２筒状支持部６２の外周面との間に、シール部材５３が配置されている。第２押圧部材４６は、非回転状態で軸方向Ｌに移動自在に支持されている。 The second pressing member 46 slides along the inner peripheral surface of the third cylindrical support portion 63 and the outer peripheral surface of the second cylindrical support portion 62. In this embodiment, a seal member 52 is disposed between the surface of the second pressing member 46 facing the inner peripheral surface of the third cylindrical support portion 63 and the inner peripheral surface of the third cylindrical support portion 63. In addition, a seal member 53 is disposed between the surface of the second pressing member 46 facing the outer peripheral surface of the second cylindrical support portion 62 and the outer peripheral surface of the second cylindrical support portion 62. The second pressing member 46 is supported in a non-rotating state so as to be freely movable in the axial direction L.

押圧駆動部４９は、第２押圧部材４６を軸方向Ｌに駆動する。本実施形態の押圧駆動部４９は、油圧室４９Ａと作動油供給部４９Ｂとを備えている。油圧室４９Ａは、第２押圧部材４６に油圧を作用させるための空間である。本実施形態では、第２筒状支持部６２と第３筒状支持部６３と第１支持壁部６Ａｂと第２押圧部材４６とで囲まれた空間に、油圧室４９Ａが形成されている。作動油供給部４９Ｂは、油圧室４９Ａに連通するように設けられており、当該油圧室４９Ａに油（作動油）を供給する。本実施形態では、作動油供給部４９Ｂにより、「油圧室に油を供給する油供給部」が構成されている。油圧室４９Ａ及び作動油供給部４９Ｂは、ケース６（本例では第１ケース部６Ａ）に形成されている。 The pressing drive unit 49 drives the second pressing member 46 in the axial direction L. The pressing drive unit 49 in this embodiment includes a hydraulic chamber 49A and a hydraulic oil supply unit 49B. The hydraulic chamber 49A is a space for applying hydraulic pressure to the second pressing member 46. In this embodiment, the hydraulic chamber 49A is formed in a space surrounded by the second cylindrical support unit 62, the third cylindrical support unit 63, the first support wall unit 6Ab, and the second pressing member 46. The hydraulic oil supply unit 49B is provided so as to communicate with the hydraulic chamber 49A and supplies oil (hydraulic oil) to the hydraulic chamber 49A. In this embodiment, the hydraulic oil supply unit 49B constitutes an "oil supply unit that supplies oil to the hydraulic chamber." The hydraulic chamber 49A and the hydraulic oil supply unit 49B are formed in the case 6 (in this example, the first case unit 6A).

作動油供給部４９Ｂから所定油圧の油が油圧室４９Ａに供給されると、その油圧によって、第２押圧部材４６が軸方向第２側Ｌ２に移動する。すると、第２押圧部材４６は、スラスト軸受９５を介して第１押圧部材４５と相対回転自在な状態で、当該第１押圧部材４５を軸方向第１側Ｌ１から押圧する。これにより、第２押圧部材４６及び第１押圧部材４５は、連動して第１摩擦材４３及び第２摩擦材４４を軸方向第２側Ｌ２に押圧し、第１摩擦材４３と第２摩擦材４４とを互いに圧接する。 When oil of a predetermined hydraulic pressure is supplied from the hydraulic oil supply unit 49B to the hydraulic chamber 49A, the hydraulic pressure moves the second pressing member 46 to the second axial side L2. Then, the second pressing member 46 presses the first pressing member 45 from the first axial side L1 while being rotatable relative to the first pressing member 45 via the thrust bearing 95. As a result, the second pressing member 46 and the first pressing member 45 work together to press the first friction material 43 and the second friction material 44 to the second axial side L2, and the first friction material 43 and the second friction material 44 are pressed against each other.

このように、摩擦係合装置４０は、第１摩擦材４３を支持する第１摩擦材支持部４１Ａを備え、回転可能に支持された第１支持部材４１と、第２摩擦材４４を支持する第２摩擦材支持部４２Ａを備え、第１支持部材４１とは独立して回転可能に支持された第２支持部材４２と、第１支持部材４１と一体的に回転するとともに当該第１支持部材４１に対して軸方向Ｌに移動自在に支持され、第１摩擦材４３と第２摩擦材４４とを互いに押し付けるように第１摩擦材４３及び第２摩擦材４４を軸方向Ｌに押圧する第１押圧部材４５と、ケース６に対して軸方向Ｌに移動自在に支持され、第１押圧部材４５と相対回転自在な状態で当該第１押圧部材４５を軸方向Ｌに押圧する第２押圧部材４６と、第２押圧部材４６を軸方向Ｌに駆動する押圧駆動部４９とを備える。 Thus, the friction engagement device 40 includes a first support member 41 that is rotatably supported and includes a first friction material support portion 41A that supports the first friction material 43, a second support member 42 that is rotatably supported independently of the first support member 41 and includes a second friction material support portion 42A that supports the second friction material 44, a first pressing member 45 that rotates integrally with the first support member 41 and is supported movably in the axial direction L relative to the first support member 41 and presses the first friction material 43 and the second friction material 44 in the axial direction L so as to press the first friction material 43 and the second friction material 44 against each other, a second pressing member 46 that is supported movably in the axial direction L relative to the case 6 and presses the first pressing member 45 in the axial direction L while being rotatable relative to the first pressing member 45, and a pressing drive unit 49 that drives the second pressing member 46 in the axial direction L.

この構成によれば、摩擦係合装置４０が、単一の押圧部材を備えるのではなく、互いに相対回転する第１押圧部材４５と第２押圧部材４６とを備え、押圧駆動部４９によって軸方向Ｌに駆動される方の第２押圧部材４６が非回転部材であるケース６に対して軸方向Ｌに移動自在に支持される。これにより、第２押圧部材４６を駆動するための作動油は回転せず遠心油圧も加わらないため、摩擦係合装置４０の制御性を向上させることができる。 According to this configuration, the friction engagement device 40 does not include a single pressing member, but includes a first pressing member 45 and a second pressing member 46 that rotate relative to each other, and the second pressing member 46 that is driven in the axial direction L by the pressing drive unit 49 is supported so as to be freely movable in the axial direction L relative to the case 6, which is a non-rotating member. As a result, the hydraulic oil for driving the second pressing member 46 does not rotate and centrifugal hydraulic pressure is not applied, improving the controllability of the friction engagement device 40.

摩擦係合装置４０が互いに相対回転する第１押圧部材４５と第２押圧部材４６とを備えることとの関係で、第１支持部材４１の第１径方向延在部４１Ｂは、第２押圧部材４６よりも軸方向第２側Ｌ２で第２軸部材２０と一体的に回転するように連結されている。また、第２支持部材４２の第２径方向延在部４２Ｂは、第１径方向延在部４１Ｂよりもさらに軸方向第２側Ｌ２で第４ギヤ２４と一体的に回転するように連結されている。 In relation to the fact that the friction engagement device 40 includes a first pressing member 45 and a second pressing member 46 that rotate relative to each other, the first radial extension portion 41B of the first support member 41 is connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20 on the second axial side L2 further than the second pressing member 46. In addition, the second radial extension portion 42B of the second support member 42 is connected to the fourth gear 24 so as to rotate integrally with the fourth gear 24 on the second axial side L2 further than the first radial extension portion 41B.

このように、第１支持部材４１は、第１摩擦材支持部４１Ａから径方向Ｒの内側へ向けて延在する第１径方向延在部４１Ｂをさらに備え、第１摩擦材支持部４１Ａは、軸方向Ｌに沿う筒状に形成され、第１径方向延在部４１Ｂは、第１押圧部材４５に対して軸方向第２側Ｌ２に配置され、第２支持部材４２は、第２摩擦材支持部４２Ａから径方向Ｒの内側へ向けて延在する第２径方向延在部４２Ｂをさらに備え、第２摩擦材支持部４２Ａは、軸方向Ｌに沿う筒状に形成され、第２径方向延在部４２Ｂは、第１径方向延在部４１Ｂに対して軸方向第２側Ｌ２に配置されている。 In this way, the first support member 41 further includes a first radial extension portion 41B extending inward in the radial direction R from the first friction material support portion 41A, the first friction material support portion 41A is formed in a cylindrical shape along the axial direction L, and the first radial extension portion 41B is disposed on the second axial side L2 relative to the first pressing member 45, and the second support member 42 further includes a second radial extension portion 42B extending inward in the radial direction R from the second friction material support portion 42A, the second friction material support portion 42A is formed in a cylindrical shape along the axial direction L, and the second radial extension portion 42B is disposed on the second axial side L2 relative to the first radial extension portion 41B.

この構成によれば、第１支持部材４１と第２軸部材２０との連結及び第２支持部材４２と第４ギヤ２４との連結の双方を、第１押圧部材４５に対して軸方向第２側Ｌ２において行うことができる。よって、第１支持部材４１及び第２支持部材４２の双方を、第１押圧部材４５及び第２押圧部材４６の軸方向Ｌの押圧力の伝達経路と交差しないように配置することができ、装置構成の簡素化を図ることができる。 With this configuration, both the first support member 41 and the second shaft member 20 and the second support member 42 and the fourth gear 24 can be connected on the second axial side L2 with respect to the first pressing member 45. Therefore, both the first support member 41 and the second support member 42 can be positioned so as not to intersect with the transmission path of the pressing force of the first pressing member 45 and the second pressing member 46 in the axial direction L, which simplifies the device configuration.

第２押圧部材４６は、第２軸部材２０の軸方向第１側Ｌ１の端部を支持する第２軸受９３と同心に、当該第２軸受９３の径方向Ｒの外側に配置されている。また、第２押圧部材４６は、第１軸部材１０の軸方向第１側Ｌ１の端部を支持する第１軸受９２と、外周部どうしを互いに対向させた状態で配置されている。こうして、第２押圧部材４６は、第２軸受９３に対して径方向Ｒの外側であって、周方向における一部が第１軸受９２と第２軸受９３との間に配置されている。そして、本実施形態では、第２押圧部材４６の軸方向Ｌにおける配置領域Ｄ３が、第１軸受９２の軸方向Ｌにおける配置領域Ｄ１及び第２軸受９３の軸方向Ｌにおける配置領域Ｄ２の双方に重複している。なお、「重複」は、全体が重複する場合だけでなく、一部どうしが重複する場合も含む概念である。 The second pressing member 46 is arranged concentrically with the second bearing 93 supporting the end of the second shaft member 20 on the first axial side L1, and is arranged outside the second bearing 93 in the radial direction R. The second pressing member 46 is arranged with the first bearing 92 supporting the end of the first shaft member 10 on the first axial side L1, with their outer peripheries facing each other. Thus, the second pressing member 46 is arranged outside the second bearing 93 in the radial direction R, and a part of the second pressing member 46 in the circumferential direction is arranged between the first bearing 92 and the second bearing 93. In this embodiment, the arrangement area D3 of the second pressing member 46 in the axial direction L overlaps with both the arrangement area D1 of the first bearing 92 in the axial direction L and the arrangement area D2 of the second bearing 93 in the axial direction L. Note that "overlap" is a concept that includes not only the case where the entirety overlaps, but also the case where parts overlap.

ここで、第１軸受９２の軸方向Ｌにおける配置領域Ｄ１は、軸方向Ｌにおける当該第１軸受９２の外輪及び内輪の最大占有範囲を表す。外輪と内輪とで配置範囲が一致する場合は、当該領域が配置領域Ｄ１となる。また、外輪と内輪とで配置範囲が異なる場合において、一方の配置領域が他方の配置領域を包含する場合には、他方を包含する方の配置領域が配置領域Ｄ１となる。また、外輪と内輪とで配置範囲が異なる場合において、一方の配置領域と他方の配置領域とが包含関係とはならない場合には、軸方向第１側Ｌ１に位置する方の軸方向第１側Ｌ１の端部から軸方向第２側Ｌ２に位置する方の軸方向第２側Ｌ２の端部までの領域が配置領域Ｄ１となる。第２軸受９３の軸方向Ｌにおける配置領域Ｄ２に関しても同様である。 Here, the arrangement area D1 in the axial direction L of the first bearing 92 represents the maximum occupancy range of the outer and inner rings of the first bearing 92 in the axial direction L. When the arrangement areas of the outer and inner rings are the same, the area is the arrangement area D1. When the arrangement areas of the outer and inner rings are different, and one arrangement area includes the other arrangement area, the arrangement area that includes the other is the arrangement area D1. When the arrangement areas of the outer and inner rings are different, and one arrangement area does not include the other arrangement area, the area from the end of the axial first side L1 located on the axial first side L1 to the end of the axial second side L2 located on the axial second side L2 is the arrangement area D1. The same applies to the arrangement area D2 in the axial direction L of the second bearing 93.

このように、第２押圧部材４６は、第２軸受９３に対して径方向Ｒの外側であって、周方向における一部が第１軸受９２と第２軸受９３との間に配置され、第２押圧部材４６の軸方向Ｌにおける配置領域Ｄ３が、第１軸受９２の軸方向Ｌにおける配置領域Ｄ１及び第２軸受９３の軸方向Ｌにおける配置領域Ｄ２の双方に重複している。 In this way, the second pressing member 46 is located radially outward of the second bearing 93, with a portion of the second pressing member 46 located between the first bearing 92 and the second bearing 93 in the circumferential direction, and the arrangement area D3 in the axial direction L of the second pressing member 46 overlaps with both the arrangement area D1 in the axial direction L of the first bearing 92 and the arrangement area D2 in the axial direction L of the second bearing 93.

この構成によれば、第２押圧部材４６の軸方向Ｌの配置領域Ｄ３を第１軸受９２の軸方向Ｌの配置領域Ｄ１及び第２軸受９３の軸方向Ｌの配置領域Ｄ２の双方と重複させることで、変速機１の軸方向寸法を小さく抑えやすい。制御性向上のために摩擦係合装置４０が第１押圧部材４５と第２押圧部材４６とを備えるように構成しながら、第１軸受９２と第２軸受９３との間のスペースを利用して第２押圧部材４６を配置して、装置全体の大型化を抑制することができる。 According to this configuration, the arrangement area D3 in the axial direction L of the second pressing member 46 overlaps with both the arrangement area D1 in the axial direction L of the first bearing 92 and the arrangement area D2 in the axial direction L of the second bearing 93, making it easier to keep the axial dimension of the transmission 1 small. While the friction engagement device 40 is configured to include the first pressing member 45 and the second pressing member 46 to improve controllability, the second pressing member 46 can be positioned using the space between the first bearing 92 and the second bearing 93, thereby preventing the device from becoming too large overall.

なお、第１軸受９２及び第２軸受９３はケース６に固定されているのに対して、第２押圧部材４６は軸方向Ｌに移動可能である。このため、第２押圧部材４６の軸方向Ｌにおける配置領域Ｄ３は、軸方向Ｌにおける第２押圧部材４６の最大可動範囲を表すものとする。本実施形態では、第２押圧部材４６の軸方向Ｌにおける配置領域Ｄ３は、その全体が第１軸受９２の軸方向Ｌにおける配置領域Ｄ１と重複している。また、第２押圧部材４６の軸方向Ｌにおける配置領域Ｄ３は、軸方向第１側Ｌ１の一部を除く部分が第２軸受９３の軸方向Ｌにおける配置領域Ｄ２と重複している。 Note that while the first bearing 92 and the second bearing 93 are fixed to the case 6, the second pressing member 46 is movable in the axial direction L. For this reason, the arrangement area D3 in the axial direction L of the second pressing member 46 represents the maximum movable range of the second pressing member 46 in the axial direction L. In this embodiment, the arrangement area D3 in the axial direction L of the second pressing member 46 entirely overlaps with the arrangement area D1 in the axial direction L of the first bearing 92. In addition, the arrangement area D3 in the axial direction L of the second pressing member 46 overlaps with the arrangement area D2 in the axial direction L of the second bearing 93, except for a portion of the first axial side L1.

第１軸受９２は、その周方向の一部が第２摩擦材支持部４２Ａよりも径方向Ｒの内側に位置するように配置されている。そして、図５に示すように、軸方向視で、第１軸受９２と第１摩擦材４３及び第２摩擦材４４とが重複するように配置されている。本実施形態ででは、第１軸受９２と第１摩擦材４３及び第２摩擦材４４とは、それぞれの外周部どうしが部分的に重複するように配置されている。 The first bearing 92 is arranged such that a portion of its circumference is located inward in the radial direction R from the second friction material support portion 42A. As shown in FIG. 5, the first bearing 92 is arranged so that the first friction material 43 and the second friction material 44 overlap when viewed in the axial direction. In this embodiment, the first bearing 92 is arranged so that the outer peripheries of the first friction material 43 and the second friction material 44 partially overlap each other.

車両用駆動装置１００は、第１摩擦材４３及び第２摩擦材４４を潤滑及び冷却するための構造（以下、単に「潤滑構造」と言う。）を備えている。この潤滑構造は、摩擦係合装置４０を支持している第２軸部材２０の内部に形成された油路を利用して構成されている。本実施形態では、第２軸部材２０の内部に、軸方向油路２０ａと径方向油路２０ｂとが形成されている。軸方向油路２０ａは、第２軸部材２０の中心部に軸方向Ｌに沿って直線状に形成されている。径方向油路２０ｂは、軸方向油路２０ａから径方向Ｒに沿って延びて第２軸部材２０の外周面に開口するように形成されている。径方向油路２０ｂは、軸方向Ｌの複数箇所に設けられている。本例では、それら複数の径方向油路２０ｂのうち、摩擦係合装置４０の軸方向Ｌにおける配置領域と重複する位置に設けられている径方向油路２０ｂを通った油が、摩擦係合装置４０に供給される。 The vehicle drive device 100 has a structure (hereinafter, simply referred to as the "lubrication structure") for lubricating and cooling the first friction material 43 and the second friction material 44. This lubrication structure is configured by utilizing an oil passage formed inside the second shaft member 20 that supports the friction engagement device 40. In this embodiment, an axial oil passage 20a and a radial oil passage 20b are formed inside the second shaft member 20. The axial oil passage 20a is formed linearly along the axial direction L at the center of the second shaft member 20. The radial oil passage 20b is formed so as to extend from the axial oil passage 20a along the radial direction R and open on the outer circumferential surface of the second shaft member 20. The radial oil passage 20b is provided at multiple locations in the axial direction L. In this example, oil that passes through the radial oil passage 20b provided at a position that overlaps with the arrangement area of the friction engagement device 40 in the axial direction L among the multiple radial oil passages 20b is supplied to the friction engagement device 40.

軸方向油路２０ａの軸方向第１側Ｌ１の開口部に連通するように、ケース６（本例では第１ケース部６Ａ）に潤滑油供給部５５が形成されている。潤滑油供給部５５から供給される油（以下、「潤滑油」と言う。）は、第２軸部材２０内の軸方向油路２０ａを通って摩擦係合装置４０の径方向Ｒの内側に供給される。そして、潤滑油は、さらに特定の径方向油路２０ｂを通って摩擦係合装置４０に供給される。 A lubricating oil supply section 55 is formed in the case 6 (first case section 6A in this example) so as to communicate with the opening of the axial oil passage 20a on the first axial side L1. The oil (hereinafter referred to as "lubricating oil") supplied from the lubricating oil supply section 55 passes through the axial oil passage 20a in the second shaft member 20 and is supplied to the inside of the friction engagement device 40 in the radial direction R. The lubricating oil is then further supplied to the friction engagement device 40 through a specific radial oil passage 20b.

本実施形態では、第１支持部材４１の軸連結部４１Ｃに、その内周面と外周面とを連通する連通油路４１ｄが形成されている。この連通油路４１ｄは、径方向油路２０ｂと連通するように設けられている。このため、径方向油路２０ｂから供給された潤滑油は、さらに連通油路４１ｄを通って、径方向Ｒの外側にある第１摩擦材支持部４１Ａ側の空間（油溜め部５６）に供給される。ここで、油溜め部５６は、第１摩擦材支持部４１Ａの内周面と第１径方向延在部４１Ｂと摺動部４５Ａとに囲まれた領域に形成される、潤滑油が溜まる部位である。第１支持部材４１は第２軸部材２０と共に回転するため、遠心油圧によって、油溜め部５６において、潤滑油は第１摩擦材支持部４１Ａの内周面側に溜まる。本実施形態では、潤滑油供給部５５、軸方向油路２０ａ、径方向油路２０ｂ、及び連通油路４１ｄにより、「油溜め部に油を供給する油供給部」が構成されている。 In this embodiment, a communication oil passage 41d is formed in the shaft connection portion 41C of the first support member 41, which communicates its inner peripheral surface with its outer peripheral surface. This communication oil passage 41d is provided so as to communicate with the radial oil passage 20b. For this reason, the lubricating oil supplied from the radial oil passage 20b is further supplied through the communication oil passage 41d to the space (oil reservoir 56) on the first friction material support portion 41A side, which is located outside the radial direction R. Here, the oil reservoir 56 is a portion where the lubricating oil is accumulated, which is formed in an area surrounded by the inner peripheral surface of the first friction material support portion 41A, the first radial extension portion 41B, and the sliding portion 45A. Since the first support member 41 rotates together with the second shaft member 20, the lubricating oil accumulates on the inner peripheral surface side of the first friction material support portion 41A in the oil reservoir 56 due to centrifugal hydraulic pressure. In this embodiment, the lubricating oil supply section 55, the axial oil passage 20a, the radial oil passage 20b, and the communicating oil passage 41d constitute an "oil supply section that supplies oil to the oil reservoir section."

第１支持部材４１の第１摩擦材支持部４１Ａに、第１油路８１が設けられている。第１油路８１は、第１摩擦材支持部４１Ａの内周面と外周面とを連通するように設けられており、油溜め部５６と第１摩擦部材及び第２摩擦部材が配置された領域（摩擦材配置領域Ｐ）とを連通する。本実施形態では、第１油路８１は、第１摩擦材支持部４１Ａを径方向Ｒに貫通するように形成されている。また、第１油路８１は、軸方向Ｌ及び周方向に分散して複数設けられている。油溜め部５６に溜まった潤滑油は、遠心油圧により、第１油路８１を通って摩擦材配置領域Ｐに供給され、第１摩擦材４３及び第２摩擦材４４を潤滑及び冷却する。 The first oil passage 81 is provided in the first friction material support portion 41A of the first support member 41. The first oil passage 81 is provided so as to communicate with the inner peripheral surface and the outer peripheral surface of the first friction material support portion 41A, and communicates the oil reservoir portion 56 with the area where the first friction member and the second friction member are arranged (friction material arrangement area P). In this embodiment, the first oil passage 81 is formed so as to penetrate the first friction material support portion 41A in the radial direction R. In addition, a plurality of first oil passages 81 are provided in a dispersed manner in the axial direction L and the circumferential direction. The lubricating oil stored in the oil reservoir portion 56 is supplied to the friction material arrangement area P through the first oil passage 81 by centrifugal hydraulic pressure, and lubricates and cools the first friction material 43 and the second friction material 44.

第１油路８１を通って摩擦材配置領域Ｐに供給される油量に比べて軸方向油路２０ａ側から油溜め部５６に流入する油量が多ければ多いほど、油溜め部５６にはより多くの潤滑油が溜まるようになる。特に本実施形態では、第１押圧部材４５の摺動部４５Ａと第１摩擦材支持部４１Ａとの間にシール部材５１が配置されており、これらの間の油密性が高くなっているので、油溜め部５６には潤滑油が溜まりやすい。油溜め部５６に溜まる潤滑油の量が多くなり過ぎると、溜まった潤滑油に遠心油圧が生じて、付勢部材４８とは別に第１押圧部材４５を押し戻すように作用する場合がある。このような遠心油圧はばらつきが大きいため、摩擦係合装置４０の制御性が悪くなる可能性がある。 The more oil that flows into the oil reservoir 56 from the axial oil passage 20a side compared to the amount of oil supplied to the friction material arrangement area P through the first oil passage 81, the more lubricating oil accumulates in the oil reservoir 56. In particular, in this embodiment, the seal member 51 is arranged between the sliding portion 45A of the first pressing member 45 and the first friction material support portion 41A, and the oil tightness between them is high, so that lubricating oil is likely to accumulate in the oil reservoir 56. If too much lubricating oil accumulates in the oil reservoir 56, centrifugal oil pressure is generated in the accumulated lubricating oil, which may act to push back the first pressing member 45 separately from the biasing member 48. Such centrifugal oil pressure varies greatly, which may deteriorate the controllability of the friction engagement device 40.

そこで本実施形態では、第１支持部材４１に、第１油路８１とは別に、第２油路８２がさらに設けられている。第２油路８２は、油溜め部５６と摩擦材配置領域Ｐ以外の空間とを連通するように設けられている。より具体的には、第２油路８２は、第１支持部材４１の第１径方向延在部４１Ｂを軸方向Ｌに貫通するように形成されている。これにより、第２油路８２は、油溜め部５６と、第１支持部材４１の第１径方向延在部４１Ｂと第２支持部材４２の第２径方向延在部４２Ｂとの軸方向Ｌの間の空間とを連通している。第２油路８２を通って油溜め部５６から流出した潤滑油は、その後、第２摩擦材支持部４２Ａに形成された貫通穴４２ｃから、第２支持部材４２の外側に排出される。 Therefore, in this embodiment, the first support member 41 is further provided with a second oil passage 82 in addition to the first oil passage 81. The second oil passage 82 is provided so as to communicate the oil reservoir 56 with a space other than the friction material arrangement area P. More specifically, the second oil passage 82 is formed so as to penetrate the first radial extension portion 41B of the first support member 41 in the axial direction L. As a result, the second oil passage 82 communicates the oil reservoir 56 with the space between the first radial extension portion 41B of the first support member 41 and the second radial extension portion 42B of the second support member 42 in the axial direction L. The lubricating oil that flows out of the oil reservoir 56 through the second oil passage 82 is then discharged to the outside of the second support member 42 from the through hole 42c formed in the second friction material support portion 42A.

第２油路８２における油溜め部５６側に開口する開口部（第２開口部８２ａ）は、第１油路８１における油溜め部５６側に開口する開口部（第１開口部８１ａ）に対して径方向Ｒの内側に離間して配置されている。これにより、油溜め部５６には第２開口部８２ａの位置に応じた一定量の潤滑油が溜まるようにして第１摩擦材４３及び第２摩擦材４４の潤滑及び冷却を適切に行えるようにしつつ、油溜め部５６に溜まる油の量が多くなり過ぎないように規制することができる。よって、油溜め部５６に溜まる油による遠心油圧によって第１押圧部材４５が受ける影響を少なく抑えることができる。 The opening (second opening 82a) of the second oil passage 82 that opens to the oil reservoir 56 side is disposed at a distance inward in the radial direction R from the opening (first opening 81a) of the first oil passage 81 that opens to the oil reservoir 56 side. This allows a certain amount of lubricating oil according to the position of the second opening 82a to accumulate in the oil reservoir 56, allowing the first friction material 43 and the second friction material 44 to be properly lubricated and cooled, while regulating the amount of oil that accumulates in the oil reservoir 56 so that it does not become too large. This makes it possible to minimize the effect on the first pressing member 45 of the centrifugal oil pressure caused by the oil that accumulates in the oil reservoir 56.

このように、第１摩擦材支持部４１Ａに、油溜め部５６と第１摩擦部材及び第２摩擦部材が配置された摩擦材配置領域Ｐとを連通する第１油路８１が設けられ、第１支持部材４１及び第１押圧部材４５の少なくとも一方に、油溜め部５６と摩擦材配置領域Ｐ以外の空間とを連通する第２油路８２が設けられ、第１油路８１における油溜め部５６側に開口する開口部を第１開口部８１ａとし、第２油路８２における油溜め部５６側に開口する開口部を第２開口部８２ａとして、第２開口部８２ａが第１開口部８１ａに対して径方向Ｒの内側に離間して配置されている。 In this way, the first friction material support part 41A is provided with a first oil passage 81 that connects the oil reservoir 56 to the friction material arrangement area P where the first friction member and the second friction member are arranged, and at least one of the first support member 41 and the first pressing member 45 is provided with a second oil passage 82 that connects the oil reservoir 56 to a space other than the friction material arrangement area P, with the opening of the first oil passage 81 that opens to the oil reservoir 56 side being the first opening 81a, and the opening of the second oil passage 82 that opens to the oil reservoir 56 side being the second opening 82a, and the second opening 82a being spaced apart radially inward from the first opening 81a.

この構成によれば、潤滑油供給部５５から供給されて油溜め部５６に溜まった油を、第１油路８１を介して摩擦材配置領域Ｐに供給することができる。よって、第１摩擦材４３及び第２摩擦材４４の潤滑を適切に行うことができる。また、油溜め部５６に溜まった油のうち、第２開口部８２ａよりも径方向Ｒの内側にある油を、第２油路８２を介して、油溜め部５６の外に排出することができる。これにより、油溜め部５６に溜まる油の量が多くなり過ぎないように規制することができる。よって、油溜め部５６に溜まる油による遠心油圧によって第１押圧部材４５が受ける影響を少なく抑えることができ、その結果、摩擦係合装置４０の制御性を向上させることができる。 According to this configuration, the oil supplied from the lubricating oil supply unit 55 and stored in the oil reservoir 56 can be supplied to the friction material arrangement area P via the first oil passage 81. Therefore, the first friction material 43 and the second friction material 44 can be properly lubricated. In addition, the oil stored in the oil reservoir 56 that is located inside the second opening 82a in the radial direction R can be discharged to the outside of the oil reservoir 56 via the second oil passage 82. This makes it possible to regulate the amount of oil stored in the oil reservoir 56 so that it does not become too large. Therefore, the effect of the centrifugal oil pressure caused by the oil stored in the oil reservoir 56 on the first pressing member 45 can be reduced, and as a result, the controllability of the friction engagement device 40 can be improved.

本実施形態では、第２開口部８２ａは、シール部材５１よりも径方向Ｒの内側に配置されている。これにより、油溜め部５６に溜まる潤滑油の量を一定量以上確保することができる。また、第２開口部８２ａは、第１径方向延在部４１Ｂの径方向Ｒの中央よりも径方向Ｒの外側に配置されている。さらに第２開口部８２ａは、付勢部材４８よりも径方向Ｒの外側に配置されている。これにより、油溜め部５６に溜まる潤滑油の量を適量に抑え、遠心油圧によって第１押圧部材４５が受ける影響を極めて小さくすることができる。 In this embodiment, the second opening 82a is positioned further inward in the radial direction R than the seal member 51. This ensures that a certain amount or more of lubricating oil is stored in the oil reservoir 56. The second opening 82a is also positioned further outward in the radial direction R than the center in the radial direction R of the first radially extending portion 41B. Furthermore, the second opening 82a is positioned further outward in the radial direction R than the biasing member 48. This keeps the amount of lubricating oil stored in the oil reservoir 56 to an appropriate amount, and greatly reduces the effect of centrifugal oil pressure on the first pressing member 45.

以上、本実施形態の車両用駆動装置１００について説明してきたが、これまで述べた主な特徴及び効果以外に、以下の特徴及び効果を有する。 The vehicle drive device 100 of this embodiment has been described above, but in addition to the main features and effects described above, it has the following features and effects.

押圧駆動部４９は、第２押圧部材４６に油圧を作用させるための油圧室４９Ａと、当該油圧室４９Ａに油を供給する作動油供給部４９Ｂと、を備え、油圧室４９Ａ及び作動油供給部４９Ｂが、ケース６に形成されている。 The pressing drive unit 49 includes a hydraulic chamber 49A for applying hydraulic pressure to the second pressing member 46, and a hydraulic oil supply unit 49B for supplying oil to the hydraulic chamber 49A. The hydraulic chamber 49A and the hydraulic oil supply unit 49B are formed in the case 6.

この構成によれば、押圧駆動部４９を構成する油圧室４９Ａ及び作動油供給部４９Ｂがケース６に形成されるので、押圧駆動部４９を回転体に配置する場合とは異なり、当該押圧駆動部４９に遠心油圧が作用することがない。このため、遠心油圧を打ち消すための構造を設ける必要がなく、装置構成の簡素化を図ることができる。 With this configuration, the hydraulic chamber 49A and hydraulic oil supply unit 49B that make up the pressure drive unit 49 are formed in the case 6, so unlike when the pressure drive unit 49 is disposed on a rotating body, centrifugal hydraulic pressure does not act on the pressure drive unit 49. Therefore, there is no need to provide a structure to counteract the centrifugal hydraulic pressure, and the device configuration can be simplified.

第１支持部材４１は、第１摩擦材支持部４１Ａから径方向Ｒの内側へ向けて延在する第１径方向延在部４１Ｂをさらに備え、第１摩擦材支持部４１Ａは、軸方向Ｌに沿う筒状に形成され、第１径方向延在部４１Ｂは、第１押圧部材４５に対して軸方向第２側Ｌ２に配置され、第２支持部材４２は、第２摩擦材支持部４２Ａから径方向Ｒの内側へ向けて延在する第２径方向延在部４２Ｂをさらに備え、第２摩擦材支持部４２Ａは、軸方向Ｌに沿う筒状に形成され、第２径方向延在部４２Ｂは、第１径方向延在部４１Ｂに対して軸方向第２側Ｌ２に配置されている。 The first support member 41 further includes a first radial extension portion 41B extending inward in the radial direction R from the first friction material support portion 41A, the first friction material support portion 41A is formed in a cylindrical shape along the axial direction L, and the first radial extension portion 41B is disposed on the second axial side L2 relative to the first pressing member 45, and the second support member 42 further includes a second radial extension portion 42B extending inward in the radial direction R from the second friction material support portion 42A, the second friction material support portion 42A is formed in a cylindrical shape along the axial direction L, and the second radial extension portion 42B is disposed on the second axial side L2 relative to the first radial extension portion 41B.

この構成によれば、第１支持部材４１と第２軸部材２０との連結及び第２支持部材４２と第４ギヤ２４との連結の双方を、第１押圧部材４５に対して軸方向第２側Ｌ２において行うことができる。よって、第１支持部材４１及び第２支持部材４２の双方を、第１押圧部材４５及び第２押圧部材４６の軸方向Ｌの押圧力の伝達経路と交差しないように配置することができ、装置構成の簡素化を図ることができる。 With this configuration, both the first support member 41 and the second shaft member 20 and the second support member 42 and the fourth gear 24 can be connected on the second axial side L2 with respect to the first pressing member 45. Therefore, both the first support member 41 and the second support member 42 can be positioned so as not to intersect with the transmission path of the pressing force of the first pressing member 45 and the second pressing member 46 in the axial direction L, which simplifies the device configuration.

車両用駆動装置１００は、変速機１と、第１軸部材１０と同軸上に配置されて第１軸部材１０と駆動連結されたロータ２Ｂを備えた回転電機２と、それぞれが車輪Ｗに駆動連結される一対の出力部材４と、差動歯車機構３と、を備え、回転電機２の側から伝達される回転が、変速機１を介して差動歯車機構３に伝達され、さらに差動歯車機構３により一対の出力部材４に分配され、変速機１は、第２軸部材２０と一体的に回転するように当該第２軸部材２０に連結された出力ギヤ２５をさらに備え、第１軸部材１０及びロータ２Ｂが配置された軸を第１軸Ｘ１、第２軸部材２０が配置された軸を第２軸Ｘ２として、差動歯車機構３は、第１軸Ｘ１及び第２軸Ｘ２に平行な第３軸Ｘ３上に配置されて、出力ギヤ２５に噛み合う差動入力ギヤ３Ａを備える。 The vehicle drive device 100 includes a transmission 1, a rotating electric machine 2 with a rotor 2B arranged coaxially with the first shaft member 10 and drivingly connected to the first shaft member 10, a pair of output members 4 each of which is drivingly connected to wheels W, and a differential gear mechanism 3. The rotation transmitted from the rotating electric machine 2 is transmitted to the differential gear mechanism 3 via the transmission 1, and is further distributed to the pair of output members 4 by the differential gear mechanism 3. The transmission 1 further includes an output gear 25 connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20. The axis on which the first shaft member 10 and the rotor 2B are arranged is the first axis X1, and the axis on which the second shaft member 20 is arranged is the second axis X2. The differential gear mechanism 3 is arranged on a third axis X3 parallel to the first axis X1 and the second axis X2, and includes a differential input gear 3A that meshes with the output gear 25.

この構成によれば、回転電機２の駆動力を、変速機１及び差動歯車機構３を介して一対の車輪Ｗに伝達させて、車両を駆動することができる。噛み合い式係合装置３０と摩擦係合装置４０とを併用した変速機１の採用により、エネルギー効率の向上と変速動作の円滑性の向上との双方を図ることができる。変速機１の装置構成の複雑化が抑えられているので、車両用駆動装置１００全体としても、その大型化を抑制することができる。また、変速機１に備えられる摩擦係合装置４０の制御性が向上されていることによっても、変速動作の円滑性のさらなる向上を図ることができる。 According to this configuration, the driving force of the rotating electric machine 2 can be transmitted to a pair of wheels W via the transmission 1 and the differential gear mechanism 3 to drive the vehicle. By adopting a transmission 1 that combines a meshing engagement device 30 and a friction engagement device 40, it is possible to improve both energy efficiency and the smoothness of the gear shifting operation. Since the complexity of the device configuration of the transmission 1 is suppressed, the size of the vehicle drive device 100 as a whole can also be suppressed. In addition, the smoothness of the gear shifting operation can be further improved by improving the controllability of the friction engagement device 40 provided in the transmission 1.

第１摩擦材４３は、第１摩擦材支持部４１Ａの外周面に支持されており、第１油路８１は、第１摩擦材支持部４１Ａを径方向Ｒに貫通するように形成され、第２油路８２は、第１支持部材４１の第１径方向延在部４１Ｂを軸方向Ｌに貫通するように形成されている。 The first friction material 43 is supported on the outer peripheral surface of the first friction material support portion 41A, the first oil passage 81 is formed to penetrate the first friction material support portion 41A in the radial direction R, and the second oil passage 82 is formed to penetrate the first radially extending portion 41B of the first support member 41 in the axial direction L.

この構成によれば、第１摩擦材支持部４１Ａを径方向Ｒに貫通する第１油路８１により、遠心油圧を利用して第１摩擦材４３及び第２摩擦材４４に油を供給し、これらの潤滑を適切に行うことができる。また、構造が複雑になりやすい第１押圧部材４５ではなく、第１支持部材４１に第２油路８２を設けることで、第２油路８２の配置自由度が高くなる。よって、油溜め部５６に溜まる油を、第２油路８２を介して適切に排出する構成を容易に実現できる。 According to this configuration, the first oil passage 81 that penetrates the first friction material support portion 41A in the radial direction R can use centrifugal oil pressure to supply oil to the first friction material 43 and the second friction material 44, thereby properly lubricating them. In addition, by providing the second oil passage 82 in the first support member 41, rather than in the first pressing member 45, which is likely to have a complex structure, the degree of freedom in arranging the second oil passage 82 is increased. Therefore, a configuration can be easily realized in which the oil that accumulates in the oil reservoir portion 56 is properly discharged via the second oil passage 82.

摺動部４５Ａに、第１押圧部材４５を摩擦材配置領域Ｐから離間させるように軸方向Ｌに付勢する付勢部材４８が取り付けられており、第２開口部８２ａは、付勢部材４８よりも径方向Ｒの外側に配置されている。 A biasing member 48 is attached to the sliding portion 45A to bias the first pressing member 45 in the axial direction L so as to move it away from the friction material arrangement area P, and the second opening 82a is positioned outside the biasing member 48 in the radial direction R.

この構成によれば、第２開口部８２ａの位置を第１摩擦材支持部４１Ａ側に比較的寄せて配置することができ、油溜め部５６に溜まる油を比較的少量に抑えることができる。よって、遠心油圧によって第１押圧部材４５が受ける影響をさらに少なく抑えることができ、摩擦係合装置４０の制御性をさらに向上させることができる。 With this configuration, the second opening 82a can be positioned relatively close to the first friction material support portion 41A, and the amount of oil that accumulates in the oil reservoir 56 can be kept relatively small. This further reduces the effect of centrifugal oil pressure on the first pressing member 45, further improving the controllability of the friction engagement device 40.

摺動部４５Ａは、第１摩擦材支持部４１Ａよりも径方向Ｒの内側に配置され、径方向Ｒに沿って延在するように形成され、摺動部４５Ａにおける第１摩擦材支持部４１Ａの内周面に対向する面である摺動対向面と、第１摩擦材支持部４１Ａの内周面との間にシール部材５１が配置されている。 The sliding part 45A is disposed radially inward of the first frictional material support part 41A and is formed to extend along the radial direction R. A seal member 51 is disposed between the inner peripheral surface of the first frictional material support part 41A and a sliding opposing surface of the sliding part 45A that faces the inner peripheral surface of the first frictional material support part 41A.

この構成によれば、シール部材５１を設けることにより、第１摩擦材支持部４１Ａの内周面に沿う領域に形成された油溜め部５６に適切に油を溜めることができ、それによって第１摩擦材４３及び第２摩擦材４４の潤滑を適切に行うことができる。一方、そのようなシール部材５１の存在によって、油溜め部５６からの油の排出がほとんど行われない構造となるが、第２油路８２を設けることで油の一部を油溜め部５６の外に排出することができるので、油溜め部５６に溜まる油を一定量以下に規制できる。 According to this configuration, by providing the sealing member 51, oil can be appropriately stored in the oil reservoir 56 formed in the area along the inner circumferential surface of the first friction material support portion 41A, thereby allowing the first friction material 43 and the second friction material 44 to be appropriately lubricated. On the other hand, the presence of such a sealing member 51 results in a structure in which almost no oil is discharged from the oil reservoir 56, but by providing the second oil passage 82, a portion of the oil can be discharged outside the oil reservoir 56, so that the amount of oil that accumulates in the oil reservoir 56 can be restricted to a certain amount or less.

車両用駆動装置１００は、摩擦係合装置４０と、第１軸Ｘ１上に配置されたロータ２Ｂを備え、車輪Ｗの駆動力源として機能する回転電機２と、それぞれが車輪Ｗに駆動連結される一対の出力部材４と、回転電機２の側から伝達される回転を変速する変速機１と、変速機１から伝達される回転を、一対の出力部材４に分配する差動歯車機構３と、回転電機２、変速機１、及び差動歯車機構３を収容する、ケース６としてのケース６と、を備え、変速機１は、第１軸Ｘ１上に配置された第１軸部材１０と、第１軸部材１０と一体的に回転するように連結された第１ギヤ１２及び第２ギヤ１４と、第１軸Ｘ１に平行な第２軸Ｘ２上に配置された第２軸部材２０と、第２軸部材２０に対して相対回転可能に支持された第３ギヤ２２及び第４ギヤ２４と、第２軸部材２０と一体的に回転するように連結された出力ギヤ２５と、を備え、第１ギヤ１２と第３ギヤ２２とが互いに噛み合うとともに、第２ギヤ１４と第４ギヤ２４とが互いに噛み合い、第３ギヤ２２及び第４ギヤ２４のいずれか一方を第２軸部材２０に対して選択的に連結する噛み合い式係合装置３０が、第２軸Ｘ２上であって、第３ギヤ２２と第４ギヤ２４との軸方向Ｌの間に配置され、差動歯車機構３は、第１軸Ｘ１及び第２軸Ｘ２に平行な第３軸Ｘ３上に配置されて、出力ギヤ２５に噛み合う差動入力ギヤ３Ａを備え、摩擦係合装置４０が、第２軸Ｘ２上であって、第３ギヤ２２及び第４ギヤ２４に対して軸方向Ｌの一方側に配置されている。 The vehicle drive device 100 includes a friction engagement device 40, a rotating electric machine 2 having a rotor 2B arranged on a first axis X1 and functioning as a driving force source for the wheels W, a pair of output members 4 each of which is drivingly connected to the wheels W, a transmission 1 that changes the speed of the rotation transmitted from the rotating electric machine 2, a differential gear mechanism 3 that distributes the rotation transmitted from the transmission 1 to the pair of output members 4, and a case 6 that houses the rotating electric machine 2, the transmission 1, and the differential gear mechanism 3. The transmission 1 includes a first shaft member 10 arranged on the first axis X1, a first gear 12 and a second gear 14 connected to rotate integrally with the first shaft member 10, a second shaft member 20 arranged on a second axis X2 parallel to the first axis X1, and a gear 12 and a gear 14 supported so as to be rotatable relative to the second shaft member 20. The differential gear mechanism 3 includes a third gear 22 and a fourth gear 24 supported on the second shaft member 20, and an output gear 25 connected to rotate integrally with the second shaft member 20. The first gear 12 and the third gear 22 mesh with each other, and the second gear 14 and the fourth gear 24 mesh with each other. A meshing engagement device 30 that selectively connects either the third gear 22 or the fourth gear 24 to the second shaft member 20 is disposed on the second shaft X2 between the third gear 22 and the fourth gear 24 in the axial direction L. The differential gear mechanism 3 is disposed on a third axis X3 parallel to the first axis X1 and the second axis X2, and includes a differential input gear 3A that meshes with the output gear 25. A friction engagement device 40 is disposed on the second shaft X2 on one side of the third gear 22 and the fourth gear 24 in the axial direction L.

この構成によれば、回転電機２の駆動力を、変速機１及び差動歯車機構３を介して一対の車輪Ｗに伝達させて、車両を駆動することができる。噛み合い式係合装置３０と摩擦係合装置４０とを併用した変速機１の採用により、エネルギー効率の向上と変速動作の円滑性の向上との双方を図ることができる。特に、変速機１に備えられる摩擦係合装置４０の制御性が向上されていることにより、変速動作の円滑性のさらなる向上を図ることができる。 With this configuration, the driving force of the rotating electric machine 2 can be transmitted to a pair of wheels W via the transmission 1 and the differential gear mechanism 3 to drive the vehicle. By adopting a transmission 1 that uses both a meshing engagement device 30 and a friction engagement device 40, it is possible to improve both energy efficiency and the smoothness of the gear shifting operation. In particular, the controllability of the friction engagement device 40 provided in the transmission 1 has been improved, which can further improve the smoothness of the gear shifting operation.

ケース６は、第２軸受９３を径方向Ｒ外側から支持する第３筒状支持部６３を備え、押圧駆動部４９は、第２押圧部材４６に油圧を作用させるための油圧室４９Ａと、当該油圧室４９Ａに油を供給する作動油供給部４９Ｂと、を備え、作動油供給部４９Ｂが、ケース６に形成され、油圧室４９Ａの内周面は、第３筒状支持部６３の外周面を用いて形成されている。 The case 6 includes a third cylindrical support portion 63 that supports the second bearing 93 from the outside in the radial direction R, and the pressing drive portion 49 includes a hydraulic chamber 49A for applying hydraulic pressure to the second pressing member 46 and a hydraulic oil supply portion 49B for supplying oil to the hydraulic chamber 49A. The hydraulic oil supply portion 49B is formed in the case 6, and the inner peripheral surface of the hydraulic chamber 49A is formed using the outer peripheral surface of the third cylindrical support portion 63.

この構成によれば、第２軸受９３を支持するためのケース６の構造（第３筒状支持部６３）を利用して油圧室４９Ａを形成することで、押圧駆動部４９を小型化することが容易となる。 With this configuration, the hydraulic chamber 49A is formed using the structure of the case 6 (third cylindrical support portion 63) for supporting the second bearing 93, making it easy to miniaturize the pressing drive portion 49.

第１軸受９２は、第１軸部材１０の軸方向第１側Ｌ１の端部を支持し、第２軸受９３は、第２軸部材２０の軸方向第１側Ｌ１の端部を支持している。 The first bearing 92 supports the end of the first shaft member 10 on the first axial side L1, and the second bearing 93 supports the end of the second shaft member 20 on the first axial side L1.

この構成によれば、軸方向Ｌにおける配置領域が互いに重複する第１軸受９２と第２軸受９３とによって、第１軸部材１０及び第２軸部材２０の双方が軸方向第１側Ｌ１の端部を支持されるので、これら第１軸部材１０及び第２軸部材２０の軸方向第１側Ｌ１への突出量を小さく抑えることができる。よって、変速機１の軸方向Ｌ寸法を小さく抑えやすい。 With this configuration, the ends of both the first shaft member 10 and the second shaft member 20 on the first axial side L1 are supported by the first bearing 92 and the second bearing 93, whose arrangement areas in the axial direction L overlap, so that the amount of protrusion of the first shaft member 10 and the second shaft member 20 on the first axial side L1 can be kept small. This makes it easier to keep the axial dimension L of the transmission 1 small.

第１軸部材１０に、第１ギヤ１２と第２ギヤ１４とが支持されており、第２軸部材２０に、第１ギヤ１２に噛み合う第３ギヤ２２と第２ギヤ１４に噛み合う第４ギヤ２４とが支持されており、第２ギヤ１４及び第４ギヤ２４は、第１ギヤ１２及び第３ギヤ２２に対して軸方向第１側Ｌ１に配置され、摩擦係合装置４０は、第４ギヤ２４よりも軸方向第１側Ｌ１に配置され、第１支持部材４１は、第２軸部材２０と一体的に回転するように連結され、第２支持部材４２は、第４ギヤ２４と一体的に回転するように連結されている。 The first gear 12 and the second gear 14 are supported on the first shaft member 10, and the third gear 22 meshing with the first gear 12 and the fourth gear 24 meshing with the second gear 14 are supported on the second shaft member 20, the second gear 14 and the fourth gear 24 are arranged on the first axial side L1 relative to the first gear 12 and the third gear 22, the friction engagement device 40 is arranged on the first axial side L1 relative to the fourth gear 24, the first support member 41 is connected to the second shaft member 20 so as to rotate integrally, and the second support member 42 is connected to the fourth gear 24 so as to rotate integrally.

この構成によれば、第１支持部材４１と第２軸部材２０との連結及び第２支持部材４２と第４ギヤ２４との連結の双方を、第１押圧部材４５に対して軸方向第２側Ｌ２において行いやすい。その結果、第１支持部材４１及び第２支持部材４２の双方を、第１押圧部材４５及び第２押圧部材４６の軸方向Ｌの押圧力の伝達経路と交差しないように配置することができる。よって、装置構成の簡素化を図ることができる。 With this configuration, both the first support member 41 and the second shaft member 20 and the second support member 42 and the fourth gear 24 can be easily connected on the second axial side L2 with respect to the first pressing member 45. As a result, both the first support member 41 and the second support member 42 can be positioned so as not to intersect with the transmission path of the pressing force of the first pressing member 45 and the second pressing member 46 in the axial direction L. This allows for a simplified device configuration.

軸方向Ｌに沿う軸方向視で、第１軸受９２と第１摩擦材４３及び第２摩擦材４４とが重複するように配置されている。 When viewed in the axial direction along the axial direction L, the first bearing 92 is arranged so as to overlap with the first friction material 43 and the second friction material 44.

この構成によれば、第１軸受９２と第１摩擦材４３及び第２摩擦材４４とを径方向Ｒにずらして配置した構成に比べて、変速機１の径方向Ｒ寸法を小さく抑えることができる。よって、装置全体の大型化を効果的に抑制することができる。 This configuration makes it possible to reduce the radial R dimension of the transmission 1 compared to a configuration in which the first bearing 92 and the first and second friction materials 43 and 44 are arranged offset in the radial direction R. This effectively prevents the device as a whole from becoming too large.

〔その他の実施形態〕
（１）上記の実施形態では、回転電機２が第１軸部材１０と駆動連結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、回転電機２が第２軸部材２０と駆動連結され、回転電機２と噛み合い式係合装置３０と摩擦係合装置４０とが第２軸Ｘ２上において同軸に配置されても良い。この場合、第１軸部材１０に出力ギヤ２５が形成されると良い。 Other embodiments
(1) In the above embodiment, a configuration in which the rotating electric machine 2 is drivingly connected to the first shaft member 10 has been described as an example. However, the present invention is not limited to such a configuration, and the rotating electric machine 2 may be drivingly connected to the second shaft member 20, and the rotating electric machine 2, the meshing engagement device 30, and the friction engagement device 40 may be coaxially arranged on the second axis X2. In this case, it is preferable that an output gear 25 is formed on the first shaft member 10.

（２）上記の実施形態では、第１支持部材４１に、油溜め部５６と摩擦材配置領域Ｐ以外の空間とを連通する第２油路８２が設けら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、例えば第１押圧部材４５に第２油路８２が設けられても良い。或いは、第１支持部材４１及び第１押圧部材４５の両方に第２油路８２が設けられても良い。 (2) In the above embodiment, a configuration has been described in which the first support member 41 is provided with a second oil passage 82 that connects the oil reservoir 56 to a space other than the friction material arrangement area P. However, the present invention is not limited to such a configuration, and the second oil passage 82 may be provided in the first pressing member 45, for example. Alternatively, the second oil passage 82 may be provided in both the first support member 41 and the first pressing member 45.

（３）上記の実施形態では、第１油路８１が第１摩擦材支持部４１Ａを径方向Ｒに貫通するように形成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、例えば第１油路８１が径方向Ｒに対して傾斜した方向に沿うように形成されても良い。 (3) In the above embodiment, a configuration in which the first oil passage 81 is formed to penetrate the first friction material support portion 41A in the radial direction R has been described as an example. However, the present invention is not limited to such a configuration, and the first oil passage 81 may be formed, for example, along a direction inclined with respect to the radial direction R.

（４）上記の実施形態では、第２油路８２が第１径方向延在部４１Ｂを軸方向Ｌに貫通するように形成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、例えば第２油路８２が軸方向Ｌに対して傾斜した方向に沿うように形成されても良い。 (4) In the above embodiment, a configuration in which the second oil passage 82 is formed to penetrate the first radially extending portion 41B in the axial direction L has been described as an example. However, the present invention is not limited to such a configuration, and the second oil passage 82 may be formed, for example, along a direction inclined with respect to the axial direction L.

（５）上記の実施形態では、第２油路８２の油溜め部５６側に開口する第２開口部８２ａがシール部材５１よりも径方向Ｒの内側であって付勢部材４８よりも径方向Ｒの外側となる位置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開口部８２ａの位置は、第１開口部８１ａに対して径方向Ｒの内側に離間していれば任意の位置であって良い。例えば第２開口部８２ａは、軸方向視でシール部材５１と重複する位置に配置されていても良いし、第１径方向延在部４１Ｂにおける軸連結部４１Ｃの近傍に配置されていても良い。 (5) In the above embodiment, the second opening 82a that opens to the oil reservoir 56 side of the second oil passage 82 is arranged in a position that is more inward in the radial direction R than the seal member 51 and more outward in the radial direction R than the biasing member 48. However, the present invention is not limited to such a configuration, and the position of the second opening 82a may be any position as long as it is spaced inward in the radial direction R from the first opening 81a. For example, the second opening 82a may be arranged in a position that overlaps with the seal member 51 when viewed in the axial direction, or may be arranged near the shaft connecting portion 41C in the first radially extending portion 41B.

（６）上記の実施形態では、押圧駆動部４９が油圧室４９Ａと作動油供給部４９Ｂとを備え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、例えば押圧駆動部４９が電動アクチュエータ等を備えて構成されても良い。 (6) In the above embodiment, the pressure drive unit 49 is described as having a hydraulic chamber 49A and a hydraulic oil supply unit 49B. However, the present invention is not limited to such a configuration, and the pressure drive unit 49 may be configured to have, for example, an electric actuator.

（７）上記の実施形態では、付勢部材４８としてコイルバネを用いて構成されたリターンスプリングを用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、例えば付勢部材４８として板バネ等を用いても良い。 (7) In the above embodiment, a configuration has been described as an example in which a return spring formed of a coil spring is used as the biasing member 48. However, the present invention is not limited to such a configuration, and for example, a leaf spring or the like may be used as the biasing member 48.

（８）上記の実施形態では、摺動部４５Ａと第１摩擦材支持部４１Ａとの間にシール部材５１が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、そのようなシール部材５１が設けられていなくても良い。 (8) In the above embodiment, a configuration in which a seal member 51 is disposed between the sliding portion 45A and the first friction material support portion 41A has been described as an example. However, the present invention is not limited to such a configuration, and such a seal member 51 does not necessarily have to be provided.

（９）上記の実施形態では、第２押圧部材４６の軸方向Ｌの配置領域Ｄ３の全体が、第１軸受９２の軸方向Ｌの配置領域Ｄ１に含まれているとともに、第２軸受９３の軸方向Ｌの配置領域Ｄ２と部分的に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、例えば第２押圧部材４６の軸方向Ｌの配置領域Ｄ３の全体が、第１軸受９２の軸方向Ｌの配置領域Ｄ１及び第２軸受９３の軸方向Ｌの配置領域Ｄ２の両方に含まれていても良い。或いは、第２押圧部材４６の軸方向Ｌの配置領域Ｄ３が、第１軸受９２の軸方向Ｌの配置領域Ｄ１及び第２軸受９３の軸方向Ｌの配置領域Ｄ２のそれぞれと部分的に重複していても良い。 (9) In the above embodiment, the entire arrangement area D3 of the second pressing member 46 in the axial direction L is included in the arrangement area D1 of the first bearing 92 in the axial direction L and partially overlaps with the arrangement area D2 of the second bearing 93 in the axial direction L. However, without being limited to such a configuration, for example, the entire arrangement area D3 of the second pressing member 46 in the axial direction L may be included in both the arrangement area D1 of the first bearing 92 in the axial direction L and the arrangement area D2 of the second bearing 93 in the axial direction L. Alternatively, the arrangement area D3 of the second pressing member 46 in the axial direction L may partially overlap with each of the arrangement area D1 of the first bearing 92 in the axial direction L and the arrangement area D2 of the second bearing 93 in the axial direction L.

（１０）上記の実施形態では、車両用駆動装置１００を電動車両用の駆動装置に適用した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、本開示の技術は、例えば所謂エンジン車両や、エンジンと回転電機２とを併用するハイブリッド車両等、他のタイプの車両用駆動装置にも適用することが可能である。 (10) In the above embodiment, a configuration in which the vehicle drive device 100 is applied to a drive device for an electric vehicle has been described as an example. However, the present disclosure is not limited to such a configuration, and can be applied to other types of vehicle drive devices, such as so-called engine vehicles and hybrid vehicles that use both an engine and a rotating electric machine 2.

（１１）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。 (11) The configurations disclosed in each of the above-described embodiments (including the above-described embodiments and other embodiments; the same applies below) can also be applied in combination with configurations disclosed in other embodiments, as long as no contradiction arises. As for other configurations, the embodiments disclosed in this specification are illustrative in all respects and can be appropriately modified within the scope of the present disclosure.

１：変速機、２：回転電機、２Ａ：ステータ、２Ｂ：ロータ、２Ｃ：ロータ軸、３：差動歯車機構、３Ａ：差動入力ギヤ、４：出力部材、６：ケース、６Ａ：第１ケース部、６Ａａ：第１周壁部、６Ａｂ：第１支持壁部、６Ｂ：第２ケース部、６Ｂａ：第２周壁部、６Ｂｂ：第２支持壁部、６Ｃ：第３ケース部、１０：第１軸部材、１２：第１ギヤ、１３：第２ギヤ形成部材、１４：第２ギヤ、２０：第２軸部材、２０ａ：軸方向油路、２０ｂ：径方向油路、２１：第３ギヤ形成部材、２２：第３ギヤ、２３：第４ギヤ形成部材、２４：第４ギヤ、２５：出力ギヤ、３０：噛み合い式係合装置、３１：第１係合部、３１Ａ：連結部材、３２：第２係合部、３３：第３係合部、３５：切替部材、４０：摩擦係合装置、４１：第１支持部材、４１Ａ：第１摩擦材支持部、４１Ｂ：第１径方向延在部、４１Ｃ：軸連結部、４１ｄ：連通油路、４２：第２支持部材、４２Ａ：第２摩擦材支持部、４２Ｂ：第２径方向延在部、４３：第１摩擦材、４４：第２摩擦材、４５：第１押圧部材、４５Ａ：摺動部、４５Ｂ：押圧部、４６：第２押圧部材、４７：保持部材、４８：付勢部材、４９：押圧駆動部、４９Ａ：油圧室、４９Ｂ：作動油供給部、５１：シール部材、５２：シール部材、５３：シール部材、５５：潤滑油供給部、５６：油溜め部、６１：第１筒状支持部、６２：第２筒状支持部、６３：第３筒状支持部、８１：第１油路、８１ａ：第１開口部、８２：第２油路、８２ａ：第２開口部、９１：ロータ軸受、９２：第１軸受、９３：第２軸受、９５：スラスト軸受、１００：車両用駆動装置、Ｄ１：配置領域、Ｄ２：配置領域、Ｄ３：配置領域、Ｌ：軸方向、Ｌ１：軸方向第１側、Ｌ２：軸方向第２側、Ｐ：摩擦材配置領域、Ｒ：径方向、Ｗ：車輪、Ｘ１：第１軸、Ｘ２：第２軸、Ｘ３：第３軸 1: Transmission, 2: Rotating electric machine, 2A: Stator, 2B: Rotor, 2C: Rotor shaft, 3: Differential gear mechanism, 3A: Differential input gear, 4: Output member, 6: Case, 6A: First case part, 6Aa: First circumferential wall part, 6Ab: First support wall part, 6B: Second case part, 6Ba: Second circumferential wall part, 6Bb: Second support wall part, 6C: Third case part, 10: First shaft member, 12: First gear, 13: Second gear forming member, 14: Second gear, 20: Second shaft member, 20a: Axial oil passage, 20b: radial oil passage, 21: third gear forming member, 22: third gear, 23: fourth gear forming member, 24: fourth gear, 25: output gear, 30: meshing type engagement device, 31: first engagement portion, 31A: connecting member, 32: second engagement portion, 33: third engagement portion, 35: switching member, 40: friction engagement device, 41: first support member, 41A: first friction material support portion, 41B: first radial extension portion, 41C: shaft connecting portion, 41d: communicating oil passage, 42: second support holding member, 42A: second friction material support portion, 42B: second radially extending portion, 43: first friction material, 44: second friction material, 45: first pressing member, 45A: sliding portion, 45B: pressing portion, 46: second pressing member, 47: holding member, 48: biasing member, 49: pressing drive portion, 49A: hydraulic chamber, 49B: hydraulic oil supply portion, 51: sealing member, 52: sealing member, 53: sealing member, 55: lubricating oil supply portion, 56: oil reservoir portion, 61: first cylindrical support portion, 62: second cylindrical shaped support part, 63: third cylindrical support part, 81: first oil passage, 81a: first opening, 82: second oil passage, 82a: second opening, 91: rotor bearing, 92: first bearing, 93: second bearing, 95: thrust bearing, 100: vehicle drive device, D1: arrangement area, D2: arrangement area, D3: arrangement area, L: axial direction, L1: first axial side, L2: second axial side, P: friction material arrangement area, R: radial direction, W: wheel, X1: first axis, X2: second axis, X3: third axis

Claims (4)

第１摩擦材を支持する第１摩擦材支持部を備え、回転可能に支持された第１支持部材と、
第２摩擦材を支持する第２摩擦材支持部を備え、前記第１支持部材とは独立して回転可能に支持された第２支持部材と、
前記第１支持部材と一体的に回転するとともに当該第１支持部材に対して軸方向に移動自在に支持され、前記第１摩擦材と前記第２摩擦材とを互いに押し付けるように前記第１摩擦材及び前記第２摩擦材を前記軸方向に押圧する第１押圧部材と、
非回転部材に対して前記軸方向に移動自在に支持され、前記第１押圧部材と相対回転自在な状態で当該第１押圧部材を前記軸方向に押圧する第２押圧部材と、
前記第２押圧部材を前記軸方向に駆動する押圧駆動部と、を備え、
前記第１摩擦材支持部は、前記軸方向に沿う筒状に形成され、
前記第２摩擦材支持部は、前記第１摩擦材支持部よりも径方向の外側に当該第１摩擦材支持部と同軸に配置され、
前記第１摩擦材は、前記第１摩擦材支持部と一体的に回転するように連結され、
前記第２摩擦材は、前記第２摩擦材支持部と一体的に回転するように連結され、
前記第１摩擦材及び前記第２摩擦材は、前記第１摩擦材支持部と前記第２摩擦材支持部との前記径方向の間において、互いに前記軸方向に対向するように配置され、
前記第１支持部材は、前記第１摩擦材支持部から前記径方向の内側へ向けて延在する径方向延在部をさらに備え、
前記第１押圧部材は、前記第１摩擦材支持部の内周面に沿って摺動する摺動部を備え、
前記摺動部は、前記第１摩擦材支持部よりも前記径方向の内側に配置され、前記径方向に沿って延在するように形成され、
前記摺動部における前記第１摩擦材支持部の内周面に対向する面である摺動対向面と、前記第１摩擦材支持部の内周面との間にシール部材が配置され、
前記第１摩擦材支持部の内周面と前記径方向延在部と前記摺動部とに囲まれた領域に油溜め部が形成され、
前記油溜め部に油を供給する油供給部が設けられ、
前記第１摩擦材支持部に、前記油溜め部と前記第１摩擦材及び前記第２摩擦材が配置された摩擦材配置領域とを連通する第１油路が設けられ、
前記第１支持部材及び前記第１押圧部材の少なくとも一方に、前記油溜め部と前記摩擦材配置領域以外の空間とを連通する第２油路が設けられ、
前記第１油路における前記油溜め部側に開口する開口部を第１開口部とし、前記第２油路における前記油溜め部側に開口する開口部を第２開口部として、前記第２開口部が前記第１開口部に対して前記径方向の内側に離間して配置されている、摩擦係合装置。 a first support member including a first friction material support portion that supports a first friction material and is rotatably supported;
a second support member including a second friction material support portion that supports a second friction material, the second support member being supported rotatably independent of the first support member;
a first pressing member that rotates integrally with the first support member, is supported by the first support member so as to be movable in the axial direction, and presses the first friction material and the second friction material in the axial direction so as to press the first friction material and the second friction material against each other;
a second pressing member that is supported on the non-rotating member so as to be movable in the axial direction and presses the first pressing member in the axial direction while being rotatable relative to the first pressing member;
a pressing drive unit that drives the second pressing member in the axial direction,
The first friction material support portion is formed in a cylindrical shape along the axial direction,
the second friction material support portion is disposed radially outward of the first friction material support portion and coaxially with the first friction material support portion,
The first friction material is connected to the first friction material support portion so as to rotate integrally with the first friction material support portion,
the second friction material is connected to the second friction material support portion so as to rotate integrally with the second friction material,
the first friction material and the second friction material are disposed between the first friction material support portion and the second friction material support portion in the radial direction so as to face each other in the axial direction,
The first support member further includes a radially extending portion extending inward in the radial direction from the first friction material support portion,
the first pressing member includes a sliding portion that slides along an inner circumferential surface of the first friction material support portion,
The sliding portion is disposed radially inward of the first friction material support portion and is formed to extend along the radial direction,
a seal member is disposed between a sliding opposing surface of the sliding portion that faces an inner circumferential surface of the first friction material support portion and the inner circumferential surface of the first friction material support portion,
an oil reservoir is formed in a region surrounded by an inner circumferential surface of the first friction material support portion, the radially extending portion, and the sliding portion;
an oil supply unit that supplies oil to the oil reservoir;
a first oil passage is provided in the first friction material support portion, the first oil passage communicating with the oil reservoir and a friction material arrangement area in which the first friction material and the second friction material are arranged;
At least one of the first support member and the first pressing member is provided with a second oil passage that communicates the oil reservoir with a space other than the friction material arrangement area,
A friction engagement device, wherein an opening in the first oil passage that opens toward the oil reservoir is a first opening, and an opening in the second oil passage that opens toward the oil reservoir is a second opening, and the second opening is positioned radially inward and spaced apart from the first opening. 前記第１摩擦材は、前記第１摩擦材支持部の外周面に支持されており、
前記第１油路は、前記第１摩擦材支持部を前記径方向に貫通するように形成され、
前記第２油路は、前記第１支持部材の前記径方向延在部を前記軸方向に貫通するように形成されている、請求項１に記載の摩擦係合装置。 The first friction material is supported on an outer circumferential surface of the first friction material support portion,
The first oil passage is formed to penetrate the first friction material support portion in the radial direction,
The friction engagement device according to claim 1 , wherein the second oil passage is formed so as to penetrate the radially extending portion of the first support member in the axial direction. 前記摺動部に、前記第１押圧部材を前記摩擦材配置領域から離間させるように前記軸方向に付勢する付勢部材が取り付けられており、
前記第２開口部は、前記付勢部材よりも前記径方向の外側に配置されている、請求項１又は２に記載の摩擦係合装置。 a biasing member that biases the first pressing member in the axial direction so as to move the first pressing member away from the friction material arrangement region is attached to the sliding portion,
The friction engagement device according to claim 1 , wherein the second opening is disposed radially outward of the biasing member. 請求項１から３のいずれか一項に記載の摩擦係合装置と、
第１軸上に配置されたロータを備え、車輪の駆動力源として機能する回転電機と、
それぞれが前記車輪に駆動連結される一対の出力部材と、
前記回転電機の側から伝達される回転を変速する変速機と、
前記変速機から伝達される回転を、一対の前記出力部材に分配する差動歯車機構と、
前記回転電機、前記変速機、及び前記差動歯車機構を収容する、前記非回転部材としてのケースと、を備え、
前記変速機は、前記第１軸上に配置された第１軸部材と、前記第１軸部材と一体的に回転するように連結された第１ギヤ及び第２ギヤと、前記第１軸に平行な第２軸上に配置された第２軸部材と、前記第２軸部材に対して相対回転可能に支持された第３ギヤ及び第４ギヤと、前記第２軸部材と一体的に回転するように連結された出力ギヤと、を備え、
前記第１ギヤと前記第３ギヤとが互いに噛み合うとともに、前記第２ギヤと前記第４ギヤとが互いに噛み合い、
前記第３ギヤ及び前記第４ギヤのいずれか一方を前記第２軸部材に対して選択的に連結する噛み合い式係合装置が、前記第２軸上であって、前記第３ギヤと前記第４ギヤとの前記軸方向の間に配置され、
前記差動歯車機構は、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、前記出力ギヤに噛み合う差動入力ギヤを備え、
前記摩擦係合装置が、前記第２軸上であって、前記第３ギヤ及び前記第４ギヤに対して前記軸方向の一方側に配置されている、車両用駆動装置。
 The friction engagement device according to any one of claims 1 to 3 ,
a rotating electric machine including a rotor disposed on a first shaft and functioning as a driving force source for the wheels;
A pair of output members each drivingly connected to one of the wheels;
a transmission that changes the speed of rotation transmitted from the rotating electric machine;
a differential gear mechanism that distributes rotation transmitted from the transmission to the pair of output members;
a case as the non-rotating member that houses the rotating electric machine, the transmission, and the differential gear mechanism,
The transmission includes a first shaft member disposed on the first shaft, a first gear and a second gear connected to rotate integrally with the first shaft member, a second shaft member disposed on a second shaft parallel to the first shaft, a third gear and a fourth gear supported to be rotatable relative to the second shaft member, and an output gear connected to rotate integrally with the second shaft member,
the first gear and the third gear mesh with each other, and the second gear and the fourth gear mesh with each other;
a meshing engagement device that selectively connects either the third gear or the fourth gear to the second shaft member is disposed on the second shaft between the third gear and the fourth gear in the axial direction,
the differential gear mechanism includes a differential input gear disposed on a third shaft parallel to the first shaft and the second shaft and meshing with the output gear;
The friction engagement device is disposed on the second shaft and on one side in the axial direction with respect to the third gear and the fourth gear.
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