JP2021088267A - Vehicular driving device - Google Patents

Vehicular driving device Download PDF

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JP2021088267A
JP2021088267A JP2019219547A JP2019219547A JP2021088267A JP 2021088267 A JP2021088267 A JP 2021088267A JP 2019219547 A JP2019219547 A JP 2019219547A JP 2019219547 A JP2019219547 A JP 2019219547A JP 2021088267 A JP2021088267 A JP 2021088267A
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oil passage
hydraulic pump
gear mechanism
differential gear
electric machine
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賢志 宮永
Kenji Miyanaga
賢志 宮永
加藤　裕
Yutaka Kato
裕 加藤
昌記 吉田
Masaki Yoshida
昌記 吉田
英知 汐田
Hidetomo Shiota
英知 汐田
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Aisin AW Co Ltd
Toyota Motor Corp
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Aisin AW Co Ltd
Toyota Motor Corp
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
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Abstract

To provide a vehicular driving device which can properly lubricate a portion needing lubrication regardless of a traveling state of a vehicle.SOLUTION: A vehicular driving device includes: a first connection oil passage 74 which connects a first supply oil passage 71 for supplying an oil to a differential gear mechanism 2 for distribution with a first hydraulic pump 61; a second connection oil passage 75 which connects a second supply oil passage 72 for supplying the oil to rotary electric machines MG1, MG2 with a second hydraulic pump 62; a third connection oil passage 76 which connects a third supply oil passage 73 for supplying the oil to a power transmission mechanism 3 and a differential gear mechanism 4 for output with the second hydraulic pump 62; and a fourth connection oil passage 77 which connects the first connection oil passage 74 with the second connection oil passage 75. A first check valve 81 is provided at the upstream side of a connection portion of the first connection oil passage 74 connected to the fourth connection oil passage 77, and a second check valve 82 is provided at the upstream side of a connection portion of the second connection oil passage 75 connected to the fourth connection oil passage 77. A maximum discharge amount of the second hydraulic pump 62 is larger than a maximum discharge amount of the first hydraulic pump 61.SELECTED DRAWING: Figure 3

Description

本発明は、第１油圧ポンプ及び第２油圧ポンプを備えた、スプリット型のハイブリッド車両用の駆動装置に関する。 The present invention relates to a drive device for a split type hybrid vehicle including a first hydraulic pump and a second hydraulic pump.

このような車両用駆動装置の一例が、下記の特許文献１に開示されている。以下、この背景技術の説明では、特許文献１における符号を括弧内に引用する。 An example of such a vehicle drive device is disclosed in Patent Document 1 below. Hereinafter, in the description of this background technique, the reference numerals in Patent Document 1 are quoted in parentheses.

特許文献１の車両用駆動装置は、内燃機関（１０）に駆動連結される入力部材（２６）と、それぞれ車輪（２９）に駆動連結される一対の出力部材（２８）と、入力される回転を一対の出力部材（２８）に分配する出力用差動歯車機構（２４）と、第１回転電機（ＭＧ１）及び第２回転電機（ＭＧ２）と、出力用差動歯車機構（２４）及び第２回転電機（ＭＧ２）に駆動連結された動力伝達機構（５６）と、入力部材（２６）の回転を動力伝達機構（５６）と第１回転電機（ＭＧ１）とに分配する分配用差動歯車機構（４０）と、入力部材（２６）の回転に連動する第１油圧ポンプ（５１）と、出力用差動歯車機構（２４）の回転に連動する第２油圧ポンプ（５２）と、を備えている（特許文献１の図１参照）。 The vehicle drive device of Patent Document 1 includes an input member (26) that is driven and connected to an internal combustion engine (10), a pair of output members (28) that are driven and connected to wheels (29), and an input rotation. The output differential gear mechanism (24), the first rotary electric machine (MG1) and the second rotary electric machine (MG2), and the output differential gear mechanism (24) and the first A differential gear for distribution that distributes the rotation of the power transmission mechanism (56) driven and connected to the two-rotary electric machine (MG2) and the rotation of the input member (26) to the power transmission mechanism (56) and the first rotary electric machine (MG1). A mechanism (40), a first hydraulic pump (51) interlocking with the rotation of the input member (26), and a second hydraulic pump (52) interlocking with the rotation of the output differential gear mechanism (24) are provided. (See FIG. 1 of Patent Document 1).

上記の車両用駆動装置には、第１油圧ポンプ（５１）から吐出された油を、分配用差動歯車機構（４０）と、第１回転電機（ＭＧ１）及び第２回転電機（ＭＧ２）とに供給する第１の油路（７１）と、第２油圧ポンプ（５２）から吐出された油を、動力伝達機構（５６）及び出力用差動歯車機構（２４）と、第１回転電機（ＭＧ１）及び第２回転電機（ＭＧ２）とに供給する第２の油路（７２）とが設けられている（特許文献１の図２参照）。 In the vehicle drive device, the oil discharged from the first hydraulic pump (51) is supplied to the distribution differential gear mechanism (40), the first rotary electric machine (MG1), and the second rotary electric machine (MG2). The oil discharged from the first oil passage (71) and the second hydraulic pump (52) to be supplied to the power transmission mechanism (56), the differential gear mechanism for output (24), and the first rotary electric machine ( A second oil passage (72) for supplying the MG1) and the second rotary electric machine (MG2) is provided (see FIG. 2 of Patent Document 1).

そして、上記の車両用駆動装置が搭載された車両が、内燃機関（１０）及び第２回転電機（ＭＧ２）の双方の駆動力により走行する場合には、第１油圧ポンプ（５１）及び第２油圧ポンプ（５２）の双方が駆動される。その結果、第１油圧ポンプ（５１）から吐出された油が、分配用差動歯車機構（４０）に供給される。更に、第２油圧ポンプ（５２）から吐出された油が、動力伝達機構（５６）及び出力用差動歯車機構（２４）に供給される。また、第１油圧ポンプ（５１）から吐出された油、及び、第２油圧ポンプ（５２）から吐出された油のうちの油圧が高い方が、第１回転電機（ＭＧ１）及び第２回転電機（ＭＧ２）に供給される。
（特許文献１の図５参照） Then, when the vehicle equipped with the above-mentioned vehicle drive device travels by the driving force of both the internal combustion engine (10) and the second rotary electric machine (MG2), the first hydraulic pump (51) and the second hydraulic pump (51) and the second Both hydraulic pumps (52) are driven. As a result, the oil discharged from the first hydraulic pump (51) is supplied to the distribution differential gear mechanism (40). Further, the oil discharged from the second hydraulic pump (52) is supplied to the power transmission mechanism (56) and the output differential gear mechanism (24). Further, the oil discharged from the first hydraulic pump (51) and the oil discharged from the second hydraulic pump (52), whichever has the higher oil pressure, is the first rotary electric machine (MG1) and the second rotary electric machine. It is supplied to (MG2).
(See FIG. 5 of Patent Document 1)

特開２０１９−１１９４０２号公報JP-A-2019-119402

上記の車両用駆動装置が搭載された車両が、第２回転電機（ＭＧ２）の駆動力のみで走行する場合には、第１油圧ポンプ（５１）は駆動されず、第２油圧ポンプ（５２）が駆動される。その結果、第２油圧ポンプ（５２）から吐出された油が、動力伝達機構（５６）及び出力用差動歯車機構（２４）と、第１回転電機（ＭＧ１）及び第２回転電機（ＭＧ２）とに供給される（特許文献１の図３参照）。つまり、分配用差動歯車機構（４０）には油が供給されない。 When the vehicle equipped with the above vehicle drive device travels only with the driving force of the second rotary electric machine (MG2), the first hydraulic pump (51) is not driven and the second hydraulic pump (52) is not driven. Is driven. As a result, the oil discharged from the second hydraulic pump (52) is the power transmission mechanism (56), the output differential gear mechanism (24), the first rotary electric machine (MG1), and the second rotary electric machine (MG2). (See FIG. 3 of Patent Document 1). That is, no oil is supplied to the distribution differential gear mechanism (40).

しかしながら、第２回転電機（ＭＧ２）の駆動力のみで走行する場合にも、分配用差動歯車機構（４０）の一部の回転要素は回転する。そのため、車両の走行状態によっては、車輪（２９）の回転に伴って分配用差動歯車機構（４０）の一部の回転要素が高速で回転する状態となる場合があった。特許文献１の車両用駆動装置では、このような場合に、分配用差動歯車機構（４０）に油が供給されないという事態が生じ得た。 However, even when traveling only with the driving force of the second rotating electric machine (MG2), some rotating elements of the distribution differential gear mechanism (40) rotate. Therefore, depending on the traveling state of the vehicle, a part of the rotating elements of the distribution differential gear mechanism (40) may rotate at high speed as the wheels (29) rotate. In the vehicle drive device of Patent Document 1, in such a case, a situation may occur in which oil is not supplied to the distribution differential gear mechanism (40).

そこで、車両の走行状態によらず、潤滑が必要な部位を適切に潤滑することができる車両用駆動装置の実現が望まれる。 Therefore, it is desired to realize a vehicle drive device capable of appropriately lubricating a portion requiring lubrication regardless of the traveling state of the vehicle.

上記に鑑みた、車両用駆動装置の特徴構成は、
内燃機関に駆動連結される入力部材と、
それぞれ車輪に駆動連結される一対の出力部材と、
入力される回転を一対の前記出力部材に分配する出力用差動歯車機構と、
第１回転電機及び第２回転電機と、
前記出力用差動歯車機構及び前記第２回転電機に駆動連結された動力伝達機構と、
前記入力部材の回転を、前記動力伝達機構と前記第１回転電機とに分配する分配用差動歯車機構と、
前記入力部材の回転に連動する第１油圧ポンプと、
前記出力用差動歯車機構の回転に連動する第２油圧ポンプと、
前記分配用差動歯車機構に油を供給する第１供給油路と、
前記第１回転電機及び前記第２回転電機のそれぞれに油を供給する第２供給油路と、
前記動力伝達機構及び前記出力用差動歯車機構のそれぞれに油を供給する第３供給油路と、
前記第１油圧ポンプと前記第１供給油路とを接続する第１接続油路と、
前記第２油圧ポンプと前記第２供給油路とを接続する第２接続油路と、
前記第２油圧ポンプと前記第３供給油路とを接続する第３接続油路と、
前記第１接続油路と前記第２接続油路とを接続する第４接続油路と、を備え、
前記第１接続油路における前記第４接続油路との接続部分よりも上流側に、油の逆流を規制する第１逆止弁が設けられ、
前記第２接続油路における前記第４接続油路との接続部分よりも上流側に、油の逆流を規制する第２逆止弁が設けられ、
前記第２油圧ポンプの最大吐出量は、前記第１油圧ポンプの最大吐出量よりも大きい点にある。 In view of the above, the characteristic configuration of the vehicle drive device is
Input members that are driven and connected to the internal combustion engine
A pair of output members that are driven and connected to the wheels, respectively.
An output differential gear mechanism that distributes the input rotation to the pair of output members,
With the 1st rotary electric machine and the 2nd rotary electric machine,
The output differential gear mechanism, the power transmission mechanism driven and connected to the second rotary electric machine, and
A distribution differential gear mechanism that distributes the rotation of the input member to the power transmission mechanism and the first rotary electric machine.
The first hydraulic pump linked to the rotation of the input member and
A second hydraulic pump that is interlocked with the rotation of the output differential gear mechanism,
A first supply oil passage for supplying oil to the distribution differential gear mechanism, and
A second supply oil passage for supplying oil to each of the first rotary electric machine and the second rotary electric machine, and
A third supply oil passage for supplying oil to each of the power transmission mechanism and the output differential gear mechanism, and
A first connecting oil passage connecting the first hydraulic pump and the first supply oil passage,
A second connecting oil passage connecting the second hydraulic pump and the second supply oil passage,
A third connecting oil passage connecting the second hydraulic pump and the third supply oil passage,
A fourth connecting oil passage connecting the first connecting oil passage and the second connecting oil passage is provided.
A first check valve that regulates the backflow of oil is provided on the upstream side of the first connecting oil passage with the connection portion with the fourth connecting oil passage.
A second check valve that regulates the backflow of oil is provided on the upstream side of the second connecting oil passage with the connection portion with the fourth connecting oil passage.
The maximum discharge amount of the second hydraulic pump is larger than the maximum discharge amount of the first hydraulic pump.

この特徴構成によれば、第１油圧ポンプ及び第２油圧ポンプの双方が駆動される場合（内燃機関及び第２回転電機のうち、少なくとも内燃機関の駆動力により車両が走行している場合）であって、第１接続油路の油圧が第２接続油路の油圧よりも低い場合（車両が比較的高速で走行している場合）には、第２油圧ポンプから吐出された油が、第２接続油路及び第２供給油路を通って、第１回転電機及び第２回転電機に供給されると共に、第２接続油路、第４接続油路、第１接続油路、及び第１供給油路を通って、分配用差動歯車機構に供給される。更に、第２油圧ポンプから吐出された油が、第３接続油路及び第３供給油路を通って、動力伝達機構及び出力用差動歯車機構に供給される。この場合、第１回転電機、第２回転電機、分配用差動歯車機構、動力伝達機構、及び出力用差動歯車機構の全てに油が十分に供給される。
一方、第１油圧ポンプ及び第２油圧ポンプの双方が駆動される場合であって、第１接続油路の油圧が第２接続油路の油圧よりも高い場合（車両が比較的低速で走行している場合）、或いは第１油圧ポンプ及び第２油圧ポンプのうち、第１油圧ポンプのみが駆動される場合（内燃機関が駆動中で車両が停車している場合）には、第１油圧ポンプから吐出された油が、第１接続油路及び第１供給油路を通って、分配用差動歯車機構に供給されると共に、第１接続油路、第４接続油路、第２接続油路、及び第２供給油路を通って、第１回転電機及び第２回転電機に供給される。この場合、第１回転電機、第２回転電機、及び分配用差動歯車機構には油が十分に供給される。一方、第２油圧ポンプの吐出圧が低い又は吐出圧がないために、第３接続油路及び第３供給油路を介して動力伝達機構及び出力用差動歯車機構に油が十分に供給されない場合がある。しかし、この場合、動力伝達機構及び出力用差動歯車機構の回転要素の回転速度は比較的低い又はゼロであるため、それらの潤滑に必要な油の量は少ない。
また、第１油圧ポンプ及び第２油圧ポンプのうち、第２油圧ポンプのみが駆動される場合（第２回転電機の駆動力のみで車両が走行している場合、又は、車両が牽引されている場合）には、第２油圧ポンプから吐出された油が、第２接続油路及び第２供給油路を通って、第１回転電機及び第２回転電機に供給されると共に、第２接続油路、第４接続油路、第１接続油路、及び第１供給油路を通って、分配用差動歯車機構に供給される。更に、第２油圧ポンプから吐出された油が、第３接続油路及び第３供給油路を通って、動力伝達機構及び出力用差動歯車機構に供給される。この場合、第１回転電機、第２回転電機、分配用差動歯車機構、動力伝達機構、及び出力用差動歯車機構の全てに油が十分に供給される。
以上のように、本構成によれば、車両の走行状態によらず、潤滑が必要な部位を適切に潤滑することができる車両用駆動装置を実現できる。 According to this characteristic configuration, when both the first hydraulic pump and the second hydraulic pump are driven (when the vehicle is running by at least the driving force of the internal combustion engine among the internal combustion engine and the second rotary electric machine). If the oil pressure in the first connection oil passage is lower than the oil pressure in the second connection oil passage (when the vehicle is traveling at a relatively high speed), the oil discharged from the second hydraulic pump is the first. It is supplied to the first rotary electric machine and the second rotary electric machine through the two connecting oil passages and the second supply oil passage, and is also supplied to the second connecting oil passage, the fourth connecting oil passage, the first connecting oil passage, and the first. It is supplied to the distribution differential gear mechanism through the supply oil passage. Further, the oil discharged from the second hydraulic pump is supplied to the power transmission mechanism and the output differential gear mechanism through the third connecting oil passage and the third supply oil passage. In this case, oil is sufficiently supplied to all of the first rotary electric machine, the second rotary electric machine, the distribution differential gear mechanism, the power transmission mechanism, and the output differential gear mechanism.
On the other hand, when both the first hydraulic pump and the second hydraulic pump are driven, and the hydraulic pressure of the first connecting oil passage is higher than the hydraulic pressure of the second connecting oil passage (the vehicle travels at a relatively low speed). If only the first hydraulic pump of the first hydraulic pump and the second hydraulic pump is driven (when the internal combustion engine is driving and the vehicle is stopped), the first hydraulic pump The oil discharged from the pump is supplied to the differential gear mechanism for distribution through the first connecting oil passage and the first supply oil passage, and also the first connecting oil passage, the fourth connecting oil passage, and the second connecting oil. It is supplied to the first rotary electric machine and the second rotary electric machine through the road and the second supply oil passage. In this case, oil is sufficiently supplied to the first rotary electric machine, the second rotary electric machine, and the distribution differential gear mechanism. On the other hand, because the discharge pressure of the second hydraulic pump is low or there is no discharge pressure, oil is not sufficiently supplied to the power transmission mechanism and the output differential gear mechanism via the third connecting oil passage and the third supply oil passage. In some cases. However, in this case, since the rotation speeds of the rotating elements of the power transmission mechanism and the output differential gear mechanism are relatively low or zero, the amount of oil required for lubrication of them is small.
Further, when only the second hydraulic pump of the first hydraulic pump and the second hydraulic pump is driven (when the vehicle is running only by the driving force of the second rotary electric machine, or the vehicle is being towed). In the case), the oil discharged from the second hydraulic pump is supplied to the first rotary electric machine and the second rotary electric machine through the second connecting oil passage and the second supply oil passage, and is also supplied to the second connecting oil. It is supplied to the differential gear mechanism for distribution through a road, a fourth connecting oil passage, a first connecting oil passage, and a first supply oil passage. Further, the oil discharged from the second hydraulic pump is supplied to the power transmission mechanism and the output differential gear mechanism through the third connecting oil passage and the third supply oil passage. In this case, oil is sufficiently supplied to all of the first rotary electric machine, the second rotary electric machine, the distribution differential gear mechanism, the power transmission mechanism, and the output differential gear mechanism.
As described above, according to this configuration, it is possible to realize a vehicle drive device capable of appropriately lubricating a portion requiring lubrication regardless of the traveling state of the vehicle.

実施形態に係る車両用駆動装置のスケルトン図Skeleton diagram of the vehicle drive device according to the embodiment 実施形態に係る車両用駆動装置における分配用差動歯車機構の周辺の構成を示す断面図Sectional drawing which shows the peripheral structure of the distribution differential gear mechanism in the vehicle drive device which concerns on embodiment. 実施形態に係る車両用駆動装置の油圧回路を示す図The figure which shows the hydraulic circuit of the drive device for a vehicle which concerns on embodiment. 第１油圧ポンプ及び第２油圧ポンプの双方が駆動される場合であって、第１接続油路の油圧が第２接続油路の油圧よりも高い場合における、油の流動態様を示す図The figure which shows the flow mode of the oil in the case where both the 1st hydraulic pump and the 2nd hydraulic pump are driven, and the oil pressure of a 1st connection oil passage is higher than the oil pressure of a 2nd connection oil passage. 第１油圧ポンプ及び第２油圧ポンプの双方が駆動される場合であって、第１接続油路の油圧が第２接続油路の油圧よりも低い場合における、油の流動態様を示す図The figure which shows the flow mode of the oil in the case where both the 1st hydraulic pump and the 2nd hydraulic pump are driven, and the oil pressure of a 1st connection oil passage is lower than the oil pressure of a 2nd connection oil passage. 第１油圧ポンプ及び第２油圧ポンプのうち、第１油圧ポンプのみが駆動される場合における、油の流動態様を示す図The figure which shows the flow mode of oil in the case where only the 1st hydraulic pump is driven among the 1st hydraulic pump and the 2nd hydraulic pump. 第１油圧ポンプ及び第２油圧ポンプのうち、第２油圧ポンプのみが駆動される場合における、油の流動態様を示す図The figure which shows the flow mode of oil in the case where only the 2nd hydraulic pump is driven among the 1st hydraulic pump and the 2nd hydraulic pump.

以下では、実施形態に係る車両用駆動装置１００について、図面を参照して説明する。図１に示すように、車両用駆動装置１００は、第１回転電機ＭＧ１及び第２回転電機ＭＧ２と、入力部材１と、分配用差動歯車機構２と、動力伝達機構３と、出力用差動歯車機構４と、一対の出力部材５と、を備えている。本実施形態では、これらはケースＣＳ（図２参照）に収容されている。 Hereinafter, the vehicle drive device 100 according to the embodiment will be described with reference to the drawings. As shown in FIG. 1, the vehicle drive device 100 includes a first rotary electric machine MG1 and a second rotary electric machine MG2, an input member 1, a distribution differential gear mechanism 2, a power transmission mechanism 3, and an output difference. It includes a dynamic gear mechanism 4 and a pair of output members 5. In this embodiment, they are housed in a case CS (see FIG. 2).

本実施形態では、第１回転電機ＭＧ１と入力部材１と分配用差動歯車機構２とのそれぞれは、その回転軸心としての第１軸Ｘ１上に配置されている。動力伝達機構３は、その回転軸心としての第２軸Ｘ２上に配置されている。第２回転電機ＭＧ２は、その回転軸心としての第３軸Ｘ３上に配置されている。出力用差動歯車機構４と一対の出力部材５とのそれぞれは、その回転軸心としての第４軸Ｘ４上に配置されている。本例では、これらの軸Ｘ１〜Ｘ４は、互いに平行に配置されている。 In the present embodiment, each of the first rotary electric machine MG1, the input member 1, and the distribution differential gear mechanism 2 is arranged on the first axis X1 as its rotation axis. The power transmission mechanism 3 is arranged on the second axis X2 as its rotation axis. The second rotary electric machine MG2 is arranged on the third axis X3 as its rotation axis. Each of the output differential gear mechanism 4 and the pair of output members 5 is arranged on the fourth axis X4 as its rotation axis. In this example, these axes X1 to X4 are arranged parallel to each other.

以下の説明では、上記の軸Ｘ１〜Ｘ４に平行な方向を、車両用駆動装置１００の「軸方向Ｌ」とする。そして、軸方向Ｌにおいて、分配用差動歯車機構２に対して第１回転電機ＭＧ１が配置される側を「軸方向第１側Ｌ１」とし、その反対側を「軸方向第２側Ｌ２」とする。また、上記の軸Ｘ１〜Ｘ４のそれぞれに直交する方向を、各軸を基準とした「径方向Ｒ」とする。なお、どの軸を基準とするかを区別する必要がない場合やどの軸を基準とするかが明らかである場合には、単に「径方向Ｒ」と記す場合がある。 In the following description, the direction parallel to the axes X1 to X4 is referred to as the "axial direction L" of the vehicle drive device 100. Then, in the axial direction L, the side on which the first rotary electric machine MG1 is arranged with respect to the distribution differential gear mechanism 2 is referred to as "axial first side L1", and the opposite side is referred to as "axial second side L2". And. Further, the direction orthogonal to each of the above axes X1 to X4 is defined as the "diameter direction R" with respect to each axis. When it is not necessary to distinguish which axis is used as a reference, or when it is clear which axis is used as a reference, it may be simply described as "diameter direction R".

入力部材１は、内燃機関ＥＧに駆動連結されている。本実施形態では、入力部材１は、伝達されるトルクの変動を減衰するダンパ装置ＤＰを介して、内燃機関ＥＧの出力軸Ｅｏに駆動連結されている。内燃機関ＥＧは、燃料の燃焼により駆動されて動力を取り出す原動機（ガソリンエンジン、ディーゼルエンジン等）である。 The input member 1 is driven and connected to the internal combustion engine EG. In the present embodiment, the input member 1 is driven and connected to the output shaft Eo of the internal combustion engine EG via a damper device DP that attenuates fluctuations in the transmitted torque. The internal combustion engine EG is a prime mover (gasoline engine, diesel engine, etc.) that is driven by combustion of fuel to extract power.

ここで、本願において「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指し、当該２つの回転要素が一体的に回転するように連結された状態、或いは当該２つの回転要素が１つ又は２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を含む。このような伝動部材としては、回転を同速で又は変速して伝達する各種の部材、例えば、軸、歯車機構、ベルト、チェーン等が含まれる。なお、伝動部材として、回転及び駆動力を選択的に伝達する係合装置、例えば、摩擦係合装置、噛み合い式係合装置等が含まれていても良い。ただし、分配用差動歯車機構２及び出力用差動歯車機構４のそれぞれの各回転要素について「駆動連結」という場合には、分配用差動歯車機構２及び出力用差動歯車機構４のそれぞれに備えられた複数の回転要素が、互いに他の回転要素を介することなく連結されている状態を指すものとする。 Here, in the present application, the "driving connection" refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or the said. It includes a state in which two rotating elements are mutably connected so that a driving force can be transmitted via one or more transmission members. Such transmission members include various members that transmit rotation at the same speed or at different speeds, such as shafts, gear mechanisms, belts, chains, and the like. The transmission member may include an engaging device that selectively transmits rotation and driving force, for example, a friction engaging device, a meshing type engaging device, and the like. However, when each rotating element of the distribution differential gear mechanism 2 and the output differential gear mechanism 4 is referred to as "drive connection", the distribution differential gear mechanism 2 and the output differential gear mechanism 4 are respectively used. It is assumed that a plurality of rotating elements provided in the above are connected to each other without interposing other rotating elements.

第１回転電機ＭＧ１は、電力の供給を受けて動力を発生するモータ（電動機）としての機能と、動力の供給を受けて電力を発生するジェネレータ（発電機）としての機能とを有している。そのため、第１回転電機ＭＧ１は、蓄電装置（図示を省略）と電気的に接続されている。この蓄電装置としては、バッテリやキャパシタ等の公知の各種の蓄電装置を用いることができる。本実施形態では、第１回転電機ＭＧ１は、内燃機関ＥＧのトルクにより発電を行って、蓄電装置を充電し、或いは第２回転電機ＭＧ２を駆動するための電力を供給するジェネレータとして機能する。ただし、第１回転電機ＭＧ１は、車両の高速走行中や内燃機関ＥＧの始動中等には、力行して駆動力（「トルク」と同義）を発生するモータとして機能する場合もある。 The first rotary electric machine MG1 has a function as a motor (motor) that receives power supply and generates power, and a function as a generator (generator) that receives power supply and generates power. .. Therefore, the first rotary electric machine MG1 is electrically connected to a power storage device (not shown). As this power storage device, various known power storage devices such as a battery and a capacitor can be used. In the present embodiment, the first rotary electric machine MG1 functions as a generator that generates electric power by the torque of the internal combustion engine EG to charge a power storage device or supply electric power for driving the second rotary electric machine MG2. However, the first rotary electric machine MG1 may function as a motor that powers and generates a driving force (synonymous with "torque") while the vehicle is traveling at high speed or the internal combustion engine EG is starting.

第１回転電機ＭＧ１は、非回転部材（ここでは、ケースＣＳ）に固定された第１ステータＳｔ１と、当該第１ステータＳｔ１に対して回転自在に支持された第１ロータＲｏ１と、を備えている。本実施形態では、第１ロータＲｏ１は、第１ステータＳｔ１に対して径方向Ｒの内側に配置されている。第１ロータＲｏ１には、軸方向Ｌに沿って延在する第１ロータ軸ＲＳ１が一体的に回転するように連結されている。本実施形態では、第１ロータ軸ＲＳ１は、第１ロータＲｏ１に対して径方向Ｒの内側に配置されている。また、本実施形態では、第１ロータ軸ＲＳ１は、軸方向Ｌの両側が開口した筒状に形成されている。 The first rotary electric machine MG1 includes a first stator St1 fixed to a non-rotating member (here, a case CS) and a first rotor Ro1 rotatably supported by the first stator St1. There is. In the present embodiment, the first rotor Ro1 is arranged inside the radial direction R with respect to the first stator St1. The first rotor shaft RS1 extending along the axial direction L is connected to the first rotor Ro1 so as to rotate integrally. In the present embodiment, the first rotor shaft RS1 is arranged inside the radial direction R with respect to the first rotor Ro1. Further, in the present embodiment, the first rotor shaft RS1 is formed in a tubular shape with both sides open in the axial direction L.

分配用差動歯車機構２は、入力部材１の回転を、動力伝達機構３と第１回転電機ＭＧ１とに分配するように構成されている。そのため、分配用差動歯車機構２を備えた車両用駆動装置１００は、所謂、スプリット型のハイブリッド車両用の駆動装置として構成されている。 The distribution differential gear mechanism 2 is configured to distribute the rotation of the input member 1 to the power transmission mechanism 3 and the first rotary electric machine MG1. Therefore, the vehicle drive device 100 provided with the distribution differential gear mechanism 2 is configured as a so-called split type hybrid vehicle drive device.

本実施形態では、分配用差動歯車機構２は、シングルピニオン型の遊星歯車機構である。具体的には、分配用差動歯車機構２は、ピニオンギヤＰ２を支持するキャリヤＣ２と、ピニオンギヤＰ２に噛み合うサンギヤＳ２と、当該サンギヤＳ２に対して径方向Ｒの外側に配置されてピニオンギヤＰ２に噛み合うリングギヤＲ２と、を備えている。 In the present embodiment, the distribution differential gear mechanism 2 is a single pinion type planetary gear mechanism. Specifically, the distribution differential gear mechanism 2 is arranged outside the radial direction R with respect to the carrier C2 that supports the pinion gear P2, the sun gear S2 that meshes with the pinion gear P2, and the sun gear S2, and meshes with the pinion gear P2. It is equipped with a ring gear R2.

本実施形態では、キャリヤＣ２は、分配用差動歯車機構２の入力要素であり、入力部材１と一体的に回転するように連結されている。具体的には、図２に示すように、入力部材１は、第１軸Ｘ１を基準とした径方向Ｒに沿って延在するように形成されたフランジ部１１と、軸方向Ｌに沿ってフランジ部１１から軸方向第１側Ｌ１に突出するように形成された第１軸部１２と、軸方向Ｌに沿ってフランジ部１１から軸方向第２側Ｌ２に突出するように形成された第２軸部１３と、を備えている。そして、フランジ部１１とキャリヤＣ２とが一体的に回転するように連結されている。 In the present embodiment, the carrier C2 is an input element of the distribution differential gear mechanism 2 and is connected to the input member 1 so as to rotate integrally. Specifically, as shown in FIG. 2, the input member 1 has a flange portion 11 formed so as to extend along the radial direction R with respect to the first axis X1 and along the axial direction L. A first shaft portion 12 formed so as to project from the flange portion 11 to the first side L1 in the axial direction, and a second shaft portion 12 formed so as to project from the flange portion 11 to the second side L2 in the axial direction along the axial direction L. It includes a two-axis portion 13. Then, the flange portion 11 and the carrier C2 are connected so as to rotate integrally.

キャリヤＣ２は、ピニオン軸Ａ２に支持されたピニオン軸受Ｐ２ａを介して、ピニオンギヤＰ２を回転可能に支持している。ピニオンギヤＰ２は、ピニオン軸Ａ２の軸心回りに回転（自転）すると共に、サンギヤＳ２を中心として回転（公転）する。ピニオンギヤＰ２は、その公転軌跡に沿って複数設けられている。本例では、ピニオン軸Ａ２は、キャリヤＣ２と一体的に回転するように連結されている。ピニオン軸Ａ２は、軸方向Ｌに沿って延在するように形成されている。ピニオン軸Ａ２の外周面と、ピニオンギヤＰ２の内周面との間に、ピニオン軸受Ｐ２ａが配置されている。 The carrier C2 rotatably supports the pinion gear P2 via a pinion bearing P2a supported by the pinion shaft A2. The pinion gear P2 rotates (rotates) around the axis of the pinion shaft A2 and rotates (revolves) around the sun gear S2. A plurality of pinion gears P2 are provided along the revolution trajectory. In this example, the pinion shaft A2 is connected so as to rotate integrally with the carrier C2. The pinion axis A2 is formed so as to extend along the axial direction L. A pinion bearing P2a is arranged between the outer peripheral surface of the pinion shaft A2 and the inner peripheral surface of the pinion gear P2.

本実施形態では、サンギヤＳ２は、第１ロータ軸ＲＳ１と一体的に回転するように連結されている。図２に示す例では、第１ロータ軸ＲＳ１における軸方向第２側Ｌ２の端部の外周面と、サンギヤＳ２の内周面とのそれぞれに、スプライン歯が形成されている。そして、それらのスプライン歯同士が係合されて、第１ロータ軸ＲＳ１とサンギヤＳ２とが一体的に回転するように連結されている。 In the present embodiment, the sun gear S2 is connected so as to rotate integrally with the first rotor shaft RS1. In the example shown in FIG. 2, spline teeth are formed on the outer peripheral surface of the end portion of the second side L2 in the axial direction of the first rotor shaft RS1 and the inner peripheral surface of the sun gear S2, respectively. Then, the spline teeth are engaged with each other, and the first rotor shaft RS1 and the sun gear S2 are connected so as to rotate integrally.

本実施形態では、リングギヤＲ２は、軸方向Ｌに沿って延在する筒状に形成された筒部材２１に対して径方向Ｒの内側であって、径方向Ｒに沿う径方向視で筒部材２１と重複する位置に配置されている。つまり、本実施形態では、分配用差動歯車機構２は、筒部材２１に対して径方向Ｒの内側であって、径方向Ｒに沿う径方向視で筒部材２１と重複する位置に配置されている。また、本実施形態では、リングギヤＲ２は、筒部材２１と一体的に回転するように連結されている。図２に示す例では、リングギヤＲ２は、筒部材２１の内周面に形成されている。ここで、２つの要素の配置に関して、「特定方向視で重複する」とは、その視線方向に平行な仮想直線を当該仮想直線と直交する各方向に移動させた場合に、当該仮想直線が２つの要素の双方に交わる領域が少なくとも一部に存在することを指す。 In the present embodiment, the ring gear R2 is inside the radial direction R with respect to the tubular member 21 formed in a tubular shape extending along the axial direction L, and is a tubular member in a radial direction along the radial direction R. It is arranged at a position overlapping with 21. That is, in the present embodiment, the distribution differential gear mechanism 2 is arranged at a position inside the tubular member 21 in the radial direction R and overlapping the tubular member 21 in the radial direction along the radial direction R. ing. Further, in the present embodiment, the ring gear R2 is connected so as to rotate integrally with the tubular member 21. In the example shown in FIG. 2, the ring gear R2 is formed on the inner peripheral surface of the tubular member 21. Here, regarding the arrangement of the two elements, "overlapping in a specific direction" means that the virtual straight line is 2 when the virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line. It means that there is at least a part of the area where both of the two elements intersect.

図１に示すように、動力伝達機構３は、出力用差動歯車機構４及び第２回転電機ＭＧ２に駆動連結されている。本実施形態では、動力伝達機構３は、第１カウンタギヤ３１と、第２カウンタギヤ３２と、これらが一体的に回転するように連結するカウンタ軸３３と、を備えたカウンタギヤ機構である。 As shown in FIG. 1, the power transmission mechanism 3 is drive-connected to the output differential gear mechanism 4 and the second rotary electric machine MG2. In the present embodiment, the power transmission mechanism 3 is a counter gear mechanism including a first counter gear 31, a second counter gear 32, and a counter shaft 33 that connects them so as to rotate integrally.

第１カウンタギヤ３１は、動力伝達機構３の入力要素である。第１カウンタギヤ３１は、第１伝達ギヤ２２に噛み合っている。本実施形態では、第１伝達ギヤ２２は、筒部材２１と一体的に回転するように連結されている。図２に示す例では、第１伝達ギヤ２２は、筒部材２１における軸方向Ｌの中央部よりも軸方向第２側Ｌ２の領域の外周面に形成されている。 The first counter gear 31 is an input element of the power transmission mechanism 3. The first counter gear 31 meshes with the first transmission gear 22. In the present embodiment, the first transmission gear 22 is connected to the tubular member 21 so as to rotate integrally. In the example shown in FIG. 2, the first transmission gear 22 is formed on the outer peripheral surface of the region of the tubular member 21 on the second side L2 in the axial direction with respect to the central portion in the axial direction L.

第２カウンタギヤ３２は、動力伝達機構３の出力要素である。本実施形態では、第２カウンタギヤ３２は、第１カウンタギヤ３１よりも小径に形成されている。また、本実施形態では、第２カウンタギヤ３２は、第１カウンタギヤ３１よりも軸方向第１側Ｌ１に配置されている。 The second counter gear 32 is an output element of the power transmission mechanism 3. In the present embodiment, the second counter gear 32 is formed to have a smaller diameter than the first counter gear 31. Further, in the present embodiment, the second counter gear 32 is arranged on the first side L1 in the axial direction with respect to the first counter gear 31.

第２回転電機ＭＧ２は、電力の供給を受けて動力を発生するモータ（電動機）としての機能と、動力の供給を受けて電力を発生するジェネレータ（発電機）としての機能とを有している。そのため、第２回転電機ＭＧ２も、第１回転電機ＭＧ１と同様に、上記蓄電装置と電気的に接続されている。本実施形態では、第２回転電機ＭＧ２は、主に車両を走行させるための駆動力を発生するモータとして機能する。ただし、車両の減速中等には、第２回転電機ＭＧ２は、車両の慣性力を電気エネルギとして回生するジェネレータとして機能する場合もある。 The second rotary electric machine MG2 has a function as a motor (motor) that receives power supply and generates power, and a function as a generator (generator) that receives power supply and generates power. .. Therefore, the second rotary electric machine MG2 is also electrically connected to the power storage device in the same manner as the first rotary electric machine MG1. In the present embodiment, the second rotary electric machine MG2 mainly functions as a motor that generates a driving force for traveling the vehicle. However, during deceleration of the vehicle or the like, the second rotary electric machine MG2 may function as a generator that regenerates the inertial force of the vehicle as electric energy.

第２回転電機ＭＧ２は、非回転部材（ここでは、ケースＣＳ）に固定された第２ステータＳｔ２と、当該第２ステータＳｔ２に対して回転自在に支持された第２ロータＲｏ２と、を備えている。本実施形態では、第２ロータＲｏ２は、第２ステータＳｔ２に対して径方向Ｒの内側に配置されている。第２ロータＲｏ２には、軸方向Ｌに沿って延在する第２ロータ軸ＲＳ２が一体的に回転するように連結されている。 The second rotary electric machine MG2 includes a second stator St2 fixed to a non-rotating member (here, a case CS) and a second rotor Ro2 rotatably supported by the second stator St2. There is. In the present embodiment, the second rotor Ro2 is arranged inside the radial direction R with respect to the second stator St2. The second rotor shaft RS2 extending along the axial direction L is connected to the second rotor Ro2 so as to rotate integrally.

第２ロータ軸ＲＳ２は、第２伝達ギヤ２３と一体的に回転するように連結されている。第２伝達ギヤ２３は、動力伝達機構３の第１カウンタギヤ３１の周方向における第１伝達ギヤ２２とは異なる位置で、第１カウンタギヤ３１と噛み合っている。 The second rotor shaft RS2 is connected so as to rotate integrally with the second transmission gear 23. The second transmission gear 23 meshes with the first counter gear 31 at a position different from that of the first transmission gear 22 in the circumferential direction of the first counter gear 31 of the power transmission mechanism 3.

出力用差動歯車機構４は、当該出力用差動歯車機構４の入力要素である差動入力ギヤ４１を備えている。差動入力ギヤ４１は、「差動入力部材」に相当する。差動入力ギヤ４１は、動力伝達機構３の第２カウンタギヤ３２に噛み合っている。出力用差動歯車機構４は、当該出力用差動歯車機構４に入力される回転、つまり、差動入力ギヤ４１の回転を、一対の出力部材５に分配するように構成されている。 The output differential gear mechanism 4 includes a differential input gear 41 which is an input element of the output differential gear mechanism 4. The differential input gear 41 corresponds to a "differential input member". The differential input gear 41 meshes with the second counter gear 32 of the power transmission mechanism 3. The output differential gear mechanism 4 is configured to distribute the rotation input to the output differential gear mechanism 4, that is, the rotation of the differential input gear 41, to the pair of output members 5.

一対の出力部材５のそれぞれは、車輪Ｗに駆動連結されている。一対の出力部材５は、出力用差動歯車機構４から軸方向Ｌの両側に突出するように配置されている。 Each of the pair of output members 5 is drive-connected to the wheel W. The pair of output members 5 are arranged so as to project from the output differential gear mechanism 4 on both sides in the axial direction L.

図２に示すように、本実施形態では、筒部材２１は、一対の第１軸受Ｂ１によって回転可能に支持されている。一対の第１軸受Ｂ１は、分配用差動歯車機構２に対して軸方向Ｌの両外側において、筒部材２１を径方向Ｒの内側から支持するように配置されている。本実施形態では、軸方向第１側Ｌ１の第１軸受Ｂ１は、ケースＣＳの第１側壁部ＣＳ１に支持されている。一方、軸方向第２側Ｌ２の第１軸受Ｂ１は、ケースＣＳの第２側壁部ＣＳ２に支持されている。こうして、筒部材２１は、一対の第１軸受Ｂ１を介して、ケースＣＳに対して回転可能に支持されている。図２に示す例では、一対の第１軸受Ｂ１のそれぞれは玉軸受である。 As shown in FIG. 2, in the present embodiment, the tubular member 21 is rotatably supported by a pair of first bearings B1. The pair of first bearings B1 are arranged so as to support the tubular member 21 from the inside of the radial direction R on both outer sides of the axial direction L with respect to the distribution differential gear mechanism 2. In the present embodiment, the first bearing B1 on the first side L1 in the axial direction is supported by the first side wall portion CS1 of the case CS. On the other hand, the first bearing B1 on the second side L2 in the axial direction is supported by the second side wall portion CS2 of the case CS. In this way, the tubular member 21 is rotatably supported with respect to the case CS via the pair of first bearings B1. In the example shown in FIG. 2, each of the pair of first bearings B1 is a ball bearing.

第１側壁部ＣＳ１及び第２側壁部ＣＳ２のそれぞれは、径方向Ｒに沿って延在するように形成されている。第１側壁部ＣＳ１は、分配用差動歯車機構２に対して、軸方向第１側Ｌ１に配置されている。一方、第２側壁部ＣＳ２は、分配用差動歯車機構２に対して、軸方向第２側Ｌ２に配置されている。 Each of the first side wall portion CS1 and the second side wall portion CS2 is formed so as to extend along the radial direction R. The first side wall portion CS1 is arranged on the first side L1 in the axial direction with respect to the distribution differential gear mechanism 2. On the other hand, the second side wall portion CS2 is arranged on the second side L2 in the axial direction with respect to the distribution differential gear mechanism 2.

本実施形態では、第１側壁部ＣＳ１から軸方向第２側Ｌ２に突出するように、第１突出部ＣＳ１ａが形成されている。そして、第１突出部ＣＳ１ａの外周面と、筒部材２１における軸方向第１側Ｌ１の端部の内周面との間に、軸方向第１側Ｌ１の第１軸受Ｂ１が配置されている。また、本実施形態では、第２側壁部ＣＳ２から軸方向第１側Ｌ１に突出するように、第２突出部ＣＳ２ａが形成されている。そして、第２突出部ＣＳ２ａの外周面と、筒部材２１における軸方向第２側Ｌ２の端部の内周面との間に、軸方向第２側Ｌ２の第１軸受Ｂ１が配置されている。 In the present embodiment, the first protruding portion CS1a is formed so as to project from the first side wall portion CS1 to the second side L2 in the axial direction. Then, the first bearing B1 on the first side L1 in the axial direction is arranged between the outer peripheral surface of the first protruding portion CS1a and the inner peripheral surface of the end portion of the first side L1 in the axial direction in the tubular member 21. .. Further, in the present embodiment, the second protruding portion CS2a is formed so as to project from the second side wall portion CS2 to the first side L1 in the axial direction. Then, the first bearing B1 on the second side L2 in the axial direction is arranged between the outer peripheral surface of the second protruding portion CS2a and the inner peripheral surface of the end portion of the second side L2 in the axial direction in the tubular member 21. ..

本実施形態では、第１ロータ軸ＲＳ１が、第１側壁部ＣＳ１を軸方向Ｌに貫通するように配置されている。そして、第１突出部ＣＳ１ａの内周面と、第１ロータ軸ＲＳ１の外周面との間に、第２軸受Ｂ２が配置されている。こうして、第１ロータ軸ＲＳ１は、第２軸受Ｂ２を介して、ケースＣＳに対して回転可能に支持されている。図２に示す例では、第２軸受Ｂ２は玉軸受である。 In the present embodiment, the first rotor shaft RS1 is arranged so as to penetrate the first side wall portion CS1 in the axial direction L. The second bearing B2 is arranged between the inner peripheral surface of the first protruding portion CS1a and the outer peripheral surface of the first rotor shaft RS1. In this way, the first rotor shaft RS1 is rotatably supported with respect to the case CS via the second bearing B2. In the example shown in FIG. 2, the second bearing B2 is a ball bearing.

本実施形態では、入力部材１は、一対の第３軸受Ｂ３によって回転可能に支持されている。具体的には、入力部材１は、第１軸部１２が第１ロータ軸ＲＳ１の径方向Ｒの内側に位置し、第２軸部１３が第２側壁部ＣＳ２を軸方向Ｌに貫通するように配置されている。そして、第１軸部１２の外周面と、第１ロータ軸ＲＳ１の内周面との間に、軸方向第１側Ｌ１の第３軸受Ｂ３が配置されている。また、第２軸部１３の外周面と、第２側壁部ＣＳ２から軸方向第１側Ｌ１に突出するように形成された第３突出部ＣＳ２ｂの内周面との間に、軸方向第２側Ｌ２の第３軸受Ｂ３が配置されている。図２に示す例では、一対の第３軸受Ｂ３のそれぞれは針状ころ軸受である。 In this embodiment, the input member 1 is rotatably supported by a pair of third bearings B3. Specifically, in the input member 1, the first shaft portion 12 is located inside the radial direction R of the first rotor shaft RS1, and the second shaft portion 13 penetrates the second side wall portion CS2 in the axial direction L. Is located in. A third bearing B3 on the first side L1 in the axial direction is arranged between the outer peripheral surface of the first shaft portion 12 and the inner peripheral surface of the first rotor shaft RS1. Further, between the outer peripheral surface of the second shaft portion 13 and the inner peripheral surface of the third protruding portion CS2b formed so as to project from the second side wall portion CS2 to the first side L1 in the axial direction, the second axial portion is formed. The third bearing B3 on the side L2 is arranged. In the example shown in FIG. 2, each of the pair of third bearings B3 is a needle roller bearing.

図１に示すように、車両用駆動装置１００は、第１油圧ポンプ６１と、第２油圧ポンプ６２と、を更に備えている。 As shown in FIG. 1, the vehicle drive device 100 further includes a first hydraulic pump 61 and a second hydraulic pump 62.

第１油圧ポンプ６１は、入力部材１の回転に連動する油圧ポンプである。そのため、第１油圧ポンプ６１は、内燃機関ＥＧの駆動力によって駆動される。本実施形態では、第１油圧ポンプ６１は、当該第１油圧ポンプ６１の回転部材である第１ポンプロータ６１１を備えている。第１ポンプロータ６１１は、入力部材１と一体的に回転するように入力部材１に連結されている。本実施形態では、第１ポンプロータ６１１は、第１ロータ軸ＲＳ１の径方向Ｒの内側を軸方向Ｌに沿って延在するポンプ軸６１２を介して、入力部材１に連結されている。図２に示す例では、ポンプ軸６１２と入力部材１の第１軸部１２とが一体的に回転するように互いに連結されている。 The first hydraulic pump 61 is a hydraulic pump that is interlocked with the rotation of the input member 1. Therefore, the first hydraulic pump 61 is driven by the driving force of the internal combustion engine EG. In the present embodiment, the first hydraulic pump 61 includes a first pump rotor 611, which is a rotating member of the first hydraulic pump 61. The first pump rotor 611 is connected to the input member 1 so as to rotate integrally with the input member 1. In the present embodiment, the first pump rotor 611 is connected to the input member 1 via a pump shaft 612 extending inside the radial direction R of the first rotor shaft RS1 along the axial direction L. In the example shown in FIG. 2, the pump shaft 612 and the first shaft portion 12 of the input member 1 are connected to each other so as to rotate integrally with each other.

第２油圧ポンプ６２は、出力用差動歯車機構４の回転に連動する油圧ポンプである。そのため、第１油圧ポンプ６１は、車両用駆動装置１００が搭載された車両が走行している場合に駆動される。本実施形態では、第２油圧ポンプ６２は、当該第２油圧ポンプ６２の回転部材である第２ポンプロータ６２１を備えている。第２ポンプロータ６２１は、出力用差動歯車機構４の差動入力ギヤ４１に従動して回転するように差動入力ギヤ４１に連結されている。本実施形態では、第２ポンプロータ６２１は、ポンプ駆動ギヤ６２２と一体的に回転するように連結されている。ポンプ駆動ギヤ６２２は、差動入力ギヤ４１の周方向における第２カウンタギヤ３２とは異なる位置で、差動入力ギヤ４１と噛み合っている。 The second hydraulic pump 62 is a hydraulic pump that is interlocked with the rotation of the output differential gear mechanism 4. Therefore, the first hydraulic pump 61 is driven when a vehicle equipped with the vehicle drive device 100 is running. In the present embodiment, the second hydraulic pump 62 includes a second pump rotor 621 which is a rotating member of the second hydraulic pump 62. The second pump rotor 621 is connected to the differential input gear 41 so as to rotate in accordance with the differential input gear 41 of the output differential gear mechanism 4. In the present embodiment, the second pump rotor 621 is connected to the pump drive gear 622 so as to rotate integrally. The pump drive gear 622 meshes with the differential input gear 41 at a position different from that of the second counter gear 32 in the circumferential direction of the differential input gear 41.

図３に示すように、車両用駆動装置１００は、油圧回路１０を備えている。油圧回路１０は、第１油圧ポンプ６１及び第２油圧ポンプ６２と、当該第１油圧ポンプ６１及び第２油圧ポンプ６２から吐出された油が流動する油路と、を備えている。本実施形態では、油圧回路１０の油路は、第１供給油路７１と、第２供給油路７２と、第３供給油路７３と、第１接続油路７４と、第２接続油路７５と、第３接続油路７６と、第４接続油路７７と、を含んでいる。 As shown in FIG. 3, the vehicle drive device 100 includes a hydraulic circuit 10. The hydraulic circuit 10 includes a first hydraulic pump 61 and a second hydraulic pump 62, and an oil passage through which oil discharged from the first hydraulic pump 61 and the second hydraulic pump 62 flows. In the present embodiment, the oil passages of the hydraulic circuit 10 are the first supply oil passage 71, the second supply oil passage 72, the third supply oil passage 73, the first connection oil passage 74, and the second connection oil passage. It includes 75, a third connecting oil passage 76, and a fourth connecting oil passage 77.

第１供給油路７１は、分配用差動歯車機構２に油を供給する油路である。第２供給油路７２は、第１回転電機ＭＧ１及び第２回転電機ＭＧ２のそれぞれに油を供給する油路である。第３供給油路７３は、動力伝達機構３及び出力用差動歯車機構４のそれぞれに油を供給する油路である。 The first supply oil passage 71 is an oil passage that supplies oil to the distribution differential gear mechanism 2. The second supply oil passage 72 is an oil passage for supplying oil to each of the first rotary electric machine MG1 and the second rotary electric machine MG2. The third supply oil passage 73 is an oil passage that supplies oil to each of the power transmission mechanism 3 and the output differential gear mechanism 4.

本実施形態では、第１供給油路７１は、分配用差動歯車機構２に加えて、第１回転電機ＭＧ１にも油を供給するように形成されている。具体的には、第１供給油路７１は、分配用差動歯車機構２に油を供給する第１分岐油路７１１と、第１回転電機ＭＧ１に油を供給する第２分岐油路７１２とに分岐している。本例では、第２分岐油路７１２は、第１回転電機ＭＧ１の回転要素（第１ロータＲｏ１、第１ロータ軸ＲＳ１）、及び当該回転要素を回転可能に支持する軸受等に、潤滑用の油を供給するように形成されている。 In the present embodiment, the first supply oil passage 71 is formed so as to supply oil to the first rotary electric machine MG1 in addition to the distribution differential gear mechanism 2. Specifically, the first supply oil passage 71 includes a first branch oil passage 711 that supplies oil to the distribution differential gear mechanism 2 and a second branch oil passage 712 that supplies oil to the first rotary electric machine MG1. Branches to. In this example, the second branch oil passage 712 is used for lubricating the rotating elements (first rotor Ro1, first rotor shaft RS1) of the first rotating electric machine MG1 and bearings that rotatably support the rotating elements. It is formed to supply oil.

本実施形態では、第２供給油路７２は、第１回転電機ＭＧ１に油を供給する第３分岐油路７２１と、第２回転電機ＭＧ２に油を供給する第４分岐油路７２２とに分岐している。本例では、第３分岐油路７２１は、第１回転電機ＭＧ１の第１ステータＳｔ１に、冷却用の油を供給するように形成されている。また、第４分岐油路７２２は、第２回転電機ＭＧ２の第２ステータＳｔ２に、冷却用の油を供給すると共に、第２回転電機ＭＧ２の回転要素（第２ロータＲｏ２、第２ロータ軸ＲＳ２）、及び当該回転要素を回転可能に支持する軸受等に、潤滑用の油を供給するように形成されている。 In the present embodiment, the second supply oil passage 72 is branched into a third branch oil passage 721 that supplies oil to the first rotary electric machine MG1 and a fourth branch oil passage 722 that supplies oil to the second rotary electric machine MG2. doing. In this example, the third branch oil passage 721 is formed so as to supply cooling oil to the first stator St1 of the first rotary electric machine MG1. Further, the fourth branch oil passage 722 supplies cooling oil to the second stator St2 of the second rotary electric machine MG2, and also supplies the rotating elements of the second rotary electric machine MG2 (second rotor Ro2, second rotor shaft RS2). ), And bearings and the like that rotatably support the rotating element, are formed so as to supply lubricating oil.

本実施形態では、第３供給油路７３は、動力伝達機構３に油を供給する第５分岐油路７３１と、出力用差動歯車機構４に油を供給する第６分岐油路７３２とに分岐している。 In the present embodiment, the third supply oil passage 73 includes a fifth branch oil passage 731 that supplies oil to the power transmission mechanism 3 and a sixth branch oil passage 732 that supplies oil to the output differential gear mechanism 4. It is branched.

第１接続油路７４は、第１油圧ポンプ６１と第１供給油路７１とを接続する油路である。第２接続油路７５は、第２油圧ポンプ６２と第２供給油路７２とを接続する油路である。第３接続油路７６は、第２油圧ポンプ６２と第３供給油路７３とを接続する油路である。第４接続油路７７は、第１接続油路７４と第２接続油路７５とを接続する油路である。 The first connecting oil passage 74 is an oil passage connecting the first hydraulic pump 61 and the first supply oil passage 71. The second connecting oil passage 75 is an oil passage connecting the second hydraulic pump 62 and the second supply oil passage 72. The third connecting oil passage 76 is an oil passage connecting the second hydraulic pump 62 and the third supply oil passage 73. The fourth connecting oil passage 77 is an oil passage connecting the first connecting oil passage 74 and the second connecting oil passage 75.

以下の説明では、第１接続油路７４における第４接続油路７７との接続部分よりも上流側の部分を「第１上流油路７４１」とし、下流側の部分を「第１下流油路７４２」とする。更に、第２接続油路７５における第４接続油路７７との接続部分よりも上流側の部分を「第２上流油路７５１」とし、下流側の部分を「第２下流油路７５２」とする。 In the following description, the portion of the first connecting oil passage 74 on the upstream side of the connecting portion with the fourth connecting oil passage 77 is referred to as the "first upstream oil passage 741", and the portion on the downstream side is referred to as the "first downstream oil passage". 742 ". Further, the portion of the second connecting oil passage 75 on the upstream side of the connecting portion with the fourth connecting oil passage 77 is referred to as "second upstream oil passage 751", and the portion on the downstream side is referred to as "second downstream oil passage 752". To do.

図２に示すように、本実施形態では、ポンプ軸６１２に、第１軸内油路６１２ａが形成されている。第１軸内油路６１２ａは、第１油圧ポンプ６１から吐出された油が流動する油路である。第１軸内油路６１２ａは、ポンプ軸６１２を軸方向Ｌに貫通するように形成されている。更に、本実施形態では、入力部材１に、第２軸内油路１ａと、複数の径方向油路１ｂとが形成されている。第２軸内油路１ａは、第１軸内油路６１２ａと連通すると共に、入力部材１の第１軸部１２における軸方向Ｌの全域と、第２軸部１３における軸方向Ｌの一部の領域とに亘って形成されている。複数の径方向油路１ｂのそれぞれは、第２軸内油路１ａと第２軸部１３の外周面とを連通するように、径方向Ｒに沿って形成されている。複数の径方向油路１ｂは、第２軸部１３の周方向に互いに間隔を空けて配置されている。 As shown in FIG. 2, in the present embodiment, the oil passage 612a in the first shaft is formed on the pump shaft 612. The oil passage 612a in the first shaft is an oil passage through which the oil discharged from the first hydraulic pump 61 flows. The oil passage 612a in the first shaft is formed so as to penetrate the pump shaft 612 in the axial direction L. Further, in the present embodiment, the input member 1 is formed with an oil passage 1a in the second shaft and a plurality of radial oil passages 1b. The oil passage 1a in the second shaft communicates with the oil passage 612a in the first shaft, and includes the entire area of the axial direction L in the first shaft portion 12 of the input member 1 and a part of the axial direction L in the second shaft portion 13. It is formed over the area of. Each of the plurality of radial oil passages 1b is formed along the radial direction R so as to communicate the oil passage 1a in the second shaft with the outer peripheral surface of the second shaft portion 13. The plurality of radial oil passages 1b are arranged so as to be spaced apart from each other in the circumferential direction of the second shaft portion 13.

また、本実施形態では、分配用差動歯車機構２のピニオン軸Ａ２に、第１ピニオン油路Ａ２ａと、第２ピニオン油路Ａ２ｂとが形成されている。第１ピニオン油路Ａ２ａは、軸方向第２側Ｌ２に向けて開口すると共に、軸方向Ｌに沿って形成されている。第２ピニオン油路Ａ２ｂは、第１ピニオン油路Ａ２ａとピニオン軸Ａ２の外周面とを連通するように、径方向Ｒに沿って形成されている。 Further, in the present embodiment, the first pinion oil passage A2a and the second pinion oil passage A2b are formed on the pinion shaft A2 of the distribution differential gear mechanism 2. The first pinion oil passage A2a opens toward the second side L2 in the axial direction and is formed along the axial direction L. The second pinion oil passage A2b is formed along the radial direction R so as to communicate the first pinion oil passage A2a and the outer peripheral surface of the pinion shaft A2.

本実施形態では、第１油圧ポンプ６１から吐出された油は、第１軸内油路６１２ａ、第２軸内油路１ａ、及び径方向油路１ｂを順に通って、第２軸部１３の外周面と第３突出部ＣＳ２ｂの内周面との間に流動する。第２軸部１３の外周面と第３突出部ＣＳ２ｂの内周面との間に流動した油は、軸方向Ｌにおけるフランジ部１１と第３突出部ＣＳ２ｂとの間に配置されたスラスト軸受である第４軸受Ｂ４を通過して、分配用差動歯車機構２と第２側壁部ＣＳ２との間に流動する。分配用差動歯車機構２と第２側壁部ＣＳ２との間に流動した油の一部は、キャリヤＣ２又はピニオン軸Ａ２に連結された案内部材２ａによって、第１ピニオン油路Ａ２ａへ案内される。案内部材２ａは、ピニオン軸Ａ２における軸方向第２側Ｌ２を向く第１ピニオン油路Ａ２ａの開口を軸方向第２側Ｌ２から覆うと共に、径方向Ｒの内側に向けて開口するように形成されている。 In the present embodiment, the oil discharged from the first hydraulic pump 61 passes through the first shaft inner oil passage 612a, the second shaft inner oil passage 1a, and the radial oil passage 1b in this order, and is connected to the second shaft portion 13. It flows between the outer peripheral surface and the inner peripheral surface of the third protruding portion CS2b. The oil that has flowed between the outer peripheral surface of the second shaft portion 13 and the inner peripheral surface of the third protruding portion CS2b is a thrust bearing arranged between the flange portion 11 and the third protruding portion CS2b in the axial direction L. It passes through a certain fourth bearing B4 and flows between the distribution differential gear mechanism 2 and the second side wall portion CS2. A part of the oil flowing between the distribution differential gear mechanism 2 and the second side wall portion CS2 is guided to the first pinion oil passage A2a by the guide member 2a connected to the carrier C2 or the pinion shaft A2. .. The guide member 2a is formed so as to cover the opening of the first pinion oil passage A2a facing the second side L2 in the axial direction of the pinion shaft A2 from the second side L2 in the axial direction and to open toward the inside of the radial direction R. ing.

第１ピニオン油路Ａ２ａに流入した油は、第２ピニオン油路Ａ２ｂを通って、ピニオン軸受Ｐ２ａに供給される。一方、分配用差動歯車機構２と第２側壁部ＣＳ２との間に流動した油の残りは、軸方向第２側Ｌ２の第１軸受Ｂ１、ピニオンギヤＰ２とリングギヤＲ２との噛み合い部、及び軸方向第１側Ｌ１の第１軸受Ｂ１に供給される。 The oil that has flowed into the first pinion oil passage A2a is supplied to the pinion bearing P2a through the second pinion oil passage A2b. On the other hand, the remaining oil flowing between the distribution differential gear mechanism 2 and the second side wall portion CS2 is the first bearing B1 on the second side L2 in the axial direction, the meshing portion between the pinion gear P2 and the ring gear R2, and the shaft. It is supplied to the first bearing B1 on the first side L1 in the direction.

本実施形態では、第１軸内油路６１２ａ、第２軸内油路１ａ、及び複数の径方向油路１ｂが第１供給油路７１として機能する。つまり、本実施形態では、第１供給油路７１は、筒部材２１に対して径方向Ｒの内側であって、軸方向Ｌにおける一対の第１軸受Ｂ１の間に油を供給するように形成されている。 In the present embodiment, the first shaft inner oil passage 612a, the second shaft inner oil passage 1a, and the plurality of radial oil passages 1b function as the first supply oil passage 71. That is, in the present embodiment, the first supply oil passage 71 is formed so as to supply oil between the pair of first bearings B1 in the axial direction L, which is inside the tubular member 21 in the radial direction R. Has been done.

図３に示すように、油圧回路１０は、第１逆止弁８１と、第２逆止弁８２と、を更に備えている。 As shown in FIG. 3, the hydraulic circuit 10 further includes a first check valve 81 and a second check valve 82.

第１逆止弁８１及び第２逆止弁８２のそれぞれは、油の逆流を規制する逆止弁である。第１逆止弁８１は、第１上流油路７４１に設けられている。第１逆止弁８１は、第１上流油路７４１における上流側（第１油圧ポンプ６１の側）から下流側（第１下流油路７４２の側）への油の流動を許容するが、その逆方向の油の流動を規制する。第２逆止弁８２は、第２上流油路７５１に設けられている。第２逆止弁８２は、第２上流油路７５１における上流側（第２油圧ポンプ６２の側）から下流側（第２下流油路７５２の側）への油の流動を許容するが、その逆方向の油の流動を規制する。 Each of the first check valve 81 and the second check valve 82 is a check valve that regulates the backflow of oil. The first check valve 81 is provided in the first upstream oil passage 741. The first check valve 81 allows oil to flow from the upstream side (the side of the first hydraulic pump 61) to the downstream side (the side of the first downstream oil passage 742) in the first upstream oil passage 741. Regulate the flow of oil in the opposite direction. The second check valve 82 is provided in the second upstream oil passage 751. The second check valve 82 allows oil to flow from the upstream side (the side of the second hydraulic pump 62) to the downstream side (the side of the second downstream oil passage 752) in the second upstream oil passage 751. Regulate the flow of oil in the opposite direction.

本実施形態では、油圧回路１０は、第１絞り部８３と、第２絞り部８４と、オイルクーラ８５と、一対のリリーフ弁８６と、を更に備えている。 In the present embodiment, the hydraulic circuit 10 further includes a first throttle portion 83, a second throttle portion 84, an oil cooler 85, and a pair of relief valves 86.

第１絞り部８３は、第１接続油路７４を流れる油の流量を制限するように構成されている。第１絞り部８３は、第１下流油路７４２に設けられている。第２絞り部８４は、第３接続油路７６を流れる油の流量を制限するように構成されている。第２絞り部８４は、第３接続油路７６に設けられている。本実施形態では、第１絞り部８３及び第２絞り部８４のそれぞれは、オリフィスである。 The first throttle portion 83 is configured to limit the flow rate of oil flowing through the first connecting oil passage 74. The first throttle portion 83 is provided in the first downstream oil passage 742. The second throttle portion 84 is configured to limit the flow rate of oil flowing through the third connecting oil passage 76. The second throttle portion 84 is provided in the third connecting oil passage 76. In the present embodiment, each of the first throttle portion 83 and the second throttle portion 84 is an orifice.

オイルクーラ８５は、第２下流油路７５２を流れる油を冷却するように構成されている。オイルクーラ８５は、例えば、油が流動する配管を備え、当該配管の外部を流動する冷媒（例えば、冷却水、空気等）と配管内の油との間で熱交換を行うことで、油を冷却するように構成されている。 The oil cooler 85 is configured to cool the oil flowing through the second downstream oil passage 752. The oil cooler 85 is provided with, for example, a pipe through which oil flows, and exchanges heat between the refrigerant (for example, cooling water, air, etc.) flowing outside the pipe and the oil in the pipe to exchange oil. It is configured to cool.

一対のリリーフ弁８６のそれぞれは、第２下流油路７５２に過剰な油圧が生じた場合に、その油圧を逃がすための弁である。本実施形態では、一対のリリーフ弁８６は、第２下流油路７５２における、オイルクーラ８５よりも上流側に設けられている。 Each of the pair of relief valves 86 is a valve for releasing the excessive oil pressure in the second downstream oil passage 752. In the present embodiment, the pair of relief valves 86 are provided on the upstream side of the oil cooler 85 in the second downstream oil passage 752.

本実施形態では、ケースＣＳの内部に形成された油貯溜部（図示を省略）に、第１ストレーナ９１と第２ストレーナ９２とが設けられている。第１油圧ポンプ６１は、油貯溜部に貯溜された油を、第１ストレーナ９１を通して汲み上げる。また、第２油圧ポンプ６２は、油貯溜部に貯溜された油を、第２ストレーナ９２を通して汲み上げる。第１ストレーナ９１及び第２ストレーナ９２のそれぞれは、油圧ポンプによって汲み上げられた油に含まれる異物を除去する濾過器である。 In the present embodiment, the first strainer 91 and the second strainer 92 are provided in the oil storage portion (not shown) formed inside the case CS. The first hydraulic pump 61 pumps the oil stored in the oil storage unit through the first strainer 91. Further, the second hydraulic pump 62 pumps the oil stored in the oil storage unit through the second strainer 92. Each of the first strainer 91 and the second strainer 92 is a filter that removes foreign matter contained in the oil pumped by the hydraulic pump.

次に、図４〜図７を用いて、第１油圧ポンプ６１及び第２油圧ポンプ６２から車両用駆動装置１００の各部への油の流動態様について説明する。なお、図４及び図５において、第１油圧ポンプ６１からの油の供給経路を太線で示し、第２油圧ポンプ６２からの油の供給経路を細線で示す。また、図６及び図７において、油が供給されない、或いは、油圧が低い方の油路を破線で示し、油が供給される、或いは、油圧が高い方の油路を実線で示す。 Next, the mode of oil flow from the first hydraulic pump 61 and the second hydraulic pump 62 to each part of the vehicle drive device 100 will be described with reference to FIGS. 4 to 7. In FIGS. 4 and 5, the oil supply path from the first hydraulic pump 61 is shown by a thick line, and the oil supply path from the second hydraulic pump 62 is shown by a thin line. Further, in FIGS. 6 and 7, the oil passage where the oil is not supplied or the oil pressure is low is shown by a broken line, and the oil passage where the oil is supplied or the oil pressure is high is shown by a solid line.

図４に示すように、第１油圧ポンプ６１及び第２油圧ポンプ６２の双方が駆動される場合、具体的には、内燃機関ＥＧ及び第２回転電機ＭＧ２のうち、少なくとも内燃機関ＥＧの駆動力により車両が走行している場合であって、第１接続油路７４の油圧が第２接続油路７５の油圧よりも高い場合、つまり、車両が比較的低速で走行している場合には、第２油圧ポンプ６２から吐出された油が、第３接続油路７６及び第３供給油路７３を通って、動力伝達機構３及び出力用差動歯車機構４に供給される。なお、このとき、第２油圧ポンプの吐出圧が低く、第３接続油路７６及び第３供給油路７３を介して動力伝達機構３及び出力用差動歯車機構４に油が十分に供給されない場合がある。しかし、この場合、動力伝達機構３及び出力用差動歯車機構４の回転要素の回転速度は比較的低いため、それらの潤滑に必要な油の量は少ない。 As shown in FIG. 4, when both the first hydraulic pump 61 and the second hydraulic pump 62 are driven, specifically, the driving force of at least the internal combustion engine EG of the internal combustion engine EG and the second rotary electric machine MG2. When the vehicle is traveling due to the above, and the oil pressure of the first connecting oil passage 74 is higher than the oil pressure of the second connecting oil passage 75, that is, when the vehicle is traveling at a relatively low speed. The oil discharged from the second hydraulic pump 62 is supplied to the power transmission mechanism 3 and the output differential gear mechanism 4 through the third connecting oil passage 76 and the third supply oil passage 73. At this time, the discharge pressure of the second hydraulic pump is low, and oil is not sufficiently supplied to the power transmission mechanism 3 and the output differential gear mechanism 4 via the third connecting oil passage 76 and the third supply oil passage 73. In some cases. However, in this case, since the rotational speeds of the rotating elements of the power transmission mechanism 3 and the output differential gear mechanism 4 are relatively low, the amount of oil required for lubrication of them is small.

更に、第１接続油路７４の油圧が第２接続油路７５の油圧よりも高いため、第１逆止弁８１が「開」状態となり、第２逆止弁８２が「閉」状態となる。その結果、第１油圧ポンプ６１から吐出された油が、第１接続油路７４及び第１供給油路７１を通って、分配用差動歯車機構２に供給されると共に、第１接続油路７４、第４接続油路７７、第２接続油路７５、及び第２供給油路７２を通って、第１回転電機ＭＧ１及び第２回転電機ＭＧ２に供給される。 Further, since the oil pressure of the first connecting oil passage 74 is higher than that of the second connecting oil passage 75, the first check valve 81 is in the "open" state and the second check valve 82 is in the "closed" state. .. As a result, the oil discharged from the first hydraulic pump 61 is supplied to the distribution differential gear mechanism 2 through the first connecting oil passage 74 and the first supply oil passage 71, and is also supplied to the first connecting oil passage. It is supplied to the first rotary electric machine MG1 and the second rotary electric machine MG2 through the 74, the fourth connecting oil passage 77, the second connecting oil passage 75, and the second supply oil passage 72.

本実施形態では、上記の場合、第１油圧ポンプ６１から吐出された油は、第１上流油路７４１を流動した後、第１下流油路７４２と第４接続油路７７とに分岐する。第１下流油路７４２に流入した油は、第１絞り部８３を通過して第１下流油路７４２を流動した後、第１分岐油路７１１を通って分配用差動歯車機構２に到達すると共に、第２分岐油路７１２を通って第１回転電機ＭＧ１に到達する。一方、第４接続油路７７に流入した油は、第２下流油路７５２を流動し、オイルクーラ８５によって冷却される。そして、オイルクーラ８５によって冷却された油は、更に第２下流油路７５２を流動した後、第３分岐油路７２１を通って第１回転電機ＭＧ１に到達すると共に、第４分岐油路７２２を通って第２回転電機ＭＧ２に到達する。 In the present embodiment, in the above case, the oil discharged from the first hydraulic pump 61 flows through the first upstream oil passage 741 and then branches into the first downstream oil passage 742 and the fourth connecting oil passage 77. The oil flowing into the first downstream oil passage 742 passes through the first throttle portion 83, flows through the first downstream oil passage 742, and then reaches the distribution differential gear mechanism 2 through the first branch oil passage 711. At the same time, it reaches the first rotary electric machine MG1 through the second branch oil passage 712. On the other hand, the oil that has flowed into the fourth connecting oil passage 77 flows through the second downstream oil passage 752 and is cooled by the oil cooler 85. Then, the oil cooled by the oil cooler 85 further flows through the second downstream oil passage 752, then reaches the first rotary electric machine MG1 through the third branch oil passage 721, and passes through the fourth branch oil passage 722. It passes through to reach the second rotary electric machine MG2.

また、本実施形態では、上記の場合、第２油圧ポンプ６２から第３接続油路７６に吐出された油は、第２絞り部８４を通過して第３接続油路７６を流動した後、第５分岐油路７３１を通って動力伝達機構３に到達すると共に、第６分岐油路７３２を通って出力用差動歯車機構４に到達する。一方、第２油圧ポンプ６２から第２上流油路７５１に吐出された油は、「閉」状態の第２逆止弁８２によって、第２逆止弁８２よりも下流側への流動が規制される。 Further, in the present embodiment, in the above case, the oil discharged from the second hydraulic pump 62 to the third connecting oil passage 76 passes through the second throttle portion 84 and flows through the third connecting oil passage 76, and then flows. It reaches the power transmission mechanism 3 through the fifth branch oil passage 731 and reaches the output differential gear mechanism 4 through the sixth branch oil passage 732. On the other hand, the oil discharged from the second hydraulic pump 62 to the second upstream oil passage 751 is regulated by the second check valve 82 in the "closed" state to flow downstream from the second check valve 82. To.

図５に示すように、第１油圧ポンプ６１及び第２油圧ポンプ６２の双方が駆動される場合、具体的には、内燃機関ＥＧ及び第２回転電機ＭＧ２のうち、少なくとも内燃機関ＥＧの駆動力により車両が走行している場合であって、第１接続油路７４の油圧が第２接続油路７５の油圧よりも低い場合、つまり、車両が比較的高速で走行している場合には、第２油圧ポンプ６２から吐出された油が、第３接続油路７６及び第３供給油路７３を通って、動力伝達機構３及び出力用差動歯車機構４に供給される。また、第１接続油路７４の油圧が第２接続油路７５の油圧よりも低いため、第１逆止弁８１が「閉」状態となり、第２逆止弁８２が「開」状態となる。その結果、第２油圧ポンプ６２から吐出された油が、第２接続油路７５及び第２供給油路７２を通って、第１回転電機ＭＧ１及び第２回転電機ＭＧ２に供給されると共に、第２接続油路７５、第４接続油路７７、第１接続油路７４、及び第１供給油路７１を通って、分配用差動歯車機構２に供給される。 As shown in FIG. 5, when both the first hydraulic pump 61 and the second hydraulic pump 62 are driven, specifically, the driving force of at least the internal combustion engine EG of the internal combustion engine EG and the second rotary electric machine MG2. When the vehicle is traveling and the oil pressure of the first connecting oil passage 74 is lower than the oil pressure of the second connecting oil passage 75, that is, when the vehicle is traveling at a relatively high speed. The oil discharged from the second hydraulic pump 62 is supplied to the power transmission mechanism 3 and the output differential gear mechanism 4 through the third connecting oil passage 76 and the third supply oil passage 73. Further, since the flood pressure of the first connecting oil passage 74 is lower than the flood pressure of the second connecting oil passage 75, the first check valve 81 is in the "closed" state and the second check valve 82 is in the "open" state. .. As a result, the oil discharged from the second hydraulic pump 62 is supplied to the first rotary electric machine MG1 and the second rotary electric machine MG2 through the second connecting oil passage 75 and the second supply oil passage 72, and the second It is supplied to the distribution differential gear mechanism 2 through the two connecting oil passages 75, the fourth connecting oil passage 77, the first connecting oil passage 74, and the first supply oil passage 71.

本実施形態では、上記の場合、第１油圧ポンプ６１から第１上流油路７４１に吐出された油は、「閉」状態の第１逆止弁８１によって、第１逆止弁８１よりも下流側への流動が規制される。第２油圧ポンプ６２から第３接続油路７６に吐出された油は、第２絞り部８４を通過して第３接続油路７６を流動した後、第５分岐油路７３１を通って動力伝達機構３に到達すると共に、第６分岐油路７３２を通って出力用差動歯車機構４に到達する。第２油圧ポンプ６２から第２上流油路７５１に吐出された油は、第２上流油路７５１を流動した後、第２下流油路７５２と第４接続油路７７とに分岐する。第２下流油路７５２に流入した油は、オイルクーラ８５によって冷却される。そして、オイルクーラ８５によって冷却された油は、更に第２下流油路７５２を流動した後、第３分岐油路７２１を通って第１回転電機ＭＧ１に到達すると共に、第４分岐油路７２２を通って第２回転電機ＭＧ２に到達する。一方、第４接続油路７７に流入した油は、第４接続油路７７を流動すると共に、第１絞り部８３を通過して第１下流油路７４２を流動した後、第１分岐油路７１１を通って分配用差動歯車機構２に到達すると共に、第２分岐油路７１２を通って第１回転電機ＭＧ１に到達する。 In the present embodiment, in the above case, the oil discharged from the first hydraulic pump 61 to the first upstream oil passage 741 is downstream from the first check valve 81 by the first check valve 81 in the “closed” state. Flow to the side is regulated. The oil discharged from the second hydraulic pump 62 to the third connecting oil passage 76 passes through the second throttle portion 84, flows through the third connecting oil passage 76, and then transmits power through the fifth branch oil passage 731. At the same time as reaching the mechanism 3, the output differential gear mechanism 4 is reached through the sixth branch oil passage 732. The oil discharged from the second hydraulic pump 62 to the second upstream oil passage 751 flows through the second upstream oil passage 751 and then branches into the second downstream oil passage 752 and the fourth connecting oil passage 77. The oil flowing into the second downstream oil passage 752 is cooled by the oil cooler 85. Then, the oil cooled by the oil cooler 85 further flows through the second downstream oil passage 752, then reaches the first rotary electric machine MG1 through the third branch oil passage 721, and passes through the fourth branch oil passage 722. It passes through to reach the second rotary electric machine MG2. On the other hand, the oil that has flowed into the fourth connecting oil passage 77 flows through the fourth connecting oil passage 77, passes through the first throttle portion 83, flows through the first downstream oil passage 742, and then flows through the first branch oil passage. It reaches the distribution differential gear mechanism 2 through 711 and reaches the first rotary electric machine MG1 through the second branch oil passage 712.

図６に示すように、第１油圧ポンプ６１及び第２油圧ポンプ６２のうち、第１油圧ポンプ６１のみが駆動される場合、具体的には、内燃機関ＥＧが駆動中で車両が停車している場合には、実線で図示したように、第１油圧ポンプ６１から吐出された油が、第１接続油路７４及び第１供給油路７１を通って、分配用差動歯車機構２に供給されると共に、第１接続油路７４、第４接続油路７７、第２接続油路７５、及び第２供給油路７２を通って、第１回転電機ＭＧ１及び第２回転電機ＭＧ２に供給される。なお、この場合における第１油圧ポンプ６１から吐出された油の流動態様については、前述した、第１油圧ポンプ６１及び第２油圧ポンプ６２の双方が駆動される場合であって、第１接続油路７４の油圧が第２接続油路７５の油圧よりも高い場合における、第１油圧ポンプ６１から吐出された油の流動態様と同様であるため、詳細な説明は省略する。 As shown in FIG. 6, when only the first hydraulic pump 61 of the first hydraulic pump 61 and the second hydraulic pump 62 is driven, specifically, the internal combustion engine EG is being driven and the vehicle is stopped. If so, as shown by the solid line, the oil discharged from the first hydraulic pump 61 is supplied to the distribution differential gear mechanism 2 through the first connecting oil passage 74 and the first supply oil passage 71. At the same time, it is supplied to the first rotary electric machine MG1 and the second rotary electric machine MG2 through the first connecting oil passage 74, the fourth connecting oil passage 77, the second connecting oil passage 75, and the second supply oil passage 72. To. Regarding the flow mode of the oil discharged from the first hydraulic pump 61 in this case, the first connection oil is the case where both the first hydraulic pump 61 and the second hydraulic pump 62 are driven as described above. Since it is the same as the flow mode of the oil discharged from the first hydraulic pump 61 when the oil pressure of the road 74 is higher than the oil pressure of the second connecting oil passage 75, detailed description thereof will be omitted.

図７に示すように、第１油圧ポンプ６１及び第２油圧ポンプ６２のうち、第２油圧ポンプ６２のみが駆動される場合、具体的には、第２回転電機ＭＧ２の駆動力のみで車両が走行している場合又は車両が牽引されている場合には、実線で図示したように、第２油圧ポンプ６２から吐出された油が、第２接続油路７５及び第２供給油路７２を通って、第１回転電機ＭＧ１及び第２回転電機ＭＧ２に供給されると共に、第２接続油路７５、第４接続油路７７、第１接続油路７４、及び第１供給油路７１を通って、分配用差動歯車機構２に供給される。更に、第２油圧ポンプ６２から吐出された油が、第３接続油路７６及び第３供給油路７３を通って、動力伝達機構３及び出力用差動歯車機構４に供給される。なお、この場合における第２油圧ポンプ６２から吐出された油の流動態様については、第１油圧ポンプ６１及び第２油圧ポンプ６２の双方が駆動される場合であって、第１接続油路７４の油圧が第２接続油路７５の油圧よりも低い場合における、第２油圧ポンプ６２から吐出された油の流動態様と同様であるため、詳細な説明は省略する。 As shown in FIG. 7, when only the second hydraulic pump 62 of the first hydraulic pump 61 and the second hydraulic pump 62 is driven, specifically, the vehicle is driven only by the driving force of the second rotary electric machine MG2. When traveling or when the vehicle is towed, the oil discharged from the second hydraulic pump 62 passes through the second connecting oil passage 75 and the second supply oil passage 72 as shown by the solid line. Then, it is supplied to the first rotary electric machine MG1 and the second rotary electric machine MG2, and also passes through the second connecting oil passage 75, the fourth connecting oil passage 77, the first connecting oil passage 74, and the first supply oil passage 71. , Is supplied to the differential gear mechanism 2 for distribution. Further, the oil discharged from the second hydraulic pump 62 is supplied to the power transmission mechanism 3 and the output differential gear mechanism 4 through the third connecting oil passage 76 and the third supply oil passage 73. Regarding the flow mode of the oil discharged from the second hydraulic pump 62 in this case, both the first hydraulic pump 61 and the second hydraulic pump 62 are driven, and the first connecting oil passage 74 Since the flow mode is the same as that of the oil discharged from the second hydraulic pump 62 when the oil pressure is lower than the oil pressure of the second connecting oil passage 75, detailed description thereof will be omitted.

以上のように、第１回転電機ＭＧ１、第２回転電機ＭＧ２、分配用差動歯車機構２、動力伝達機構３、及び出力用差動歯車機構４のうち、第１油圧ポンプ６１の油の供給対象となり得るのは、第１回転電機ＭＧ１、第２回転電機ＭＧ２、分配用差動歯車機構２である。一方、第１回転電機ＭＧ１、第２回転電機ＭＧ２、分配用差動歯車機構２、動力伝達機構３、及び出力用差動歯車機構４のうち、第２油圧ポンプ６２の油の供給対象となり得るのは、それらの全てである。そのため、第２油圧ポンプ６２の最大吐出量は、第１油圧ポンプ６１の最大吐出量よりも大きい。ここで、第１油圧ポンプ６１の最大吐出量は、使用範囲として想定される範囲内での第１ポンプロータ６１１の最高回転速度において、第１油圧ポンプ６１から吐出される油の単位時間あたりの吐出量である。同様に、第２油圧ポンプ６２の最大吐出量は、使用範囲として想定される範囲内での第２ポンプロータ６２１の最高回転速度において、第２油圧ポンプ６２から吐出される油の単位時間あたりの吐出量である。したがって、仮に第１ポンプロータ６１１の最高回転速度と第２ポンプロータ６２１の最高回転速度とが同じである場合には、第２油圧ポンプ６２の体格は第１油圧ポンプ６１の体格よりも大きく設計されると良い。また、仮に第１油圧ポンプ６１の体格と第２油圧ポンプ６２の体格とが同じである場合には、第２ポンプロータ６２１の最高回転速度が第１ポンプロータ６１１の最高回転速度よりも高くなるように設計されると良い。 As described above, the oil supply of the first hydraulic pump 61 of the first rotary electric machine MG1, the second rotary electric machine MG2, the distribution differential gear mechanism 2, the power transmission mechanism 3, and the output differential gear mechanism 4 Targets are the first rotary electric machine MG1, the second rotary electric machine MG2, and the distribution differential gear mechanism 2. On the other hand, of the first rotary electric machine MG1, the second rotary electric machine MG2, the distribution differential gear mechanism 2, the power transmission mechanism 3, and the output differential gear mechanism 4, the oil of the second hydraulic pump 62 can be supplied. Is all of them. Therefore, the maximum discharge amount of the second hydraulic pump 62 is larger than the maximum discharge amount of the first hydraulic pump 61. Here, the maximum discharge amount of the first hydraulic pump 61 is per unit time of the oil discharged from the first hydraulic pump 61 at the maximum rotation speed of the first pump rotor 611 within the range assumed as the range of use. It is the discharge amount. Similarly, the maximum discharge amount of the second hydraulic pump 62 is the maximum rotation speed of the second pump rotor 621 within the range assumed as the range of use, and the maximum discharge amount of the oil discharged from the second hydraulic pump 62 per unit time. It is the discharge amount. Therefore, if the maximum rotation speed of the first pump rotor 611 and the maximum rotation speed of the second pump rotor 621 are the same, the physique of the second hydraulic pump 62 is designed to be larger than the physique of the first hydraulic pump 61. It would be nice to be done. If the physique of the first hydraulic pump 61 and the physique of the second hydraulic pump 62 are the same, the maximum rotation speed of the second pump rotor 621 becomes higher than the maximum rotation speed of the first pump rotor 611. It should be designed as.

〔その他の実施形態〕
（１）上記の実施形態では、一対の第１軸受Ｂ１が、分配用差動歯車機構２に対して軸方向Ｌの両外側において、筒部材２１を径方向Ｒの内側から支持するように配置され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、例えば、一対の第１軸受Ｂ１が、分配用差動歯車機構２に対して径方向Ｒの外側であって、径方向Ｒに沿う径方向視で、分配用差動歯車機構２と重複する位置に配置されていても良い。この場合、第１供給油路７１が、筒部材２１に対して径方向Ｒの内側であって、軸方向Ｌにおける一対の第１軸受Ｂ１の間に油を供給するように形成されていなくても良い。例えば、第１供給油路７１が、軸方向第１側Ｌ１の第１軸受Ｂ１に対して軸方向第１側Ｌ１から分配用差動歯車機構２に対して油を供給するように形成されていても良い。 [Other Embodiments]
(1) In the above embodiment, the pair of first bearings B1 are arranged so as to support the tubular member 21 from the inside of the radial direction R on both outer sides of the axial direction L with respect to the distribution differential gear mechanism 2. The configuration described above was described as an example. However, without being limited to such a configuration, for example, the pair of first bearings B1 is outside the radial direction R with respect to the distribution differential gear mechanism 2 and is viewed in the radial direction along the radial direction R. Therefore, it may be arranged at a position overlapping with the distribution differential gear mechanism 2. In this case, the first supply oil passage 71 is not formed so as to supply oil between the pair of first bearings B1 in the axial direction L, which is inside the tubular member 21 in the radial direction R. Is also good. For example, the first supply oil passage 71 is formed so as to supply oil to the distribution differential gear mechanism 2 from the axial first side L1 to the first bearing B1 on the axial first side L1. You may.

（２）上記の実施形態では、第１絞り部８３が第１下流油路７４２に設けられ、第２絞り部８４が第３接続油路７６に設けられ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、第１絞り部８３及び第２絞り部８４のいずれか一方のみが設けられていても良い。或いは、第１絞り部８３及び第２絞り部８４の双方が設けられていなくても良い。 (2) In the above embodiment, the configuration in which the first throttle portion 83 is provided in the first downstream oil passage 742 and the second throttle portion 84 is provided in the third connecting oil passage 76 has been described as an example. However, without being limited to such a configuration, only one of the first throttle portion 83 and the second throttle portion 84 may be provided. Alternatively, both the first throttle portion 83 and the second throttle portion 84 may not be provided.

（３）上記の実施形態では、第１油圧ポンプ６１の第１ポンプロータ６１１が、ポンプ軸６１２を介して入力部材１の第１軸部１２に連結され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、第１油圧ポンプ６１が入力部材１の回転に連動する構成であれば良い。言い換えると、第１ポンプロータ６１１が入力部材１と同期回転するように、つまり、第１ポンプロータ６１１の回転速度と入力部材１の回転速度との比が一定となる状態でこれらが回転するように構成されていれば良い。したがって、例えば、第１ポンプロータ６１１が入力部材１の第２軸部１３及びフランジ部１１のいずれか一方に連結されていても良い。 (3) In the above embodiment, the configuration in which the first pump rotor 611 of the first hydraulic pump 61 is connected to the first shaft portion 12 of the input member 1 via the pump shaft 612 has been described as an example. However, the configuration is not limited to such a configuration, and the first hydraulic pump 61 may be configured to be interlocked with the rotation of the input member 1. In other words, the first pump rotor 611 rotates synchronously with the input member 1, that is, they rotate in a state where the ratio of the rotation speed of the first pump rotor 611 to the rotation speed of the input member 1 is constant. It suffices if it is configured in. Therefore, for example, the first pump rotor 611 may be connected to either the second shaft portion 13 or the flange portion 11 of the input member 1.

（４）上記の実施形態では、第２油圧ポンプ６２の第２ポンプロータ６２１が、差動入力ギヤ４１と噛み合うポンプ駆動ギヤ６２２と一体的に回転するように連結され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、第２油圧ポンプ６２が出力用差動歯車機構４の回転に連動する構成であれば良い。言い換えると、第２ポンプロータ６２１が出力用差動歯車機構４の差動入力ギヤ４１と同期回転するように、つまり、第２ポンプロータ６２１の回転速度と差動入力ギヤ４１の回転速度との比が一定となる状態でこれらが回転するように構成されていれば良い。したがって、例えば、第２ポンプロータ６２１と、差動入力ギヤ４１、カウンタ軸３３、或いは第１伝達ギヤ２２とが、ギヤ機構やチェーン等を介して同期回転するように連結されていても良い。より具体的には、例えば、ポンプ駆動ギヤ６２２が、動力伝達機構３の第１カウンタギヤ３１、第２カウンタギヤ３２、又は第１伝達ギヤ２２に噛み合う構成としても良い。或いは、第２ポンプロータ６２１が、動力伝達機構３のカウンタ軸３３と一体的に回転するように連結されていても良い。 (4) In the above embodiment, a configuration in which the second pump rotor 621 of the second hydraulic pump 62 is connected so as to rotate integrally with the pump drive gear 622 that meshes with the differential input gear 41 has been described as an example. .. However, the configuration is not limited to such a configuration, and the second hydraulic pump 62 may be configured to be interlocked with the rotation of the output differential gear mechanism 4. In other words, the second pump rotor 621 rotates synchronously with the differential input gear 41 of the output differential gear mechanism 4, that is, the rotation speed of the second pump rotor 621 and the rotation speed of the differential input gear 41. It suffices if they are configured to rotate in a state where the ratio is constant. Therefore, for example, the second pump rotor 621 and the differential input gear 41, the counter shaft 33, or the first transmission gear 22 may be connected so as to rotate synchronously via a gear mechanism, a chain, or the like. More specifically, for example, the pump drive gear 622 may be configured to mesh with the first counter gear 31, the second counter gear 32, or the first transmission gear 22 of the power transmission mechanism 3. Alternatively, the second pump rotor 621 may be connected so as to rotate integrally with the counter shaft 33 of the power transmission mechanism 3.

（５）なお、上述した各実施形態で開示された構成は、矛盾が生じない限り、他の実施形態で開示された構成と組み合わせて適用することも可能である。その他の構成に関しても、本明細書において開示された実施形態は全ての点で単なる例示に過ぎない。したがって、本開示の趣旨を逸脱しない範囲内で、適宜、種々の改変を行うことが可能である。 (5) The configurations disclosed in each of the above-described embodiments can be applied in combination with the configurations disclosed in other embodiments as long as there is no contradiction. With respect to other configurations, the embodiments disclosed herein are merely exemplary in all respects. Therefore, various modifications can be made as appropriate without departing from the gist of the present disclosure.

〔上記実施形態の概要〕
以下では、上記において説明した車両用駆動装置（１００）の概要について説明する。 [Outline of the above-described embodiment]
The outline of the vehicle drive device (100) described above will be described below.

車両用駆動装置（１００）は、
内燃機関（ＥＧ）に駆動連結される入力部材（１）と、
それぞれ車輪（Ｗ）に駆動連結される一対の出力部材（５）と、
入力される回転を一対の前記出力部材（５）に分配する出力用差動歯車機構（４）と、
第１回転電機（ＭＧ１）及び第２回転電機（ＭＧ２）と、
前記出力用差動歯車機構（４）及び前記第２回転電機（ＭＧ２）に駆動連結された動力伝達機構（３）と、
前記入力部材（１）の回転を、前記動力伝達機構（３）と前記第１回転電機（ＭＧ１）とに分配する分配用差動歯車機構（２）と、
前記入力部材（１）の回転に連動する第１油圧ポンプ（６１）と、
前記出力用差動歯車機構（４）の回転に連動する第２油圧ポンプ（６２）と、
前記分配用差動歯車機構（２）に油を供給する第１供給油路（７１）と、
前記第１回転電機（ＭＧ１）及び前記第２回転電機（ＭＧ２）のそれぞれに油を供給する第２供給油路（７２）と、
前記動力伝達機構（３）及び前記出力用差動歯車機構（４）のそれぞれに油を供給する第３供給油路（７３）と、
前記第１油圧ポンプ（６１）と前記第１供給油路（７１）とを接続する第１接続油路（７４）と、
前記第２油圧ポンプ（６２）と前記第２供給油路（７２）とを接続する第２接続油路（７５）と、
前記第２油圧ポンプ（６２）と前記第３供給油路（７３）とを接続する第３接続油路（７６）と、
前記第１接続油路（７４）と前記第２接続油路（７５）とを接続する第４接続油路（７７）と、を備え、
前記第１接続油路（７４）における前記第４接続油路（７７）との接続部分よりも上流側（７４１）に、油の逆流を規制する第１逆止弁（８１）が設けられ、
前記第２接続油路（７５）における前記第４接続油路（７７）との接続部分よりも上流側（７５１）に、油の逆流を規制する第２逆止弁（８２）が設けられ、
前記第２油圧ポンプ（６２）の最大吐出量は、前記第１油圧ポンプ（６１）の最大吐出量よりも大きい。 The vehicle drive device (100)
An input member (1) that is driven and connected to an internal combustion engine (EG),
A pair of output members (5) that are driven and connected to the wheels (W), respectively.
An output differential gear mechanism (4) that distributes the input rotation to the pair of output members (5), and
With the 1st rotary electric machine (MG1) and the 2nd rotary electric machine (MG2),
A power transmission mechanism (3) driven and connected to the output differential gear mechanism (4) and the second rotary electric machine (MG2),
A distribution differential gear mechanism (2) that distributes the rotation of the input member (1) to the power transmission mechanism (3) and the first rotary electric machine (MG1).
The first hydraulic pump (61) interlocked with the rotation of the input member (1) and
The second hydraulic pump (62) interlocked with the rotation of the output differential gear mechanism (4) and
A first supply oil passage (71) for supplying oil to the distribution differential gear mechanism (2), and
A second supply oil passage (72) for supplying oil to each of the first rotary electric machine (MG1) and the second rotary electric machine (MG2), and
A third supply oil passage (73) for supplying oil to each of the power transmission mechanism (3) and the output differential gear mechanism (4), and
A first connecting oil passage (74) connecting the first hydraulic pump (61) and the first supply oil passage (71),
A second connecting oil passage (75) connecting the second hydraulic pump (62) and the second supply oil passage (72), and
A third connecting oil passage (76) connecting the second hydraulic pump (62) and the third supply oil passage (73),
A fourth connecting oil passage (77) connecting the first connecting oil passage (74) and the second connecting oil passage (75) is provided.
A first check valve (81) for regulating the backflow of oil is provided on the upstream side (741) of the first connecting oil passage (74) with respect to the connecting portion with the fourth connecting oil passage (77).
A second check valve (82) for regulating the backflow of oil is provided on the upstream side (751) of the second connecting oil passage (75) with respect to the connecting portion with the fourth connecting oil passage (77).
The maximum discharge amount of the second hydraulic pump (62) is larger than the maximum discharge amount of the first hydraulic pump (61).

この構成によれば、第１油圧ポンプ（６１）及び第２油圧ポンプ（６２）の双方が駆動される場合（内燃機関（ＥＧ）及び第２回転電機（ＭＧ２）のうち、少なくとも内燃機関（ＥＧ）の駆動力により車両が走行している場合）であって、第１接続油路（７４）の油圧が第２接続油路（７５）の油圧よりも低い場合（車両が比較的高速で走行している場合）には、第２油圧ポンプ（６２）から吐出された油が、第２接続油路（７５）及び第２供給油路（７２）を通って、第１回転電機（ＭＧ１）及び第２回転電機（ＭＧ２）に供給されると共に、第２接続油路（７５）、第４接続油路（７７）、第１接続油路（７４）、及び第１供給油路（７１）を通って、分配用差動歯車機構（２）に供給される。更に、第２油圧ポンプ（６２）から吐出された油が、第３接続油路（７６）及び第３供給油路（７３）を通って、動力伝達機構（３）及び出力用差動歯車機構（４）に供給される。この場合、第１回転電機（ＭＧ１）、第２回転電機（ＭＧ２）、分配用差動歯車機構（２）、動力伝達機構（３）、及び出力用差動歯車機構（４）の全てに油が十分に供給される。
一方、第１油圧ポンプ（６１）及び第２油圧ポンプ（６２）の双方が駆動される場合であって、第１接続油路（７４）の油圧が第２接続油路（７５）の油圧よりも高い場合（車両が比較的低速で走行している場合）、或いは第１油圧ポンプ（６１）及び第２油圧ポンプ（６２）のうち、第１油圧ポンプ（６１）のみが駆動される場合（内燃機関（ＥＧ）が駆動中で車両が停車している場合）には、第１油圧ポンプ（６１）から吐出された油が、第１接続油路（７４）及び第１供給油路（７１）を通って、分配用差動歯車機構（２）に供給されると共に、第１接続油路（７４）、第４接続油路（７７）、第２接続油路（７５）、及び第２供給油路（７２）を通って、第１回転電機（ＭＧ１）及び第２回転電機（ＭＧ２）に供給される。この場合、第１回転電機（ＭＧ１）、第２回転電機（ＭＧ２）、及び分配用差動歯車機構（２）には油が十分に供給される。一方、第２油圧ポンプ（６２）の吐出圧が低い又は吐出圧がないために、第３接続油路（７６）及び第３供給油路（７３）を介して動力伝達機構（３）及び出力用差動歯車機構（４）に油が十分に供給されない場合がある。しかし、この場合、動力伝達機構（３）及び出力用差動歯車機構（４）の回転要素の回転速度は比較的低い又はゼロであるため、それらの潤滑に必要な油の量は少ない。
また、第１油圧ポンプ（６１）及び第２油圧ポンプ（６２）のうち、第２油圧ポンプ（６２）のみが駆動される場合（第２回転電機（ＭＧ２）の駆動力のみで車両が走行している場合、又は、車両が牽引されている場合）には、第２油圧ポンプ（６２）から吐出された油が、第２接続油路（７５）及び第２供給油路（７２）を通って、第１回転電機（ＭＧ１）及び第２回転電機（ＭＧ２）に供給されると共に、第２接続油路（７５）、第４接続油路（７７）、第１接続油路（７４）、及び第１供給油路（７１）を通って、分配用差動歯車機構（２）に供給される。更に、第２油圧ポンプ（６２）から吐出された油が、第３接続油路（７６）及び第３供給油路（７３）を通って、動力伝達機構（３）及び出力用差動歯車機構（４）に供給される。この場合、第１回転電機（ＭＧ１）、第２回転電機（ＭＧ２）、分配用差動歯車機構（２）、動力伝達機構（３）、及び出力用差動歯車機構（４）の全てに油が十分に供給される。
以上のように、本構成によれば、車両の走行状態によらず、潤滑が必要な部位を適切に潤滑することができる車両用駆動装置（１００）を実現できる。 According to this configuration, at least the internal combustion engine (EG) of the case where both the first hydraulic pump (61) and the second hydraulic pump (62) are driven (internal combustion engine (EG) and second rotary electric machine (MG2)). ), And the oil pressure of the first connecting oil passage (74) is lower than the oil pressure of the second connecting oil passage (75) (the vehicle is traveling at a relatively high speed). In this case, the oil discharged from the second hydraulic pump (62) passes through the second connecting oil passage (75) and the second supply oil passage (72) to the first rotary electric machine (MG1). 2nd connecting oil passage (75), 4th connecting oil passage (77), 1st connecting oil passage (74), and 1st supply oil passage (71) while being supplied to the 2nd rotary electric machine (MG2). Through, it is supplied to the differential gear mechanism (2) for distribution. Further, the oil discharged from the second hydraulic pump (62) passes through the third connecting oil passage (76) and the third supply oil passage (73), and passes through the power transmission mechanism (3) and the output differential gear mechanism. It is supplied to (4). In this case, oil is applied to all of the first rotary electric machine (MG1), the second rotary electric machine (MG2), the distribution differential gear mechanism (2), the power transmission mechanism (3), and the output differential gear mechanism (4). Is fully supplied.
On the other hand, when both the first hydraulic pump (61) and the second hydraulic pump (62) are driven, the hydraulic pressure of the first connecting oil passage (74) is higher than the hydraulic pressure of the second connecting oil passage (75). Also high (when the vehicle is traveling at a relatively low speed), or when only the first hydraulic pump (61) of the first hydraulic pump (61) and the second hydraulic pump (62) is driven (when it is driven (61). When the internal combustion engine (EG) is being driven and the vehicle is stopped), the oil discharged from the first hydraulic pump (61) is discharged from the first connecting oil passage (74) and the first supply oil passage (71). ) Is supplied to the distribution differential gear mechanism (2), and the first connecting oil passage (74), the fourth connecting oil passage (77), the second connecting oil passage (75), and the second connecting oil passage (75). It is supplied to the first rotary electric machine (MG1) and the second rotary electric machine (MG2) through the supply oil passage (72). In this case, oil is sufficiently supplied to the first rotary electric machine (MG1), the second rotary electric machine (MG2), and the distribution differential gear mechanism (2). On the other hand, because the discharge pressure of the second hydraulic pump (62) is low or there is no discharge pressure, the power transmission mechanism (3) and the output via the third connecting oil passage (76) and the third supply oil passage (73). Oil may not be sufficiently supplied to the differential gear mechanism (4). However, in this case, since the rotation speeds of the rotating elements of the power transmission mechanism (3) and the output differential gear mechanism (4) are relatively low or zero, the amount of oil required for lubrication of them is small.
Further, when only the second hydraulic pump (62) of the first hydraulic pump (61) and the second hydraulic pump (62) is driven (the vehicle runs only by the driving force of the second rotary electric machine (MG2)). When the vehicle is being towed, the oil discharged from the second hydraulic pump (62) passes through the second connecting oil passage (75) and the second supply oil passage (72). Then, it is supplied to the first rotary electric machine (MG1) and the second rotary electric machine (MG2), and the second connection oil passage (75), the fourth connection oil passage (77), the first connection oil passage (74), And, it is supplied to the distribution differential gear mechanism (2) through the first supply oil passage (71). Further, the oil discharged from the second hydraulic pump (62) passes through the third connecting oil passage (76) and the third supply oil passage (73), and passes through the power transmission mechanism (3) and the output differential gear mechanism. It is supplied to (4). In this case, oil is applied to all of the first rotary electric machine (MG1), the second rotary electric machine (MG2), the distribution differential gear mechanism (2), the power transmission mechanism (3), and the output differential gear mechanism (4). Is fully supplied.
As described above, according to this configuration, it is possible to realize a vehicle drive device (100) capable of appropriately lubricating a portion requiring lubrication regardless of the traveling state of the vehicle.

ここで、軸方向（Ｌ）に沿って延在する筒状に形成された筒部材（２１）と、
前記筒部材（２１）を回転可能に支持する一対の軸受（Ｂ１）と、を更に備え、
前記分配用差動歯車機構（２）は、前記筒部材（２１）に対して径方向（Ｒ）の内側であって、前記径方向（Ｒ）に沿う径方向視で前記筒部材（２１）と重複する位置に配置され、
一対の前記軸受（Ｂ１）は、前記分配用差動歯車機構（２）に対して前記軸方向（Ｌ）の両外側において、前記筒部材（２１）を前記径方向（Ｒ）の内側から支持するように配置され、
前記第１供給油路（７１）は、前記筒部材（２１）に対して前記径方向（Ｒ）の内側であって、前記軸方向（Ｌ）における一対の前記軸受（Ｂ１）の間に油を供給するように形成されていると好適である。 Here, the tubular member (21) formed in a tubular shape extending along the axial direction (L) and
A pair of bearings (B1) that rotatably support the tubular member (21) are further provided.
The distribution differential gear mechanism (2) is inside the tubular member (21) in the radial direction (R), and the tubular member (21) is viewed in the radial direction along the radial direction (R). Placed in a position that overlaps with
The pair of bearings (B1) support the tubular member (21) from the inside of the radial direction (R) on both outer sides of the axial direction (L) with respect to the distribution differential gear mechanism (2). Arranged to do
The first supply oil passage (71) is inside the tubular member (21) in the radial direction (R), and oil is provided between the pair of bearings (B1) in the axial direction (L). It is preferable that it is formed so as to supply.

この構成では、分配用差動歯車機構（２）の径方向（Ｒ）の外側を囲むように筒部材（２１）が配置され、分配用差動歯車機構（２）の軸方向（Ｌ）の両側に軸受が配置されている。そのため、分配用差動歯車機構（２）に油を供給し難い構造となっている。
しかし、本構成によれば、第１供給油路（７１）により、筒部材（２１）に対して径方向（Ｒ）の内側であって、軸方向（Ｌ）における一対の軸受の間に油が供給される。これにより、分配用差動歯車機構（２）を適切に潤滑することができる。 In this configuration, the tubular member (21) is arranged so as to surround the outside of the distribution differential gear mechanism (2) in the radial direction (R), and is in the axial direction (L) of the distribution differential gear mechanism (2). Bearings are arranged on both sides. Therefore, it is difficult to supply oil to the distribution differential gear mechanism (2).
However, according to this configuration, due to the first supply oil passage (71), oil is inside the tubular member (21) in the radial direction (R) and between the pair of bearings in the axial direction (L). Is supplied. As a result, the distribution differential gear mechanism (2) can be appropriately lubricated.

また、前記第１接続油路（７４）における、前記第４接続油路（７７）との接続部分よりも下流側（７４２）に、前記第１接続油路（７４）を流れる油の流量を制限する絞り部（８３）が設けられていると好適である。 Further, in the first connecting oil passage (74), the flow rate of oil flowing through the first connecting oil passage (74) is applied to the downstream side (742) of the connecting portion with the fourth connecting oil passage (77). It is preferable that a limiting portion (83) is provided.

この構成によれば、第１油圧ポンプ（６１）及び第２油圧ポンプ（６２）の一方から分配用差動歯車機構（２）に供給される油の量を適切に制御することが容易となる。 According to this configuration, it becomes easy to appropriately control the amount of oil supplied from one of the first hydraulic pump (61) and the second hydraulic pump (62) to the distribution differential gear mechanism (2). ..

また、前記第１油圧ポンプ（６１）の回転部材である第１ポンプロータ（６１１）は、前記入力部材（１）と一体的に回転するように前記入力部材（１）に連結され、
前記第２油圧ポンプ（６２）の回転部材である第２ポンプロータ（６２１）は、前記出力用差動歯車機構（４）の入力要素である差動入力部材（４１）に従動して回転するように前記差動入力部材（４１）に連結されていると好適である。 Further, the first pump rotor (611), which is a rotating member of the first hydraulic pump (61), is connected to the input member (1) so as to rotate integrally with the input member (1).
The second pump rotor (621), which is a rotating member of the second hydraulic pump (62), rotates in accordance with the differential input member (41), which is an input element of the output differential gear mechanism (4). It is preferable that the differential input member (41) is connected to the differential input member (41) as described above.

この構成によれば、第１油圧ポンプ（６１）の第１ポンプロータ（６１１）が、入力部材（１）と一体的に回転するように入力部材（１）に連結されている。これにより、第１油圧ポンプ（６１）を、適切に入力部材（１）の回転に連動させることができる。
また、本構成によれば、第２油圧ポンプ（６２）の第２ポンプロータ（６２１）が、出力用差動歯車機構（４）の差動入力部材（４１）に従動して回転するように差動入力部材（４１）に連結されている。これにより、第２油圧ポンプ（６２）を、適切に出力用差動歯車機構（４）の回転に連動させることができる。 According to this configuration, the first pump rotor (611) of the first hydraulic pump (61) is connected to the input member (1) so as to rotate integrally with the input member (1). As a result, the first hydraulic pump (61) can be appropriately linked to the rotation of the input member (1).
Further, according to this configuration, the second pump rotor (621) of the second hydraulic pump (62) rotates in accordance with the differential input member (41) of the output differential gear mechanism (4). It is connected to the differential input member (41). As a result, the second hydraulic pump (62) can be appropriately linked to the rotation of the output differential gear mechanism (4).

本開示に係る技術は、第１油圧ポンプ及び第２油圧ポンプを備えた、スプリット型のハイブリッド車両用の駆動装置に利用することができる。 The technology according to the present disclosure can be used in a drive device for a split type hybrid vehicle equipped with a first hydraulic pump and a second hydraulic pump.

１００ ：車両用駆動装置
１ ：入力部材
２ ：分配用差動歯車機構
３ ：動力伝達機構
４ ：出力用差動歯車機構
５ ：出力部材
６１ ：第１油圧ポンプ
６２ ：第２油圧ポンプ
７１ ：第１供給油路
７２ ：第２供給油路
７３ ：第３供給油路
７４ ：第１接続油路
７５ ：第２接続油路
７６ ：第３接続油路
７７ ：第４接続油路
８１ ：第１逆止弁
８２ ：第２逆止弁
ＭＧ１ ：第１回転電機
ＭＧ２ ：第２回転電機
ＥＧ ：内燃機関
Ｗ ：車輪 100: Vehicle drive device 1: Input member 2: Distributing differential gear mechanism 3: Power transmission mechanism 4: Output differential gear mechanism 5: Output member 61: First hydraulic pump 62: Second hydraulic pump 71: No. 1 supply oil passage 72: 2nd supply oil passage 73: 3rd supply oil passage 74: 1st connection oil passage 75: 2nd connection oil passage 76: 3rd connection oil passage 77: 4th connection oil passage 81: 1st Check valve 82: 2nd check valve MG1: 1st rotary electric machine MG2: 2nd rotary electric machine EG: Internal engine W: Wheels

Claims (4)

内燃機関に駆動連結される入力部材と、
それぞれ車輪に駆動連結される一対の出力部材と、
入力される回転を一対の前記出力部材に分配する出力用差動歯車機構と、
第１回転電機及び第２回転電機と、
前記出力用差動歯車機構及び前記第２回転電機に駆動連結された動力伝達機構と、
前記入力部材の回転を、前記動力伝達機構と前記第１回転電機とに分配する分配用差動歯車機構と、
前記入力部材の回転に連動する第１油圧ポンプと、
前記出力用差動歯車機構の回転に連動する第２油圧ポンプと、
前記分配用差動歯車機構に油を供給する第１供給油路と、
前記第１回転電機及び前記第２回転電機のそれぞれに油を供給する第２供給油路と、
前記動力伝達機構及び前記出力用差動歯車機構のそれぞれに油を供給する第３供給油路と、
前記第１油圧ポンプと前記第１供給油路とを接続する第１接続油路と、
前記第２油圧ポンプと前記第２供給油路とを接続する第２接続油路と、
前記第２油圧ポンプと前記第３供給油路とを接続する第３接続油路と、
前記第１接続油路と前記第２接続油路とを接続する第４接続油路と、を備え、
前記第１接続油路における前記第４接続油路との接続部分よりも上流側に、油の逆流を規制する第１逆止弁が設けられ、
前記第２接続油路における前記第４接続油路との接続部分よりも上流側に、油の逆流を規制する第２逆止弁が設けられ、
前記第２油圧ポンプの最大吐出量は、前記第１油圧ポンプの最大吐出量よりも大きい、車両用駆動装置。 Input members that are driven and connected to the internal combustion engine
A pair of output members that are driven and connected to the wheels, respectively.
An output differential gear mechanism that distributes the input rotation to the pair of output members,
With the 1st rotary electric machine and the 2nd rotary electric machine,
The output differential gear mechanism, the power transmission mechanism driven and connected to the second rotary electric machine, and
A distribution differential gear mechanism that distributes the rotation of the input member to the power transmission mechanism and the first rotary electric machine.
The first hydraulic pump linked to the rotation of the input member and
A second hydraulic pump that is interlocked with the rotation of the output differential gear mechanism,
A first supply oil passage for supplying oil to the distribution differential gear mechanism, and
A second supply oil passage for supplying oil to each of the first rotary electric machine and the second rotary electric machine, and
A third supply oil passage for supplying oil to each of the power transmission mechanism and the output differential gear mechanism, and
A first connecting oil passage connecting the first hydraulic pump and the first supply oil passage,
A second connecting oil passage connecting the second hydraulic pump and the second supply oil passage,
A third connecting oil passage connecting the second hydraulic pump and the third supply oil passage,
A fourth connecting oil passage connecting the first connecting oil passage and the second connecting oil passage is provided.
A first check valve that regulates the backflow of oil is provided on the upstream side of the first connecting oil passage with the connection portion with the fourth connecting oil passage.
A second check valve that regulates the backflow of oil is provided on the upstream side of the second connecting oil passage with the connection portion with the fourth connecting oil passage.
A vehicle drive device in which the maximum discharge amount of the second hydraulic pump is larger than the maximum discharge amount of the first hydraulic pump. 軸方向に沿って延在する筒状に形成された筒部材と、
前記筒部材を回転可能に支持する一対の軸受と、を更に備え、
前記分配用差動歯車機構は、前記筒部材に対して径方向の内側であって、前記径方向に沿う径方向視で前記筒部材と重複する位置に配置され、
一対の前記軸受は、前記分配用差動歯車機構に対して前記軸方向の両外側において、前記筒部材を前記径方向の内側から支持するように配置され、
前記第１供給油路は、前記筒部材に対して前記径方向の内側であって、前記軸方向における一対の前記軸受の間に油を供給するように形成されている、請求項１に記載の車両用駆動装置。 A tubular member formed in a tubular shape extending along the axial direction,
A pair of bearings that rotatably support the tubular member is further provided.
The distribution differential gear mechanism is arranged at a position inside the tubular member in the radial direction and overlapping the tubular member in a radial direction along the radial direction.
The pair of bearings are arranged so as to support the tubular member from the inside in the radial direction on both outer sides in the axial direction with respect to the differential gear mechanism for distribution.
The first supply oil passage according to claim 1, wherein the first supply oil passage is formed inside the tubular member in the radial direction and supplies oil between the pair of bearings in the axial direction. Vehicle drive unit. 前記第１接続油路における、前記第４接続油路との接続部分よりも下流側に、前記第１接続油路を流れる油の流量を制限する絞り部が設けられている、請求項１又は２に記載の車両用駆動装置。 Claim 1 or claim 1, wherein a throttle portion for limiting the flow rate of oil flowing through the first connecting oil passage is provided on the downstream side of the connecting portion of the first connecting oil passage with the fourth connecting oil passage. 2. The vehicle drive device according to 2. 前記第１油圧ポンプの回転部材である第１ポンプロータは、前記入力部材と一体的に回転するように前記入力部材に連結され、
前記第２油圧ポンプの回転部材である第２ポンプロータは、前記出力用差動歯車機構の入力要素である差動入力部材に従動して回転するように前記差動入力部材に連結されている、請求項１から３のいずれか一項に記載の車両用駆動装置。 The first pump rotor, which is a rotating member of the first hydraulic pump, is connected to the input member so as to rotate integrally with the input member.
The second pump rotor, which is a rotating member of the second hydraulic pump, is connected to the differential input member so as to rotate in accordance with the differential input member which is an input element of the output differential gear mechanism. , The vehicle drive device according to any one of claims 1 to 3.
JP2019219547A 2019-12-04 2019-12-04 Vehicular driving device Pending JP2021088267A (en)

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