Hybrid drive system
Abstract
The hybrid driving device includes an input member, a rotating electric machine, a power distribution device for distributing and transmitting a torque transmitted to the input member to the rotating electric machine and a distribution output member, and outputting a torque transmitted to the distribution output member a possible output gear; and an output bearing for rotatably supporting the distribution output member from the radially inner side. In the power split device, the entirety of the power split device is disposed radially inside the distribution output member and overlapping with the distribution output member at the same position in the axial direction, and the ring gear of the power split device is disposed on the inner circumferential surface of the distribution output member. is provided integrally with the distribution output member. The output gear is provided integrally with the distribution output member on an outer peripheral surface of the distribution output member. The output bearing and the output gear are arranged to overlap at the same position in the axial direction.

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Expires 10 February 2031.
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17 claims: 2 independent, 15 dependent
- 1엔진에 구동연결되는 입력부재와, 회전전기기기와, 상기 입력부재에 전달되는 토크를 상기 회전전기기기와 분배출력부재에 분배하여 전달하는 동력분배장치와, 상기 분배출력부재에 전달되는 토크를 차륜 측에 출력가능하게 설치된 출력기어를 구비하는 하이브리드 구동장치에 있어서, 상기 분배출력부재의 반경방향 내측에 배치되고 상기 분배출력부재를 반경방향 내측으로부터 회전가능하게 지지하는 출력베어링을 구비하고, 상기 동력분배장치는, 그 전체가 상기 분배출력부재의 반경방향 내측에 상기 분배출력부재와 축방향에 있어서 동일 위치에서 중첩하여 배치됨과 함께, 상기 동력분배장치의 링기어가 상기 분배출력부재의 내주면에 상기 분배출력부재와 일체적으로 구비되고, 상기 출력기어는, 상기 분배출력부재의 외주면에 상기 분배출력부재와 일체적으로 구비되며, 상기 출력베어링과 상기 출력기어는, 축방향에 있어서 동일 위치에서 중첩하여 배치되어 있고, 상기 회전전기기기는, 제1 회전전기기기로서 구비되고, 상기 하이브리드 구동장치는, 상기 제1 회전전기기기와는 상이한 축 상에 배치되는 제2 회전전기기기를 더욱 포함하고, 상기 출력기어는, 상기 제2 회전전기기기에 구동연결되어 있고, 축방향을 따라서 상기 엔진, 상기 동력분배장치, 상기 제1 회전전기기기의 순으로 배치되고, 상기 출력기어는, 카운터기어기구를 통하여 상기 차륜 측에 구동연결되고, 상기 제2 회전전기기기는, 상기 카운터기어기구를 통하여 상기 출력기어에 구동연결됨과 함께, 상기 분배출력부재와 반경방향으로 중복되지 않고, 상기 카운터기어기구의 회전축과 반경방향으로 중복되고, 상기 제1 회전전기기기와 축방향으로 중복되도록 배치되고, 상기 출력베어링은, 상기 동력분배장치에 대하여 축방향에 있어서의 상기 엔진 측에 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 2청구항 1에 있어서, 상기 회전전기기기의 로터를 회전가능하게 지지하는 로터베어링과, 차동입력기어를 구비하고, 상기 차동입력기어에 전달되는 토크를 복수의 상기 차륜에 분배하여 전달하는 차동기어장치와, 상기 출력기어에 치합(齒合)하는 제1 기어와, 상기 차동입력기어에 치합하는 제2 기어를 구비하고, 상기 제1 기어와 상기 제2 기어가 일체 회전하도록 형성된 카운터 기어기구 를 더욱 포함하고, 상기 제2 기어와 상기 로터베어링이 축방향에 있어서 동일 위치에서 중첩하여 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 3청구항 1 또는 청구항 2에 있어서, 상기 출력베어링은, 제1 출력베어링으로서 구비되고, 상기 하이브리드 구동장치는, 상기 회전전기기기의 로터를 회전가능하게 지지하는 로터베어링과, 상기 제1 출력베어링과는 축방향의 상이한 위치에서 상기 분배출력부재를 지지하도록 배치된 제2 출력베어링 을 더욱 포함하고, 상기 제2 출력베어링과 상기 로터베어링이 축방향에 있어서 동일 위치에서 중첩하여 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 4청구항 1에 있어서, 상기 출력베어링을 제1 출력베어링으로 함과 함께, 상기 제1 출력베어링과는 축방향의 상이한 위치에서 상기 분배출력부재를 지지하도록 배치된 제2 출력베어링과, 상기 제1 회전전기기기의 로터와 일체 회전하도록 구동연결된 통형상의 로터축과, 상기 로터축을 회전가능하게 지지하는 로터베어링과, 상기 입력부재를 회전가능하게 지지하는 입력베어링 을 더욱 구비하고, 상기 제2 출력베어링은, 상기 분배출력부재를 반경방향 내측으로부터 회전가능하게 지지함과 함께, 축방향에 있어서의 상기 동력분배장치와 상기 제1 회전전기기기 사이에 배치되고, 상기 입력부재와 상기 동력분배장치의 연결부가, 상기 동력분배장치에 대하여 축방향에 있어서의 상기 엔진 측에 배치되고, 상기 입력부재는, 상기 연결부로부터 축방향으로, 상기 동력분배장치에 대하여 상기 제1 회전전기기기의 위치까지 뻗어나와 있는 연재(延在)부를 더욱 구비하고, 상기 연재부는, 상기 로터축의 반경방향 내측에 배치되고, 상기 로터베어링은, 축방향에 있어서의 상기 동력분배장치와 상기 제1 회전전기기기 사이에 배치되고, 상기 입력베어링은, 축방향에 있어서의 상기 동력분배장치와 상기 제1 회전전기기기 사이로서, 상기 로터축의 내주면과 상기 연재부의 외주면 사이에 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 5청구항 4에 있어서, 상기 연재부는, 상기 연결부에 대하여 상기 엔진 측인 상기 입력부재의 부분보다 작은 직경인 것 을 특징으로 하는 하이브리드 구동장치.
- 6청구항 4에 있어서, 오일펌프와, 상기 오일펌프를 구동하는 펌프구동축을 더욱 구비하고, 상기 오일펌프는, 상기 제1 회전전기기기에 대하여 축방향에 있어서의 상기 엔진 측과는 반대측에 배치되고, 상기 펌프구동축은, 상기 로터축의 반경방향 내측에, 상기 오일펌프로부터 상기 연재부까지 축방향으로 뻗어나와서, 상기 연재부와 일체 회전하도록 연결되고, 상기 펌프구동축 및 상기 입력부재는, 그 내경부에 있어서, 상기 오일펌프로부터 축방향으로, 상기 동력분배장치와 축방향으로 중복하는 위치까지 뻗는 축 내부유로를 가지고 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 7청구항 6에 있어서, 차동입력기어를 구비하고, 상기 차동입력기어에 전달되는 토크를 복수의 상기 차륜에 분배하여 전달하는 차동기어장치와, 상기 출력기어에 치합하는 제1 기어와, 상기 차동입력기어에 치합하는 제2 기어를 구비하며, 상기 제1 기어와 상기 제2 기어가 일체 회전하도록 형성된 카운터 기어기구 를 더욱 포함하고, 상기 제2 기어와 상기 로터베어링이 축방향에 있어서 동일 위치에서 중첩하여 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 8청구항 7에 있어서, 상기 제1 기어의 축방향 길이는, 상기 출력기어의 축방향 길이보다 길게 설정되고, 상기 제1 기어의 부분 중 상기 출력기어에 대하여 치합하고 있지 않은 부분인 비(非)치합부가, 축방향으로 상기 입력부재가 상기 엔진에 연결되는 측에 위치하도록, 상기 제1 기어와 상기 출력기어의 치합위치가 설정되어 있으며, 상기 제1 기어는, 상기 제2 회전전기기기에 구동연결되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 9청구항 6에 있어서, 상기 제2 출력베어링과 상기 로터베어링이 축방향에 있어서 동일 위치에서 중첩하여 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 10청구항 9에 있어서, 상기 입력부재, 상기 제1 회전전기기기, 상기 제2 회전전기기기, 상기 동력분배장치, 상기 분배출력부재, 및 상기 출력기어가 수용되는 케이스 를 더욱 포함하고, 상기 케이스는, 반경방향으로 뻗는 지지벽과, 상기 지지벽과 일체적으로 형성되고 축방향으로 뻗는 원통형의 통형상부를 구비하고, 상기 통형상부의 외주면에 접하여 상기 제2 출력베어링이 배치됨과 함께, 상기 통형상부의 내주면에 접하여 상기 로터베어링이 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 11청구항 1에 있어서, 기어부와 소정의 지지점을 중심으로 요동가능하게 구성된 걸쇠부를 구비하고, 상기 기어부에 상기 걸쇠부가 계합한 상태로 상기 분배출력부재의 회전을 강제로 정지시키는 락기구 를 더욱 포함하고, 상기 기어부가, 상기 분배출력부재의 외주면에서 상기 출력기어와는 축방향의 상이한 위치에 상기 분배출력부재와 일체적으로 구비되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 12청구항 1에 있어서, 상기 입력부재, 제1 회전전기, 제2 회전전기, 상기 동력분배장치, 상기 분배출력부재, 및 상기 출력기어를 수용하는 케이스를 구비하고, 상기 분배출력부재를 회전가능하게 지지하는 상기 출력베어링이, 상기 케이스의 반경방향으로 뻗는 지지벽과 일체적으로 형성되고 축방향으로 뻗는 원통형상의 통형상부의 외주면과, 상기 분배출력부재의 내주면에 접하여 배치되는 것 을 특징으로 하는 하이브리드 구동장치.
- 13청구항 1에 있어서, 상기 출력베어링을 제1 출력베어링으로 함과 함께, 상기 제1 출력베어링과는 축방향의 상이한 위치에서 상기 분배출력부재를 지지하도록 배치된 제2 출력베어링을 구비하고, 상기 2개의 출력지지베어링인 상기 제1 출력베어링 및 상기 제2 출력베어링은, 상기 링기어에 대하여 축방향 양측으로 나뉘어서 배치됨과 함께, 상기 분배출력부재의 내주면과 상기 케이스 사이에 배치되고, 상기 분배출력부재를 반경방향 내측으로부터 상기 케이스에 대하여 회전가능하게 지지하는 것 을 특징으로 하는 하이브리드 구동장치.
- 14청구항 1에 있어서, 상기 입력부재를 회전가능하게 지지하는 입력베어링을 구비하고, 상기 입력베어링은 케이스에 마련된 통형상부의 내주면과 상기 입력부재 외주면 사이에 마련되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 15청구항 14에 있어서, 상기 입력베어링과, 출력베어링이 축방향에서 중첩하는 위치에 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 16청구항 1 또는 청구항 2에 있어서, 상기 제1 회전전기기기의 로터와 일체 회전하도록 구동연결된 통형상의 로터축과, 상기 로터축을 회전가능하게 지지하는 로터베어링과, 상기 입력부재를 회전가능하게 지지하는 입력베어링 을 더욱 구비하고, 상기 입력부재는, 상기 입력부재와 상기 동력분배장치의 연결부로부터 축방향으로, 상기 동력분배장치에 대하여 상기 제1 회전전기기기의 위치까지 뻗어나와 있는 연재(延在)부를 더욱 구비하고, 상기 연재부는, 상기 로터축의 반경방향 내측에 배치되고, 상기 로터베어링은, 축방향에 있어서의 상기 동력분배장치와 상기 제1 회전전기기기 사이에 배치되고, 상기 입력베어링은, 축방향에 있어서의 상기 동력분배장치와 상기 제1 회전전기기기 사이로서, 상기 로터축의 내주면과 상기 연재부의 외주면 사이에 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
- 17엔진에 구동연결되는 입력부재와, 회전전기기기와, 상기 입력부재에 전달되는 토크를 상기 회전전기기기와 분배출력부재에 분배하여 전달하는 동력분배장치와, 상기 분배출력부재에 전달되는 토크를 차륜 측에 출력가능하게 설치된 출력기어를 구비하는 하이브리드 구동장치에 있어서, 상기 분배출력부재의 반경방향 내측에 배치되고 상기 분배출력부재를 반경방향 내측으로부터 회전가능하게 지지하는 출력베어링을 구비하고, 상기 동력분배장치는, 그 전체가 상기 분배출력부재의 반경방향 내측에 상기 분배출력부재와 축방향에 있어서 동일 위치에서 중첩하여 배치됨과 함께, 상기 동력분배장치의 링기어가 상기 분배출력부재의 내주면에 상기 분배출력부재와 일체적으로 구비되고, 상기 출력기어는, 상기 분배출력부재의 외주면에 상기 분배출력부재와 일체적으로 구비되며, 상기 출력베어링과 상기 출력기어는, 축방향에 있어서 동일 위치에서 중첩하여 배치되어 있고, 상기 회전전기기기는, 제1 회전전기기기로서 구비되고, 상기 하이브리드 구동장치는, 상기 제1 회전전기기기와는 상이한 축 상에 배치되는 제2 회전전기기기를 더욱 포함하고, 상기 출력기어는, 상기 제2 회전전기기기에 구동연결되어 있고, 축방향을 따라서 상기 엔진, 상기 동력분배장치, 상기 제1 회전전기기기의 순으로 배치되고, 상기 출력기어는, 카운터기어기구를 통하여 상기 차륜 측에 구동연결되고, 상기 제2 회전전기기기는, 상기 카운터기어기구를 통하여 상기 출력기어에 구동연결됨과 함께, 상기 분배출력부재와 반경방향으로 중복되지 않고, 상기 카운터기어기구의 회전축과 반경방향으로 중복되고, 상기 제1 회전전기기기와 축방향으로 중복되도록 배치되고, 상기 출력베어링은, 상기 동력분배장치에 대하여 축방향에 있어서의 상기 엔진 측에 배치되어 있고, 차동입력기어를 가지고 상기 차동입력기어에 전달되는 토크를 복수의 상기 차륜에 분배하여 전달하는 차동기어장치를 더욱 구비하고, 상기 카운터기어기구는, 상기 출력기어에 맞물리는 제1 기어와, 상기 차동입력기어에 맞물리는 제2 기어를 가지고, 상기 제1 기어와 상기 제2 기어가 일체 회전하도록 형성되고, 상기 제2 기어는, 상기 제1 기어에 대하여 축방향에 있어서의 상기 제1 회전전기기기 측에 배치되고, 상기 제2 기어는, 상기 분배출력부재와 축방향으로 중복되도록 배치되어 있는 것 을 특징으로 하는 하이브리드 구동장치.
Independent claims17
58 paragraphs, as filed
Hybrid drive system
The present invention relates to an input member driven and connected to an engine, a rotating electric machine, and a power distribution device (that is, a power transmission device) for distributing and transmitting torque transmitted to the input member to the rotating electric machine and a distribution output member. ) and a hybrid driving device having an output gear installed to output the torque transmitted to the distribution output member to the wheel side.
As the hybrid drive device as described above, for example, the device described in Japanese Patent Laid-Open No. 2000-217205 has already been known. In the apparatus described in Japanese Patent Laid-Open No. 2000-217205, as shown in FIGS. 2 and 4 of Japanese Patent Laid-Open No. 2000-217205, a power distribution device (planetary gear unit 13) )), the ring gear R acting as an output rotation element is formed integrally with the distribution output member on the inner circumferential surface of the distribution output member formed in a cylindrical shape, and the distribution output member includes the input member (output shaft 12). It is connected to the sleeve-shaped member (output shaft 14) formed so as to enclose it through a flange-shaped connecting member extending in the radial direction. The sleeve-shaped member is disposed on the engine side and radially inward in the axial direction with respect to the distribution output member, and at an end of the sleeve-shaped member on the engine side in the axial direction, a counter drive gear 15 acting as an output gear is provided. It is formed on the outer peripheral surface of the sleeve-shaped member.
The rotor or distribution output member of the rotating electric machine (generator motor 16), which is a rotating member inside the case 10, needs to be rotatably supported with respect to a non-rotating member such as the case, so that they are each a rotor. It is supported by bearings and output bearings. Here, in the hybrid device described in Japanese Patent Laid-Open No. 2000-217205, an output bearing is disposed between the case and the sleeve-like member, and the rotor bearing is disposed between the case and the rotor shaft of the rotating electric machine. The distribution output member is connected to the rotor shaft of the rotating electric machine through the ring gear integrally formed with the distribution output member and other rotating elements of the power distribution device, and is connected to the sleeve-like member through the connecting member. Thereby, the distribution output member is rotatably supported by the case through the sleeve-shaped member and the output bearing as well as the rotor shaft and the rotor bearing of the rotating electric machine. At this time, since the output bearing is disposed in contact with the outer circumferential surface of the sleeve-like member having a relatively small diameter, it is possible to use the output bearing having a relatively small diameter. For this reason, it becomes possible to reduce the cost of the output bearing, and it becomes possible to reduce the overall manufacturing cost of the hybrid drive device.
However, in the hybrid drive device described in Japanese Patent Laid-Open No. 2000-217205, the power distribution device, the output bearing, and the output gear are arranged side by side at different positions in the axial direction at a predetermined interval. With this arrangement, the power split device and the output gear occupy a wide range of space in the axial direction. As a result, there is a problem in that the axial dimension of the entire hybrid drive device becomes large. Further, since the output bearing is disposed in contact with the outer circumferential surface of the sleeve-shaped member, the axial position of the output gear integrally formed on the outer circumferential surface of the same sleeve-like member is restricted by the output bearing. Thereby, the degree of freedom with respect to the axial position of the output gear is lowered, so that the degree of freedom also with respect to the axial position of the respective components disposed on the downstream side of the power transmission path with respect to the output gear is reduced. Accordingly, even from this point of view, with this configuration, the axial dimension of the entire hybrid drive device tends to increase.
<p>Accordingly, it is desired to realize a hybrid drive device capable of shortening the axial dimension of the entire device.</p>
<p>An aspect of the present invention includes an input member driven and connected to an engine, a rotating electric machine, a power distribution device for distributing and transmitting torque transmitted to the input member to the rotating electric machine and a distribution output member, and the distribution output member It relates to a hybrid driving device having an output gear installed to output torque transmitted to a wheel side. The hybrid driving device includes an output bearing disposed radially inside the distribution output member and rotatably supporting the distribution output member from the radial inside. In the power split device, the entirety of the power split device is disposed radially inside the distribution output member and overlapping with the distribution output member at the same position in the axial direction, and the ring gear of the power split device is disposed on the inner circumferential surface of the distribution output member. is provided integrally with the distribution output member. The output gear is provided integrally with the distribution output member on an outer circumferential surface of the distribution output member. The output bearing and the output gear are disposed to overlap at the same position in the axial direction.</p><p>However, as used herein, the term "drive connection" refers to a state in which two rotating elements are connected to transmit a driving force, and a state in which the two rotating elements are connected to rotate integrally, or the two rotating elements are one or It is used as a concept including a state in which the driving force can be transmitted through two or more electric (power transmission) members.</p><p>In addition, "rotating electric machine" is used as a concept including both a motor (electric motor), a generator (generator), and a motor-generator that performs the functions of both the motor and the generator, if necessary.</p><p>Also herein, the term "overlapping" in a predetermined direction with respect to two members means that each of the two members has at least a portion that is co-located with each other with respect to the arrangement in the predetermined direction. it means.</p><p>According to the above configuration, since the entire power distribution device is disposed to overlap the distribution output member at the same position in the axial direction inside the radial direction of the distribution output member, the power distribution device is disposed in the space occupied by the distribution output member in the axial direction. can be placed. In addition, since the output gear is integrally installed on the outer circumferential surface of the distribution output member, even the output gear may be disposed in the space occupied by the distribution output member in the axial direction. Accordingly, by making the power distribution device and the output gear fit in the space occupied by the distribution output member, the axial length of the space occupied by the distribution output member, the power distribution device and the output gear can be shortened.</p><p>In addition, since the output bearing rotatably supporting the distribution output member is disposed radially inside the distribution output member, the output gear is integrated with the outer circumferential surface of the distribution output member without being constrained by the axial position by the output bearing. can be provided with That is, the degree of freedom regarding the axial position of the output gear can be increased. Therefore, in order to maintain the high precision of the axial alignment of the distribution output member, even when the output bearing is arranged to support the axial end of the distribution output member, the output gear is overlapped with the output bearing at the same position in the axial direction. This allows for disposition of the output gear closer to the axial end of the distributing output member. Accordingly, each of the components disposed on the downstream side of the power transmission path with respect to the output gear can also be disposed closer to the axial end of the distribution output member. As a result, it becomes easy to arrange each of the components arranged on the downstream side of the output gear at an appropriate position in the axial direction.</p><p>Accordingly, it is possible to effectively shorten the axial length of the space occupied by the distribution output member, the power distribution device, the output gear, and each component disposed on the downstream side of the output gear. Therefore, a hybrid drive capable of shortening the overall axial dimension of the device can be provided.</p><p>The hybrid driving device according to an aspect of the present invention includes a rotor bearing for rotatably supporting a rotor of the rotating electric machine, and a differential input gear, and distributes and transmits torque transmitted to the differential input gear to a plurality of wheels. a differential gear device comprising: a differential gear device, a first gear meshing with the output gear, and a second gear meshing with the differential input gear, wherein the first gear and the second gear rotate integrally A counter gear mechanism may be further included. The second gear and the rotor bearing may be disposed to overlap at the same position in the axial direction.</p><p>In the hybrid driving device, the output bearing may be provided as a first output bearing. The hybrid driving device may include a rotor bearing for rotatably supporting the rotor of the rotating electric machine, and a second axial position configured to support the distribution output member at an axial position different from an axial position at which the first output bearing is disposed. It may further include an output bearing. The second output bearing and the rotor bearing may be overlapped at the same position in the axial direction.</p><p>In the hybrid driving device, the rotary electric machine may be provided as a first rotary electric machine. The hybrid driving device may further include a second rotary electric machine disposed on a different axis from the axis on which the first rotary electric machine is disposed. The output gear may be driven and connected to the second rotating electric machine.</p><p>Here, the hybrid drive device includes a rotor bearing for rotatably supporting the rotor of the first rotating electric machine, and a differential input gear, and a differential for distributing and transmitting torque transmitted to the differential input gear to a plurality of wheels. It may further include a gear device, a counter gear mechanism comprising a first gear meshing with the output gear and a second gear meshing with the differential input gear, wherein the first gear and the electric second gear rotate integrally. have. The second gear and the rotor bearing may be disposed to overlap at the same position in the axial direction.</p><p>According to this configuration, the torque (engine torque) of the input member transmitted to the distribution output member can be transmitted to the wheel side through the counter gear mechanism and the differential gear device.</p><p>Further, in this configuration, the second gear of the counter gear mechanism and the rotor bearing are arranged to overlap at the same position in the axial direction. Usually, the first gear and the second gear of the counter gear mechanism are arranged in axial direction at a relatively narrow interval in many cases. When the rotor bearing and the second gear of the counter gear mechanism are arranged to overlap in the axial direction with the structure as described above, the rotor of the first rotating electric machine rotatably supported by the rotor bearing and the rotor bearing may be disposed adjacent to the side of the distribution output member on which the output gear is formed in the axial direction. Therefore, since the first rotating electric machine can be arranged close to the side of the distribution output member, the axial dimension of the entire device can be shortened even considering the arrangement of the first rotating electric machine.</p><p>In the hybrid driving device, the axial length of the first gear may be set to be longer than the axial length of the output gear, and among the parts of the first gear, a non-mechanical part that does not mesh with the output gear. ) A mutual meshing position between the first gear and the output gear may be set so that the meshing part is located on the side where the input member is connected to the engine in the axial direction. Furthermore, the first gear may be driven and connected to the second rotating electric machine.</p><p>In the hybrid driving device having a configuration in which a second rotary electric machine is driven and connected to an output gear installed so as to output a torque transmitted to a distribution output member on a wheel side, the output gear is connected to the first gear of the counter gear mechanism and a gear (hereinafter referred to as a "second rotating electric machine output gear") installed to output torque from the second rotating electric machine may be configured to mesh with both sides. In this configuration, typically, since the second rotating electric machine outputs a large assist torque for driving the vehicle in many cases, the maximum value of the torque that can be transmitted from the output gear to the first gear and the When comparing the maximum value of the torque that can be transmitted from the output gear of the two-rotating electric machine to the first gear, the latter is often set to a larger value. As a result, the axial length of the second rotary electric machine output gear is set longer than the axial length of the output gear in many cases. In this case, in order to efficiently transmit the torque output by the second rotary electric machine to the first gear without wasting while suppressing an increase in the axial dimension of the entire device, the axial length of the first gear is equal to the second It is set equal to the axial length of the output gear of the rotating electric machine, and therefore the axial length of the first gear is set longer than the axial length of the output gear.</p><p>According to this configuration, on the premise of setting the lengths in the axial direction of the first gear and the output gear as described above, the open space that meets the engine side in the axial direction and is formed at a predetermined position from the input member in the radial direction can be efficiently used. And it is possible to arrange a non-engaging portion that is a surplus with respect to the output gear among the portions of the first gear in the open space. Accordingly, while both the torque transmitted to the distribution output member and the torque from the second rotary electric machine are efficiently transmitted to the counter gear mechanism and the wheel side, the overall axial dimension of the apparatus can be shortened.</p><p>In the hybrid driving device, the output bearing may be provided as a first output bearing. The hybrid driving device includes a rotor bearing rotatably supporting the rotor of the first rotating electric machine, and a second distributing output member disposed to support the distribution output member at an axial position different from a position at which the first output bearing is disposed. Output bearings may be included. The second output bearing and the rotor bearing may be overlapped at the same position in the axial direction.</p><p>According to this configuration, the second output bearing rotatably supporting the distribution output member and the rotor bearing rotatably supporting the rotor of the first rotating electric machine are arranged to overlap at the same position in the axial direction. Therefore, compared with the case where they are arranged at different positions in the axial direction, the axial length of the space occupied by the second output bearing and the rotor bearing can be shortened by at least an amount in which they are arranged overlapping each other. . In addition, as a result, the distribution output member rotatably supported by the second output bearing and the rotor of the first rotating electric machine rotatably supported by the rotor bearing may be disposed adjacent to each other in the axial direction. have. Accordingly, the length of the space occupied by the first rotating electric machine and the distribution output member in the axial direction can be greatly shortened. As a result, when even the arrangement of the first rotating electric machine is considered, the axial dimension of the entire device can be shortened.</p><p>The above-described hybrid driving device may further include a case accommodating the input member, the first rotary electric machine, the second rotary electric machine, the power distribution device, the distribution output member, and the output gear. . The case has a support wall extending in a radial direction, and a cylindrical cylindrical portion integrally formed with the support wall and extending in the axial direction, the second output bearing is disposed so as to be in contact with an outer circumferential surface of the cylindrical portion, The rotor bearing may be disposed so as to be in contact with the inner circumferential surface of the cylindrical portion.</p><p>According to this configuration, by disposing the rotor bearing and the second output bearing in contact with the inner and outer peripheral surfaces of the cylindrical portion integrally formed on the support wall of the case, the rotor bearing and the second output bearing are axially aligned. An overlapping arrangement can be easily realized. In addition, by commonizing a portion for arranging the rotor bearing and the second output bearing in the case, the structure of the case can be simplified, and thus the manufacturing cost can be reduced.</p><p>The hybrid driving device further includes a gear portion and a pawl portion configured to be oscillating about a predetermined support point, and forcing rotation of the distribution output member in a state in which the lock portion is engaged with the gear portion. It may include a lock mechanism to stop it. The gear unit may be an outer peripheral surface of the distribution output member and may be integrally provided with the distribution output member at a position in an axial direction different from that of the output gear.</p><p>According to this configuration, by engaging the clasp portion with the gear portion of the lock mechanism, rotation of the distribution output member is forcibly stopped, thereby preventing the wheel from rotating. Accordingly, the hybrid driving device may include a parking lock function for maintaining the vehicle in a completely stopped state.</p><p>At this time, by the configuration in which the gear unit is provided at a position different from the output gear in the axial direction, the gear unit may be integrally provided on the outer peripheral surface of the distribution output member without interfering with the output gear. As a result, it is possible to configure the lock mechanism while suppressing an increase in the axial length by accommodating the gear portion in the space occupied by the power distribution device, the output gear, and the distribution output member.</p>
<p>The features, advantages, and technical and industrial significance of the present invention will be described in detail with reference to the accompanying drawings in the Detailed Description of Embodiments of the Present Invention, wherein like reference numerals refer to like elements.</p>
1 is a schematic diagram of a hybrid driving device according to an embodiment of the present invention. 2 is a cross-sectional view in a plane perpendicular to the axial direction of the hybrid driving device according to the embodiment of the present invention. 3 is an axially developed cross-sectional view of a hybrid driving device according to an embodiment of the present invention. 4 is a cross-sectional view of a main part of a hybrid driving device according to an embodiment of the present invention.
An embodiment of a hybrid driving device according to the present invention will be described with reference to the accompanying drawings. This hybrid drive device 1 is a drive device for a hybrid vehicle capable of running using both the engine E and the rotary electric machines MG1 and MG2 as drive sources. The hybrid drive device 1 according to the present embodiment is arranged in the width direction of the vehicle adjacent to the engine E that is lateral to the vehicle, and the engine in the axial direction of the output shaft Eo of the engine E. It is a hybrid drive device for a front engine front drive (FF) vehicle of a configuration connected to (E).
This hybrid drive device 1 is configured as a hybrid drive device of a so-called two-motor split type. The hybrid driving device 1 includes an input shaft I connected to the engine E, a first rotating electric machine MG1 having a first rotor Ro1, and an engine transmitted to the input shaft I A power distribution device (PT, hereinafter referred to as a 'power transmission device') for distributing and transmitting the torque of (E) to the first rotating electric machine MG1 and the distribution output member 21, and the distribution output member 21 ) and an output gear 22 installed so as to output the torque transmitted to the wheel (W) side. In addition, a second rotary electric machine MG2 is driven and connected to the distribution output member 21 and the output gear 22 through a counter gear mechanism C. In this type of configuration, the hybrid driving device 1 according to the present embodiment includes the power transmission device PT, the arrangement configuration of the distribution output member 21 and the output gear 22, and the output gear ( 22) and an arrangement configuration of an output bearing (61) for rotatably supporting the distribution output member (21).
That is, as shown in FIGS. 3 and 4 , the entire power transmission device PT is disposed to overlap the distribution output member 21 and the distribution output member 21 in the radial direction of the entirety in the axial direction. do. The ring gear R of the power transmission device PT is provided integrally with the distribution output member 21 on the inner circumferential surface 21b of the distribution output member 21, and the output gear 22 includes: It is provided integrally with the distribution output member 21 on the outer peripheral surface 21a of the distribution output member 21 . Furthermore, the hybrid driving device 1 has an output bearing 61 disposed radially inside the distribution output member 21 and rotatably supporting the distribution output member 21 from the radial inside. . The output bearing 61 and the output gear 22 are disposed to overlap in the axial direction. By the combination of these characteristic arrangements, the hybrid drive device 1 capable of shortening the overall axial dimension of the device is realized. Hereinafter, the hybrid driving device 1 according to the present embodiment will be described in more detail. However, in this embodiment, the term "overlapping" of the two members in a predetermined direction means that each of the two members has at least a part of a portion that is at the same position with respect to the arrangement in the predetermined direction. it means.
<b>1. </b><b>hybrid</b><b> Overall configuration of the drive unit</b>
First, the overall configuration of the hybrid driving device 1 according to the present embodiment will be described. 1 and 3 , the input shaft (I) is driven and connected to the engine (E). Here, the engine E is an internal combustion engine driven by combustion of fuel, and for example, various known engines such as a gasoline engine or a diesel engine may be used. In this embodiment, the input shaft (I) is connected to an engine output shaft (Eo) such as a crankshaft of the engine (E) through a damper (D). However, the input shaft (I) may be directly connected to the engine output shaft (Eo) through the damper (D) and the clutch or the like, or without the intervention of the damper (D) or the clutch. In this embodiment, the input shaft I acts as an "input member" of the present invention.
The first rotary electric machine MG1 includes a first stator St1 fixed to the case 2 and a first rotor Ro1 rotatably supported inside the first stator St1 in the radial direction. do. The first rotor Ro1 is driven and connected to the sun gear S to rotate integrally with the sun gear S of the power transmission device PT. The first rotating electric machine MG1 has a function as a motor (ie, electric motor) that generates power (ie, driving force) by receiving power, and a generator that generates power by receiving power (ie, driving force) (i.e., a generator). Accordingly, the first rotating electric machine MG1 is electrically connected to a power storage device (not shown). In this embodiment, a battery is used as the power storage device. However, a capacitor or the like may be used as the power storage device. In the present embodiment, the first rotating electric machine MG1 generates electricity by the torque of the input shaft I (that is, the engine E) mainly input through the power transmission device PT, and uses the battery. It functions as a generator for charging or supplying electric power for driving the second rotating electric machine MG2. However, the first rotating electric machine MG1 can also function as a motor that outputs a driving force while running at a high speed of the vehicle or when the engine E is started.
The second rotary electric machine MG2 includes a second stator St2 fixed to the case 2 and a second rotor Ro2 rotatably supported inside the second stator St2 in the radial direction. be prepared The second rotor Ro2 is driven and connected to the second rotary electric machine output gear 37 so as to rotate together with the second rotary electric machine output gear 37 . The second rotary electric machine MG2 has a function as a motor (ie, electric motor) that generates power (ie, driving force) by receiving power, and a generator that generates power by receiving power (ie, driving force) (i.e., generator). Accordingly, the second rotary electric machine MG2 is also electrically connected to a battery as a power storage device (not shown). In the present embodiment, the second rotary electric machine MG2 mainly functions as a motor that assists the driving force for driving the vehicle. However, when the vehicle is decelerating or the like, the second rotary electric machine MG2 may function as a generator that regenerates the vehicle's inertial force as electric energy.
In the present embodiment, the power transmission device PT is a single-pinion type planetary gear mechanism disposed on the same axis as the input shaft I. That is, the power transmission device PT includes a carrier CA supporting a plurality of pinion gears, and three rotating members, a sun gear S and a ring gear R respectively meshing with the pinion gears. . The sun gear S is driven and connected to the first rotor shaft 31 of the first rotor Ro1 of the first rotating electric machine MG1 to rotate integrally with the first rotor shaft 31 . The carrier CA is driven and connected to the input shaft I to rotate integrally with the input shaft I. The ring gear R is integrally formed with the distribution output member 21 . The three rotating members (rotating elements) of the power transmission device PT are, in the order of rotation speed, 1) the sun gear S (ie, the first rotation member), 2) the carrier CA (ie, the second rotating member), and 3) the ring gear R (that is, the third rotating member). However, the 'order of rotation speed' refers to any one of the order from high speed to low speed or from low speed to high speed, and depends on the rotational state of the planetary gear mechanism constituting the power distribution device (PT). Therefore, it can be either, but in any case, the order of the rotating members is not changed.
The power transmission device PT distributes and transmits the torque from the engine E transmitted to the input shaft I to the first rotating electric machine MG1 and the distribution output member 21 . In the power transmission device PT, the input shaft I is driven and connected to a carrier CA that is intermediate in the order of rotation speed. In addition, the first rotor Ro1 of the first rotating electric machine MG1 is driven and connected to the sun gear S which becomes one side in the order of the rotation speed, and the other side becomes the other side in the order of the rotation speed The ring gear R is integrally formed with the distribution output member 21 . In the hybrid drive device 1 according to the present embodiment , the torque in the positive direction from the engine E through the input shaft I to the carrier CA intermediate in the order of rotation speed (that is, in the positive direction) torque) is transmitted, and the torque in the negative direction output from the first rotating electric machine MG1 through the first rotor shaft 31 to the sun gear S which becomes one side in the order of rotation speed ( That is, torque in the negative direction) is transmitted. The negative direction torque of the first rotating electric machine MG1 serves to receive a reaction force of the torque of the engine E, and as a result, the power transmission device PT is transmitted to the carrier CA through the input shaft I A portion of the torque transmitted to the engine E is distributed to the first rotating electric machine MG1, and the torque attenuated with respect to the torque of the engine E is distributed to the distribution output member 21 through the ring gear R forward to
Here, in the present embodiment, the distribution output member 21 is a substantially cylindrical member provided to surround the radially outer side of the power transmission device PT. The ring gear R of the power transmission device PT is integrally formed with the distribution output member 21 on the inner peripheral surface 21b of the distribution output member 21 . In addition, the output gear 22 is integrally formed with the distribution output member 21 on the outer peripheral surface 21a of the distribution output member 21 . That is, in the present embodiment, the ring gear R and the output gear 22 of the power transmission device PT are integrally formed on the inner peripheral surface and the outer peripheral surface of the distribution output member 21 , respectively. As a result, the torque transmitted to the distribution output member 21 through the ring gear R of the power transmission device PT can be output to the wheel W side through the output gear 22 .
The hybrid drive device 1 according to the present embodiment also includes a counter gear mechanism C. As shown in FIG. The counter gear mechanism C reverses the rotational direction of the output gear 22 and also transmits the torque output from the output gear 22 to the wheel W side. Such a counter gear mechanism C is comprised so that it may have the counter shaft 41, the 1st gear 42, and the 2nd gear 43. The first gear 42 meshes with the output gear 22 . Also, the first gear 42 meshes with the second rotary electric machine output gear 37 at a position different from that of the output gear 22 in the circumferential direction. The second gear 43 meshes with a differential input gear 46 of an output differential gear device DF to be described later. Accordingly, the counter gear mechanism C reverses the rotation directions of the output gear 22 and the second rotary electric machine output gear 37, and the torque transmitted to the output gear 22 and the second rotation The torque of the electric machine MG2 is transmitted to the differential gear device DF for output.
Further, the hybrid drive device 1 according to the present embodiment also includes a differential gear device DF for output. The differential gear device for output (DF) includes a differential input gear (46), and distributes and transmits the torque transmitted to the differential input gear (46) to the plurality of wheels (W). In this embodiment, the differential gear device DF for output is a differential gear mechanism provided with a plurality of bevel gears meshing with each other. The differential gear device DF distributes the torque transmitted to the differential input gear 46 through the second gear 43 of the counter gear mechanism C, and the left and right two wheels W through the axle O. ) transmits the divided torque to each. However, at this time, the output differential gear device DF reverses the rotation direction of the second gear 43 and transmits the reversed rotation to the wheel W. As a result, the hybrid drive device 1 rotates the wheel W in the same direction as the rotational direction of the input shaft I (that is, the engine E), and the input shaft I (that is, the engine) during forward travel. (E)) and the second rotating electric machine MG2 and the torque in the same direction are transmitted to the wheel W, thereby driving the vehicle.
However, in the hybrid driving device 1 according to the present embodiment, as shown in FIG. 2 , the first shaft ( A1), a second shaft A2 on which the second rotary electric machine MG2 is disposed, a third shaft A3 on which the output differential gear device DF is disposed, and a fourth shaft on which the counter gear mechanism C is disposed. It has a four-axis configuration, each having an axis A4 separately. The first axis A1, the second axis A2, the third axis A3, and the fourth axis A4 are all arranged parallel to each other. In addition, in the illustrated embodiment, the first axis A1 , the second axis A2 , and the third axis A3 are arranged such that a line connecting these axes forms a triangle when viewed in the axial direction. and the fourth axis A4 is disposed inside the triangle when viewed in the axial direction.
<b>2. </b><b>hybrid</b><b> Mechanical configuration of each part of the drive unit</b>
Next, the mechanical configuration of each part of the hybrid drive device 1 according to the present embodiment will be described. The aforementioned input shaft (I), the first rotary electric machine (MG1), the second rotary electric machine (MG2), the power transmission device (PT), the distribution output member (21), the output gear (22), the counter gear mechanism (C) ) and the differential gear device DF for output are both housed inside the case 2 . As shown in FIG. 3 , in the present embodiment, the case 2 includes a case body 2a and one axial side of the case body 2a (the right side of FIG. 3: hereinafter, "one side in the axial direction") a front cover 2b that can be attached to the axial direction It can be divided into a cover (2c). These are fastened and fixed to each other using fastening members such as bolts.
In the case body 2a, the first rotary electric machine MG1 and the second rotary electric machine MG2 are mainly accommodated. In addition, in the receiving space P formed between the case body 2a and the front cover 2b, mainly the input shaft I, the power transmission device PT, the distribution output member 21, and the output gear 22 ), a counter gear mechanism (C), and a differential gear device (DF) for output are accommodated. The case body 2a includes a case outer peripheral wall 3 formed in an irregular cylindrical shape so as to cover at least the outer periphery of the first rotating electric machine MG1 and the second rotating electric machine MG2, and the case outer peripheral wall ( 3) and an intermediate support wall 7 for blocking the end opening on one side in the axial direction. The case outer peripheral wall 3 and the intermediate support wall 7 are integrally formed. In addition, the front cover 2b covers at least the outer periphery of the power transmission device PT, the distribution output member 21, the output gear 22, the counter gear mechanism C, and the differential gear device for output (DF). It includes a partition wall 10 formed in an irregular cylindrical shape so as to have an irregular cylindrical shape, and an end support wall 4 for blocking an end opening on one side of the partition wall 10 in the axial direction. The partition wall 10 and the end support wall 4 are integrally formed. The rear cover 2c is a substantially flat member having a shape corresponding to the outer shape of the case outer circumferential wall 3 so as to close the end opening on the other axial side of the case outer circumferential wall 3 of the case body 2a. is formed as
The end support wall 4 has a shape extending at least in the radial direction. In this embodiment, the end support wall 4 extends in the radial and circumferential directions. A through hole in the axial direction is formed in the end support wall 4 . The input shaft (I) inserted into the through hole penetrates the end support wall (4) and is inserted into the case (2). The end support wall 4 is, around the input shaft I, toward the other side in the axial direction (that is, on the side of the power transmission device PT that becomes the receiving space P side when viewed from the end support wall 4 ). toward) and a cylindrical (boss-shaped) axial projection 5 protruding. In addition, the end support wall 4 has a cylindrical shape protruding toward the other side in the axial direction at a position spaced apart from the axial projection 5 on the radially outer side of the axial projection 5 in the same manner ( boss-shaped axial projections 6 . Both of these axial projections 5 and 6 are integrally formed on the end supporting wall 4 .
The intermediate support wall 7 has a shape extending at least in the radial direction. In this embodiment, the intermediate support wall 7 extends in the radial and circumferential directions. A through hole in the axial direction is formed in the intermediate support wall 7 . The first rotor shaft 31 of the first rotary electric machine MG1 inserted into this through-hole penetrates the intermediate support wall 7 and in the receiving space P, the sun gear S of the power transmission device PT. ) is connected to The intermediate support wall 7 is, around the first rotor shaft 31, toward one side in the axial direction (that is, the power transmission device that becomes the receiving space P side when viewed from the intermediate support wall 7 ). and a cylindrical (boss-shaped) axial projection 8 protruding (toward the PT). This axial projection (8) is integrally formed with the intermediate support wall (7). Accordingly, in this embodiment, the axial projection 5 and the axial projection 6 integrally formed with the end support wall 4, and the shaft integrally formed with the intermediate support wall 7 The direction protrusions 8 are disposed to face each other in the accommodation space P. In this embodiment, the intermediate support wall 7 functions as a 'support wall' in the present invention, and the axial projection 8 of the intermediate support wall 7 is a 'cylindrical part' in the present invention. functions as '.
As shown in FIG. 3 , a pump cover 2d is attached to an end face of the rear cover 2c on one side in the axial direction that is the inner side of the case 2 . The pump cover 2d is fastened to the rear cover 2c by means of a fastening member such as a bolt or the like in a state in which the pump cover 2d is in contact with one side in the axial direction with respect to the rear cover 2c. A pump chamber is formed between the rear cover 2c and the pump cover 2d, and an oil pump 55 is disposed in the pump chamber. As such an oil pump 55, in this embodiment, an internal gear pump having an inner rotor and an outer rotor is used. In this embodiment, the inner rotor of the oil pump 55 is driven by the tubular pump drive shaft 54 connected to the input shaft I so as to rotate together with the input shaft I. Then, the oil discharged from the oil pump 55 passes through the shaft internal flow path 52 formed in the inner diameter portion of the pump drive shaft 54 and the input shaft I, the power transmission device PT, and a plurality of gears. and a plurality of bearings to lubricate and cool these parts. The pump cover 2d is a cylindrical (boss-shaped) shaft that protrudes toward one side in the axial direction (that is, toward the side of the first rotary electric machine MG1 which is the side facing the inside of the case 2). directional projections 9 . This axial projection 9 is integrally formed with the pump cover 2d.
The input shaft I is a shaft for inputting torque from the engine E into the hybrid drive device 1, and as shown in Figs. 3 and 4, at one end in the axial direction to the engine E Connected. Here, the input shaft (I) is disposed in a state penetrating the case (2), and is connected to the engine output shaft (Eo) of the engine (E) through a damper (D) on one side of the axial direction of the end support wall (4) and rotates together with the engine output shaft Eo. The damper D is a device that transmits the rotation of the engine output shaft Eo to the input shaft I while damping (ie, attenuating) the torsional vibration of the engine output shaft Eo. Any of a variety of known devices can be used as the damper (D). In the present embodiment, the damper D is symmetrical in the axial direction and is configured to have a shape in which the width in the axial direction is gradually narrowed from the input shaft I in the radial direction outward. The input shaft (I) is supported by the axial projection (5) of the end support wall (4) in a rotatable state through the first needle bearing (69). In addition, between the end support wall 4 and the input shaft I, an oil seal 59 for preventing leakage of oil to one side in the axial direction (ie, the damper D and the engine E side) is disposed. . Further, in the present embodiment, the first rotor shaft 31 of the first rotary electric machine MG1 is formed in a tubular shape having an axial through hole in its inner diameter portion. The end of the input shaft I on the other side in the axial direction is inserted into the through hole of the first rotor shaft 31 . At this time, the input shaft (I) is supported by the first rotor shaft (31) in a rotatable state through the second needle bearing (70).
The input shaft I is provided with the flange part 51 extending radially from the said input shaft I in the axial direction center part. The flange portion 51 is integrally formed with the input shaft I. The flange portion 51 passes between the sun gear S connected to the first rotor shaft 31 of the first rotary electric machine MG1 and the axial projection 5 of the end support wall 4, It is connected to the carrier CA of the power transmission device PT. On both sides in the axial direction of the flange portion 51, the axial protrusion 5 of the end support wall 4 and the sun gear S are provided through a first thrust bearing 67 and a second thrust bearing 68, respectively. are in contact That is, the first thrust bearing 67 is disposed between the end face of the flange portion 51 on the one side in the axial direction and the end face on the other side in the axial direction of the protrusion portion 5 in the axial direction so as to be in contact with them. Further, the second thrust bearing 68 is disposed between the end face of the flange portion 51 on the other side in the axial direction and the end face of the sun gear S on the one side in the axial direction so as to be in contact with them.
The first rotor shaft 31 is configured to input the torque from the first rotary electric machine MG1 to the sun gear S of the power transmission device PT (or transmit the torque transmitted to the sun gear S to the first As a shaft (for input to the rotary electric machine MG1), as shown in FIGS. 3 and 4, it is spline-connected to the sun gear S at one end of the axial direction. The first rotor shaft 31 is supported by the axial projection 8 of the intermediate support wall 7 in a rotatable state through the first rotor bearing 63 . Further, the first rotor shaft 31 rotates through the second rotor bearing 64 at an axial position different from that of the first rotor bearing 63 (that is, the end on the other side in the axial direction in this embodiment). As possible, it is supported by the axial projection 9 of the pump cover 2d. In the present embodiment, a rotation sensor 57 for detecting the rotational phase of the first rotor Ro1 of the first rotary electric machine MG1 is disposed so as to surround the circumference of the first rotor shaft 31 . The rotation sensor 57 is disposed adjacent to and on one side in the axial direction of the pump cover 2d and the second rotor bearing 64 in the axial direction. As this type of rotation sensor 57, a resolver or the like can be used. In this embodiment, the first rotor bearing 63 functions as a 'rotor bearing' of the present invention.
The distribution output member 21 is disposed radially outside the sun gear S and the carrier CA so as to surround the sun gear S and the carrier CA. The distribution output member 21 is a cylindrical member that occupies almost the entire axial direction of the accommodation space P. As shown in FIG. The ring gear R of the power distribution device PT is integrally formed with the distribution output member 21 on the inner peripheral surface 21b of the distribution output member 21 . The ring gear R is formed in the central portion of the distribution output member 21 in the axial direction. In the present embodiment, the distribution output member 21 is provided with two axially stepped portions 23 and 24 on its inner peripheral surface 21b. Here, the 'step in the axial direction' on the inner circumferential surface is formed at a predetermined position in the axial direction of the distribution output member 21 and becomes a portion in which the inner diameter of the distribution output member 21 changes at this position. The inner diameter of the portion between the two stepped portions 23 and 24 in the axial direction is formed to be smaller than the inner diameter of the portion that is outside the two stepped portions 23 and 24 in the axial direction, respectively. . And the ring gear R is formed in the inner peripheral surface 21b of the distribution output member 21 in the said small diameter part. Accordingly, the entire power transmission device PT is disposed to overlap the distribution output member 21 and the distribution output member 21 in the axial direction inside the distribution output member 21 in the radial direction.
The distribution output member 21 is rotatably supported with respect to the case 2 at a plurality of positions in the axial direction (two places in this embodiment). In the present embodiment, the distribution output member 21 includes a first output bearing 61 and a second output bearing 62 disposed radially inside the distribution output member 21 at both ends of the distribution output member 21 in the axial direction. Thereby, it is supported in a rotatable state with respect to the case (2). More specifically, the distribution output member 21 has a large-diameter portion on the one axial side of the inner peripheral surface 21b and an axial projection 6 of the end support wall 4 at the end of the one side in the axial direction. ) is rotatably supported through the first output bearing 61 disposed between. In addition, the distribution output member 21, at the other end of the axial direction, is disposed between the large-diameter portion on the other axial side of the inner peripheral surface 21b and the axial projection 8 of the intermediate support wall 7 . 2 It is rotatably supported through an output bearing (62). In this way, the distribution output member 21 has the axial projection 6 of the end support wall 4 and the axial projection 8 of the intermediate support wall 7 disposed opposite to each other in the receiving space P. , is rotatably supported from the radially inward by two output bearings (61, 62). In this way, by adopting the configuration in which the distribution output member 21 is supported from the radially inside, compared with the configuration in which the distribution output member 21 is supported from the radial outside, the two output bearings 61 and 62 are can be hardened.
An output gear 22 is formed on the outer peripheral surface 21a of the distribution output member 21 . That is, in this embodiment, the output gear 22 is, for example, a sleeve-like member having a relatively small diameter which is formed to surround the input shaft I while being radially connected to the distribution output member 21 via another member. (See, for example, FIG. 4 of Japanese Patent Laid-Open No. 2000-217205), etc., but is formed integrally with the distribution output member 21 on the outer peripheral surface 21a of the distribution output member 21. do. As described above, in the present embodiment, since the distribution output member 21 is supported from the inside in the radial direction by the two output bearings 61 and 62, the distribution output member 21 is formed on the outer peripheral surface 21a of the The formed output gear 22 is not limited by the axial position by the two output bearings 61 and 62 . Accordingly, this configuration has the advantage that the degree of freedom with respect to the axial position of the output gear 22 becomes extremely high.
Accordingly, in this embodiment, the output gear 22 is formed in a positioning position that is disposed closer to the end of the one axial side of the distribution output member 21 (that is, the side adjacent to the engine E). has been As a result, with respect to the output gear 22, also for each configuration such as the counter gear mechanism C, the second rotary electric machine MG2, and the output differential gear device DF, which are arranged on the downstream side of the power transmission path, the shaft It is possible to arrange it closer to one side of the direction (that is, the side adjacent to the engine E). However, in the positioning of the output gear 22 as described above, the output gear 22 is the first output bearing 61 disposed at the end of the one side in the axial direction inside the distribution output member 21 in the radial direction. ) and axially overlapping. Therefore, compared with the case where the distribution output member 21, the first output bearing 61, and the output gear 22 are arranged in an axial direction, the axial length of the space in which they are arranged is further shortened.
In addition, in this embodiment, at the end of the other axial side (that is, the side adjacent to the intermediate support wall 7) of the outer peripheral surface 21a of the distribution output member 21, a parking gear 82 is provided. is formed The parking gear 82 is integrally formed with the distribution output member 21 . The parking gear 82 is disposed radially inside the distribution output member 21 so as to overlap in the axial direction with the second output bearing 62 disposed at the other end in the axial direction as well. Accordingly, the axial length of the space in which the distribution output member 21 , the second output bearing 62 , and the parking gear 82 are arranged is further shortened compared to the case where they are arranged in a row in the axial direction. The parking gear 82 constitutes a part of the parking lock mechanism 81 . In this embodiment, as shown in Fig. 2, the parking lock mechanism 81 includes a lock member 83 configured to be swingable about a predetermined swing support point 84, and the lock member ( The clasp portion 85 is integrally formed with the 83 . The lock member 83 and the clasp 85 are oscillated within a predetermined movable range by a cam mechanism not shown or the like. In a state in which the latch portion 85 is engaged with the parking gear 82 and they are engaged, the parking lock mechanism 81 forcibly stops the rotation of the distribution output member 21 . On the other hand, in a state in which the latch portion 85 does not mesh with the parking gear 82 and the engagement is released, the parking lock mechanism 81 permits rotation of the distribution output member 21 . In this embodiment, the parking gear 82 functions as a 'gear part' of the present invention, and the parking lock mechanism 81 functions as a 'lock mechanism' of the present invention.
The second rotor shaft 36 is a shaft for inputting the driving force from the second rotary electric machine MG2 to the second rotary electric machine output gear 37 integrally formed with the shaft member 38, and is shown in FIG. As shown, the inner circumferential surface of the shaft member 38 at the one end in the axial direction is spline-connected to the outer circumferential surface of the other end of the shaft member 38 in the axial direction. The second rotor shaft 36 and the shaft member 38 which rotate together are supported by the case 2 in a state of being rotatable through a plurality of bearings at a plurality of positions in the axial direction. In addition, although not shown, a rotation sensor such as a resolver for detecting a rotational phase of the second rotor Ro2 of the second rotary electric machine MG2 is provided to surround the second rotor shaft 36 .
The first gear 42 and the second gear 43 constituting the counter gear mechanism C are formed integrally with the counter shaft 41, respectively. Therefore, the counter shaft 41, the 1st gear 42, and the 2nd gear 43 all rotate together. In the present embodiment, the second gear 43 is disposed on the other side of the first gear 42 in the axial direction. Further, the counter shaft 41 is rotatably supported with respect to the case 2 at a plurality of positions in the axial direction (two places in this embodiment). In the present embodiment, the counter shaft 41 is rotatably supported with respect to the case 2 via the first counter bearing 65 at the end of the one side in the axial direction, and is rotatably supported at the end of the other side in the axial direction. It is rotatably supported with respect to the case (2) via a counter bearing (66). The first gear support member 44 supporting the first gear 42 is disposed adjacent to the other axial side of the first counter bearing 65 , and supports the second gear 43 supporting the second gear 43 . The member 45 is disposed adjacent to one side of the second counter bearing 66 in the axial direction. However, the size of the second gear 43 is set smaller than the size of the first gear 42 . The gear ratio (dimension ratio) of these gears can be appropriately changed according to vehicle characteristics and the like.
2 and 3 , the first gear 42 meshes with both the output gear 22 and the second rotary electric machine output gear 37 . In the present embodiment, the second rotary electric machine MG2 basically outputs a relatively large assist torque to drive the vehicle. Therefore, the maximum value of the torque that can be transmitted from the output gear 22 to the first gear 42 is compared with the maximum value of the torque that can be transmitted from the second rotary electric machine output gear 37 to the first gear 42 . If you do, the latter will be larger. Therefore, in the hybrid drive device 1 according to the present embodiment, the axial length of the second rotary electric machine output gear 37 is the axial length of the output gear 22 in order to enable greater torque transmission. set longer. And, in the present embodiment, while suppressing an increase in the axial dimension of the entire hybrid drive device 1 , the torque output from the second rotary electric machine MG2 is efficiently transferred to the first gear 42 without waste. In order to transmit, the axial length of the first gear 42 is set equal to the axial length of the second rotary electric machine output gear 37 . As a result, the axial length of the first gear 42 is longer than the axial length of the output gear 22 . Accordingly, the first gear 42 is provided with the output gear 22 and a portion that does not mesh with each other (hereinafter referred to as a non-meshing portion N (refer to FIG. 4 )).
The first gear 42 and the output gear 22 are mutually meshing positions so that the ends on the other side in the axial direction are meshed with each other in a state in which they are aligned with each other. In other words, as for the first gear 42 and the output gear 22 , the entire non-engagement portion N of the first gear 42 is on one side of the axial direction of the output gear 22 (that is, close to the engine E). side), their mutual meshing positions are set. In the present embodiment, at a position overlapping with the first counter bearing 65 disposed adjacent to one axial side of the first gear 42 (that is, the side close to the engine E) in the axial direction, A congruence (N) is arranged. However, the end support wall 4 at the radial position corresponding to the portion (or the non-engagement portion N) where the output gear 22 and the first gear 42 mesh is formed, as shown in FIG. , is formed thin in the axial direction. And the non-engaging part N of the 1st gear 42 is arrange|positioned in the empty space formed in the radial direction outer side of the counter gear mechanism C side of the axial projection part 6 of the end support wall 4 . Therefore, by effectively utilizing the empty space formed on the radially outer side of the axial projection 6, the counter gear mechanism C can be arranged as close as possible to one side of the axial direction (that is, the side close to the engine E). be able to Further, as a result, even the second rotary electric machine MG2 directly driven and connected to the counter gear mechanism C and the differential gear device DF for output are also on one side in the axial direction (that is, the side close to the engine E). can be placed as close as possible to the
<b>3. </b><b>hybrid</b><b> Arrangement of each part of the driving device</b>
Next, the arrangement of each part of the hybrid drive device 1 according to the present embodiment will be described. Here, according to the characteristic configuration of the present invention, the arrangement of each component mainly accommodated in the accommodation space P will be described. In particular, the disposition of each component centering on the first output bearing 61 and the second output bearing 62 for rotatably supporting the distribution output member 21 will be described.
First, the arrangement of each component centering on the second output bearing 62 is concentrated. The first rotor bearing 63 is disposed radially inside the second output bearing 62 to overlap the second output bearing 62 in the axial direction. In this embodiment, the second output bearing 62 and the first rotor bearing 63 are both arranged in contact with the axial projection 8 integrally formed with the intermediate support wall 7 . Here, the axial projection 8 has an axial length slightly longer than the axial length of the second output bearing 62 and the first rotor bearing 63 . Then, in contact with the outer peripheral surface 8a of the axial projection 8, aligned in the axial direction with respect to the end on the one side in the axial direction, the second output bearing 62 is disposed, and the inner peripheral surface of the axial projection 8 The first rotor bearing 63 is disposed in contact with (8b) and aligned in the axial direction with respect to the end on the other side in the axial direction. Accordingly, a part of the one axial side of the first rotor bearing 63 (that is, it occupies most in this embodiment) and a part of the other axial side of the second output bearing 62 in the axial direction are placed overlapping.
Further, in the present embodiment, the second gear 43 of the counter gear mechanism C overlaps the second output bearing 62 in the axial direction on the radially outer side of the second output bearing 62 . are placed In addition, the second gear 43 is disposed radially outwardly of the first rotor bearing 63 , also overlapping with the first rotor bearing 63 in the axial direction. In the present embodiment, the second output bearing 62 and the first rotor bearing 63 are disposed to overlap the second gear 43 in the axial direction as a whole, respectively. With this configuration, the first rotor bearing 63 , the second output bearing 62 , and the second gear 43 are all arranged to overlap each other in the axial direction. However, in this embodiment, since the parking gear 82 formed on the outer circumferential surface 21a of the distribution output member 21 is disposed to overlap the second output bearing 62 in the axial direction, the first rotor bearing ( 63), the second output bearing 62, the parking gear 82, and the second gear 43 are all arranged to overlap each other in the axial direction.
Next, the arrangement of each component centering on the first output bearing 61 is concentrated. The output gear 22 is disposed radially outside the first output bearing 61 to overlap the first output bearing 61 in the axial direction. As described above, the output gear 22 is integrally formed on the outer peripheral surface 21a of the distribution output member 21 close to the end of the distribution output member 21 on one side in the axial direction. Further, the first output bearing 61 is arranged in alignment with the distributing output member 21 and one end of the axial direction and in contact with the inner peripheral surface 21b of the distributing output member 21 . Accordingly, a part of the one axial side of the output gear 22 and a part of the other axial side of the first output bearing 61 (which occupies most in the present embodiment) are arranged to overlap in the axial direction. . However, since the first gear 42 of the counter gear mechanism C meshes with the output gear 22 , the first gear 42 also overlaps the first output bearing 61 in the axial direction.
Further, in the present embodiment, the first needle bearing 69 is disposed radially inside the first output bearing 61 to overlap the first output bearing 61 in the axial direction. In the present embodiment, the first needle bearing 69 is disposed to overlap the first output gear 61 in the axial direction as a whole. Further, in the present embodiment, the first counter bearing 65 is disposed radially outside the first output bearing 61 , overlapping the first output bearing 61 in the axial direction. In the present embodiment, the first counter bearing 65 is disposed so that a part of the other axial side thereof slightly overlaps with a part of the one axial side of the first output bearing 61 in the axial direction. Therefore, in this embodiment, the first needle bearing 69, the first output bearing 61, the output gear 22, the first gear 42, and the first counter bearing 65 are all axially oriented. will overlap.
However, referring to FIG. 4 , in the configuration of this embodiment, the first output bearing 61 , the non-matching portion N of the first gear 42 , and the first counter bearing 65 are from the input shaft I With the arrangement in this order toward the radially outward direction, the amount each extending toward the axial one side (that is, the side close to the engine E) in this order increases. In addition, the end support wall 4 is also configured to have a shape in which steps are formed. However, in this embodiment, the shape of the damper D disposed between the end support wall 4 and the engine E is symmetrical in the axial direction, and is directed radially outward from the input shaft I. It has a shape in which the width in the axial direction gradually becomes narrower. Accordingly, since these components have shapes complementary to each other in the axial direction and are disposed opposite to each other, problems such as enlarging the axial dimensions of these components do not exist in reality.
In the hybrid driving device 1 according to the present embodiment, the output gear 22 is formed on the outer peripheral surface 21a of the distribution output member 21 formed in a cylindrical shape. Accordingly, the distribution output member 21 and the output gear 22 (herein, when another member is interposed between the distribution output member 21 and the output gear 22, the other member is also included). The axial length of the space becomes the same as the axial length of the distribution output member 21, so that it becomes very short. Further, in this embodiment, the power transmission device PT is disposed radially inside the distribution output member 21 having a short axial length, overlapping the distribution output member 21 in the axial direction. Further, with respect to the arrangement of each component, the arrangement as described above centering on the two output bearings 61 and 62 for rotatably supporting the distribution output member 21 is applied. As a result, in the space occupied by the distribution output member 21 in the axial direction (a space substantially equal to the accommodation space P), the power distribution device PT, the first output bearing 61, and the second output bearing ( 62), the first rotor bearing 63, the parking gear 82, the first gear 42, and all the components such as the second gear 43 can be arranged.
Further, in the present embodiment, by arranging the first rotor bearing 63 to overlap the second output bearing 62 in the axial direction, the first rotary electric machine MG1 axially moves the power distribution device PT ) and the distribution output member 21 may be disposed close to each other. Accordingly, the first rotating electric machine MG1, the distribution output member 21 and the output gear 22 (when another member is interposed between the distribution output member 21 and the output gear 22, the other member Also included), the axial length of the space occupied can be greatly shortened. As a result, in the hybrid drive device 1 according to the present embodiment, the axial dimension of the entire device can be greatly shortened compared to the related art.
<b>[others </b><b>Example</b><b>]</b>
(1) In the above embodiment, both the first output bearing 61 and the second output bearing 62 are disposed radially inside the distribution output member 21, and the distribution output member 21 includes: It is rotatably supported from the radially inside by two output bearings (61, 62). However, the present invention is not limited thereto. That is, when at least the first output bearing 61 is disposed radially inside the distribution output member 21 , the output gear 22 may be disposed to overlap the first output bearing 61 in the axial direction. Accordingly, in another embodiment of the present invention, the second output bearing 62 is disposed on the radially outer side of the distribution output member 21 , and the distribution output member 21 is configured to provide a second output from the other side in the axial direction. It is rotatably supported from radially outward by bearings 62 .
(2) In the above-described embodiment, the second output bearing 62 is disposed in contact with the outer peripheral surface 8a of the axial projection 8, and the first rotor in contact with the inner peripheral surface 8b of the axial projection 8 A bearing 63 is arranged. However, the present invention is not limited thereto. That is, in another embodiment of the present invention, the second output bearing 62 and the first rotor bearing 63 are not arranged so as to be in contact with the inner periphery and the outer periphery of a single portion such as the axial protrusion 8, They are arranged so as to be in contact with different portions of the case 2, respectively.
(3) In the above-described embodiment, the second gear 43 is disposed to overlap the first rotor bearing 63 in the axial direction. However, the present invention is not limited thereto. That is, in another embodiment of the present invention, the second gear 43 is disposed at a position that does not overlap the first rotor bearing 63 in the axial direction. That is, in another embodiment of the present invention, with respect to the axial arrangement, the entire second gear 43 is arranged to be in an axial position different from that of the first rotor bearing 63 (ie, a completely different position). do.
(4) In the above-described embodiment, the first rotor bearing 63 is disposed to overlap the second output bearing 62 in the axial direction. However, the present invention is not limited thereto. That is, in another embodiment of the present invention, the first rotor bearing 63 is disposed at a position that does not overlap the second output bearing 62 in the axial direction. That is, in another embodiment of the present invention, with respect to the axial arrangement, the entire first rotor bearing 63 is axially different from that of the second output bearing 62 (that is, a completely different position). placed so as to
(5) In the above embodiment, the parking gear 82 constituting a part of the parking lock mechanism 81 is formed on the outer peripheral surface 21a of the distribution output member 21 and is integral with the distribution output member 21 is formed negatively. However, the present invention is not limited thereto. That is, in another embodiment of the present invention, the parking gear 82 is formed on a member other than the distribution output member 21 .
(6) In the above embodiment, the ring gear R of the power transmission device PT is integrally formed with the distribution output member 21 on the inner circumferential surface 21b of the distribution output member 21, On the outer peripheral surface 21a of the distribution output member 21 , the output gear 22 and the parking gear 82 are integrally formed with the distribution output member 21 . However, the present invention is not limited thereto. That is, in another embodiment of the present invention, for example, any one or more of the ring gear R, the output gear 22, and the parking gear 82 of the power distribution device PT (referred to as "integrated gear" in this paragraph) ) is integrally formed with the other member and the 'other member' is fixed to the distribution output member 21 , so that the integrated gear is provided integrally with the distribution output member 21 . In this case, when fixing the 'other member' on which the integrated gear is formed to the distribution output member 21 , any configuration, such as fastening using welding or bolts, may be employed.
(7) Regarding other configurations, the embodiments disclosed herein are merely exemplary in all respects, and the present invention is not limited thereto. That is, as long as the structure described in the claims of the present invention and the structures equivalent thereto are provided, all structures in which a part of the structures not described in the claims are appropriately modified are naturally included in the technical scope of the present invention.
The present invention provides an input member driven and connected to an engine, a rotary electric machine, a power distribution device for distributing and transmitting torque transmitted to the input member to the rotary electric machine and a distribution output member, and a torque transmitted to the distribution output member. It can be suitably applied to a hybrid driving device having an output gear that is outputably installed on the wheel side.
5 sheets
Sheet 1 Sheet 2 Sheet 3 Sheet 4 Sheet 5
Every citation, both ways
| Document | Relation | Office | Cited during |
|---|---|---|---|
| JP2009166740A | Cites | Japan | Examiner |
14 members in 6 offices
Priority claims9
| Document | Office | Kind | Date |
|---|---|---|---|
| 2010051859 | Japan | A | |
| 2010051859 | Japan | A | |
| P2010051859 | Japan | – | |
| 2011053872 | Japan | W | |
| 2011053872 | Japan | W | |
| JPP2010051859 | – | – | – |
| JP20100051859 | – | – | – |
| PCTJP2011053872 | – | – | – |
| WO2011JP53872 | – | – | – |
Members14
| Document | Office | Kind | |
|---|---|---|---|
| WO2011111519A1 | World Intellectual Property Organization (WIPO) | A1 | |
| JP2011183946A | Japan | A | |
| EP2507532A1 | European Patent Office (EPO) | A1 | |
| KR20120117897A | Republic of Korea | A | |
| CN102770689A | China | A | |
| US2013008284A1 | United States of America | A1 | |
| US2013023369A1 | United States of America | A1 | |
| US2013023372A1 | United States of America | A1 | |
| KR101420552B1This record | Republic of Korea | B1 | |
| US8808128B2 | United States of America | B2 | |
| US8870697B2 | United States of America | B2 | |
| US8882622B2 | United States of America | B2 | |
| CN102770689B | China | B | |
| EP2507532B1 | European Patent Office (EPO) | B1 |
8 legal events, as the office reported them to INPADOC
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| Request for examinationA201 | A201 |
Numbers
- Publication
- 10-1420552
- Publication, DOCDB
- 101420552
- Publication, EPODOC
- KR101420552B
- Application
- 1020127022018
- Application, DOCDB
- 20127022018
- Application, EPODOC
- KR20127022018
Titles4
- Korean
- 하이브리드 구동장치
- English
- Hybrid drive system
- Unlabeled
- 하이브리드 구동장치{Hybrid drive system}
- Unlabeled
- Hybrid drive system
Classification
- CPC, 12
- F16H3/727
- F16H1/28
- B60K6/40
- B60K6/445
- F16H57/082
- F16H2037/0866
- Y02T10/62
- Y10S475/90
- Y10T74/19014
- Y10T74/2186
- F16H3/72
- F16H57/08
- IPC, 5
- B60K6 445
- B60L50 16
- F16H1 28
- F16H3 72
- F16H57 08