JP2012171371A - Driving device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a driving device for a vehicle capable of restraining an increase in design and manufacturing cost when arranging and constituting an oil passage to an engaging device and a hydraulic control valve for the engaging device.SOLUTION: The driving device for the vehicle includes a transmission for shifting and transmitting the rotation of an input member connected to a rotating electric machine to an output member connected to a wheel, and the engaging device for selectively connecting the input member to an internal combustion engine. The driving device further includes a first hydraulic control device provided with the hydraulic control valve of the transmission, a second hydraulic control device separated from the first hydraulic control device arranged under an upper end of the first hydraulic control device and provided with the hydraulic control valve of the engaging device, an oil storage part, and a hydraulic pump. The first hydraulic control device is stored in the oil storage part. The second hydraulic control device is stored in an oil-tight chamber, and includes a first discharge oil passage to the oil-tight chamber from the engaging device, and a second discharge oil passage to the oil storage part from the oil-tight chamber.

Description

  The present invention includes an input member that is drivingly connected to a rotating electrical machine, an output member that is drivingly connected to a wheel, a transmission that shifts the rotation of the input member and transmits the rotation to the output member, and the input member is an internal combustion engine. And an engagement device that selectively drives and connects to the vehicle.

  As a vehicle drive device for a hybrid vehicle including an internal combustion engine and a rotating electrical machine as a drive force source, for example, a device described in Patent Document 1 below is already known. The vehicle drive device for a hybrid vehicle described in Patent Document 1 includes an engagement device that selectively drives and connects an internal combustion engine to a power transmission mechanism. And it is comprised so that an internal combustion engine can be isolate | separated from a power transmission mechanism by releasing an engagement apparatus by controlling the hydraulic pressure supplied to an engagement apparatus so that a vehicle can be driven with the driving force of only a rotary electric machine. Yes. That is, in the technique of Patent Document 1, an engagement device capable of selectively drivingly connecting an internal combustion engine and a power transmission system by hydraulic control is provided along with the hybrid vehicle. An electromagnetic hydraulic control valve and a hydraulic circuit for controlling the hydraulic pressure supplied to the engagement device are provided.

  For this reason, it is necessary to provide a hydraulic oil supply passage for the engagement device, a discharge oil passage for the oil supplied to the engagement device, and a hydraulic control valve for the engagement device in the vehicle drive device. Placement and configuration are problematic in terms of design and manufacturing costs.

JP 2009-35241 A

  Therefore, an increase in design and manufacturing cost is suppressed when arranging and configuring an oil passage to the engagement device and a hydraulic control valve for the engagement device for selectively drivingly connecting the internal combustion engine to the power transmission mechanism. There is a need for a vehicle drive device that can be used.

  An input member that is drivingly connected to a rotating electrical machine, an output member that is drivingly connected to a wheel, a transmission that shifts the rotation of the input member and transmits the rotation to the output member, and the input member that is an internal combustion engine And an engaging device selectively drivingly coupled to the engine, the characteristic configuration of the vehicle driving device includes a first hydraulic control device provided with a hydraulic control valve for controlling the hydraulic pressure supplied to the transmission, A second hydraulic control device provided separately from the first hydraulic control device and disposed below the upper end of the first hydraulic control device and provided with a hydraulic control valve for controlling the hydraulic pressure supplied to the engagement device; An oil reservoir that stores oil to be supplied to the first hydraulic control device and the second hydraulic control device; and the oil stored in the oil reservoir is sucked to generate hydraulic pressure, and the first hydraulic control device And a hydraulic pump supplied to the second hydraulic control device The first hydraulic control device is housed in the oil reservoir, and the second hydraulic control device is housed in an oil tight chamber formed in an oil tight manner outside the oil reservoir, An oil-tight first discharge oil passage for sending the oil discharged from the engagement device to the oil-tight chamber, and an oil-tight second for sending the oil discharged from the oil-tight chamber to the oil reservoir And a drain oil passage.

In the present application, the “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that functions as both a motor and a generator as necessary.
In the present application, “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 two This is used as a concept including a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like. In addition, as such a transmission member, an engagement element that selectively transmits rotation and driving force, such as a friction clutch or a meshing clutch, may be included.

  As described above, the provision of the engagement device necessitates a hydraulic control system for the engagement device. According to the above characteristic configuration, the hydraulic control valve for the engagement device is separated from the first hydraulic control device provided with the hydraulic control valve for the transmission, and is provided in the second hydraulic control device. It is easy to secure a mounting space for the hydraulic control device for the engaging device. Compared to the case where the hydraulic control valve for the engagement device and the hydraulic control valve for the transmission are integrated in the first hydraulic control device, the hydraulic pressure of the vehicle using only the conventional internal combustion engine as the driving force source is provided. Since it is not necessary to change the design of the control device, an increase in the design and manufacturing cost of the hydraulic control device can be suppressed. Moreover, according to said characteristic structure, since the common oil storage part and the hydraulic pump are provided in the 1st hydraulic control apparatus and the 2nd hydraulic control apparatus, when providing a dedicated oil storage part and a hydraulic pump in each, In comparison, an increase in manufacturing cost can be suppressed.

  Thus, by providing the oil reservoir and the hydraulic pump common to the first hydraulic control device and the second hydraulic control device, the oil supplied from the second hydraulic control device to the engagement device, and the second hydraulic control The oil drained from the apparatus needs to be discharged to a common oil reservoir and the oil needs to be recirculated by a hydraulic pump. According to said characteristic structure, the oil-tight 1st discharge oil path for sending the oil discharged | emitted from the engagement apparatus to an oil-tight chamber, and the oil for sending the oil discharged | emitted from the oil-tight chamber to an oil storage part And a dense second oil discharge passage, the oil discharge passage from the engagement device to the oil reservoir is made oil-tight. Therefore, the oil supplied from the second hydraulic control device to the engagement device is discharged to the oil-tight chamber through the first discharge oil passage at a pressure corresponding to the supply pressure, and from the oil-tight chamber through the second discharge oil passage. And sent to the oil reservoir. In addition, since the second hydraulic control device is accommodated in the oil tight chamber, the oil drained from the second hydraulic control device is also discharged into the oil tight chamber, and the oil tight first drain is generated by the supply pressure and the drain pressure. It is sent to the oil reservoir through the two drain oil passages. Therefore, the oil discharge passage for oil discharged from the engagement device and the oil discharge passage for oil drained from the second hydraulic control device can be shared by the oil tight chamber and the second discharge oil passage. Cost can be reduced. Then, the oil discharged from the engagement device and the oil drained from the second hydraulic control device can be sent to the oil reservoir using the supply pressure and the drain pressure through the oil-tight oil passage. . Therefore, there is no need to provide a dedicated hydraulic pump for sending oil, and an increase in manufacturing cost can be suppressed.

  Further, as in the above characteristic configuration, when the second hydraulic control device is disposed below the upper end of the first hydraulic control device, the oil in the oil tight chamber housing the second hydraulic control device is In order to send the oil pressure to the oil reservoir that houses the first hydraulic control device, it is necessary to send oil upward by a predetermined height difference, and hydraulic pressure to be sent upward by the height difference is required. According to said characteristic structure, oil can be sent to an oil storage part from an oil-tight chamber with the hydraulic pressure more than a high-low difference using an oil-tight discharge oil path using a supply pressure and a drain pressure. Therefore, even when there is the predetermined height difference, there is no need to provide a dedicated hydraulic pump for sending oil, and an increase in manufacturing cost can be suppressed.

  Here, a first case that houses the transmission and a second case that houses the rotating electrical machine and the engagement device are further provided, and the first hydraulic control device is attached to a lower portion of the first case. The second hydraulic control device is attached to a lower portion of the second case, the first drain oil passage is provided in the second case, and the second drain oil passage is connected to the second case from the second case. It is preferable that the configuration is provided over one case.

  As in this configuration, when the oil tight chamber is arranged below the oil level of the oil reservoir and the opening on the oil reservoir portion side of the second discharge oil passage, the oil tight chamber is It will be filled with oil up to the top. And the upper part of the oil filled in the oil-tight chamber will be located below the oil level and the opening located above either the opening, the upper part of the oil filled in the oil-tight chamber, and the oil reservoir A difference in height occurs between the oil level and the one located above the opening on the oil storage portion side of the second discharge oil passage. Therefore, it is necessary to send the oil in the oil tight chamber upward by this height difference, and a hydraulic pressure larger than the hydraulic pressure corresponding to this height difference is required. According to the configuration as described above, by using the supply pressure and the drain pressure by the oil-tight discharge oil passage, a hydraulic pressure larger than the hydraulic pressure corresponding to the height difference can be generated. Oil can be sent from the oil-tight chamber to the oil reservoir without providing a pump.

  Here, a first case that houses the transmission and a second case that houses the rotating electrical machine and the engagement device are further provided, and the first hydraulic control device is attached to a lower portion of the first case. The second hydraulic control device is attached to a lower portion of the second case, the first drain oil passage is provided in the second case, and the second drain oil passage is connected to the second case from the second case. It is suitable if it is provided over one case.

  As in this configuration, the first hydraulic control device for the transmission is attached to the lower portion of the first case that accommodates the transmission, and the second hydraulic control device for the engagement device accommodates the engagement device. By being attached to the lower part of the second case, the transmission device and the first hydraulic control device and the engagement device and the second hydraulic control device can be arranged close to each other. It is possible to shorten the oil passage formed in the container, simplify it, and reduce the manufacturing cost.

Moreover, according to said structure, since the 1st discharge | emission oil path is provided in the 2nd case where the 2nd hydraulic control apparatus is attached, it is the 2nd case from the attachment part vicinity of the 2nd hydraulic control apparatus. Inside, the first drain oil passage can be provided by effectively using the case. Therefore, the number of parts for forming the oil passage can be reduced. Moreover, since the oil path is formed in the second case, oil tightness can be easily ensured.
Further, according to the above configuration, the second drain oil passage extends from the second case where the second hydraulic control device is attached to the first case where the first hydraulic control device is attached. Since it is provided in the case and the first case, the case is effectively used across the second case and the first case from the vicinity of the attachment portion of the second hydraulic control device to the vicinity of the attachment portion of the first hydraulic control device. Thus, a second discharge oil passage can be provided. Therefore, the number of parts for forming the oil passage can be reduced. Also, since the oil passage is formed in the second case and the first case, it is easy to ensure the oil tightness as long as the sealing of the joint between the second case and the first case is ensured. Can do.

  A first case that houses the transmission, and a second case that houses the rotating electrical machine and the engagement device; and the oil storage portion is a lower part of the first case and the first case. The oil tight chamber is surrounded by a second oil pan attached to the lower part of the second case and the second oil pan. Is preferred.

  According to this configuration, the oil reservoir can be formed by effectively using the first case. Moreover, since an oil storage part can be made to adjoin to a 1st case, the communication between an oil storage part and the 2nd exhaust oil path provided in a 1st case can be implement | achieved easily. Moreover, according to said structure, an oil-tight chamber can be formed using the 2nd case effectively. Further, since the oil tight chamber can be adjacent to the second case, it is possible to easily realize communication between the oil tight chamber and the first exhaust oil passage and the second exhaust oil passage provided in the second case. it can.

It is a mimetic diagram showing a schematic structure of a drive transmission system of a vehicle drive device concerning an embodiment of the present invention. It is a figure which shows schematic structure of the hydraulic control system of the vehicle drive device which concerns on embodiment of this invention. It is sectional drawing of the drive device for vehicles which concerns on embodiment of this invention. It is sectional drawing of the drive device for vehicles which concerns on embodiment of this invention.

[First embodiment]
An embodiment of a vehicle drive device 1 (hereinafter referred to as drive device 1) according to the present invention will be described with reference to the drawings. FIG. 1 is a schematic diagram illustrating a schematic configuration of a drive device 1 according to the present embodiment. As shown in this figure, the drive device 1 according to the present embodiment schematically includes an internal combustion engine IE and a rotating electrical machine MG as drive force sources, and the drive force of these drive force sources is converted to a torque converter TC and a shift gear. It has the structure which transmits to a wheel via the apparatus TM. The driving device 1 includes an input shaft I that is drivingly connected to the rotating electrical machine MG, an output shaft O that is drivingly connected to the wheels, a transmission TM that shifts the rotation of the input shaft I and transmits it to the output shaft O, and an input And an internal combustion engine separation clutch C1 as an engagement device for selectively drivingly connecting the shaft I to the internal combustion engine IE. The drive device 1 according to the present embodiment includes a torque converter TC on a power transmission path between the rotating electrical machine MG and the transmission device TM. The input shaft I is an “input member” in the present invention, and the output shaft O is an “output member” in the present invention.

  In such a configuration, as shown in FIGS. 1 and 2, the drive device 1 is provided with a first hydraulic control provided with a transmission hydraulic control valve 90 as a hydraulic control valve that controls the hydraulic pressure supplied to the transmission TM. The device VB1 and the first hydraulic control device VB1 are separated and disposed below the upper end 83 of the first hydraulic control device VB1, and serve as a hydraulic control valve that controls the hydraulic pressure supplied to the internal combustion engine separation clutch C1. A second hydraulic control device VB2 provided with a combined hydraulic control valve 93, an oil reservoir OT1 for storing oil to be supplied to the first hydraulic controller VB1 and the second hydraulic controller VB2, and stored in the oil reservoir OT1 And a hydraulic pump OP that sucks the generated oil to generate hydraulic pressure and supplies the hydraulic pressure to the first hydraulic control device VB1 and the second hydraulic control device VB2.

  The first hydraulic control device VB1 is accommodated in the oil reservoir OT1, and the second hydraulic control device VB2 is accommodated in the oil tight chamber OT2 formed in an oil tight manner outside the oil reservoir OT1. The oil-tight first exhaust oil passage PE1 for sending the oil discharged from the internal combustion engine separation clutch C1 to the oil-tight chamber OT2, and the oil for sending the oil discharged from the oil-tight chamber OT2 to the oil reservoir OT1 It is characterized in that it has a dense second discharge oil passage PE2. In the present invention, up and down means up and down in the vertical direction when the drive device 1 is mounted on a vehicle, and up and down in FIGS. 1 to 4 corresponds to up and down in the vertical direction. Hereinafter, the drive device 1 according to the present embodiment will be described in detail.

1. Configuration of Drive Transmission System of Drive Device First, the configuration of the drive transmission system of the drive device 1 according to the present embodiment will be described. As shown in FIG. 1, the drive device 1 includes an internal combustion engine IE and a rotating electrical machine MG as driving force sources for driving a vehicle. This is a drive device for a hybrid vehicle. In the present embodiment, the drive device 1 includes a torque converter TC and a transmission device TM, and the torque converter TC and the transmission device TM change the rotational speeds of the internal combustion engine IE and the rotating electrical machine MG as driving force sources. At the same time, the torque is converted and transmitted to the output shaft O. In the drive device 1 according to the present embodiment, the internal combustion engine IE, the rotating electrical machine MG, the torque converter TC, and the transmission device TM are arranged coaxially and are arranged in this order along the axial direction from the internal combustion engine IE side. ing. Further, the internal combustion engine connecting shaft EC, the input shaft I, and the output shaft O are also arranged coaxially therewith. Here, the axis of each member of the drive device 1 arranged on the same axis is set as a device axis X1. Further, in the description of the embodiment, when the axial direction, the radial direction, and the circumferential direction are simply referred to, the direction based on the device axis X1 is assumed.

  The internal combustion engine IE is a prime mover that outputs power by the combustion of fuel. For example, various known internal combustion engines such as a gasoline engine and a diesel engine can be used. In this example, an output rotation shaft such as a crankshaft of the internal combustion engine IE is drivingly connected to the input shaft I via the internal combustion engine connection shaft EC and the internal combustion engine separation clutch C1. Thereby, the internal combustion engine separation clutch C1 selectively connects the input shaft I to the internal combustion engine IE. The internal combustion engine separation clutch C1 is a friction engagement element that is engaged or released by the hydraulic pressure supplied from the second hydraulic pressure control device VB2. As such a friction engagement element, for example, a wet multi-plate clutch or a wet multi-plate brake is preferably used. Note that it is also preferable that the output rotation shaft of the internal combustion engine IE is drivingly connected integrally with the internal combustion engine connecting shaft EC, or driven and connected via another member such as a damper.

  The rotating electrical machine MG includes a stator St fixed to the second case CS2, and a rotor Ro that is rotatably supported on the radially inner side of the stator St. The rotor Ro of the rotating electrical machine MG is drivingly connected so as to rotate integrally with the input shaft I. That is, in the present embodiment, both the internal combustion engine IE and the rotating electrical machine MG are drivingly connected to the input shaft I. The rotating electrical machine MG is electrically connected to a battery (not shown) as a power storage device. The rotating electrical machine MG can perform a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. It is possible. That is, the rotating electrical machine MG is powered by receiving power supplied from the battery, or stores in the battery the power generated by the rotational driving force transmitted from the internal combustion engine IE or the wheels. Note that the battery is an example of a power storage device, and another power storage device such as a capacitor may be used, or a plurality of types of power storage devices may be used in combination.

  In the present embodiment, a torque converter TC is provided on the power transmission path between the rotating electrical machine MG and the transmission TM. The torque converter TC is a device that transmits the rotational driving force of the internal combustion engine IE and the rotating electrical machine MG as a driving force source to the transmission device TM (input shaft I). The torque converter TC includes a pump impeller 11 as an input side rotating member that is drivingly connected to the rotating electrical machine MG, a turbine runner 12 as an output side rotating member that is drivingly connected to the transmission device TM (input shaft I), And a stator 14 provided with a one-way clutch. The torque converter TC transmits the driving force between the drive-side pump impeller 11 and the driven-side turbine runner 12 via oil filled therein.

  The torque converter TC includes a lockup clutch C2 as a frictional engagement element for lockup. The lock-up clutch C2 is coupled so as to rotate the pump impeller 11 and the turbine runner 12 together so as to eliminate the rotational speed difference (slip) between the pump impeller 11 and the turbine runner 12 and increase the transmission efficiency. It is a clutch. Therefore, when the lockup clutch C2 is engaged, the torque converter TC transmits the driving force of the driving force source directly to the transmission device TM (input shaft I) without using oil. In the present embodiment, the torque converter TC is supplied with oil regulated by the first hydraulic control device VB1, and the lockup clutch C2 is engaged or released by the hydraulic pressure supplied from the first hydraulic control device VB1. To do.

  Further, the drive device 1 includes a hydraulic pump OP that is drivingly connected to the input side rotating member (pump impeller 11) side of the torque converter TC. The hydraulic pump OP is driven by the rotational driving force transmitted from the driving force source, sucks the oil stored in the oil storage unit OT1 to generate hydraulic pressure, and generates the first hydraulic control device VB1 and the second hydraulic control device. Supply to VB2.

  A transmission TM is drivingly connected to an input shaft I as an output shaft of the torque converter TC. In the present embodiment, the transmission apparatus TM is a stepped automatic transmission apparatus having a plurality of shift stages having different speed ratios. The transmission apparatus TM includes a gear mechanism such as a planetary gear mechanism and a plurality of friction engagement elements in order to form the plurality of shift stages. In this example, the plurality of friction engagement elements are engagement elements such as clutches and brakes each having a friction material. Each of the plurality of friction engagement elements is supplied with oil regulated by the first hydraulic control device VB1, and is engaged or released. As such a friction engagement element, for example, a wet multi-plate clutch or a wet multi-plate brake is preferably used. The torque transmitted from the transmission apparatus TM to the output shaft O is distributed and transmitted to the left and right wheels via the output differential gear mechanism.

2. Case of Drive Device Each component of the drive device 1 such as the rotating electrical machine MG, the torque converter TC, the transmission device TM, and the input shaft I is housed in a substantially cylindrical case. In the present embodiment, as shown in FIG. 1, the case of the drive device 1 includes a first case CS1 that mainly houses the transmission TM and the torque converter TC, and the internal combustion engine IE side with respect to the first case CS1. And a second case CS2 that mainly accommodates the rotary electric machine MG, the internal combustion engine separation clutch C1, and the internal combustion engine connection shaft EC.

  The first case CS1 includes a substantially cylindrical first peripheral wall 21a, an intermediate partition wall 21b provided between the torque converter TC and the transmission device TM in the axial direction, and the output shaft O side from the transmission device TM in the axial direction. And an output side end partition wall 21c provided on the right side in FIG.

  The second case CS2 includes a substantially cylindrical second peripheral wall 22a, an input side end partition wall 22b provided on the internal combustion engine IE side (left side in FIG. 1) from the rotating electrical machine MG in the axial direction, and an input side end partition wall. A cylindrical protrusion 22c protruding in the axial direction from the radial center of 22b. The rotary electric machine MG, the internal combustion engine separation clutch C1, and the torque converter TC are housed in the space between the input side end partition wall 22b and the intermediate partition wall 21b in the case of the drive device 1, and the intermediate partition wall 21b and the output side end section are accommodated. The transmission TM is accommodated in a space between the partition wall 21c.

  As will be described later, the first hydraulic control device VB1 and the first oil pan 51 are attached to the lower portion of the first case CS1, and the second hydraulic control device VB2 and the second oil pan 52 are attached to the lower portion of the second case CS2. It is attached. Here, the second hydraulic control device VB2 is separated from the first hydraulic control device VB1, and is disposed below the upper end portion 83 of the first hydraulic control device VB1. Also, an oil-tight first drain oil passage PE1 is provided in the wall surface of the second case CS2, and the oil-tight second drain oil extends in the wall surface from the second case CS2 to the first case CS1. A path PE2 is provided.

3. Hydraulic Control System Next, the configuration of the hydraulic control system of the drive device 1 will be described with reference to FIG. As described above, the drive device 1 is separated from the first hydraulic control device VB1 provided with the transmission hydraulic control valve 90 for controlling the hydraulic pressure supplied to the transmission TM and the first hydraulic control device VB1. A second hydraulic control device VB2 provided below the upper end portion 83 of the one hydraulic control device VB1 and provided with an engagement device hydraulic control valve 93 for controlling the hydraulic pressure supplied to the internal combustion engine separation clutch C1. Yes. And the drive device 1 produces | generates oil_pressure | hydraulic by attracting the oil storage part OT1 which stores the oil supplied to 1st hydraulic control apparatus VB1 and 2nd hydraulic control apparatus VB2, and the oil stored by the oil storage part OT1. And a hydraulic pump OP that supplies the first hydraulic control device VB1 and the second hydraulic control device VB2.

  The first hydraulic control device VB1 is accommodated in the oil reservoir OT1, and the second hydraulic control device VB2 is accommodated in an oil tight chamber OT2 formed in an oil tight manner outside the oil reservoir OT1. The driving device 1 sends the oil discharged from the internal combustion engine separation clutch C1 to the oil tight chamber OT2, and the oil discharged from the oil tight chamber OT2 to the oil reservoir OT1. Oil-tight second discharge oil passage PE2.

  When the internal combustion engine separation clutch C1 is provided along with the hybrid as in the present embodiment, a hydraulic control system for the internal combustion engine separation clutch C1 is required. Unlike the present embodiment, when the hydraulic control system for the internal combustion engine separating clutch C1 is integrated with a hydraulic control system such as the transmission TM to constitute an integrated hydraulic control system, the hydraulic control system is enlarged. To do. Since the space below the case of the drive device 1 to which the hydraulic control device for the transmission TM or the like is attached is limited, the hydraulic control device is enlarged for the hydraulic control system for the internal combustion engine separation clutch C1. It is not easy. In addition, when the hydraulic control system for the internal combustion engine separation clutch C1 is integrated into a hydraulic control system such as the transmission TM, the hydraulic control apparatus may be complicated and the design and manufacturing costs may increase. When only the hydraulic control system for the internal combustion engine separation clutch C1 is changed in design, it is necessary to design including the hydraulic control system for the transmission TM because of the integration. May increase.

  In the present embodiment, as described above, the oil-tight chamber OT2 is formed in an oil-tight manner outside the oil reservoir OT1. Therefore, it is possible to suppress the oil reservoir OT1 from being elongated in the direction of the device axis X1 as compared with the configuration in which the first hydraulic controller VB1 and the second hydraulic controller VB2 are accommodated in the oil reservoir OT1. As a result, it is possible to suppress the oil in the oil reservoir OT1 from moving greatly due to the acceleration / deceleration of the vehicle, and the hydraulic pump OP from being able to properly suck the oil.

  In the present embodiment, as described above, the engagement device hydraulic control valve 93 for the internal combustion engine separation clutch C1 is separated from the first hydraulic control device VB1 for the transmission TM and provided in the second hydraulic control device VB2. With this configuration, it becomes easy to secure a mounting space for the hydraulic control device for the internal combustion engine separation clutch C1, and the increase in the design and manufacturing cost of the hydraulic control device is suppressed as compared with the case of integration. it can.

In this way, when the engagement device hydraulic control valve 93 for the internal combustion engine separation clutch C1 is separated from the first hydraulic control device VB1 and provided in the second hydraulic control device VB2, the present embodiment is Differently, it is conceivable to include two sets of an oil reservoir that stores oil and a hydraulic pump that serves as a hydraulic pressure supply source. When obtaining a driving force source from the input shaft I or the like in order to secure a driving force source of the hydraulic pump provided on the second hydraulic control device VB2 side, it is not easy to configure a driving force transmission mechanism, or an electric motor When a motor is provided, the cost is high.
In the present embodiment, since the oil reservoir OT1 and the hydraulic pump OP that are common to the first hydraulic control device VB1 and the second hydraulic control device VB2 are provided, an increase in manufacturing cost can be suppressed.

  Thus, by providing the common oil reservoir OT1 and the hydraulic pump OP, the oil discharged from the internal combustion engine separation clutch C1 after being supplied from the second hydraulic control device VB2 to the internal combustion engine separation clutch C1, and the first It is necessary to drain the oil drained from the two hydraulic control device VB2 to the common oil reservoir OT1 and circulate the oil.

In the present embodiment, as described above, the oil-tight first discharged oil passage PE1 for sending the oil discharged from the internal combustion engine separation clutch C1 to the oil-tight chamber OT2, and the oil discharged from the oil-tight chamber OT2 are used as oil. Since the oil-tight second exhaust oil passage PE2 for sending to the reservoir OT1 is provided, the exhaust oil passage from the internal combustion engine separation clutch C1 to the oil reservoir OT1 is oil-tight. Naturally, the supply oil path from the second hydraulic control device VB2 to the internal combustion engine separation clutch C1 is also oil-tight. Therefore, the oil supplied from the second hydraulic control device VB2 to the internal combustion engine separation clutch C1 is discharged to the oil-tight chamber OT2 through the first discharge oil passage PE1 at a pressure corresponding to the supply pressure, and from the oil-tight chamber OT2 The oil is delivered to the oil reservoir OT1 through the two-discharge oil passage PE2.
Further, since the second hydraulic control device VB2 is accommodated in the oil tight chamber OT2, the oil drained from the second hydraulic control device VB2 is discharged into the oil tight chamber OT2, and the oil is supplied by the above supply pressure and drain pressure. It is sent to the oil reservoir OT1 through the dense second drain oil passage PE2.

  Here, since the pressure corresponding to the supply pressure is the pressure of the oil discharged from the internal combustion engine separation clutch C1, it is at least lower than the drain pressure. For this reason, it is possible to prevent the oil from flowing back through the drain oil passage of the engagement device hydraulic control valve 93 by the pressure corresponding to the supply pressure acting in the oil tight chamber OT2.

  As a result, the oil discharge oil passage discharged from the internal combustion engine separation clutch C1 and the oil discharge oil passage drained from the second hydraulic control device VB2 are shared by the oil tight chamber OT2 and the second discharge oil passage PE2. Manufacturing cost can be reduced. Then, the oil discharged from the internal combustion engine separation clutch C1 and the oil drained from the second hydraulic control device VB2 are supplied to the oil reservoir OT1 by using the supply pressure and the drain pressure through the oil-tight oil passage. Can send. Therefore, there is no need to provide a hydraulic pump for sending oil, and an increase in manufacturing cost can be suppressed.

  When the second hydraulic control device VB2 is disposed below the upper end portion 83 of the first hydraulic control device VB1 as in the present embodiment, normally, an oil-tight chamber that houses the second hydraulic control device VB2 In order to send the oil of OT2 to the oil reservoir OT1 housing the first hydraulic control device VB1, it is necessary to send the oil upward by a predetermined height difference, and a hydraulic pressure larger than the height difference is required. . According to the present embodiment, as described above, the supply pressure and the drain pressure can be used by the oil-tight discharge oil passage, so that a hydraulic pressure with a high and low difference can be generated, and the oil-tight chamber OT2 can provide oil. Oil can be sent to the reservoir OT1. Therefore, even if the height difference occurs, there is no need to provide a hydraulic pump for sending oil, and an increase in manufacturing cost can be suppressed.

In the present embodiment, the oil-tight chamber OT2 is located above either the oil level 80 of the oil stored in the oil storage unit OT1 or the opening 81 on the oil storage unit OT1 side of the second discharge oil passage PE2. It is arranged below. In the example shown in FIG. 2, the opening 81 of the second discharge oil passage PE2 is located above the oil level 80, and the entire oil-tight chamber OT2 is more than the opening 81 of the second discharge oil passage PE2. It is arranged below. Here, the oil level 80 is an oil level in a state in which the drive device 1 is filled with a specified amount of oil recommended in a service manual or the like.
Or the structure arrange | positioned below the opening part 81 of the 2nd discharge | emission oil path PE2 may be sufficient as the oil-tight chamber OT2. In this case, the oil level 80 may be above or below the opening 81. Further, the opening 81 of the second discharge oil passage PE2 may be arranged below the oil level 80. In this case, the oil tight chamber OT <b> 2 is disposed below the oil level 80.

  As in the present embodiment, the oil tight chamber OT2 is disposed below the oil level 80 of the oil reservoir OT1 and the opening 81 on the oil reservoir OT1 side of the second discharged oil passage PE2 below the one located above. Then, the oil-tight chamber OT2 is filled with oil up to the upper part thereof. Then, the upper part of the oil filled in the oil tight chamber OT2 is located below the oil level 80 or the opening 81, and the upper part of the oil filled in the oil tight chamber OT2 A difference in height occurs between the oil level 80 and the opening 81 that is located above. Therefore, it is necessary to send the oil in the oil tight chamber OT2 upward by this height difference, and a hydraulic pressure larger than this height difference is required. As described above, according to the present embodiment, the supply pressure and the drain pressure can be used by the oil-tight discharge oil passage, so that the hydraulic pressure for sending the oil upward is generated by the difference in height. The oil can be sent from the oil tight chamber OT2 to the oil reservoir OT1.

  Also, as in the example shown in FIG. 2, when a height difference occurs between the upper part of the oil filled in the oil tight chamber OT <b> 2 and the opening 81, the predetermined height difference defined by the hardware configuration is Therefore, the hydraulic pressure acting on the second discharged oil passage PE2 is stabilized, and fluctuations in the flow rate of the oil flowing through the second discharged oil passage PE2 can be suppressed. Therefore, the fluctuation | variation of the flow volume of the oil which circulates through the hydraulic control system for internal combustion engine separation clutch C1 can be suppressed. Thereby, for example, fluctuations in the cooling performance of the friction member 100 of the internal combustion engine separation clutch C1 can be suppressed, and fluctuations in the engagement pressure of the internal combustion engine separation clutch C1 can be suppressed.

  In the present embodiment, as described above, the first hydraulic control device VB1 is attached to the lower part of the first case CS1 that houses the transmission TM, and the second hydraulic control device VB2 includes the rotating electrical machine MG and the internal combustion engine separation clutch. It is attached to the lower part of the second case CS2 that houses C1. The first drain oil passage PE1 is provided in the second case CS2, and the second drain oil passage PE2 extends from the second case CS2 to the first case CS1 in the second case CS2 and the first case CS1. Is provided. In the present embodiment, the first discharge oil passage PE1 and the second discharge oil passage PE2 are formed in a tubular shape in the wall surfaces of the first case CS1 and the second case CS2, and are oil-tight oil passages.

Thus, the first hydraulic control device VB1 for the transmission TM is attached to the lower part of the first case CS1 that houses the transmission TM, and the second hydraulic control device VB2 for the internal combustion engine separation clutch C1 is an internal combustion engine separation. It is attached to the lower part of the second case CS2 that houses the clutch C1. As a result, the transmission TM and the first hydraulic control device VB1 and the internal combustion engine separation clutch C1 and the second hydraulic control device VB2 can be arranged close to each other and formed between them. The oil passage can be shortened and simplified.
In addition, since the first drain oil passage PE1 is provided in the second case CS2 to which the second hydraulic control device VB2 is attached, the first drain oil passage PE1 enters the second case CS2 from the vicinity of the attachment portion of the second hydraulic control device VB2. The case can be used effectively to provide the first discharge oil passage PE1, and the number of parts for forming the oil passage can be reduced. Moreover, since the oil passage is formed in the second case CS2, oil tightness can be easily ensured.
The second drain oil passage PE2 extends from the second case CS2 to which the second hydraulic control device VB2 is attached to the first case CS1 to which the first hydraulic control device VB1 is attached. Since it is provided in one case CS1, the case covers the second case CS2 and the first case CS1 from the vicinity of the attachment portion of the second hydraulic control device VB2 to the vicinity of the attachment portion of the first hydraulic control device VB1. Effectively, the second discharge oil passage PE2 can be provided, and the number of parts for forming the oil passage can be reduced. Moreover, since the oil path is formed in the second case CS2 and the first case CS1, oil tightness can be easily ensured.

  Further, since the second hydraulic control device VB2 is disposed at the lower part of the second case CS2 in which the rotating electrical machine MG is accommodated, the second hydraulic control device VB2 is disposed away from the device axis X1 by the radial width of the rotating electrical machine MG. ing. The first hydraulic control device VB1 is disposed away from the device axis X1 by the radial width of the transmission device TM. Here, the outer diameter of the rotating electrical machine MG is larger than the outer diameter of the transmission apparatus TM. Therefore, the second hydraulic control device VB2 is disposed below the upper end portion 83 of the first hydraulic control device VB1. Even in such a case, as described above, oil can be sent from the oil-tight chamber OT2 to the oil reservoir OT1 without providing a hydraulic pump. In addition, since the height difference can be allowed as described above, it is possible to prevent the dimensional design such as the radial width of the rotating electrical machine MG from being restricted due to the arrangement of the second hydraulic control device VB2.

Further, the drive device 1 supplies the oil-tight first supply oil for sending the oil regulated by the second hydraulic control device VB2 to the first oil chamber 96 in which the friction member of the internal combustion engine separation clutch C1 is accommodated. A path PI1 and an oil-tight third supply oil path PI3 for sending the oil regulated by the second hydraulic control device VB2 to the hydraulic cylinder 97 of the internal combustion engine separation clutch C1 are provided. Further, the drive device 1 includes an oil-tight second supply oil passage PI2 for sending the oil boosted by the hydraulic pump OP to the second hydraulic control device VB2.
In the present embodiment, the first supply oil passage PI1 and the third supply oil passage PI3 are provided in the second case CS2, similarly to the first discharge oil passage PE1, and the second supply oil passage PI2 Similarly to the oil passage PE2, the second case CS2 and the first case CS1 are provided from the second case CS2 to the first case CS1. In the present embodiment, the first supply oil passage PI1, the second supply oil passage PI2, and the third supply oil passage PI3 are formed in a tubular shape in the wall surface of the first case CS1 or the second case CS2, and are oil-tight. It is considered as an oil passage.

As a result, the first supply oil passage PI1 and the third supply oil passage PI3 are effectively used in the second case CS2 from the mounting portion of the second hydraulic control device VB2 in the same manner as the first discharge oil passage PE1. Thus, the first supply oil passage PI1 and the third supply oil passage PI3 can be provided, and the number of parts for forming the oil passage can be reduced. Moreover, since the oil passage is formed in the second case CS2, oil tightness can be easily ensured.
In addition, the second supply oil passage PI2 has a first hydraulic control device VB1 attached from the second case CS2 to which the second hydraulic control device VB2 is attached, like the second discharge oil passage PE2. Since it is provided in the second case CS2 and the first case CS1 over the case CS1, the second supply oil passage PI2 can be provided by effectively using the case, and the oil passage can be formed. The number of parts can be reduced. Moreover, since the oil path is formed in the second case CS2 and the first case CS1, oil tightness can be easily ensured.

  In the present embodiment, the oil reservoir OT1 is configured to be surrounded by a first case CS1 and a first oil pan 51 attached to the lower part of the first case CS1. The oil-tight chamber OT2 is configured to be surrounded by a second case CS2 and a second oil pan 52 attached to the lower portion of the second case CS2.

  Thereby, oil storage part OT1 can be formed using the 1st case CS1 effectively. In addition, since the oil reservoir OT1 can be adjacent to the first case CS1, communication between the oil reservoir OT1 and the second drain oil passage PE2 provided in the first case CS1 can be easily realized. . Similarly, the oil-tight chamber OT2 can be formed by effectively using the second case CS2. Further, since the oil-tight chamber OT2 can be adjacent to the second case CS2, communication between the oil-tight chamber OT2 and the first exhaust oil passage PE1 and the second exhaust oil passage PE2 provided in the second case CS2 is facilitated. Can be realized.

  Further, since the first oil pan 51 constituting the oil reservoir OT1 and the second oil pan 52 constituting the oil-tight chamber OT2 are configured separately, the first oil pan 51 is obtained by acceleration / deceleration of the vehicle. It is possible to suppress the movement of the oil inside the hydraulic pump OP and prevent the hydraulic pump OP from properly sucking the oil.

  In the present embodiment, the drive device 1 includes a converter hydraulic control valve 91 that controls the hydraulic pressure supplied to the torque converter TC. The converter hydraulic control valve 91 is provided in the first hydraulic control device VB1. The converter hydraulic control valve 91 is composed of one or a plurality of hydraulic control valves.

  In the present embodiment, the drive device 1 includes a pressure regulator valve 92 that regulates the line pressure that is the output pressure of the hydraulic pump OP. The pressure regulator valve 92 is provided in the first hydraulic control device VB1.

The line pressure that is the output pressure of the hydraulic pump OP is supplied to the transmission hydraulic control valve 90 and the converter hydraulic control valve 91 provided in the first hydraulic control device VB1.
The transmission hydraulic pressure control valve 90 controls the hydraulic pressure supplied to the transmission TM by reducing the line pressure. The oil supplied from the transmission hydraulic control valve 90 to the transmission TM is used for operation of a hydraulic servo mechanism such as a friction engagement element provided in the transmission TM and cooling of the friction engagement element, and is provided in the transmission TM. It is also used for lubrication and cooling of gear mechanisms and bearings. And the oil supplied to transmission TM is discharged to oil storage part OT1 via an oil passage not shown. Note that the transmission hydraulic control valve 90 corresponds to each hydraulic supply element and includes a single hydraulic control valve or a plurality of hydraulic control valves.
The converter hydraulic pressure control valve 91 controls the hydraulic pressure supplied to the torque converter TC by reducing the line pressure. The oil supplied from the converter hydraulic control valve 91 to the torque converter TC via an oil passage (not shown) is used for the operation and cooling of the lock-up clutch C2 of the torque converter TC, and for transmitting the driving force in the torque converter TC. Used as oil. And the oil supplied to torque converter TC is discharged | emitted to the oil storage part OT1 via the oil path not shown.

  Further, the oil of the line pressure that is the output pressure of the hydraulic pump OP is sent to the second hydraulic control device VB2 provided with the engagement device hydraulic control valve 93 through the second supply oil passage PI2. In the example shown in FIG. 2, the second supply oil passage PI2 is an oil passage for sending line pressure oil from the first hydraulic control device VB1 to the second hydraulic control device VB2. The second supply oil passage PI2 may be an oil passage that directly sends the oil of the line pressure from the hydraulic pump OP to the second hydraulic control device VB2 without going through the first hydraulic control device VB1. .

  In the present embodiment, as shown in FIG. 2, the engagement device hydraulic control valve 93 includes a cylinder hydraulic control valve 94 that controls the hydraulic pressure supplied to the hydraulic cylinder 97 of the internal combustion engine separation clutch C1, and an internal combustion engine separation clutch C1. A circulation hydraulic pressure control valve 95 for controlling the hydraulic pressure supplied to the first oil chamber 96 in which a friction member or the like is accommodated.

  The cylinder hydraulic control valve 94 controls (regulates) the hydraulic pressure supplied to the hydraulic cylinder 97 of the internal combustion engine separation clutch C1 by reducing the line pressure. Then, the oil regulated by the cylinder hydraulic control valve 94 is sent to the hydraulic cylinder 97 of the internal combustion engine separation clutch C1 through the third supply oil passage PI3. Note that the third supply oil passage PI3 also serves as a discharge oil passage for the oil supplied to the hydraulic cylinder 97 of the internal combustion engine separation clutch C1. The oil drained from the cylinder hydraulic control valve 94 is directly discharged to the oil tight chamber OT2. In the example shown in FIG. 2, a linear solenoid valve that is a hydraulic control valve having the functions of a solenoid and a pressure regulating valve (pressure reducing valve) is used as the cylinder hydraulic control valve 94. As the cylinder hydraulic control valve 94, a DUTY solenoid valve and a pressure regulating valve (pressure reducing valve) in which a solenoid function and a pressure regulating valve (pressure reducing valve) function are separated may be used.

  The circulation hydraulic pressure control valve 95 reduces the line pressure and controls (regulates) the hydraulic pressure supplied to the first oil chamber 96 of the internal combustion engine separation clutch C1. Then, the oil regulated by the circulation hydraulic control valve 95 is sent to the first oil chamber 96 of the internal combustion engine separation clutch C1 through the first supply oil passage PI1. The first oil chamber 96 accommodates the friction member 100 and the like of the internal combustion engine separation clutch C1, and is formed in an oil-tight manner. In the first oil chamber 96, the oil supplied to the supply port 98 of the first oil chamber 96 flows (circulates) through a predetermined path (circulation path) in the first oil chamber 96, and the first oil chamber 96. It is configured to be discharged from the discharge port 99. The circulation path of the first oil chamber 96 is configured such that oil flows along the friction member 100. Therefore, the oil supplied to the first oil chamber 96 circulates in the first oil chamber 96 and cools the friction member 100. The oil that circulates in the first oil chamber 96 and is discharged from the first oil chamber 96 is sent to the oil-tight chamber OT2 through the first discharge oil passage PE1. Further, the oil drained from the circulation hydraulic control valve 95 is directly discharged to the oil tight chamber OT2. In the example shown in FIG. 2, a pressure regulating valve (pressure reducing valve) of the type that simultaneously opens and closes the oil passage from the original pressure and opens and closes the oil passage to the drain is used as the circulation hydraulic pressure control valve 95. Note that a pressure regulating valve (pressure reducing valve) of a type that only opens and closes an oil passage to the drain may be used as the circulation hydraulic control valve 95.

4). Detailed Configuration of Drive Device Next, a detailed configuration of each part of the drive device 1 according to the present embodiment will be described with reference to FIGS. 3 and 4. 3 and 4 show a substantially vertical section of a portion below the device axis X1 and closer to the internal combustion engine IE than the transmission TM. FIG. 3 shows a discharge oil passage from the internal combustion engine separation clutch C1 or the second hydraulic control device VB2, and FIG. 4 shows a supply oil passage to the internal combustion engine separation clutch C1 or the second hydraulic control device VB2. Yes. The configuration shown in FIGS. 3 and 4 is the same except for the configuration of these oil passages. Hereinafter, a detailed configuration of each part of the drive device 1 will be described mainly with reference to FIG.

  As described above, the drive device 1 includes the rotating electrical machine MG, the torque converter TC, the transmission TM, the internal combustion engine separation clutch C1, the lockup clutch C2, the internal combustion engine coupling shaft EC, the input shaft I, and the output shaft O. . In the present embodiment, the internal combustion engine separation clutch C1 is disposed on the radially inner side of the rotating electrical machine MG, and the lockup clutch C2 is disposed in the housing 13 of the torque converter TC. The rotating electrical machine MG, the internal combustion engine separation clutch C1, the torque converter TC, and the transmission device TM are arranged in this order along the axial direction from the internal combustion engine IE side. Further, the internal combustion engine connecting shaft EC, the input shaft I, and the output shaft O are arranged in this order along the axial direction from the internal combustion engine IE side. Each of these components is accommodated in a case of a drive device as a non-rotating member. Hereinafter, the configuration of each part of the drive device 1 will be described in detail.

4-1. Case of drive device 4-1-1. As described above, the second case CS2 is roughly the cylindrical second peripheral wall 22a, the input side end partition wall 22b provided on the internal combustion engine IE side, and the diameter of the input side end partition wall 22b. And a cylindrical protrusion 22c protruding in the axial direction from the center of the direction.
The input-side end partition wall 22b has a shape extending at least in the radial direction, and here is a substantially flat disk-shaped wall portion extending in the radial direction and the circumferential direction. Further, a cylindrical projecting portion 22c that projects in the axial direction toward the torque converter TC is provided at the radial center of the input side end partition 22b. In this example, the cylindrical projecting portion 22c is a cylindrical boss projecting from the radially inner end of the input side end partition 22b toward the torque converter TC. A through hole penetrating in the axial direction is formed in the central portion in the radial direction of the cylindrical protrusion 22c, and the internal combustion engine connecting shaft EC is inserted through the through hole. In the present embodiment, a third bearing 67 is disposed between the inner peripheral surface of the cylindrical protrusion 22c and the internal combustion engine connection shaft EC. The internal combustion engine connecting shaft EC is supported by the third bearing 67 so as to be rotatable with respect to the second case CS2. In the present embodiment, a needle bearing is used as the third bearing 67. The space between the inner peripheral surface of the cylindrical protrusion 22c and the internal combustion engine connecting shaft EC is closed in an oil-tight state by an oil seal 68 on the internal combustion engine IE side.

In the wall surface of the second case CS2, as described above, the oil tight chamber OT2 or the second hydraulic control device VB2 and the internal combustion engine separation clutch C1 are communicated with each other through an oil tight oil passage. One discharge oil passage PE1, a first supply oil passage PI1, and a third supply oil passage PI3 are formed.
In the example shown in FIG. 3, the first exhaust oil passage PE1 has the wall surfaces of the input side end partition wall 22b and the cylindrical projecting portion 22c so that the internal combustion engine separation clutch C1 and the oil tight chamber OT2 communicate with each other through the oil passage. It is formed in a tubular shape inside. Specifically, as shown by the arrows in FIG. 3, the oil discharged from the discharge port 99 of the first oil chamber 96 passes through the oil passage 110 formed inside the internal combustion engine connecting shaft EC, and then the cylinder. The first protruding oil passage PE1 formed in the wall surface of the protruding portion 22c and the input side end partition wall 22b passes through the first discharged oil passage PE1 and is sent to the oil tight chamber OT2.

In the example shown in FIG. 4, the first supply oil passage PI1 has a second peripheral wall 22a and an input-side end partition wall 22b so that the internal combustion engine separation clutch C1 and the second hydraulic control device VB2 communicate with each other through the oil passage. And it is formed in the tubular shape in the wall surface of the cylindrical protrusion 22c. The first supply oil passage PI1 is disposed at a position in the circumferential direction different from the first discharge oil passage PE1 in the cylindrical projecting portion 22c and the input side end partition wall 22b.
Specifically, as shown by the arrows in FIG. 4, the oil sent from the second hydraulic control device VB2 is formed in the wall surfaces of the second peripheral wall 22a, the input side end partition wall 22b, and the cylindrical protrusion 22c. After passing through the first supply oil passage PI <b> 1, the oil is supplied from the end of the cylindrical protrusion 22 c to the supply port 98 of the first oil chamber 96. The first supply oil passage PI1 has a second peripheral wall so as to communicate between the lower end portion of the first supply oil passage PI1 formed in the wall surface of the input side end partition wall 22b and the second hydraulic control device VB2. It is formed in the lower outer wall surface of 22a so as to open downward. A second hydraulic control device VB2 is attached to the lower side of the second peripheral wall 22a where the oil passage is formed, and the lower opening of the first supply oil passage PI1 is formed by the upper end surface of the second hydraulic control device VB2. An oil-tight oil passage is formed.

  The third supply oil passage PI3 is not shown in FIGS. 3 and 4, but, like the first supply oil passage PI1, is provided between the hydraulic cylinder 97 of the internal combustion engine separation clutch C1 and the second hydraulic control device VB2. Are formed in a tubular shape within the wall surfaces of the second peripheral wall 22a, the input side end partition wall 22b, and the cylindrical protrusion 22c.

  Further, in the wall surface of the second case CS2, the oil-tight chamber OT2 or the second hydraulic control device VB2, and the oil storage unit OT1 or the first hydraulic control device VB1 are extended over the first case CS1 and the second case CS2. The second exhaust oil passage PE2 and the second supply oil passage PI2 are formed so as to communicate with each other through an oil-tight oil passage.

  In the example shown in FIG. 3, the second discharge oil passage PE2 is formed in a tubular shape in the wall surface of the second peripheral wall 22a so that the oil tight chamber OT2 and the oil reservoir OT1 communicate with each other through the oil passage. Specifically, the first discharge oil passage PE1 is formed so as to extend in the axial direction from the lower surface of the second peripheral wall 22a where the oil-tight chamber OT2 is disposed to the first case CS1 side in the wall surface of the second peripheral wall 22a. ing.

  In the example shown in FIG. 4, the second supply oil passage PI2 has a tubular shape in the wall surface of the second peripheral wall 22a so that the second hydraulic control device VB2 and the first hydraulic control device VB1 communicate with each other through the oil passage. Is formed. Specifically, the second supply oil passage PI2 extends in the axial direction within the wall surface of the second peripheral wall 22a from the first case CS1 side to the lower surface of the second peripheral wall 22a where the second hydraulic control device VB2 is disposed. Is formed.

4-1-2. As described above, the first case CS1 is roughly formed of a cylindrical first peripheral wall 21a, an intermediate partition wall 21b provided between the torque converter TC and the transmission device TM in the axial direction, and a shaft. And an output side end partition wall 21c (see FIGS. 1 and 2) provided on the output shaft O side of the transmission TM in the direction.
The intermediate partition wall 21b has a shape extending at least in the radial direction, and here is a substantially flat disk-shaped wall portion extending in the radial direction and the circumferential direction. Moreover, in this embodiment, the intermediate partition 21b is comprised as a member different from the 1st surrounding wall 21a, and is fastened by the level | step-difference part formed in the internal peripheral surface of the 1st surrounding wall 21a with fastening members, such as a volt | bolt. It is fixed. The intermediate partition wall 21b is provided with a hydraulic pump OP. Here, the hydraulic pump cover 41 is attached to the surface of the intermediate partition wall 21b on the torque converter TC side. A hydraulic pump chamber 43 that accommodates the hydraulic pump rotor 42 is formed between the intermediate partition wall 21 b and the hydraulic pump cover 41. These hydraulic pump rotor 42 and hydraulic pump chamber 43 constitute a hydraulic pump OP. The hydraulic pump cover 41 is fastened and fixed to the intermediate partition wall 21b by a fastening member such as a bolt while being in contact with the intermediate partition wall 21b from the torque converter TC side. A through-hole penetrating in the axial direction is formed in the central portion in the radial direction of the intermediate partition wall 21b and the hydraulic pump cover 41, and the input shaft I is inserted through the through-hole. Further, the hydraulic pump drive shaft 46 and the stator support shaft 16 are also inserted into the through hole. The hydraulic pump drive shaft 46 is a cylindrical shaft portion that rotates integrally with the housing 13 of the torque converter TC, is disposed on the radially outer side of the input shaft I, and is drivingly connected to the hydraulic pump rotor 42. The stator support shaft 16 is a cylindrical shaft portion that is fixed to the intermediate partition wall 21b and supports the stator 14 of the torque converter TC, and is disposed between the input shaft I and the hydraulic pump drive shaft 46 in the radial direction. Yes. The intermediate partition wall 21b and the hydraulic pump cover 41 are formed with a first intake oil passage L1 that is an intake oil passage of the hydraulic pump OP and a first discharge oil passage L2 that is a discharge oil passage (see FIG. 2). .

  The hydraulic pump rotor 42 of the hydraulic pump OP is drivingly connected to the hydraulic pump drive shaft 46 by spline engagement or the like. Therefore, the hydraulic pump rotor 42 is configured to rotate integrally with the pump impeller 11 of the torque converter TC and the rotor Ro of the rotating electrical machine MG. In the present embodiment, the hydraulic pump OP is an inscribed gear pump having an inner rotor and an outer rotor as the hydraulic pump rotor 42. The hydraulic pump OP is arranged coaxially with the rotating electrical machine MG, the torque converter TC, and the transmission TM, and is connected so that the inner rotor rotates integrally with the pump impeller 11 of the torque converter TC at the center in the radial direction. Has been. Accordingly, as the pump impeller 11 rotates, the hydraulic pump OP discharges oil to generate a hydraulic pressure, which is supplied to the first hydraulic control device VB1 and the second hydraulic control device VB2.

  As shown in FIG. 2, the hydraulic pump OP sucks oil from the oil reservoir OT1 through a strainer (not shown) and the first suction oil passage L1, and discharges the oil to the first discharge oil passage L2. The oil discharged from the hydraulic pump OP is sent to the first hydraulic control device VB1 through the first discharge oil passage L2. The pressure regulator valve 92 provided in the first hydraulic control device VB1 regulates the line pressure that is the output pressure of the hydraulic pump OP. Therefore, the oil pressure of each oil passage such as the first discharge oil passage L2 communicating with the discharge port of the hydraulic pump OP is regulated as a line pressure by the pressure regulator valve 92. Then, the oil having the line pressure is supplied to the transmission hydraulic control valve 90 and the second hydraulic control device VB2 provided in the first hydraulic control device VB1 via each oil passage.

  Further, in the wall surface of the first case CS1, the oil tight chamber OT2 or the second hydraulic control device VB2 and the oil storage unit OT1 or the first hydraulic control device VB1 are extended over the first case CS1 and the second case CS2. The second exhaust oil passage PE2 and the second supply oil passage PI2 are formed so as to communicate with each other through an oil-tight oil passage.

In the example shown in FIG. 3, the second exhaust oil passage PE2 is formed in a tubular shape in the wall surface of the first peripheral wall 21a so that the oil tight chamber OT2 and the oil reservoir OT1 communicate with each other through the oil passage. .
Specifically, the second drain oil passage PE2 is formed so as to extend from the end portion of the first peripheral wall 21a on the second case CS2 side toward the oil reservoir OT1 in the wall surface of the first peripheral wall 21a. Yes. The second oil discharge passage PE2 is open on the oil reservoir OT1 side, and an opening 81 on the oil reservoir OT1 side is formed. In the example shown in FIG. 3, the opening 81 of the second discharge oil passage PE2 is positioned above the oil level 80, and the oil tight chamber OT2 is below the opening 81 of the second discharge oil passage PE2. Has been placed.

  In the example shown in FIG. 4, the second supply oil passage PI2 is tubular in the wall surface of the first peripheral wall 21a so as to communicate between the second hydraulic control device VB2 and the first hydraulic control device VB1 through the oil passage. Is formed. Specifically, the second supply oil passage PI2 extends from the first hydraulic control device VB1 to the end of the first peripheral wall 21a on the second case CS2 side in the wall surface of the first peripheral wall 21a toward the oil-tight chamber OT2. It is formed to extend.

4-2. Rotating electric machine As shown in FIG. 3, the rotating electric machine MG is arranged closer to the internal combustion engine IE than the torque converter TC. In the present embodiment, the rotating electrical machine MG is disposed between the input-side end partition wall 22b and the torque converter TC in the axial direction. Further, the rotating electrical machine MG is disposed radially outward with respect to the internal combustion engine coupling shaft EC and the internal combustion engine separation clutch C1. The stator St of the rotating electrical machine MG is fixed to the second case CS2. The rotor Ro is supported by the second case CS2 in a rotatable state. The rotor Ro is connected to the pump impeller 11 and the housing 13 of the torque converter TC via the rotor support member 62 so as to rotate integrally. The rotor support member 62 is a member that extends at least in the radial direction and supports the rotor Ro. In the present embodiment, a cylindrical boss 62a is provided at the radially inner end of the rotor support member 62, and between the inner peripheral surface of the boss 62a and the cylindrical protrusion 22c of the second case CS2. A first bearing 61 is disposed on the front side. The rotor Ro and the rotor support member 62 are supported by the first bearing 61 so as to be rotatable with respect to the second case CS2. In the present embodiment, a ball bearing is used as the first bearing 61. In addition, a rotation sensor 63 is disposed between the rotor support member 62 and the input-side end partition wall 22b in the axial direction and outside the boss portion 62a in the radial direction. The rotation sensor 63 is a sensor that detects the rotational position of the rotor Ro of the rotating electrical machine MG, and a resolver or the like can be suitably used. Here, the sensor stator 63a of the rotation sensor 63 is fixed to the input side end partition wall 22b, and the sensor rotor 63b of the rotation sensor 63 is fixed to the boss portion 62a of the rotor support member 62.

4-3. Input Clutch As shown in FIG. 3, the internal combustion engine separation clutch C <b> 1 is arranged at a position inside the rotating electrical machine MG in a radial direction and having a portion overlapping the rotating electrical machine MG when viewed in the radial direction of the rotating electrical machine MG. Yes. Further, the internal combustion engine separation clutch C <b> 1 is disposed on the torque converter TC side in the axial direction with respect to the rotor support member 62. The internal combustion engine separation clutch C1 is an engagement device for selectively drivingly connecting the internal combustion engine connecting shaft EC, the rotary electric machine MG, and the pump impeller 11 of the torque converter TC. In the present embodiment, the internal combustion engine separation clutch C1 is a friction engagement device. An input clutch hub 71 that is an input side member of the internal combustion engine separation clutch C1 is provided integrally with the internal combustion engine coupling shaft EC. Specifically, the input clutch hub 71 is a disk-shaped member that is formed integrally with the internal combustion engine coupling shaft EC and extends radially outward from the end of the transmission engine TM side of the internal combustion engine coupling shaft EC. . An input clutch drum 72, which is an output side member of the internal combustion engine separation clutch C1, is connected to rotate integrally with the housing 13 of the torque converter TC and the rotor support member 62 of the rotating electrical machine MG. Specifically, the input clutch drum 72 is joined to the inner peripheral surface of the boss portion 62a of the rotor support member 62, and the outer periphery of the step portion 13b formed at the radial intermediate portion of the housing 13 of the torque converter TC. It is joined to the surface. The input clutch drum 72 also serves as a housing for the internal combustion engine separation clutch C1, and houses the input clutch hub 71, the piston 75, the friction member 100, and the like inside. The input clutch drum 72 is sealed at the joint with other members so that the internal oil does not leak outside, and the inside is in an oil-tight state.

The hydraulic cylinder 97 of the internal combustion engine separation clutch C1 is configured to be surrounded by an input clutch drum 72 that functions as a cylinder and a piston 75. The hydraulic cylinder 97 is formed oil-tight with a sealing material.
The first oil chamber 96 of the internal combustion engine separation clutch C1 accommodates the friction member 100 and the like of the internal combustion engine separation clutch C1, and is formed in an oil-tight manner. In the first oil chamber 96, as described above, the oil supplied to the supply port 98 of the first oil chamber 96 flows (circulates) through a predetermined path (circulation path) in the first oil chamber 96, and the first oil chamber 96 It is configured to be discharged from the discharge port 99 of the oil chamber 96. In the present embodiment, the supply port 98 of the first oil chamber 96 is formed by a gap between the input clutch hub 71 and the radially inner end of the input clutch drum 72. The oil supplied to the supply port 98 flows radially outward in a radially extending space (circulation path) formed between the piston 75 and the input clutch hub 71. The oil that has flowed outward in the radial direction flows through gaps (circulation paths) formed along the plurality of friction members 100. At this time, the friction member 100 is cooled. Thereafter, the oil flowing along the friction member 100 is directed radially inward in a radially extending space (circulation path) formed between the input clutch hub 71 and the first housing member 66 of the torque converter TC. Flowing. Then, oil is discharged from the discharge port 99 of the first oil chamber 96. In the space formed between the input clutch hub 71 and the first housing member 66, the discharge port 99 is a gap that is narrowed (squeezed) on the radially inner side. The gap of the discharge port 99 functions as an orifice, and the hydraulic pressure in the first oil chamber 96 becomes the hydraulic pressure regulated by the second hydraulic control device VB2.

  The oil discharged from the first oil chamber 96 is oil-tight chamber by the oil-tight first discharge oil passage PE1 provided in the wall surface of the cylindrical protruding portion 22c and the input side end partition wall 22b of the second case CS2. Sent to OT2. In the example shown in FIG. 3, the oil discharged from the discharge port 99 of the first oil chamber 96 is provided in an oil-tight space between the internal combustion engine connection shaft EC and the first housing member 66, the internal combustion engine connection shaft EC. The oil-tight oil passage 110, the oil-tight gap between the internal combustion engine connecting shaft EC and the cylindrical protrusion 22c of the second case CS2, and the first discharge oil passage PE1 and the cylindrical protrusion 22c. It flows through the communication port 111 communicating with the inner peripheral surface in order, and is discharged from the first oil chamber 96 to the first discharge oil passage PE1.

  On the other hand, as shown in FIG. 4, the oil pressure-regulated by the second hydraulic control device VB2 is placed in the wall surfaces of the second peripheral wall 22a, the input side end partition wall 22b, and the cylindrical protrusion 22c of the second case CS2. The oil is supplied to the first oil chamber 96 through the oil-tight first supply oil passage PI1. In the example shown in FIG. 4, the oil pressure-adjusted by the second hydraulic control device VB2 passes through the first supply oil passage PI1 and passes through the first supply oil passage PI1 that opens at the axial end of the cylindrical protrusion 22c. It exits from the open end, flows through an oil-tight gap between the cylindrical protrusion 22 c and the input clutch hub 71, and is supplied to the first oil chamber 96.

4-4. Torque Converter As shown in FIG. 3, the torque converter TC is disposed between the rotating electrical machine MG and the transmission TM in the axial direction. The torque converter TC includes a pump impeller 11, a turbine runner 12, a stator 14, and a housing 13 that accommodates them. In the present embodiment, the lockup clutch C2 and the damper 15 are also accommodated in the housing 13. The housing 13 is configured to rotate integrally with the pump impeller 11. Here, the pump impeller 11 is integrally provided inside the housing 13.

  In the present embodiment, the housing 13 is configured by joining a first housing member 66 on the rotating electrical machine MG side and a second housing member 65 on the transmission device TM side. The first housing member 66 is a cylindrical member formed so as to cover the rotating electrical machine MG side of the torque converter TC. In this example, the first housing member 66 is a stepped cylindrical member in which a step portion 13b is formed in a radially intermediate portion. ing. The inner peripheral surface of the input clutch drum 72 is joined to the outer peripheral surface of the stepped portion 13b, so that the housing 13 is connected to rotate integrally with the input clutch drum 72 of the internal combustion engine separation clutch C1. . A lockup clutch C2 is housed inside the stepped portion 13b in the radial direction. The second housing member 65 is a cover member formed so as to cover the transmission TM side of the torque converter TC, and in this example, an arc-shaped cross section in which a radial intermediate portion bulges toward the transmission TM. The annular member has a shape. A hydraulic pump drive shaft 46 that extends in the axial direction toward the transmission device TM is integrally provided at the radially inner end of the second housing member 65. The hydraulic pump drive shaft 46 is a cylindrical shaft portion that rotates integrally with the housing 13 of the torque converter TC, and is disposed coaxially with the input shaft I and radially outside the input shaft I. A second bearing 64 is disposed between the outer peripheral surface of the hydraulic pump drive shaft 46 and the inner peripheral surface of the through hole of the hydraulic pump cover 41. The hydraulic pump drive shaft 46 and the housing 13 of the torque converter TC are supported by the second bearing 64 so as to be rotatable with respect to the first case CS1. In the present embodiment, a needle bearing is used as the second bearing 64. An end of the hydraulic pump drive shaft 46 on the transmission device TM side is connected to rotate integrally with the hydraulic pump rotor 42 of the hydraulic pump OP. Here, the connection between the hydraulic pump drive shaft 46 and the hydraulic pump rotor 42 is performed by spline engagement.

  The first housing member 66 and the second housing member 65 are integrally joined by welding or the like. Further, when viewed as the drive device 1 as a whole, the rotor Ro of the rotating electrical machine MG that rotates integrally, the housing 13 of the torque converter TC, and the input clutch drum 72 of the internal combustion engine separation clutch C1 are arranged on the internal combustion engine connecting shaft EC side. It is rotatably supported by the case of the drive device 1 through one bearing 61, and is rotatably supported by the second case CS2 through the second bearing 64 on the transmission device TM side.

  The turbine runner 12 of the torque converter TC is disposed on the rotary electric machine MG side of the pump impeller 11 inside the housing 13 so as to face the pump impeller 11. The turbine runner 12 is coupled to rotate integrally with the input shaft I. Here, the radially inner end of the turbine runner 12 is spline-engaged with the input shaft I. The stator 14 of the torque converter TC is disposed between the pump impeller 11 and the turbine runner 12 in the axial direction. The stator 14 is supported on the stator support shaft 16 via a one-way clutch. As described above, the stator support shaft 16 is a cylindrical shaft portion and is fixed to the intermediate partition wall 21b on the transmission device TM side. The torque converter TC is capable of transmitting torque between the drive-side pump impeller 11 and the driven-side turbine runner 12 via oil filled in the housing 13.

  As shown in FIG. 3, the lock-up clutch C <b> 2 is disposed on the inner side in the radial direction of the stepped portion 13 b of the housing 13 and on the rotating electrical machine MG side in the axial direction with respect to the turbine runner 12. The lock-up clutch C2 is an engagement device for engaging the pump impeller 11 and the turbine runner 12 to stop transmission of the driving force via the oil and bring them into a direct connection state (lock-up state). . In the present embodiment, the lockup clutch C2 is a friction engagement device. A lockup clutch hub 73 that is an input side member of the lockup clutch C <b> 2 is provided to rotate integrally with the housing 13. Specifically, the lock-up clutch hub 73 is connected to the boss portion of the first housing member 66 of the housing 13 by spline engagement on the radially inner side. Further, a lockup clutch drum 74 that is an output side member of the lockup clutch C <b> 2 is drivingly connected to the turbine runner 12 and the input shaft I via the damper 15. Specifically, the lockup clutch drum 74 is formed integrally with the input side member 15 a of the damper 15. Note that the piston, the friction plate, and the like of the lock-up clutch C2 are also accommodated in the radially inner space of the step portion 13b. In the present embodiment, the lockup clutch C2 is disposed adjacent to the internal combustion engine separation clutch C1 in the axial direction with the first housing member 66 interposed therebetween.

  The damper 15 is disposed between the lockup clutch C2 and the turbine runner 12 in the axial direction. The damper 15 is provided to absorb the vibration of the driving force transmitted between the pump impeller 11 and the turbine runner 12 when the lockup clutch C2 is engaged. In this embodiment, the damper 15 is for vibration absorption provided between the input side member 15a and the output side member 15b configured to be relatively movable in the circumferential direction, and between the input side member 15a and the output side member 15b. It has a spring. The input side member 15a of the damper 15 is connected to rotate integrally with the lockup clutch drum 74 of the lockup clutch C2. Further, the output side member 15b of the damper 15 is connected so as to rotate integrally with the turbine runner 12 and the input shaft I.

4-5. Although not shown in FIG. 3, the transmission TM is arranged on the output shaft O side of the intermediate partition wall 21b, that is, on the opposite side (right side in FIG. 3) from the torque converter TC across the intermediate partition wall 21b. . In the present embodiment, the transmission apparatus TM is a stepped automatic transmission apparatus having a plurality of shift stages having different speed ratios.

4-6. First Hydraulic Control Device, First Oil Pan The first hydraulic control device VB1 is provided with a transmission hydraulic control valve 90 that controls the hydraulic pressure supplied to the transmission TM. In the present embodiment, as shown in FIG. 2, the first hydraulic control device VB1 controls the pressure regulator valve 92 that regulates the line pressure, and the hydraulic pressure that reduces the line pressure and supplies it to the transmission TM (regulation). ) And a converter hydraulic control valve 91 that controls (regulates) the hydraulic pressure supplied to the torque converter TC by reducing the line pressure. The first hydraulic control device VB1 is a hydraulic control valve including a valve body having a groove (oil passage) stretched like an ant's nest, and a spool, a spring, a solenoid, and the like attached in the valve body. And an orifice or the like. The first hydraulic control device VB1 is accommodated in the oil reservoir OT1. The oil storage unit OT1 stores oil to be supplied to the first hydraulic control device VB1 and the second hydraulic control device VB2.

  In the present embodiment, as shown in FIG. 3, the first hydraulic control device VB1 is attached to the lower portion of the first case CS1 that houses the transmission TM (the lower surface of the first peripheral wall 21a). A first oil pan 51 is attached to the lower portion of the first case CS1 (the lower surface of the first peripheral wall 21a) so as to cover the lower side and the periphery of the first hydraulic control device VB1. That is, the oil reservoir OT1 is configured to be surrounded by the first case CS1 (first peripheral wall 21a) and the first oil pan 51, and the first hydraulic control device VB1 is accommodated in the oil reservoir OT1. ing. Further, in order to prevent the oil stored in the first oil pan 51 from leaking to the outside, the upper surface of the first oil pan 51 and the lower surface of the first case CS1 (first peripheral wall 21a) are joined. A seal member is interposed on the surface. As described above, the oil supplied from the transmission hydraulic control valve 90 of the first hydraulic control device VB1 to the transmission TM is used for the operation and cooling of a plurality of engagement elements provided in the transmission TM, and the transmission It is also used for lubrication and cooling of gear mechanisms and bearings provided by TM. And the oil which flowed out of the transmission TM after finishing such a role flows downward by gravity, and is collect | recovered by the oil storage part OT1 in the 1st oil pan 51 arrange | positioned under the transmission TM. Further, the oil drained from each hydraulic control valve of the first hydraulic control device VB1 is directly discharged to the oil reservoir OT1.

4-7. The second hydraulic control device, the second oil pan The second hydraulic control device VB2 is separated from the first hydraulic control device VB1 and is disposed below the upper end portion 83 of the first hydraulic control device VB1, and the internal combustion engine separation clutch An engagement device hydraulic control valve 93 that controls the hydraulic pressure supplied to C1 is provided. The upper end portion (here, the upper surface) of the second hydraulic control device VB2 is a mounting surface of the second hydraulic control device VB2, and is in contact with the lower end portion of the second case CS2. Further, the upper end portion 83 (upper surface here) of the first hydraulic control device VB1 is a mounting surface of the first hydraulic control device VB1, and is in contact with the lower end portion of the first case CS1. In the present embodiment, the mounting surface of the second hydraulic control device VB2 is disposed below the mounting surface of the first hydraulic control device VB1.

In the present embodiment, the second hydraulic control device VB2 is a cylinder hydraulic control valve that controls the hydraulic pressure supplied to the hydraulic cylinder 97 of the internal combustion engine separation clutch C1, as the engagement device hydraulic control valve 93, as shown in FIG. 94 and a circulation hydraulic pressure control valve 95 for controlling the hydraulic pressure supplied to the first oil chamber 96 in which the friction member 100 of the internal combustion engine separation clutch C1 and the like are accommodated. The second hydraulic control device VB2 is a hydraulic control valve comprising a valve body having a groove (oil passage) stretched like an ant's nest, and a spool, a spring, a solenoid and the like attached in the valve body. And an orifice or the like. The second hydraulic control device VB2 is accommodated in an oil tight chamber OT2 formed in an oil tight manner outside the oil reservoir OT1.
In the present embodiment, as shown in FIG. 3, the second hydraulic control device VB2 is attached to the lower part of the second case CS2 that houses the rotating electrical machine MG (the lower surface of the second peripheral wall 22a). A second oil pan 52 is attached to the lower portion of the second case CS2 (the lower surface of the second peripheral wall 22a) with a fastening member such as a bolt so as to cover the lower side and the periphery of the second hydraulic control device VB2. That is, the oil tight chamber OT2 is configured to be surrounded by the second case CS2 (second peripheral wall 22a) and the second oil pan 52, and the second hydraulic control device VB2 is accommodated in the oil tight chamber OT2. Further, a seal member 55 is interposed on the joint surface between the upper surface of the second oil pan 52 and the lower surface of the second case CS2 (second peripheral wall 22a). The second oil pan 52 is provided below the rotating electrical machine MG. That is, the second oil pan 52 is disposed at a position that is radially outward with respect to the rotating electrical machine MG and has a portion that overlaps the rotating electrical machine MG when viewed in the radial direction.

5. Other Embodiments Finally, other embodiments of the present invention will be described. Note that the configuration of each embodiment described below is not limited to being applied independently, and can be applied in combination with the configuration of other embodiments as long as no contradiction arises.

(1) In the above embodiment, the first exhaust oil passage PE1, the second exhaust oil passage PE2, the first supply oil passage PI1, the second supply oil passage PI2, and the third supply oil passage PI3 are arranged in the first case CS1. Or the case where it was equipped in the wall of 2nd case CS2 was demonstrated as an example. However, the embodiment of the present invention is not limited to this. That is, all or a part of the first discharge oil passage PE1, the second discharge oil passage PE2, the first supply oil passage PI1, the second supply oil passage PI2, and the third supply oil passage PI3 is the first case CS1 or the second supply oil passage PI3. The two cases CS2 may be configured to be oil-tight inside or outside, and for example, all or part of each oil passage may be formed of a tubular member or the like.

(2) In the above embodiment, the case where the hydraulic pump OP is configured by a mechanical pump has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the hydraulic pump OP may be composed of one or both of a mechanical pump and an electric pump.

(3) In the above embodiment, the case where the drive device 1 is provided with the torque converter TC and the first hydraulic control device VB1 is provided with the converter hydraulic control valve 91 has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the drive device 1 may not be provided with the torque converter TC, and the rotating electrical machine MG and the input shaft I may be connected without the torque converter TC. Accordingly, the first hydraulic control device VB1 Alternatively, the converter hydraulic control valve 91 may not be provided.
Further, the drive device 1 may be provided with a second engagement device such as a friction engagement device instead of the torque converter TC, and a hydraulic control valve for controlling the hydraulic pressure supplied to the second engagement device. May be provided in the first hydraulic control device VB1 or the second hydraulic control device VB2.

(4) In the above embodiment, the case where the transmission TM is a stepped automatic transmission has been described as an example. However, the embodiment of the present invention is not limited to this. That is, when the transmission apparatus TM is a transmission apparatus other than the stepped automatic transmission apparatus, such as a continuously variable automatic transmission apparatus capable of continuously changing the transmission gear ratio, one preferred embodiment of the present invention. One. Even in this case, the transmission hydraulic control valve 90 supplies hydraulic pressure to a hydraulic servo mechanism or the like provided in the transmission TM.

(5) In the above embodiment, the case where the drive device 1 includes the first case CS1 and the second case CS2 as the case of the drive device 1 has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the drive device 1 may be configured to include a case in which the first case CS1 and the second case CS2 are integrated, or may include a case divided into three or more.
In any case, the first hydraulic control device VB1 is attached to the lower part of the case of the drive device 1 below the transmission TM, and the second hydraulic control device VB2 includes the rotating electrical machine MG and the internal combustion engine separation clutch C1. It is comprised so that it may be attached to the lower part of the case of the drive device 1 under one or both of these. Further, the first exhaust oil passage PE1, the second exhaust oil passage PE2, the first supply oil passage PI1, the second supply oil passage PI2, and the third supply oil passage PI3 are provided in any case (in the wall surface). You may comprise as follows. The oil reservoir OT1 may be configured to be surrounded by any case and the first oil pan 51 attached to the lower portion of the case. The oil-tight chamber OT2 You may make it comprise by the 2nd oil pan 52 attached to the lower part.

(6) In the above embodiment, the first hydraulic control device VB1 is attached to the lower portion of the first case CS1, and the second hydraulic control device VB2 is attached to the lower portion of the second case CS2. explained. However, the embodiment of the present invention is not limited to this. That is, the first hydraulic control device VB1 may be installed at a location other than the lower portion of the first case CS1, and the second hydraulic control device VB2 may be installed at a location other than the lower portion of the second case CS2. For example, you may make it attach to the side of 1st case CS1 or 2nd case CS2.

(7) In the above embodiment, the oil-tight chamber OT2 is configured to be surrounded by the second case CS2 and the second oil pan 52 attached to the lower part of the second case CS2, and the oil reservoir OT1 is As an example, the case has been described in which the case CS1 is surrounded by the first oil pan 51 attached to the lower portion of the first case CS1. However, the embodiment of the present invention is not limited to this. That is, the oil tight chamber OT2 may be configured by a chamber provided inside the second case CS2, and the oil reservoir OT1 may be configured by a chamber provided inside the first case CS1.

  The present invention includes an input member that is drivingly connected to a rotating electrical machine, an output member that is drivingly connected to a wheel, a transmission that shifts the rotation of the input member and transmits the rotation to the output member, and the input member is an internal combustion engine. And an engagement device that selectively drives and couples to the vehicle drive device.

MG: rotating electric machine IE: internal combustion engine TM: transmission TC: torque converter I: input member (input shaft)
O: Output member (output shaft)
EC: Internal combustion engine connecting shaft C2: Lock-up clutch C1: Engine separation clutch (engagement device)
VB1: first hydraulic control device VB2: second hydraulic control device OT1: oil reservoir OT2: oil tight chamber OP: hydraulic pump PE1: first discharge oil passage PE2: second discharge oil passage PI1: first supply oil passage PI2: Second supply oil path PI3: Third supply oil path L1: First suction oil path L2: First discharge oil path CS1: First case CS2: Second case 21a: First peripheral wall (first case)
21b: Intermediate partition (first case)
21c: Output side end bulkhead (first case)
22a: Second peripheral wall (second case)
22b: Input side end bulkhead (second case)
22c: cylindrical protrusion (second case)
1: Vehicle drive device 11: Pump impeller (torque converter)
12: Turbine runner (torque converter)
14: Stator (torque converter)
51: First oil pan 52: Second oil pan 80: Oil surface of oil storage part 81: Opening part 83 on the oil storage part side of the second discharge oil passage: Upper end part 90 of the first hydraulic control device: Transmission oil pressure Control valve 91: Converter hydraulic control valve 92: Pressure regulator valve 93: Engagement device hydraulic control valve 94: Cylinder hydraulic control valve (engagement device hydraulic control valve)
95: Circulation hydraulic control valve (engagement device hydraulic control valve)
96: first oil chamber 97: hydraulic cylinder 98: first oil chamber supply port 99: first oil chamber discharge port 100: friction material of engine separation clutch

Claims (4)

An input member that is drivingly connected to the rotating electrical machine, an output member that is drivingly connected to the wheel, a transmission that shifts the rotation of the input member and transmits it to the output member, and the input member is selectively used for the internal combustion engine An engagement device for driving and coupling, and a vehicle drive device comprising:
A first hydraulic control device provided with a hydraulic control valve for controlling the hydraulic pressure supplied to the transmission;
A second hydraulic control device provided with a hydraulic control valve that is separated from the first hydraulic control device and is disposed below the upper end of the first hydraulic control device and controls the hydraulic pressure supplied to the engagement device When,
An oil reservoir for storing oil to be supplied to the first hydraulic control device and the second hydraulic control device;
A hydraulic pump that sucks oil stored in the oil storage section to generate hydraulic pressure, and supplies the hydraulic pressure to the first hydraulic control device and the second hydraulic control device, and
The first hydraulic control device is accommodated in the oil reservoir,
The second hydraulic control device is housed in an oil tight chamber formed in an oil tight manner outside the oil reservoir,
An oil-tight first discharge oil passage for sending the oil discharged from the engagement device to the oil-tight chamber, and an oil-tight first discharge passage for sending the oil discharged from the oil-tight chamber to the oil reservoir. A vehicle drive device comprising: a second oil discharge passage.   2. The oil tight chamber according to claim 1, wherein the oil tight chamber is disposed below an oil level of the oil reservoir and an opening on the oil reservoir portion side of the second drain oil passage. Vehicle drive device. A first case that houses the transmission, and a second case that houses the rotating electrical machine and the engagement device,
The first hydraulic control device is attached to a lower portion of the first case,
The second hydraulic control device is attached to a lower portion of the second case,
3. The vehicle drive according to claim 1, wherein the first drain oil passage is provided in the second case, and the second drain oil passage is provided from the second case to the first case. apparatus. A first case that houses the transmission, and a second case that houses the rotating electrical machine and the engagement device,
The oil reservoir is configured to be surrounded by a first oil pan attached to the first case and a lower portion of the first case,
4. The vehicle drive device according to claim 1, wherein the oil tight chamber is configured to be surrounded by the second case and a second oil pan attached to a lower portion of the second case. 5. .

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