Hybrid drive device

The disclosure of Japanese Patent Application No. 2012-027850 filed on Feb. 10, 2012, U.S. Provisional Application No. 61/676,031 filed on Jul. 26, 2012, and Japanese Patent Application No. 2012-158159 filed on Jul. 13, 2012 including the specification, drawings and abstract is incorporated herein by reference in its entirety.

The present invention relates to hybrid drive devices that are mounted on vehicles etc., and more particularly to hybrid drive devices that include an engine connection clutch between an engine coupling shaft member and an input shaft member of a speed change mechanism having a rotating electrical machine coupled thereto.

In recent years, hybrid vehicles combining an internal combustion engine and a motor generator (hereinafter simply referred to as the “motor”) as power sources have been developed. In a hybrid drive device proposed as one form of hybrid drive devices for use in such hybrid vehicles, a rotating electrical machine (motor generator) drivingly coupled to an input shaft of a speed change mechanism, and an engine connecting clutch performing engagement/disengagement of (engaging or disengaging) an engine coupling clutch drivingly coupled to an internal combustion engine and the input shaft are placed in a portion of a starting device (e.g., a torque converter etc.) of a common automatic transmission so that a parallel hybrid drive device is formed by simple replacement (see Japanese Patent Application Publication No. 2008-24298 (JP 2008-24298 A)).

A lubricating method is also possible in which the engine connecting clutch is hermetically sealed and contained in a clutch accommodating case to circulate lubricating oil in a so-called oil-tight manner. In this method, however, the clutch accommodating case is filled with oil. Therefore, the engine connecting clutch has great drag loss especially during EV driving during which the engine connecting clutch is disengaged and the motor generator is used, etc. This hinders improvement in fuel economy (electricity economy) and improvement in controllability. Accordingly, as described in, e.g., Korean Patent Application Publication No. 10-2010-0008470, it is preferable to lubricate (cool) the engine connecting clutch by supplying lubricating oil from the central axis without hermetically sealing the engine connecting clutch.

However, in the hybrid drive device of JP 2008-24298 A, a transmission path is formed by the engine connecting clutch, the rotating electrical machine, the speed change mechanism, and wheels sequentially from the internal combustion engine, and a mechanical oil pump drivingly coupled to the input shaft of the speed change mechanism (on the speed change mechanism side of the engine connecting clutch) is provided so that an oil pressure hydraulically controlling the speed change mechanism can be generated during EV driving using the driving force of the rotating electrical machine with the engine connecting clutch being disengaged. Accordingly, when starting the vehicle while slipping the engine connecting clutch by the driving force of the internal combustion engine, the engine connecting clutch is kept in the slipped state for a long time. However, the mechanical oil pump drivingly coupled to the input shaft of the speed change mechanism is not driven together with the wheels while the vehicle is stopped, and lubricating oil cannot be supplied to the engine connecting clutch.

As described above, when starting the vehicle by using the driving force of the internal combustion engine, etc., there is a case where the engine connecting clutch is slipped for a long time. In this case, a large amount of heat is generated by the engine connecting clutch, whereby an extremely larger amount of lubricating oil (e.g., several times to a dozen of times) is required as compared to the lubricating method in which the lubricating oil is circulated in the oil-tight manner.

German Patent Application Publication No. 10-2009-042933 discloses a hybrid drive device provided with an oil pump that is driven by the driving force of an internal combustion engine or the driving force of a rotating electrical machine by using two one-way clutches. However, this German Patent Application Publication does not describe how to cool an engine connecting clutch.

It is an object of the present invention to provide a hybrid drive device that reduces drag of an engine connecting clutch and that is capable of ensuring capability to cool the engine connecting clutch.

A hybrid drive device according to an aspect of the present invention includes: an engine coupling shaft member that is drivingly coupled to an internal combustion engine; a speed change mechanism that shifts rotation received by an input shaft member and outputs the shifted rotation to a wheel; a rotating electrical machine drivingly coupled to the input shaft member; a housing case containing the rotating electrical machine; an engine connecting clutch that has a first friction plate drivingly coupled to the engine coupling shaft member, a second friction plate drivingly coupled to the input shaft member, and a hydraulic servo engaging or disengaging the first friction plate and the second friction plate, and that has both the first friction plate and the second friction plate placed in the housing case; a first lubricating oil passage that scatters lubricating oil from radially inside to radially outside of the first friction plate and the second friction plate to lubricate the first friction plate and the second friction plate; a coupling member; a first one-way clutch that is interposed between the engine coupling shaft member and the coupling member, and that is not engaged when rotation of the engine coupling shaft member becomes lower than rotation of the coupling member; a second one-way clutch that is interposed between the rotating electrical machine and the coupling member, and that is not engaged when rotation of the rotating electrical machine becomes lower than rotation of the coupling member; and an engine driven oil pump that is drivingly coupled to the coupling member and generates an oil pressure to be supplied to the first lubricating oil passage by a driving force of the internal combustion engine or a driving force of the rotating electrical machine regardless of engagement or disengagement of the engine connecting clutch.

Thus, the hybrid drive device of the aspect of the present invention includes the engine driven oil pump that generates the oil pressure to be supplied to the first lubricating oil passage by the driving force of the internal combustion engine or the driving force of the rotating electrical machine regardless of engagement or disengagement of the engine connecting clutch. Accordingly, drag of the engine connecting clutch can be reduced as compared to, e.g., the case where lubricating oil is circulated in a case in which the first friction plate and the second friction plate are hermetically sealed. Moreover, especially when starting the vehicle by using the driving force of the internal combustion engine, which requires a large amount of lubricating oil for the first and second friction plates placed in air, the engine connecting clutch can be engaged with a sufficient amount of lubricating oil being generated by the engine driven oil pump by driving of the internal combustion engine. Thus, capability to cool the engine connecting clutch can be ensured.

The hybrid drive device according to the aspect of the present invention may further include: a second lubricating oil passage that supplies the oil to the rotating electrical machine.

Thus, since the hybrid drive device of the aspect of the present invention includes the second lubricating oil passage that supplies oil to the rotating electrical machine, oil can be supplied from the second lubricating oil passage to the rotating electrical machine independently of the first lubricating oil passage, whereby oil can be supplied at a required flow rate to the engine connecting clutch without being affected by oil supply to the rotating electrical machine.

In the hybrid drive device according to the aspect of the present invention, the engine coupling shaft member may have a recessed portion in an axial tip end of the engine coupling shaft member, the input shaft member may have a tip end of the input shaft member inserted in the recessed portion, and the input shaft member and the recessed portion may be sealed by a seal member, the input shaft member may have a first oil passage formed in an axial direction and closed at the tip end, a second oil passage formed so as to extend through the input shaft member in a radial direction from the first oil passage, and a third oil passage formed parallel to the first oil passage in the axial direction and opened at the tip end, the engine coupling shaft member may have a fourth oil passage communicating with the third oil passage and formed in the axial direction, and a fifth oil passage formed so as to extend through the engine coupling shaft member in the radial direction from the fourth oil passage, the first lubricating oil passage may be formed by the first oil passage and the second oil passage, and the second lubricating oil passage may be formed by the third oil passage, the fourth oil passage, and the fifth oil passage.

Thus, since the first lubricating oil passage is formed by the first oil passage and the second oil passage, the second lubrication oil passage is formed by the third oil passage, the fourth oil passage, and the fifth oil passage, and the seal member is placed between the input shaft member and the recessed portion, the first lubricating oil passage and the second lubricating oil passage can be prevented from crossing each other.

In the hybrid drive device according to the aspect of the present invention, the first one-way clutch and the second one-way clutch may be lubricated by oil supplied from the second lubricating oil passage.

Thus, since the first one-way clutch and the second one-way clutch can be lubricated by the oil supplied from the second lubricating oil passage, a required flow rate can be supplied to the engine connecting clutch without being affected by lubrication of the first one-way clutch and the second one-way clutch. Moreover, the first one-way clutch and the second one-way clutch can be cooled with a stable amount of lubricating oil without being affected by heat generation of the engine connecting clutch.

In the hybrid drive device according to the aspect of the present invention, the oil that has lubricated the first one-way clutch and the second one-way clutch may be supplied to the rotating electrical machine.

Thus, since oil that has lubricated the first one-way clutch and the second one-way clutch is supplied to the rotating electrical machine, the size of the engine driven oil pump and an electric oil pump can be reduced as compared to the case where a lubricating oil passage that is used to lubricate the first one-way clutch and the second one-way clutch is additionally provided independently of the first lubricating oil passage and the second lubricating oil passage.

The hybrid drive device according to the aspect of the present invention may include: flow rate adjusting means that adjusts a flow rate of oil to be supplied to the first lubricating oil passage. The second lubricating oil passage may branch off at a position upstream of the flow rate adjusting means.

Thus, since the rotating electrical machine is lubricated by the second lubricating oil passage that branches off from the first lubricating oil passage at a position upstream of the flow rate adjusting means, a required flow rate can be supplied to the engine connecting clutch without being affected by cooling of the rotating electrical machine. Moreover, the rotating electrical machine can be cooled by the second lubricating oil passage that does not cross the first lubricating oil passage, while being hardly affected by flow rate adjustment of the flow rate adjusting means, and the rotating electrical machine can be cooled with a stable amount of lubricating oil without being affected by heat generation of the engine connecting clutch.

In the hybrid drive device according to the aspect of the present invention, the engine connecting clutch may have a clutch drum drivingly coupled to the input shaft member, the second friction plate may have an outer peripheral side of the second friction plate drivingly coupled to the clutch drum, and the clutch drum may have a through hole that is positioned so as to at least partially overlap the second friction plate as viewed in a radial direction, and that discharges the oil supplied to the first and second friction plates.

Thus, since the clutch drum of the engine connecting clutch has the through hole that is positioned so as to at least partially overlap the second friction plate as viewed in the radial direction, and that discharges the oil supplied to the first and second friction plates, a large amount of lubricating oil that has cooled the first and second friction plates can be discharged into the housing case for circulation.

The hybrid drive device according to the aspect of the present invention may include: a control portion that controls a hydraulic control device so as to supply the oil pressure generated by the engine driven oil pump to the engine connecting clutch while the engine connecting clutch is slipped.

Thus, capability to cool the engine connecting clutch can be ensured even when the engine connecting clutch is in the slipped state.

FIG. 1 is a schematic diagram showing a hybrid car to which the present invention can be applied;

FIG. 2 is a sectional view showing an input portion 9 1 according to a first reference example;

FIG. 3 is a sectional view showing an input portion 9 2 according to a second reference example;

FIG. 4 is a sectional view showing an input portion 9 3 according to a first embodiment;

FIG. 5 is a sectional view showing an input portion 9 4 according to a second embodiment;

FIG. 6 is a diagram showing a lubricating circuit of a hydraulic control device; and

FIG. 7 is a sectional view showing an input portion 9 5 according to a third embodiment.

First Reference Example

A hybrid drive device 1 according to a first reference example of the present invention will be described below with reference to FIGS. 1 and 2 . The hybrid drive device 1 according to the first reference example is preferably mounted on front engine front drive (FF) vehicles, and the lateral direction in the figures corresponds to the lateral direction in the state where the hybrid drive device 1 is actually mounted on a vehicle. For convenience of description, the “front side” refers to the side of a driving source such as an engine, and the “rear side” refers to the opposite side from the driving source. As used herein, the expression “drivingly coupled” refers to the state where rotating elements are coupled together so that the driving force can be transmitted therebetween, and is used as a concept including the state where the rotating elements are coupled together so as to rotate together, or the state where the rotating elements are coupled together so that the driving force can be transmitted therebetween via a clutch etc.

[General Configuration of Hybrid Drive Device]

As shown in FIG. 1 , a hybrid vehicle (hereinafter simply referred to as the “vehicle”) 100 has a rotating electrical machine (motor generator) 3 in addition to an internal combustion engine 2 as driving sources. The hybrid drive device 1 forming a power train of the vehicle 100 has a speed change mechanism 7 provided on a power transmission path L between the internal combustion engine 2 and wheels 6 , an input portion 9 placed between the speed change mechanism 7 and the internal combustion engine 2 to receive power from the internal combustion engine 2 , and a connection portion 14 connecting the input portion 9 to the internal combustion engine 2 while absorbing pulsations of the internal combustion engine 2 .

The connection portion 14 is provided with a damper 12 that is connected to a crankshaft 2 a of the internal combustion engine 2 via a drive plate 11 , and the damper 12 is connected to an engine coupling shaft (engine coupling shaft member) 13 that serves also as an input member as the input portion 9 . That is, the engine coupling shaft 13 is drivingly coupled to the internal combustion engine 2 via the damper 12 .

The input portion 9 includes a clutch (engine connecting clutch) K 0 that permits and blocks power transmission between the engine coupling shaft 13 and an input shaft 15 of the speed change mechanism 7 , and the motor generator (rotating electrical machine) 3 drivingly coupled to a clutch housing 50 . The motor generator (hereinafter simply referred to as the “motor”) 3 has a rotor 4 coupled to the clutch housing 50 , and a stator 5 placed radially outward of the rotor 4 so as to face the rotor 4 .

The clutch K 0 is a multi-plate clutch formed by a plurality of inner friction plates (first friction plates) 17 and a plurality of outer friction plates (second friction plates) 19 which are accommodated in a space S 1 inside the clutch housing 50 . The clutch housing 50 is coupled to the input shaft (input shaft member) 15 of the speed change mechanism 7 so as to rotate together therewith. That is, the clutch K 0 has the inner friction plates 17 that are drivingly coupled to a transmission path L 1 on the internal combustion engine side of the transmission path L, and the outer friction plates 19 that are drivingly coupled to a transmission path L 2 on the wheel side of the transmission path L, and the clutch housing 50 is also drivingly coupled to the transmission path L 2 on the wheel side.

The speed change mechanism 7 is, e.g., a speed change mechanism capable of changing the transmission path based on the engagement state of a plurality of friction engagement elements (clutches and brakes) to attain six forward speeds and one reverse speed. An output member of the speed change mechanism 7 is connected to the driving wheels 6 via a differential unit D. The speed change mechanism 7 may be, e.g., a stepped speed change mechanism that attains three to five forward speeds or seven or more forward speeds, or a stepless speed change mechanism such as a belt type continuously variable transmission, a toroidal continuously variable transmission, or a cone ring type continuously variable transmission. That is, the present invention can be applied to any speed change mechanism.

As described above, in the hybrid drive device 1 , the connection portion 14 , the input portion 9 having the clutch K 0 and the motor 3 , and the speed change mechanism 7 are sequentially arranged from the internal combustion engine 2 side toward the wheel 6 side. When the vehicle travels by driving both the internal combustion engine 2 and the motor 3 , a control portion (ECU) 20 controls a hydraulic control device 21 to engage the clutch K 0 . During EV driving during which the vehicle travels only by the driving force of the motor 3 drivingly coupled to the transmission path L 2 on the wheel side, the control portion 21 controls the hydraulic control device 21 to disengage the clutch K 0 , thereby disconnecting the transmission path L 1 on the internal combustion engine 2 side from the transmission path L 2 on the wheel 6 side.

[Configuration of Input Portion]

The configuration of the input portion 9 will be described in detail below with reference to FIG. 2 . As shown in FIG. 2 , the clutch K 0 and the motor 3 are accommodated in a housing case 26 fixed by a bolt 29 to a transmission case 23 accommodating the speed change mechanism 7 . An internal space S 2 of the housing case 26 in which the clutch K 0 and the motor 3 are accommodated is separated from the connection portion 14 by a partition wall 27 integrally attached to the housing case 26 , thereby forming a closed space.

The engine coupling shaft 13 that is connected to the internal combustion engine 2 via the damper 12 of the connection portion 14 , and the input shaft 15 of the speed change mechanism 7 are coaxially arranged on the center side of the housing case 26 . The engine coupling shaft 13 is rotatably supported with respect to the partition wall 27 by a needle bearing b 3 , and is rotatably supported with respect to the partition wall 27 via a ball bearing b 2 , which is fitted in a support portion 83 a of a pump body 83 fixed to the partition wall 27 and described in detail below, a rotor hub 51 , and a needle bearing b 4 .

The input shaft 15 is rotatably supported via a cylinder member 41 , described in detail below, by a ball bearing b 1 that is fitted in a support portion 73 a of a pump body 73 fixed to a partition wall 24 fixed to the transmission case 23 .

A flange portion 13 a is formed at the rear end on the speed change mechanism 7 side of the engine coupling shaft 13 . A clutch hub 49 , with which the plurality of inner friction plates 17 of the clutch K 0 are spline engaged, are fixedly attached to the flange portion 13 a . That is, the inner friction plates 17 are drivingly coupled to the engine coupling shaft 13 .

The clutch K 0 generally has the plurality of inner friction plates 17 , the outer friction plates 19 arranged alternately with the inner friction plates 17 , and a hydraulic servo 40 that performs engagement/disengagement of (engages or disengages) the inner friction plates 17 and the outer friction plates 19 . The hydraulic servo 40 has the cylinder member 41 forming a hydraulic cylinder of the hydraulic servo 40 and drivingly coupled to the input shaft 15 , a drum member 42 fixedly attached to the outer peripheral side of a flange portion 41 b of the cylinder member 41 , a piston 43 placed so as to be axially movable with respect to the cylinder member 41 and placed so that its tip end faces the outer friction plate 19 (or the inner friction plate 17 ), a return plate 44 positioned with respect to a boss portion 41 a of the cylinder member 41 by a snap ring 48 , and a return spring 45 provided in a compressed manner between the piston 43 and the return plate 44 . A hydraulic oil chamber 46 is formed between the cylinder member 41 and the piston 43 , and a canceling oil chamber 47 that cancels a centrifugal oil pressure is formed between the piston 43 and the return plate 44 .

The cylinder member 41 and the drum member 42 form an integral clutch drum, and the plurality of outer friction plates 19 are spline engaged with the inner side of the drum member 42 . That is, the outer friction plates 19 are drivingly coupled to the input shaft 15 via the drum member 42 and the cylinder member 41 .

On the other hand, the stator 5 of the motor 3 is fixed between the outer peripheral side of the clutch K 0 and the inner peripheral side of the housing case 26 . The stator 5 has a stator core 5 a , and coil ends 5 b , 5 b forming looped portions of a coil wound around the stator core 5 a and protruding on both axial sides of the stator core 5 a . The rotor 4 of the motor 3 is placed so as to face the inner peripheral side of the stator core 5 a with a predetermined gap therebetween.

The rotor hub 51 supporting the rotor 4 is fixed to the drum member 42 by a bolt 55 . The rotor hub 51 has a drum-shaped holding portion 51 b that grips and holds a rotor core 4 a of the rotor 4 , and a flange-shaped support portion 51 a that supports the holding portion 51 b with respect to the pump body 83 and the engine coupling shaft 13 . The support portion 51 a is rotatably supported by the ball bearing b 2 and the needle bearing b 4 with respect to the pump body 83 and the engine coupling shaft 13 , and is also supported in the axial direction by a thrust bearing b 6 provided between the support portion 51 a and the flange portion 13 a of the engine coupling shaft 13 . A thrust bearing b 5 is provided between the flange portion 13 a of the engine coupling shaft 13 and the boss portion 41 a of the cylinder member 41 , so that the engine coupling shaft 13 and the cylinder member 41 are positioned and supported in the axial direction.

The cylinder member 41 , the drum member 42 , and the rotor hub 51 , which are described above, form the clutch housing 50 including the space S 1 where the hydraulic servo 40 , the inner friction plates 17 , and the outer friction plates 19 are arranged. A plurality of communication holes 51 c are formed in the support portion 51 a of the rotor hub 51 forming the clutch housing 50 so as to be located radially outward of the outer friction plates 19 (preferably, so as to open to the inner peripheral surface of the holding portion 51 b ). These communication holes 51 c allow the space S 1 included in the clutch housing 50 to communicate with the internal space S 2 of the housing case 26 . That is, the clutch K 0 is a wet multi-plate clutch in which the inner friction plates 17 and the outer friction plates 19 are not made oil-tight (non-oil-tight) and are open to the atmosphere in the housing case 26 so that the inner friction plates 17 and the outer friction plates 19 are arranged in air.

The clutch housing 50 is accurately and firmly supported by a so-called both end support structure by the ball bearing b 2 supporting the support portion 51 a of the rotor hub 51 on the front side of the clutch housing 50 and the ball bearing b 1 supporting the cylinder member 41 on the rear side of the clutch housing 50 . This can ensure high support accuracy of the rotor 4 , and can reduce the air gap between the rotor 4 and the stator 5 , thereby improving performance as the motor 3 .

In the clutch K 0 configured as described above, when an engagement pressure is supplied from the hydraulic control device 21 to the hydraulic oil chamber 46 of the hydraulic servo 40 through an oil passage a 11 formed in the partition wall 24 , oil passages a 12 , a 13 , a 14 formed in the input shaft 15 , and an oil passage a 15 formed in the boss portion 41 a of the cylinder member 41 based on a command of the control portion 20 , the piston 43 moves forward in the axial direction against the biasing force of the return spring 45 to engage the inner friction plates 17 and the outer friction plates 19 . Thus, the internal combustion engine 2 is drivingly coupled to the speed change mechanism 7 , and the vehicle 100 is brought into a hybrid driving state where the vehicle 100 can travel by using the driving forces of the internal combustion engine 2 and the motor 3 .

On the contrary, when the engagement pressure is discharged (drained) from the hydraulic oil chamber 46 of the hydraulic servo 40 through the oil passages a 11 to a 15 by the hydraulic control device 21 based on a command of the control portion 20 , the piston 43 moves rearward in the axial direction based on the biasing force of the return spring 45 to disengage the inner friction plates 17 and the outer friction plates 19 . Thus, the internal combustion engine 2 is disconnected from the speed change mechanism 7 , and the vehicle 100 is brought into an EV driving state where the vehicle 100 can travel by using only the driving force of the motor 3 .

A lubrication pressure (a pressure to be supplied to a lubricating oil passage) generated by the hydraulic control device 21 based on an oil pressure generated by an input-shaft cooperative oil pump 70 and an engine driven oil pump 80 , which will be described later in detail, is supplied from an oil passage in the partition wall 24 , not shown, through a lubricating oil passage a 21 formed in the input shaft 15 to a lubricating oil passage a 22 formed by the gap between the engine coupling shaft 13 and the input shaft 15 , and is supplied to the canceling oil chamber 47 through a lubricating oil passage a 23 formed in the boss portion 41 a of the cylinder member 41 . The lubricating oil that has overflown the cancelling oil chamber 47 flows from the thrust bearing b 5 through a through hole 49 a of the clutch hub 49 , and is scattered to the inner friction plates 17 and the outer friction plates 19 , thereby lubricating and cooling the inner friction plates 17 and the outer friction plates 19 . That is, the lubricating oil passages a 21 to a 23 are oil passages that are used to scatter the lubricating oil from the center side of the clutch K 0 to lubricate the clutch K 0 .

The lubricating oil that has lubricated and cooled the inner friction plates 17 and the outer friction plates 19 flows through a through hole 42 a of the drum member 42 , and is discharged to a region between the drum member 42 and the holding portion 51 b of the rotor hub 51 in the space S 1 in the clutch housing 50 . The lubricating oil that is present in the region between the drum member 42 and the holding portion 51 b of the rotor hub 51 in the space S 1 in the clutch housing 50 is discharged into the internal space S 2 of the housing case 26 through the plurality of communication holes 51 c , is guided downward along the inner surface of the housing case 26 , and is collected by an oil pan, not shown, attached to the lower part of the hybrid drive device 1 .

[Configuration of Input-Shaft Cooperative Oil Pump]

The configuration of the input-shaft cooperative oil pump 70 will be described below. The input-shaft cooperative oil pump 70 is provided on the outer periphery of the input shaft 15 so as to be located between the clutch K 0 and the speed change mechanism 7 in the axial direction. The input-shaft cooperative pump 70 has a drive gear 71 and a driven gear 72 which form an internal gear oil pump, and has the pump body 73 accommodating the drive gear 71 and the driven gear 72 . The input-shaft cooperative oil pump 70 is formed by fastening the partition wall 24 to the pump body 73 by a bolt 79 so that the partition wall 24 closing the speed change mechanism 7 serves as a cover closing the gear accommodating portion of the pump body 73 .

The drive gear 71 of the input-shaft cooperative oil pump 70 is drivingly coupled to the rear end side of the boss portion 41 a of the cylinder member 41 coupled to the outer periphery of the input shaft 15 . Specifically, this driving coupling is implemented by engaging a key formed on the inner peripheral side of the drive gear 71 with a key groove formed in the rear end of the boss portion 41 a . That is, the input-shaft cooperative oil pump 70 is placed on the transmission path L 2 located on the speed change mechanism 7 side of the clutch K 0 (see FIG. 1 ) so that the input-shaft cooperative oil pump 70 is drivingly coupled to the motor 3 , and is drivingly coupled to the internal combustion engine 2 when the clutch K 0 is engaged.

A rotor (exciting coil) 61 is fixedly attached to the inner peripheral side of the drum member 42 fixed to the rotor 4 of the motor 3 , and a stator (detection coil) 62 is fixedly attached to the outer peripheral side of the support portion 73 a of the pump body 73 by a bolt 69 so as to face the rotor 61 . The rotor 61 and the stator 62 form a resolver 60 that detects rotation of the motor 3 .

The input-shaft cooperative oil pump 70 thus drivingly coupled to the input shaft 15 is driven by the driving force of the motor 3 and the internal combustion engine 2 or by the inertial force of the vehicle via the speed change mechanism 7 when in a coast state (when the engine brake is in operation) during EV driving or hybrid driving. The input-shaft cooperative oil pump 70 thus sucks the oil through an input port 70 a communicating with the oil pan, not shown, and generates an oil pressure from a discharge port 70 b to supply the oil pressure to the hydraulic control device 21 through the oil passage formed in the partition wall 24 , etc.

The input-shaft cooperative oil pump 70 is drivingly coupled to the input shaft 15 of the speed change mechanism 7 . Accordingly, while the vehicle is stopped, the input-shaft cooperative oil pump 70 is also stopped and no oil pressure can be generated unless, e.g., the vehicle is brought into a special state where the speed change mechanism 7 is brought into a neutral state and the input shaft 15 is driven by the motor 3 and the internal combustion engine 2 (by engaging the clutch K 0 ) (e.g., the state where the motor 3 is driven by the driving force of the internal combustion engine 2 to perform charging, etc.). Accordingly, during normal stopping of the vehicle (when charging is not particularly required, etc.), an electric oil pump, not shown, supplies a required oil pressure to the hydraulic control device 21 .

[Configuration of Engine Driven Oil Pump]

The configuration of the engine driven oil pump 80 will be described below. The engine driven oil pump 80 is provided on the outer periphery of the engine coupling shaft 13 so as to be located between the internal combustion engine 2 (the connection portion 14 ) and the clutch K 0 in the axial direction, and to be located on the inner peripheral side of the coil end 5 b on the internal combustion engine 2 side of the motor 3 . That is, the engine driven oil pump 80 is positioned so as to overlap the motor 3 in the axial direction as viewed in the radial direction.

The engine driven oil pump 80 has a drive gear 81 and a driven gear 82 which form an internal gear oil pump, and has the pump body 83 accommodating the drive gear 81 and the driven gear 82 . The engine driven oil pump 80 is formed by fastening the pump body 83 to the partition wall 27 by a bolt 89 so that the partition wall 27 closing the housing case 26 serves as a cover closing the gear accommodating portion of the pump body 83 .

The drive gear 81 of the engine driven oil pump 80 is drivingly coupled to the outer periphery of the engine coupling shaft 13 . Specifically, this driving coupling is implemented by a coupling structure 88 formed by engaging a key formed on the inner peripheral side of the drive gear 81 with a key groove formed in the engine coupling shaft 13 . That is, the engine driven oil pump 80 is placed so that it can be drivingly coupled to the transmission path L 1 located on the internal combustion engine 2 side of the clutch K 0 (see FIG. 1 ).

The engine driven oil pump 80 thus drivingly coupled to the engine coupling shaft 13 is driven by the driving forces of the motor 3 and the internal combustion engine 2 or by the inertial force of the vehicle via the speed change mechanism 7 when in the coast state (when the engine brake is in operation) during hybrid driving. In particular, when starting the vehicle from its stopped state by the driving force of the internal combustion engine 2 while slip engaging the clutch K 0 , the engine driven oil pump 80 is driven by the driving force of the internal combustion engine 2 from before engagement of the clutch K 0 (i.e., from when the vehicle is in the stopped state).

When driven as described above, the engine driven oil pump 80 sucks oil from an input port 80 a communicating with the oil pan, not shown, and generates an oil pressure from a discharge port 80 b to supply the oil pressure to the hydraulic control device 21 through an oil passage formed in the partition wall 27 , etc., even while the vehicle is stopped. Accordingly, when starting the vehicle by the driving force of the internal combustion engine 2 , not only the oil pressure of the electric oil pump, not shown, but also the oil pressure of the engine driven oil pump 80 are applied. Thus, the lubrication pressure, which is used to supply a large amount of lubricating oil required in the slip engaged state when starting the vehicle, can be generated not only by the electric oil pump but also by the engine driven oil pump 80 .

Conclusion of First Reference Example

As described above, the hybrid drive device 1 of the first reference example includes the engine driven oil pump 80 that generates an oil pressure to be supplied to the first lubricating oil passage, which is used to supply the lubricating oil to the first and second friction plates 17 , 19 placed in air, by the driving force of the internal combustion engine 2 regardless of engagement or disengagement of the clutch K 0 . Accordingly, drag of the clutch K 0 can be reduced as compared to, e.g., the case where lubricating oil is circulated in a case in which the first friction plates 17 and the second friction plates 19 are hermetically sealed. Moreover, especially when starting the vehicle by using the driving force of the internal combustion engine 2 , which requires a large amount of lubricating oil for the first and second friction plates 17 , 19 placed in the air, the clutch K 0 can be engaged with a sufficient amount of lubricating oil being generated by the engine driven oil pump 80 by driving of the internal combustion engine 2 . Thus, capability to cool the clutch K 0 can be ensured.

Moreover, an increase in size of the electric oil pump can be prevented as compared to, e.g., the case where an electric oil pump is provided and the clutch K 0 is cooled by the electric oil pump. This eliminates the need to secure a large amount of lubricating oil by the electric oil pump. Since an increase in size of the electric oil pump can be prevented, mountability on vehicles can be improved and cost reduction can be achieved.

The hybrid drive device 1 further includes the input-shaft cooperative oil pump 70 that is drivingly coupled to the input shaft 15 to generate an oil pressure to be supplied to the hydraulic control device 21 . Thus, in particular, even during EV driving, the speed change mechanism 7 can be hydraulically controlled by the oil pressure that is generated by the input-shaft cooperative oil pump 70 . Since the oil pressure required to hydraulically control the speed change mechanism 7 can be generated by the input-shaft cooperative oil pump 70 , the oil pressure to be generated by the engine driven oil pump 80 can be reduced, and the engine driven oil pump 80 can be reduced in size.

On the contrary, during hybrid driving that requires a high oil pressure (an engagement pressure for the clutches and the brakes) for the speed change mechanism 7 , the engine driven oil pump 80 is driven by the internal combustion engine 2 . Thus, the speed change mechanism 7 need not be hydraulically controlled only by the oil pressure that is generated by the input-shaft cooperative oil pump 70 . Namely, the oil pressure can be generated by both the input-shaft cooperative oil pump 70 and the engine driven oil pump 80 , whereby the oil pressure to be generated by the input-shaft cooperative oil pump 70 can also be reduced, and the input-shaft cooperative oil pump 70 can also be reduced in size.

The engine driven oil pump 80 is positioned so as to overlap the motor 3 in the axial direction as viewed in the radial direction. Thus, the engine driven oil pump 80 can be placed so as to be accommodated on the inner peripheral side of the motor 3 , and the hybrid drive device 1 can be made compact in the axial direction.

In the hybrid drive device 1 , the communication holes 51 c that allow the space S 1 included in the clutch housing 50 to communicate with the internal space S 2 of the housing case 26 are merely formed in the clutch housing 50 . Thus, the circulation type clutch K 0 that circulates the lubricating oil in an oil-tight manner can be easily changed to the structure in which the space S 1 included in the clutch housing 50 is open to the atmosphere in the internal space S 2 of the housing case 26 .

Second Reference Example

A second reference example, which is obtained by partially changing the first reference example, will be described with reference to FIG. 3 . In the description of the second reference example, portions similar to those of the first reference example are denoted by the same reference characters, and description thereof will be omitted.

An input portion 9 2 of the hybrid drive device 1 of the second reference example is different from the first reference example in the structure of the oil pressure discharge path of the engine driven oil pump. Specifically, as shown in FIG. 3 , an engine driven oil pump 180 is provided on the outer periphery of the engine coupling shaft 13 so as to be located between the internal combustion engine 2 (the connection portion 14 ) and the clutch K 0 in the axial direction, and to be located on the inner peripheral side of the coil end 5 b on the internal combustion engine 2 side of the motor 3 , like the engine driven oil pump 80 of the first reference example.

The engine driven oil pump 180 has a drive gear 181 and a driven gear 182 which form an internal gear oil pump, and has a pump body 183 accommodating the drive gear 181 and the driven gear 182 . The engine driven oil pump 180 is formed by fastening the pump body 183 to the partition wall 27 by a bolt 189 so that the partition wall 27 closing the housing case 26 serves as a cover closing the gear accommodating portion of the pump body 183 . The pump body 183 supports the ball bearing b 2 by a support portion 183 a , and rotatably supports the rotor hub 51 and the engine coupling shaft 13 .

Like the first reference example, the drive gear 181 of the engine driven oil pump 180 is drivingly coupled to the outer periphery of the engine coupling shaft 13 . More specifically, this driving coupling is implemented by a coupling structure 188 formed by engaging a key formed on the inner peripheral side of the drive gear 181 with a key groove formed in the engine coupling shaft 13 . That is, the engine driven oil pump 180 is placed so that it can be drivingly coupled to the transmission path L 1 located on the internal combustion engine 2 side of the clutch K 0 (see FIG. 1 ).

The engine driven oil pump 180 thus drivingly coupled to the engine coupling shaft 13 is driven by the driving forces of the motor 3 and the internal combustion engine 2 or by the inertial force of the vehicle via the speed change mechanism 7 when in the coast state (when the engine brake is in operation) during hybrid driving. In particular, when starting the vehicle from its stopped state by the driving force of the internal combustion engine 2 while slip engaging the clutch K 0 , the engine driven oil pump 180 is driven by the driving force of the internal combustion engine 2 from before engagement of the clutch K 0 (i.e., from when the vehicle is in the stopped state).

When driven, the engine driven oil pump 180 according to the second reference example sucks oil from an input port 180 a communicating with the oil pan, not shown, and generates an oil pressure from a discharge port 180 b , even while the vehicle is stopped. The oil pressure discharged from the discharge port 180 b is supplied from a lubricating oil passage a 31 , which is formed in the pump body 183 so as to directly communicate with the discharge port 180 b , through lubricating oil passages a 32 , a 33 formed in the engine coupling shaft 13 to the lubricating oil passage a 22 formed by the gap between the engine coupling shaft 13 and the input shaft 15 , and is supplied to the cancelling oil chamber 47 via the lubricating oil passage a 23 formed in the boss portion 41 a of the cylinder member 41 . The lubricating oil that has overflown the cancelling oil chamber 47 flows from the thrust bearing b 5 through the through hole 49 a of the clutch hub 49 , and is scattered to the inner friction plates 17 and the outer friction plates 19 , thereby lubricating and cooling the inner friction plates 17 and the outer friction plates 19 .

Accordingly, when starting the vehicle by the driving force of the internal combustion engine 2 , a large amount of lubricating oil required in the slip engaged state when starting the vehicle is not supplied to the lubricating oil passage via the hydraulic control device 21 by using the oil pressure generated by the electric oil pump, not shown, but is supplied from the engine driven oil pump 180 directly to the inner friction plates 17 and the outer friction plates 19 without via the hydraulic control device 21 .

According to the hybrid drive device 1 of the second reference example configured as described above, the engine driven oil pump 180 is dedicated to generating the oil pressure to be supplied to the lubricating oil passage. This can reduce the size of the engine driven oil pump 180 , can reduce the drag resistance of the engine driven oil pump 180 during hybrid driving using the driving force of the internal combustion engine 2 , and can improve fuel economy of the vehicle.

Since the engine driven oil pump 180 is dedicated to generating the oil pressure to be supplied to the lubricating oil passage, the generated oil pressure is low, and the seal structure between the pump body 183 and the partition wall 27 can be simplified, and the engine driven oil pump 180 can be made compact.

The lubricating oil passages a 31 to a 33 are connected to the discharge port 180 b of the engine driven oil pump 180 without via the hydraulic control device 21 . That is, this can eliminate the need for an oil passage leading from the engine driven oil pump 180 to the center side of the clutch K 0 (e.g., the input shaft 15 ) via the hydraulic control device 21 , and thus can simplify the hybrid drive device 1 and can achieve cost reduction, etc. Since the clutch K 0 is not engaged during EV driving, the clutch K 0 need not be lubricated, and all the oil passages that are used to supply the lubricating oil from the hydraulic control device 21 to the center side of the clutch K 0 (e.g., the input shaft 15 ) can be eliminated.

Since the configuration, operation, and effects of the hybrid drive device 1 according to the second reference example are otherwise similar to those of the first reference example, description thereof will be omitted.

First Embodiment

A first embodiment, which is obtained by partially changing the first reference example, will be described with reference to FIG. 4 . In the description of the first embodiment, portions similar to those of the first reference example are denoted by the same reference characters, and description thereof will be omitted.

An input portion 9 3 of the hybrid drive device 1 of the first embodiment is different from the first reference example in that the input-shaft cooperative oil pump 70 is eliminated and in that the structure of the engine driven oil pump is changed so that an engine driven oil pump 280 can be driven by either the internal combustion engine 2 or the motor 3 .

Specifically, as shown in FIG. 4 , the input-shaft cooperative oil pump 70 is eliminated in the input portion 9 3 as compared to the first reference example (see FIG. 2 ). Thus, a support portion 26 a supporting the ball bearing b 1 is formed in a wall-like portion on the speed change mechanism 7 side of the housing case 26 , so that the housing case 26 directly rotatably supports the cylinder member 41 and the input shaft 15 . The stator 62 of the resolver 60 is fixed to the housing case 26 by the bolt 69 .

On the other hand, in the input portion 9 3 , the engine driven oil passage 280 is provided on the outer periphery of the engine coupling shaft 13 so as to be located between the internal combustion engine 2 (the connection portion 14 ) and the clutch K 0 in the axial direction, and to be located on the inner peripheral side of the coil end 5 b on the internal combustion engine 2 side of the motor 3 .

The engine driven oil pump 280 has a drive gear 281 and a driven gear 282 which form an internal gear oil pump, and has a pump body 283 accommodating the drive gear 281 and the driven gear 282 , and a pump cover 284 . The engine driven oil pump 280 is formed by fastening the pump body 283 to the pump cover 284 by a bolt 289 so that the pump cover 284 closes the gear accommodating portion of the pump body 283 .

An outer edge portion of the pump body 283 is fastened to the partition wall 27 by a bolt 288 , so that the engine driven oil pump 280 is fixed to and supported by the partition wall 27 and the housing case 26 . Thus, the pump body 283 supports the ball bearing b 2 by a support portion 283 a , and rotatably supports the rotor hub 51 and the engine coupling shaft 13 .

The drive gear 281 of the engine driven oil pump 280 is drivingly coupled to a coupling member 285 rotatably placed on the outer peripheral side of the engine coupling shaft 13 . Specifically, this driving coupling is implemented by engaging a key formed on the inner peripheral side of the drive gear 281 with a key groove formed in the coupling member 285 . A first one-way clutch F 1 is provided on the inner peripheral side of the rear end side (the speed change mechanism 7 side) of the coupling member 285 so as to be interposed between the coupling member 285 and the engine coupling shaft 13 . A second one-way clutch F 2 is provided on the outer peripheral side of the rear end side (the speed change mechanism 7 side) of the coupling member 285 so as to be interposed between the coupling member 285 and the rotor hub 51 . That is, the coupling member 285 , the first one-way clutch F 1 , and the second one-way clutch F 2 form a coupling structure 290 that couples the engine coupling shaft 13 to the engine driven oil pump 280 .

Namely, when rotation of the engine coupling shaft 13 (i.e., the internal combustion engine 2 ) becomes lower than rotation of the coupling member 285 , the first one-way clutch F 1 is not engaged. When the rotation of the coupling member 285 becomes equal to the rotation of the engine coupling shaft 13 , the first one-way clutch F 1 is engaged, and the engine driven oil pump 280 is drivingly coupled to the internal combustion engine 2 , and is driven by the driving force of the internal combustion engine 2 . When rotation of the rotor hub 51 (i.e., the motor 3 ) becomes lower than rotation of the coupling member 285 , the second one-way clutch F 2 is not engaged. When the rotation of the coupling member 285 becomes equal to the rotation of the rotor hub 51 , the second one-way clutch F 2 is engaged, and the engine driven oil pump 280 is drivingly coupled to the motor 3 , and is driven by the driving force of the motor 3 .

That is, the engine driven oil pump 280 is placed so that it can be drivingly coupled to the transmission path L 1 located on the internal combustion engine 2 side of the clutch K 0 , and so that it can be drivingly coupled to the transmission path L 2 located on the speed change mechanism 7 side of the clutch K 0 (see FIG. 1 ). When the clutch K 0 is engaged, the transmission path L 1 is drivingly coupled to the transmission path L 2 , whereby rotation of the internal combustion engine 2 becomes equal to rotation of the motor 3 , and the engine driven oil pump 280 is driven by this rotation.

The engine driven oil pump 280 , which is thus drivingly coupled to the engine coupling shaft 13 via the first one-way clutch F 1 or is drivingly coupled to the rotor hub 51 via the second one-way clutch F 2 , is driven by the driving force of the motor 3 or by the inertial force of the vehicle via the speed change mechanism 7 when in the coast state (when the engine brake is in operation) during EV driving, and is driven by the driving forces of the motor 3 and the internal combustion engine 2 or by the inertial force of the vehicle via the speed change mechanism 7 when in the coast state (when the engine brake is in operation) during hybrid driving.

When starting the vehicle from its stopped state by the driving force of the internal combustion engine 2 while slip engaging the clutch K 0 , the first one-way clutch F 1 is engaged from before engagement of the clutch K 0 (i.e., from when the vehicle is in the stopped state), and thus the engine driven oil pump 280 is driven by the driving force of the internal combustion engine 2 .

When driven in this manner, the engine driven oil pump 280 sucks oil from an input port 280 a communicating with the oil pan, not shown, and generates an oil pressure from a discharge port 280 b , even while the vehicle is stopped. The oil pressure thus generated is supplied to the hydraulic control device 21 through the oil passage formed in the partition wall 27 , etc. Accordingly, when starting the vehicle by the driving force of the internal combustion engine 2 , not only the oil pressure of the electric oil pump, not shown, but also the oil pressure of the engine driven oil pump 280 are applied. Thus, the lubrication pressure, which is used to supply a large amount of lubricating oil required in the slip engaged state when starting the vehicle, can be generated not only by the electric oil pump but also by the engine driven oil pump 280 .

A lubrication pressure generated by the hydraulic control device 21 based on the oil pressure generated by the engine driven oil pump 280 or the electric oil pump, not shown, is supplied from an oil passage in the partition wall 24 , not shown, through lubricating oil passages a 41 , a 42 formed in the input shaft 15 to the canceling oil chamber 47 through a lubricating oil passage a 43 formed in the boss portion 41 a of the cylinder member 41 . The lubricating oil that has overflown the cancelling oil chamber 47 or the lubricating oil that has passed through an oil passage a 44 flows from the thrust bearing b 5 through the through hole 49 a of the clutch hub 49 , and is scattered to the inner friction plates 17 and the outer friction plates 19 , thereby lubricating and cooling the inner friction plates 17 and the outer friction plates 19 . That is, the lubricating oil passages a 41 to a 44 are oil passages that are used to scatter the lubricating oil from the center side of the clutch K 0 to lubricate the clutch K 0 .

The lubricating oil supplied from the lubricating oil passage a 41 formed in the input shaft 15 to a lubricating oil passage a 45 formed by the gap between the engine coupling shaft 13 and the input shaft 15 is guided to the inner peripheral side of the coupling member 285 through oil passages a 46 , a 47 formed in the engine coupling shaft 13 , thereby lubricating the first one-way clutch F 1 and lubricating the second one-way clutch F 2 and the ball bearing b 2 through the key groove of the coupling member 285 .

The hybrid drive device 1 of the first embodiment configured as described above includes the engine driven oil pump 280 that generates an oil pressure to be supplied to the first lubricating oil passage, which is used to supply the lubricating oil to the first and second friction plates 17 , 19 placed in air, by the driving force of the internal combustion engine 2 regardless of engagement or disengagement of the clutch K 0 . Accordingly, drag of the clutch K 0 can be reduced as compared to, e.g., the case where lubricating oil is circulated in a case in which the first friction plates 17 and the second friction plates 19 are hermetically sealed. Moreover, especially when starting the vehicle by using the driving force of the internal combustion engine 2 , which requires a large amount of lubricating oil for the first and second friction plates 17 , 19 placed in the air, the clutch K 0 can be engaged with a sufficient amount of lubricating oil being generated by the engine driven oil pump 280 by driving of the internal combustion engine 2 . Thus, capability to cool the clutch K 0 can be ensured.

Moreover, an increase in size of the electric oil pump can be prevented as compared to, e.g., the case where an electric oil pump is provided and the clutch K 0 is cooled by the electric oil pump. This eliminates the need to secure a large amount of lubricating oil by the electric oil pump. Since an increase in size of the electric oil pump can be prevented, mountability on vehicles can be improved and cost reduction can be achieved.

Moreover, the engine driven oil pump 280 can be rotated by the driving force of the internal combustion engine 2 via the first one-way clutch F 1 during hybrid driving using the driving force of the internal combustion engine 2 , and can be rotated by the driving force of the motor 3 via the second one-way clutch F 2 during EV driving using the driving force of the motor 3 . This can eliminate the need for, e.g., the input-shaft cooperative oil pump 70 , whereby the hybrid drive device 1 can be made compact, and cost reduction can be achieved.

Since the control portion 20 is provided which controls the hydraulic control device 21 so as to supply the oil pressure generated by the engine driven oil pump 280 to the clutch K 0 while the clutch K 0 is slipped. Thus, capability to cool the clutch K 0 can be ensured even when the clutch K 0 is in the slipped state.

Since the configuration, operation, and effects of the hybrid drive device 1 according to the first embodiment are otherwise similar to those of the first reference example, description thereof will be omitted.

Second Embodiment

A second embodiment, which is obtained by partially changing the first embodiment, will be described with reference to FIG. 5 . In the description of the second embodiment, portions similar to those of the first embodiment are denoted by the same reference characters, and description thereof will be omitted.

An input portion 9 4 of the second embodiment is different from the first embodiment in that the first one-way clutch F 1 and the second one-way clutch F 2 are extended in the axial direction in order to increase their torque capacity. An angular ball bearing 90 is placed in the resultant axially relatively long space formed on the outer peripheral side of the first and second one-way clutches F 1 , F 2 , so that the rotor hub 51 of the motor 3 is rotatably supported with respect to a pump body 383 of an engine driven oil pump 380 by the angular ball bearing 90 .

The rotor 4 is thus supported with relatively high accuracy by the angular ball bearing 90 . This eliminates the need to support the rotor 4 by the clutch drum of the clutch K 0 , namely the need for the double-supported structure, and thus eliminates the need for such a support structure of the rotor hub 51 by the cylinder member 41 and the drum member 42 as in the first embodiment. Accordingly, the cylinder member 41 need not be supported with respect to the housing case 26 (see FIG. 4 ), and the partition wall of the housing case 26 can be eliminated, whereby the hybrid drive device 1 can be made compact in the axial direction.

The input portion 9 4 according to the second embodiment will be described below with reference to FIG. 5 . The engine coupling shaft 13 that is connected to the internal combustion engine 2 via the damper 12 of the connection portion 14 , and the input shaft 15 of the speed change mechanism 7 are coaxially arranged on the center side of the housing case 26 . The engine coupling shaft 13 has a recessed portion 13 b formed in its end located on the opposite side from the engine 2 , so that the recessed portion 13 b has its central portion recessed toward the engine 2 . The tip end on the engine 2 side of the input shaft 15 is inserted in the recessed portion 13 b . That is, the tip end of the input shaft 15 is fitted in the recessed portion 13 b , so that the engine coupling shaft 13 and the input shaft 15 are rotatable relative to each other and form a single shaft shape. The outer peripheral surface of the input shaft 15 and the recessed portion 13 b of the engine coupling shaft 13 are sealed by a seal ring (seal member) d 1 buried in the circumferential direction in the outer peripheral surface of the input shaft 15 . The oil passage structure will be described in detail later.

The engine coupling shaft 13 is rotatably supported with respect to the partition wall 27 by a ball bearing b 3 , and is rotatably supported with respect to the partition wall 27 via a support member 386 , which is fixed to the pump body 383 fixed to the partition wall 27 and described in detail below, the angular ball bearing 90 , a sleeve portion 51 d of the rotor hub 51 , and a coupling mechanism 390 of the engine driven oil pump 380 . The coupling mechanism 390 of the engine driven oil pump 380 is formed by a coupling member 385 coupled to a drive gear 381 of the engine driven oil pump 380 , the one-way clutch F 2 placed between the sleeve portion 51 d of the rotor hub 51 and the coupling member 385 and needle bearings b 23 , b 24 placed at both ends of the one-way clutch F 2 , and the one-way clutch F 2 placed between the engine coupling member 13 and the coupling member 385 and needle bearings b 21 , b 22 placed at both ends of the one-way clutch F 1 .

The input shaft 15 is rotatably supported by a needle bearing b 13 with respect to a sleeve-like member 25 provided on the inner periphery of a boss portion 24 a formed on the inner peripheral side of the partition wall 24 fixed to the transmission case 23 (see FIG. 2 ).

The flange portion 13 a is formed at the rear end on the speed change mechanism 7 side of the engine coupling shaft 13 . A clutch hub 149 , with which the plurality of inner friction plates 17 of the clutch K 0 are spline engaged, are fixedly attached to the flange portion 13 a . That is, the inner friction plates 17 are drivingly coupled to the engine coupling shaft 13 .

The clutch K 0 generally has the plurality of inner friction plates 17 , the outer friction plates 19 arranged alternately with the inner friction plates 17 , and a hydraulic servo 140 that performs engagement/disengagement of (engages or disengages) the inner friction plates 17 and the outer friction plates 19 . The hydraulic servo 140 has a cylinder member 141 forming a hydraulic cylinder of the hydraulic servo 140 , drivingly coupled to the input shaft 15 by spline engagement, and rotatably supported by the boss portion 24 a , a drum member 142 fixedly attached to the outer peripheral side of a flange portion 141 b of the cylinder member 141 , a piston 143 placed so as to be axially movable with respect to the cylinder member 141 and placed so that its tip end faces the outer friction plate 19 (or the inner friction plate 17 ), a return plate 144 positioned with respect to a boss portion 141 a of the cylinder member 141 by a snap ring 148 , and a return spring 145 provided in a compressed manner between the piston 143 and the return plate 144 . A hydraulic oil chamber 146 is formed between the cylinder member 141 and the piston 143 , and a canceling oil chamber 147 that cancels a centrifugal oil pressure is formed between the piston 143 and the return plate 144 .

The cylinder member 141 and the drum member 142 form an integral clutch drum, and the plurality of outer friction plates 19 are spline engaged with the inner side of the drum member 142 . That is, the outer friction plates 19 are drivingly coupled to the input shaft 15 via the drum member 142 and the cylinder member 141 . Splines 142 s are formed on the outer peripheral side of the drum member 142 forming the clutch drum, and are spline engaged with splines 51 s of the rotor hub 51 described in detail below. That is, the rotor 4 of the motor 3 is drivingly coupled to the input shaft 15 via the clutch drum of the clutch K 0 . The boss portion 141 a of the cylinder member 141 is rotatably positioned in the axial direction by thrust bearings b 14 , b 15 between the boss portion 24 a of the partition wall 24 and the flange portion 13 a of the engine coupling shaft 13 .

The drum member 142 of the clutch drum of the clutch K 0 is open to the engine 2 side in the axial direction, and a through hole 142 a is formed in the drum member 142 so as to at least partially overlap the outer friction plate 19 as viewed in the radial direction. The lubricating oil flowing from a through hole 149 a formed in the clutch hub 149 flows between the inner and outer friction plates 17 , 19 to lubricate and cool the inner and outer friction plates 17 , 19 , and is discharged from the through hole 142 a (part of the lubricating oil is discharged from the open side of the drum member 142 ) into the housing case 26 . That is, the clutch K 0 is a wet multi-plate clutch in which the inner friction plates 17 and the outer friction plates 19 are not made oil-tight (non-oil-tight) and are open to the atmosphere in the housing case 26 so that the inner friction plates 17 and the outer friction plates 19 are arranged in air. A wall-like portion 26 b surrounding the coil end 5 b described below is formed in the housing case 26 , so that the lubricating oil that has cooled the clutch K 0 is prevented from directly contacting the coil end 5 b.

The stator 5 of the motor 3 is fixed between the outer peripheral side of the clutch K 0 and the inner peripheral side of the housing case 26 by fastening the stator 5 to the partition wall 27 fixed to the housing case 26 by using a bolt 99 . The stator 5 has the stator core 5 a , and the coil ends 5 b , 5 b forming looped portions of a coil wound around the stator core 5 a and protruding on both axial sides of the stator core 5 a . The rotor 4 of the motor 3 is placed so as to face the inner peripheral side of the stator core 5 a with a predetermined gap therebetween. Since the stator 5 is fixed to the partition wall 27 , the stator 5 is satisfactory as a support structure with the rotor 4 rotatably supported by the partition wall 27 . In this case, the number of locations for fixing a part is reduced by one as compared to the case where, e.g., the stator 5 is fixed to the housing case 26 . Thus, the support accuracy of the stator 5 and the rotor 4 is improved.

The rotor hub 51 supporting the rotor 4 has the drum-shaped holding portion 51 b that grips and holds the rotor core 4 a of the rotor 4 , the flange-shaped support portion 51 a that supports the holding portion 51 b , and the sleeve portion 51 d having a sleeve shape and connected to the inner peripheral side of the support portion 51 a . The holding portion 51 b and the support portion 51 a are welded together, and the support portion 51 a and the sleeve portion 51 d are welded together, thereby forming the integral rotor hub 51 . The angular ball bearing 90 formed by two ball bearings b 11 , b 12 is fastened by a nut 393 , whereby the sleeve portion 51 d is rotatably supported with respect to the support member 386 fixed to the pump body 383 . The support portion 51 a is also supported in the axial direction by a thrust bearing b 16 with respect to the clutch hub 149 welded to the flange portion 13 a of the engine coupling shaft 13 .

A retaining member 95 is placed between the thrust bearing b 16 and the support portion 51 a of the rotor hub 51 so as to be fitted in a through hole 51 f . An outer peripheral portion of the retaining member 95 is bent toward the engine 2 so that the lubricating oil flowing from the inner peripheral side is guided to the angular ball bearing 90 .

The support member 386 supporting the angular ball bearing 90 is configured as a separate member from the pump body 383 of the engine driven oil pump 380 described in detail below, and is placed so as to cover the outer peripheral side of the angular ball bearing 90 . Since the support member 386 is thus configured as a separate member from the pump body 383 , the set of the rotor hub 51 , the angular ball bearing 90 , and the support member 386 can be fixed to the pump body 383 after fastening the angular ball bearing 90 to the rotor hub 51 by a nut 392 .

A rotor (exciting coil) 161 is fixedly attached to the inner peripheral side of the rotor hub 51 supporting the rotor 4 of the motor 3 , and a stator (detection coil) 162 is fixedly attached to the outer peripheral side of the support member 386 by a bolt 169 so as to face the rotor 161 . The rotor 161 and the stator 162 form a resolver 160 that detects rotation of the motor 3 .

Specifically, when mounting the rotor hub 51 , the rotor 161 of the resolver 160 is fixedly attached to the inner peripheral side of the rotor hub 51 , and the stator 162 of the resolver 160 is fixedly attached to the outer peripheral side of the support member 386 by the bolt 169 . The circumferential position of the bolt 169 that fixes the stator 162 of the resolver 160 is located in phase with a bolt 389 that fastens the pump body 383 and a pump cover 384 .

Next, the ball bearing b 12 is mounted to the support member 386 so as to contact a protruding portion 386 b of the support member 386 , the ball bearing b 12 is fixed to the support member 386 by a snap ring 91 , and the ball bearing b 11 is mounted to the support member 386 . Then, the rotor hub 51 is mounted to the inner peripheral side of the angular ball bearing 90 , and is fastened by the nut 392 . A protruding portion 386 a formed on the engine 2 side of the support member 386 is fitted in the pump body 383 like a spigot joint, and a plurality of bolt holes 386 c formed in the support member 386 are aligned with through holes 51 e of the rotor hub 51 in the rotating direction. A plurality of bolts 391 are fixedly attached to the pump body 383 via the support member 386 , whereby the support member 386 is mounted to the pump body 383 . The number of through holes 51 e of the rotor hub 51 may be one, or may be the same as the plurality of bolt holes 386 c.

The structure of the engine driven oil pump 380 will be described below. The engine driven oil pump 380 is provided on the outer periphery of the engine coupling shaft 13 so as to be located between the internal combustion engine 2 (the connection portion 14 ) and the clutch K 0 in the axial direction, and to be located on the inner peripheral side of the coil end 5 b on the internal combustion engine 2 side of the motor 3 .

The engine driven oil pump 380 has a drive gear 381 and a driven gear 382 which form an internal gear oil pump, and has the pump body 383 accommodating the drive gear 381 and the driven gear 382 , and the pump cover 384 . The engine driven oil pump 380 is formed by fastening the pump body 383 to the pump cover 384 by the bolt 389 so that the pump cover 384 closes the gear accommodating portion of the pump body 383 . A hole 383 a in which the bolt 389 is tightened is formed in the pump body 383 . The hole 383 a is formed in phase with the bolt 169 that fixes the stator 162 of the resolver 160 as described above.

An outer edge portion of the pump body 383 is fastened to the partition wall 27 by a bolt 388 , so that the engine driven oil pump 380 is fixed to and supported by the partition wall 27 and the housing case 26 . Thus, the pump body 383 supports the rotor hub 51 and the rotor 4 with high accuracy via the support member 386 and the angular ball bearing 90 , and rotatably supports the engine coupling shaft 13 via the needle bearings b 21 , b 22 , b 23 , b 24 and the coupling member 385 described in detail below.

The drive gear 381 of the engine driven oil pump 380 can be drivingly coupled to the engine coupling shaft 13 and the rotor hub 51 (i.e., the rotor 4 ) via the coupling mechanism 390 . That is, the drive gear 381 of the engine driven oil pump 380 is drivingly coupled to the coupling member 385 rotatably placed on the outer peripheral side of the engine coupling shaft 13 . Specifically, this driving coupling is implemented by engaging a key formed on the inner peripheral side of the drive gear 381 with a key groove formed in the coupling member 385 . The first one-way clutch F 1 is provided on the inner peripheral side of the rear end side (the speed change mechanism 7 side) of the coupling member 385 so as to be interposed between the coupling member 385 and the engine coupling shaft 13 . The second one-way clutch F 2 is provided on the outer peripheral side of the rear end side (the speed change mechanism 7 side) of the coupling member 385 so as to be interposed between the coupling member 385 and the sleeve portion 51 d of the rotor hub 51 .

In the second embodiment, the axial lengths of the first and second one-way clutches F 1 , F 2 are increased in order to increase the torque capacity of the first and second one-way clutches F 1 , F 2 . Moreover, the needle bearings b 21 , b 22 are placed on both sides of the first one-way clutch F 1 in the axial direction and the needle bearings b 23 , b 24 are placed on both sides of the second one-way clutch F 2 in the axial direction in order to achieve satisfactory tilting accuracy when the first and second one-way clutches F 1 , F 2 are engaged. This improves rotation support accuracy of the engine coupling shaft 13 that is supported via the angular ball bearing 90 and the needle bearings b 21 , b 22 , b 23 , b 24 .

According to the coupling mechanism 390 thus configured, when rotation of the engine coupling shaft 13 (i.e., the internal combustion engine 2 ) becomes lower than rotation of the coupling member 385 , the first one-way clutch F 1 is not engaged. When the rotation of the coupling member 385 becomes equal to the rotation of the engine coupling shaft 13 , the first one-way clutch F 1 is engaged, and the engine driven oil pump 380 is drivingly coupled to the internal combustion engine 2 , and is driven by the driving force of the internal combustion engine 2 . When rotation of the rotor hub 51 (i.e., the motor 3 ) becomes lower than rotation of the coupling member 385 , the second one-way clutch F 2 is not engaged. When the rotation of the coupling member 385 becomes equal to the rotation of the rotor hub 51 , the second one-way clutch F 2 is engaged, and the engine driven oil pump 380 is drivingly coupled to the motor 3 , and is driven by the driving force of the motor 3 .

That is, the engine driven oil pump 380 is placed so that it can be drivingly coupled to the transmission path L 1 located on the internal combustion engine 2 side of the clutch K 0 , and so that it can be drivingly coupled to the transmission path L 2 located on the speed change mechanism 7 side of the clutch K 0 (see FIG. 1 ). When the clutch K 0 is engaged, the transmission path L 1 is drivingly coupled to the transmission path L 2 , whereby rotation of the internal combustion engine 2 becomes equal to rotation of the motor 3 , and the engine driven oil pump 380 is driven by this rotation.

The engine driven oil pump 380 , which is thus drivingly coupled to the engine coupling shaft 13 via the first one-way clutch F 1 or is drivingly coupled to the rotor hub 51 via the second one-way clutch F 2 , is driven by the driving force of the motor 3 or by the inertial force of the vehicle via the speed change mechanism 7 when in the coast state (when the engine brake is in operation) during EV driving, and is driven by the driving forces of the motor 3 and the internal combustion engine 2 or by the inertial force of the vehicle via the speed change mechanism 7 when in the coast state (when the engine brake is in operation) during hybrid driving.

When starting the vehicle from its stopped state by the driving force of the internal combustion engine 2 while slip engaging the clutch K 0 , the first one-way clutch F 1 is engaged from before engagement of the clutch K 0 (i.e., from when the vehicle is in the stopped state), and thus the engine driven oil pump 380 is driven by the driving force of the internal combustion engine 2 .

When driven in this manner, the engine driven oil pump 380 sucks oil from an input port 380 a communicating with the oil pan, not shown, and generates an oil pressure from a discharge port 380 b , even while the vehicle is stopped. The oil pressure thus generated is supplied to the hydraulic control device 21 through an oil passage formed in the partition wall 27 , etc. Accordingly, when starting the vehicle by the driving force of the internal combustion engine 2 , not only the oil pressure of the electric oil pump, not shown, but also the oil pressure of the engine driven oil pump 380 are applied. Thus, the lubrication pressure, which is used to supply a large amount of lubricating oil required in the slip engaged state when starting the vehicle, can be generated not only by the electric oil pump but also by the engine driven oil pump 380 .

Various oil passage structures in the input portion 9 4 will be described below with reference to FIGS. 5 and 6 . As shown in FIG. 5 , the engagement pressure of the clutch K 0 , which is supplied from the hydraulic control device 21 through the partition wall 24 , flows from an oil passage a 51 of the sleeve-like member 25 and through an oil passage a 52 of the boss portion 24 a , and communicates with the hydraulic oil chamber 146 via an oil passage a 53 of the cylinder member 141 of the clutch drum.

When the engagement pressure is supplied from the hydraulic control device 21 to the hydraulic oil chamber 146 of the hydraulic servo 140 through the oil passages a 51 , a 52 formed in the partition wall 24 and the sleeve-like member 25 and the oil passage a 53 formed in the boss portion 141 a of the cylinder member 141 based on a command of the control portion 20 , the piston 143 moves forward in the axial direction against the biasing force of the return spring 145 to engage the inner friction plates 17 and the outer friction plates 19 . Thus, the internal combustion engine 2 is drivingly coupled to the speed change mechanism 7 , and the vehicle 100 is brought into a hybrid driving state where the vehicle 100 can travel by using the driving forces of the internal combustion engine 2 and the motor 3 .

On the contrary, when the engagement pressure is discharged (drained) from the hydraulic oil chamber 146 of the hydraulic servo 140 through the oil passages a 51 to a 53 by the hydraulic control device 21 based on a command of the control portion 20 , the piston 143 moves rearward in the axial direction based on the biasing force of the return spring 145 to disengage the inner friction plates 17 and the outer friction plates 19 . Thus, the internal combustion engine 2 is disconnected from the speed change mechanism 7 , and the vehicle 100 is brought into an EV driving state where the vehicle 100 can travel by using only the driving force of the motor 3 .

In a portion not shown in the figure, the lubricating oil that lubricates the clutch K 0 is supplied from the partition wall 24 through the sleeve-like member 25 to an oil passage (first oil passage) a 61 formed in the axial direction in the input shaft 15 . The oil passage a 61 has its end closed on the engine 2 side of the input shaft 15 . The oil passage a 61 communicates with an oil passage a 63 of the cylinder member 141 through a radial oil passage (second oil passage) a 62 formed so as to extend through the input shaft 15 , and communicates with the cancelling oil chamber 147 .

The oil passage a 61 is open to the outer peripheral side of the input shaft 15 through a radial oil passage a 64 formed in the input shaft 15 . The lubricating oil that is scattered from the oil passage a 64 lubricates the thrust bearing b 15 between the cylinder member 141 and the engine coupling shaft 13 , and is guided radially inward of the clutch hub 149 . The lubricating oil is further guided to the inner friction plates 17 and the outer friction plates 19 through the through hole 149 a of the clutch hub 149 . The lubricating oil that has lubricated the inner friction plates 17 and the outer friction plates 19 of the clutch K 0 is discharged to the outside of the clutch K 0 within the housing case 26 through the through hole 142 a of the drum member 142 of the clutch drum. This lubricating oil is guided along the inner wall of the housing case 26 by the wall-like portion 26 b so as not to contact the coil end 5 b , and is collected by the oil pan, not shown.

In a portion not shown in the figure, the lubricating oil that lubricates the motor 3 is supplied from the partition wall 24 through the sleeve-like member 25 to an oil passage (third oil passage) a 71 formed in the axial direction in the input shaft 15 so as to be parallel to the oil passage a 61 . The oil passage a 71 has its end opened on the engine 2 side of the input shaft 15 . The lubricating oil flows into an oil passage a 72 in the recessed portion 13 b of the engine coupling shaft 13 , flows through an oil passage (fourth oil passage) a 73 formed in the axial direction in the recessed portion 13 b , and is discharged to the inner peripheral side of the coupling member 385 through an oil passage (fifth oil passage) a 74 formed in the radial direction so as to extend through the engine coupling shaft 13 .

Part of the lubricating oil discharged to the inner peripheral side of the coupling member 385 is guided to an oil passage a 75 formed in the radial direction in the coupling member 385 , and the remaining lubricating oil is guided to the needle bearing b 22 , the first one-way clutch F 1 , and the needle bearing b 21 . Since the oil passage a 75 has a smaller sectional area (i.e., a smaller diameter) than the oil passage a 74 , an appropriate amount of the lubricating oil is directed from the oil passage a 74 to the oil passage a 75 , and the remaining lubricating oil is guided to the needle bearing b 22 , the first one-way clutch F 1 , and the needle bearing b 21 .

Part of the lubricating oil that has passed through the oil passage a 75 is also guided to the needle bearing b 24 , the second one-way clutch F 2 , and the needle bearing b 23 , and lubricates the needle bearing b 24 , the second one-way clutch F 2 , and the needle bearing b 23 . The lubricating oil that has lubricated the needle bearing b 22 , the first one-way clutch F 1 , and the needle bearing b 21 , and the lubricating oil that has lubricated the needle bearing b 24 , the second one-way clutch F 2 , and the needle bearing b 23 are guided to the thrust bearing b 16 provided at the tip end of the flange portion 13 a of the engine coupling shaft 13 , and are guided to the through hole 51 f of the rotor hub 51 by the retaining member 95 described above, thereby lubricating the angular ball bearing 90 .

The lubricating oil that has thus lubricated the angular ball bearing 90 and the lubricating oil that has been guided from the oil passage a 75 to the outer peripheral side gather toward the lower side along the inner surface of the support member 386 held stationary, and are guided to the inside of the rotor hub 51 through a groove 386 d formed on the lower side of the support member 386 . The lubricating oil thus guided to the inside of the rotor hub 51 is directed in the axial direction by an oil passage a 82 through an oil passage a 81 formed in the rotor hub 51 , and is supplied to both coil ends 5 b , 5 b from oil passages a 83 , a 84 , thereby cooling the motor 3 .

A lubricating circuit that supplies lubrication in the hydraulic control device 21 will be described with reference to FIG. 6 . As shown in FIG. 6 , the hydraulic control device 21 that is controlled by the control portion 20 has an oil pressure supply source 400 that regulates the oil pressure generated by the engine driven oil pump 380 or the electric oil pump to a lubrication pressure (e.g., a secondary pressure etc.) by a regulator valve, not shown, etc. and outputs the lubrication pressure to an oil passage c 1 . The hydraulic control device 21 has oil passages c 11 to c 14 as the first lubricating oil passage that branches off from the oil passage c 1 to connect to the oil passage a 61 as a lubricating oil passage of the clutch K 0 , and an oil passage c 21 as the second lubricating oil passage that branches off from the oil passage c 1 to connect to the oil passage a 71 as a lubricating oil passage of the motor 3 . The first lubricating oil passage is provided with flow rate adjusting means 410 that adjusts the amount of lubricating oil. That is, the second lubricating oil passage branches off from the oil passage c 1 at a position upstream of the flow rate adjusting means 410 , and is not affected so much by the flow rate adjustment of the flow rate adjusting means 410 described in detail later.

In the present embodiment, the first lubricating oil passage is defined as an oil passage including the oil passages c 11 to c 14 branching off from the oil passage c 1 , and the oil passages a 61 to a 64 (see FIG. 5 ). The second lubricating oil passage is defined as an oil passage including the oil passage c 21 branching off from the oil passage c 1 , the oil passages a 71 to a 75 , and the oil passages a 81 to a 84 (see FIG. 5 ).

The flow rate adjusting means 410 has a solenoid valve SL that outputs an ON/OFF signal pressure, a switch valve 401 that is switched by the signal pressure, a small diameter orifice 403 provided in the oil passage c 12 , and a large diameter orifice 402 provided in the oil passage c 13 .

Accordingly, when, e.g., disengagement of the clutch K 0 is performed or engagement of the clutch K 0 is completed, and only a small amount of lubricating oil is required for the inner friction plates 17 and the outer friction plates 19 , the solenoid valve SL is switched off according to a command of the control portion 20 , and the switch valve 401 is switched to the OFF position, whereby the oil pressure supply source 400 communicates with the oil passage a 61 , which is located upstream of the lubricating oil passage of the clutch K 0 , through the path passing through the small diameter orifice 403 , namely through the oil passages c 1 , c 11 , c 12 , c 14 . Thus, a sufficient small amount of lubricating oil is supplied to the clutch K 0 .

When, e.g., the operation of engaging the clutch K 0 is being performed (during slipping), and a large amount of lubricating oil is required due to a large amount of heat generation of the inner friction plates 17 and the outer friction plates 19 , the solenoid valve SL is switched on according to a command of the control portion 20 , and the switch valve 401 is switched to the ON position, whereby the oil pressure supply source 400 communicates with the oil passage a 61 , which is located upstream of the lubricating oil passage of the clutch K 0 , through the path passing through the large diameter orifice 402 , namely through the oil passages c 1 , c 11 , c 13 , c 14 . Thus, a large amount of lubricating oil is supplied to the clutch K 0 , and the clutch K 0 is sufficiently cooled.

On the other hand, the oil passage c 21 as the second lubricating oil passage is hardly affected by the flow rate adjustment of the flow rate control means 410 . After branching off from the oil passage c 1 , the oil passage c 21 , the oil passages a 71 to a 75 , and the oil passages a 81 to a 84 supply the lubricating oil to the motor 3 as a lubricating oil passage of another route without crossing the first lubricating oil passage (the oil passages c 11 to c 14 , the oil passages a 61 to a 64 ). Thus, the motor 3 can be cooled with a stable amount of lubricating oil without being affected by heat generation of the clutch K 0 .

As described above, the hybrid drive device 1 of the second embodiment includes the engine driven oil pump 380 that generates an oil pressure to be supplied to the first lubricating oil passage, which is used to supply the lubricating oil to the first and second friction plates 17 , 19 placed in air, by the driving force of the internal combustion engine 2 regardless of engagement or disengagement of the clutch K 0 . Accordingly, drag of the clutch K 0 can be reduced as compared to, e.g., the case where lubricating oil is circulated in a case in which the first friction plates 17 and the second friction plates 19 are hermetically sealed. Moreover, especially when starting the vehicle by using the driving force of the internal combustion engine 2 , which requires a large amount of lubricating oil for the first and second friction plates 17 , 19 placed in the air, the clutch K 0 can be engaged with a sufficient amount of lubricating oil being generated by the engine driven oil pump 380 by driving of the internal combustion engine 2 . Thus, capability to cool the clutch K 0 can be ensured.

Moreover, an increase in size of the electric oil pump can be prevented as compared to, e.g., the case where an electric oil pump is provided and the clutch K 0 is cooled by the electric oil pump. This eliminates the need to secure a large amount of lubricating oil by the electric oil pump. Since an increase in size of the electric oil pump can be prevented, mountability on vehicles can be improved and cost reduction can be achieved.

The hybrid drive device 1 of the second embodiment is structured to include the clutch K 0 formed by the inner friction plates 17 and the outer friction plates 19 which are placed so as to be open in the housing case 26 , and further includes the engine driven oil pump 380 that generates an oil pressure to be supplied to the lubricating oil passage by the driving force of the internal combustion engine 2 regardless of engagement or disengagement of the clutch K 0 . Accordingly, especially when starting the vehicle by using the driving force of the internal combustion engine 2 , which requires a large amount of lubricating oil for the inner and outer friction plates 17 , 19 placed in the air, the clutch K 0 can be engaged with a sufficient amount of lubricating oil being generated by the engine driven oil pump 380 by driving of the internal combustion engine 2 . This eliminates the need to secure a large amount of lubricating oil by the electric oil pump, and prevents an increase in size of the electric oil pump, whereby mountability on vehicles can be improved and cost reduction can be achieved.

Since the second lubricating oil passage that supplies the lubricating oil to the motor 3 is provided, oil can be supplied to the motor 3 from the second lubricating oil passage independently of the first lubricating oil passage. Thus, oil can be supplied at a required flow rate to the clutch K 0 without being affected by oil supply to the motor 3 .

Moreover, the first lubricating oil passage is formed by the oil passage a 61 and the oil passage a 64 , the second lubricating oil passage is formed by the oil passage a 71 , the oil passage a 73 , and the oil passage a 74 , and the seal ring d 1 is placed between the input shaft 15 and the recessed portion 13 b . This can prevent the first and second lubricating oil passages from crossing each other.

The engine driven oil pump 380 can be rotated by the driving force of the engine 2 via the first one-way clutch F 1 during hybrid driving using the driving force of the engine 2 , and can be rotated by the driving force of the motor 3 via the second one-way clutch F 2 during EV driving using the driving force of the motor 3 . This can eliminate the need for, e.g., the input-shaft cooperative oil pump, whereby the hybrid drive device can be made compact, and cost reduction can be achieved. Since the first one-way clutch F 1 and the second one-way clutch F 2 can be lubricated by the oil supplied from the second lubricating oil passages c 21 , a 71 to a 75 , a required flow rate can be supplied to the clutch K 0 without being affected by lubrication of the first one-way clutch F 1 and the second one-way clutch F 2 . Moreover, the first one-way clutch F 1 and the second one-way clutch F 2 can be cooled with a stable amount of lubricating oil without being affected by heat generation of the clutch K 0 .

Moreover, the oil that has lubricated the first one-way clutch F 1 and the second one-way clutch F 2 is supplied to the motor 3 . This can reduce the size of the engine driven oil pump 380 and the electric oil pump as compared to the case where a lubricating oil passage that is used to lubricate the first one-way clutch F 1 and the second one-way clutch F 2 is additionally provided independently of the first lubricating oil passage and the second lubricating oil passage.

Since the motor 3 is lubricated by the second lubricating oil passage c 21 , a 71 to a 75 , a 81 to a 84 branched off from the first lubricating oil passage at a position upstream of the flow rate adjusting means 410 , a required flow rate can be supplied to the clutch K 0 without being affected by cooling of the motor 3 . Moreover, the motor 3 can be cooled by the second lubricating oil passage that does not cross the first lubricating oil passage c 11 to c 14 , a 61 to a 64 , while being hardly affected by the flow rate adjustment of the flow rate adjusting means 410 , and the motor 3 can be cooled with a stable amount of lubricating oil without being affected by heat generation of the clutch K 0 .

Moreover, the drum member 142 of the clutch drum of clutch K 0 has the through hole 142 a that is positioned so as to at least partially overlap the outer friction plate 19 as viewed in the radial direction and that discharges the oil supplied to the inner friction plates 17 and the outer friction plates 19 . This allows a large amount of lubricating oil that has cooled the inner friction plates 17 and the outer friction plates 19 to be discharged and circulated in the housing case 26 .

Since the control portion 20 is provided which controls the hydraulic control device 21 so as to supply the oil pressure generated by the engine driven oil pump 380 to the clutch K 0 while the clutch K 0 is slipped. Thus, capability to cool the clutch K 0 can be ensured even when the clutch K 0 is in the slipped state.

Third Embodiment

A third embodiment, which is obtained by partially changing the second embodiment, will be described with reference to FIG. 7 . In the description of the third embodiment, portions similar to those of the second embodiment are denoted by the same reference characters, and description thereof will be omitted.

An input portion 9 5 of the third embodiment is different from the second embodiment in that an engine driven oil pump 580 is placed on the outer periphery of the transmission case 23 so as to be located on the speed change mechanism 7 side of the motor 3 on an axis parallel to the engine coupling shaft 13 . The stator 162 of the resolver 160 is not fixed to the support member 386 of the angular ball bearing 90 but to a cylindrical base portion 27 a of the partition wall 27 by the bolt 169 , and the support member 386 is fixed to the base portion 27 a by the bolt 391 .

Specifically, the coupling member 385 is placed so that it can be coupled to one of the engine coupling shaft 13 (i.e., the engine 2 ) and the rotor hub 51 (the motor 3 ), which has a higher rotational speed, via the first one-way clutch F 1 and the second one-way clutch F 2 , and the axial tip end on the engine 2 side of the coupling member 385 is spline engaged with a sprocket 571 that is rotatably supported by the partition wall 27 via a ball bearing b 31 , and is drivingly coupled to the sprocket 571 in the rotating direction.

A chain 570 meshes with the sprocket 571 , and a sprocket 572 meshing with the chain 570 is placed on an axis parallel to the sprocket 571 . The sprocket 572 is rotatably supported by a ball bearing b 32 with respect to the partition wall 27 , and the inner peripheral side of the sprocket 572 is spline engaged with a transmission shaft 573 so that the sprocket 572 is drivingly coupled to the transmission shaft 573 in the rotating direction.

The transmission shaft 573 is placed so as to extend through a through hole 26 c formed in the housing case 26 . The transmission shaft 573 is rotatably supported by the partition wall 27 via the sprocket 572 and the ball bearing b 32 , and is rotatably supported by the partition wall 24 fixedly attached to the transmission case 23 via a ball bearing b 33 . That is, the transmission shaft 573 is rotatably supported by the double-supported structure.

The engine driven oil pump 580 of the third embodiment is a so-called internal gear pump, and has a drive gear 581 drivingly coupled to the transmission shaft 573 , a driven gear 582 placed so as to mesh with the outer periphery of the drive gear 581 , a pump body 587 covering the drive gear 581 and the driven gear 582 from the outer peripheral side, and a pump cover 584 closing the pump body 587 . The pump body 587 is fixed to the partition wall 24 by a bolt 588 , and the pump cover 584 is fixed to the partition wall 24 by a bolt 589 via the pump body 587 .

The engine driven oil pump 580 is placed so as to be integrally fixed to the transmission case 23 , and to protrude to the outside from a body portion of the transmission case 23 . The engine driven oil pump 580 is preferably placed near the oil pan, not shown, and is preferably located below the input shaft 15 . However, the engine driven oil pump 580 may be placed on a lateral side of the input shaft 15 or above the input shaft 15 .

The first one-way clutch F 1 , the second one-way clutch F 2 , the coupling member 385 , the sprocket 571 , the chain 570 , the sprocket 572 , the transmission shaft 573 , etc. described above form a transmission mechanism 590 capable of drivingly coupling the engine driven oil pump 580 to the engine coupling shaft 13 or the rotor hub 51 .

In the engine driven oil pump 580 having the above structure, when the coupling member 385 is rotated by the engine coupling shaft 13 (the engine 2 ) or the rotor hub 51 (the motor 3 ) via the first one-way clutch F 1 or the second one-way clutch F 2 , the drive gear 581 is rotated and driven via the sprocket 571 , the chain 570 , the sprocket 572 , and the transmission shaft 573 , and is rotated and driven together with the driven gear 582 meshing with the drive gear 581 , and the engine driven oil pump 580 sucks oil from an input port 580 a connected to the oil pan, and generates an oil pressure to discharge the oil pressure to an output port, not shown. The oil pressure thus generated, together with the oil pressure generated by the electric oil pump, not shown, serves as a source pressure of the oil pressure supply source 400 (see FIG. 6 ) of the hydraulic control device 21 .

As shown in FIG. 7 , the lubricating oil that has passed through the first lubricating oil passage c 11 to c 14 from the oil pressure supply source 400 flows in the partition wall 24 and the sleeve-like member 25 , is guided to an oil passage a 60 of the input shaft 15 , flows through the oil passages a 61 , a 64 and through an oil passage a 65 formed in the cylinder member 141 of the clutch K 0 , and is guided to the through hole 149 a of the clutch hub 149 to cool the inner friction plates 17 and the outer friction plates 19 . Then, this lubricating oil is discharged from the through hole 142 a of the drum member 142 into the housing case 26 , and is returned into the oil pan. The lubricating oil flows from an oil passage in the sleeve-like member 25 and between the sleeve-like member 25 and the input shaft 15 , and is supplied to the oil passage a 63 communicating with the cancelling oil chamber 147 .

As shown in FIG. 7 , the lubricating oil that has passed through the second lubricating oil passage c 21 from the oil pressure supply source 400 flows in the partition wall 24 and the sleeve-like member 25 , is guided to an oil passage a 70 of the input shaft 15 , flows through the oil passages a 71 to a 75 , and is guided to the oil passage a 81 through the groove 386 d of the support member 386 and along the inner surface of the rotor hub 51 . Then, this lubricating oil is discharged through the oil passages a 82 to a 84 to cool the coil ends 5 b , 5 b , and flows in the housing case 26 back into the oil pan.

As described above, in the input portion 9 5 of the third embodiment, the engine driven oil pump 580 is placed on the outer peripheral side of the speed change mechanism 7 . Thus, the engine driven oil pump 580 need not be placed on the inner peripheral side of the motor 3 , whereby an increase in size of the input portion 9 5 in the axial direction can be prevented, and the motor 3 and the clutch K 0 can be reduced in diameter.

In the third embodiment, a wave spring 19 w is formed on the outer peripheral side of each outer friction plate 19 of the clutch K 0 . This wave spring 19 w keeps the outer friction plates 19 and the inner friction plates 17 separated from each other at regular intervals when the clutch K 0 is disengaged, so that drag resistance is reduced.

Since the configuration, operation, and effects of the third embodiment are otherwise similar to those of the second embodiment, description thereof will be omitted.

[Other Possibilities of Hybrid Drive Device]

The hybrid drive devices 1 of the first and second reference examples and the first to third embodiments are described with respect to an example in which the motor 3 is directly drivingly coupled to the input shaft 15 via the clutch housing 50 . However, the present invention is not limited to this, and the present invention is applicable to an example in which the motor is placed on other axis parallel to the input shaft 15 and is coupled to the input shaft 15 by a gear mechanism, a chain, etc.

The first and second reference examples and the first to third embodiments are described with respect to an example in which each of the input-shaft cooperative oil pump 70 and the engine driven oil pump 80 , 180 , 280 , 380 , 580 is an internal gear pump. However, the present invention is not limited to this, and each of these oil pumps may have any structure. For example, each of these oil pumps may be a crescent internal gear pump, a vane pump, an external gear pump, etc.

In the first and second reference examples and the first to third embodiments, the hybrid drive device includes the electric oil pump, not shown, in addition to the input-shaft cooperative oil pump 70 and the engine driven oil pump 80 , 180 , 280 , 380 , 580 . However, while the vehicle is stopped with the internal combustion engine 2 being stopped (idle stop), the oil pressure can be supplied to the hydraulic control device 21 by forming a neutral state by driving the input-shaft cooperative oil pump 70 or the engine driven oil pump 80 , 180 , 280 , 380 , 580 by the motor 3 and disengaging the clutch or brake of the speed change mechanism 7 . Thus, the electric oil pump may be eliminated.

The hybrid drive device according to the present invention can be used in vehicles such as passenger ears and trucks, and are preferably used as a hybrid drive device that is required to reduce drag of an engine connecting clutch and to ensure capability to cool the engine connecting clutch.