JP2012067803A - Starting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a starting device excellent in controllability of a frictional engaging device while highly maintaining cooling performance of the frictional engaging device.SOLUTION: This starting device SM includes the frictional engaging device CL arranged so as to be capable of switching the transmission and cutoff of driving force between an input member I driven by/connected to an internal combustion engine and an output member M driven by/connected to a wheel. The frictional engaging device CL includes a pair of frictional members 31, an inside support member 21, an outside support member 26, a pressing member 41, a return spring 49, and a holding member 47. The inside support member 21 includes a first oil supply part P1 arranged on the pressing direction side to the holding member 47, filling oil in a housing CH for storing the frictional engaging device CL and supplying the oil to a radial directional inside end part of a first space V1 between the holding member 47 and the inside support member 21, and a second oil supply part P2 for supplying the oil to a radial directional inside end part of a second space V2 between the holding member 47 and the pressing member 41.

Description

  The present invention relates to a starting device including a friction engagement device that is provided so as to be able to switch between transmission and interruption of a driving force between an input member that is drivingly connected to an internal combustion engine and an output member that is drivingly connected to a wheel.

  In general, in a so-called engine vehicle having only an internal combustion engine as a driving force source, when the vehicle starts, the differential rotational speed between an input member that is drivingly connected to the internal combustion engine and an output member that is drivingly connected to wheels is absorbed. However, a starting device that transmits the driving force between them is required. Such a starting device is, for example, in a hybrid vehicle including an internal combustion engine and a rotating electrical machine as a driving force source, by drivingly connecting the rotating electrical machine to the output side of the starting device and driving the rotating electrical machine in a state where the internal combustion engine is disconnected. It can also be used for the purpose of starting the vehicle by force.

  As such a starting device, for example, the following Patent Document 1 is provided to be able to switch between transmission and interruption of driving force between an input member drivingly connected to an internal combustion engine and an output member drivingly connected to a wheel. Devices with friction engagement devices have been proposed. In such a starting device, the state of the friction engagement device is appropriately switched between the released state, the slip state, and the fully engaged state by controlling the supply hydraulic pressure, thereby absorbing the differential rotational speed and separating the internal combustion engine. A state can be realized.

  Here, in the starting device described in Patent Document 1, the inner support member (clutch hub) that supports one of the pair of friction members (friction plates) (inner friction plate) from the radially inner side is the holding member (return plate). ) Through the pressing direction side of the pressing member (piston) that presses the friction member in the axial direction. Then, in the axial direction in the housing, oil is supplied from the radially inner end of the space formed between the holding member (return plate) holding the return spring and the inner support member, and the supplied oil is Flows radially outward along the inner support member within the housing, cools the plurality of friction members of the friction engagement device (wet multi-plate clutch mechanism), and then presses the inner support member in the pressing direction on the inner support member Along the inner diameter of the housing and discharged to the outside of the housing. In that case, oil distribute | circulates in the state with which it filled with the housing which accommodates a friction engagement apparatus. Therefore, the cooling performance of the friction engagement device can be maintained high.

  However, in the starting device of Patent Document 1, in the axial direction in the housing, in the space formed between the holding member and the pressing member, only the radially outer end is opened and the radially inner end is closed. ing. Therefore, when oil flows through the housing as described above, it is difficult for oil to flow into the space between the holding member and the pressing member, and the oil in the space is sucked by the oil flowing radially outward. . Therefore, the hydraulic pressure level locally decreases in the space, and a negative pressure relative to other parts (hereinafter, such a relative negative pressure is simply referred to as “negative pressure”). May occur. When such a negative pressure is generated, a force for moving the pressing member to the holding member side (pressing direction side) acts on the pressing member, which may affect the controllability of the friction engagement device. is there. Therefore, there remains room for improvement regarding the controllability of the friction engagement device.

JP 2010-105615 A

  Therefore, it is desired to realize a starter that is excellent in controllability while maintaining high cooling performance of the friction engagement device.

  Features of a starter device including a friction engagement device that can switch between transmission and interruption of driving force between an input member that is drivingly connected to an internal combustion engine and an output member that is drivingly connected to a wheel according to the present invention The friction engagement device includes a pair of friction members, an inner support member that supports one of the pair of friction members from the radially inner side, and an outer side that supports the other of the pair of friction members from the radially outer side. A support member, a pressing member that presses the pair of friction members in the axial direction so as to engage with each other, and a return spring that biases the pressing member in a counter-pressing direction that is opposite to the pressing direction of the pressing member And a holding member that holds the return spring, and the inner support member is disposed on the pressing direction side with respect to the holding member and extends radially outward, and the friction engagement device The The housing is filled with oil of a predetermined pressure or more, and the radially inner end portion of the first space formed between the holding member and the inner support member in the axial direction in the housing A first oil supply section that supplies oil to the first space, and in a pressing state of the pressing member, a second space formed between the holding member and the pressing member in the axial direction in the housing. In the point which equips a radial direction inner side edge part with the 2nd oil supply part which supplies oil to said 2nd space.

“Drive coupling” represents a state in which two rotating elements are coupled so as to be able to transmit a driving force, and the two rotating elements are coupled so as to rotate integrally, or the two rotating elements. Is used as a concept including a state in which a driving force can be transmitted through one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like. Here, “driving force” is used synonymously with torque.
The “pressed state” means a state in which the pressing member presses the pair of friction members with a pressure equal to or higher than a predetermined pressure so that the pair of friction members rotate integrally.

According to said characteristic structure, since the oil more than predetermined pressure is satisfy | filled in the housing, the friction engagement apparatus accommodated in the inside of a housing can be cooled effectively with a large amount of oil. At that time, in the housing, the radially inner ends of both the first space formed between the holding member and the inner support member in the axial direction and the second space formed between the holding member and the pressing member. Oil can be supplied to the sections from the first oil supply section and the second oil supply section, respectively. Therefore, in order to cool the friction member of the friction engagement device, when the oil is circulated radially outward in the housing, the oil is sufficiently supplied not only to the first space but also to the second space. It is possible to suppress the generation of negative pressure in the second space.
Here, the second oil supply unit is configured to supply oil to the radially inner end of the second space, particularly in the pressed state of the pressing member. Therefore, even when the pressing member is pressed, that is, when the friction engagement device is pressed so that the pair of friction members rotate integrally, it is possible to suppress the negative pressure in the second space almost certainly. Can do. Thereby, it can suppress that the resistance force by a negative pressure acts on a press member also in the press state which is a condition where it is calculated | required especially on a control to move a press member to a non-pressing direction side. Therefore, it is possible to suppress the influence on the controllability of the friction engagement device.
Therefore, according to said characteristic structure, the start apparatus excellent also in the controllability can be provided, maintaining the cooling performance of a friction engagement apparatus high.

  Here, it is preferable that the second oil supply unit has an opening on the side opposite to the pressing direction of a through hole provided so as to penetrate the holding member in the axial direction.

  According to this configuration, oil can be appropriately supplied from the opening on the side opposite to the pressing direction of the through hole provided in the holding member to the radially inner end of the second space. Moreover, in this structure, there exists an advantage that the supply port of a 2nd oil supply part can be simply comprised only by providing the through-hole of an axial direction in a holding member.

  Further, the pressing member has a cylindrical pressing tube portion extending in the axial direction at a radially inner end portion, and in the pressing state, the pressing tube portion is disposed close to the holding member, and the holding member Of these, it is preferable that the through hole is provided at a position adjacent to the outer side in the radial direction with respect to the proximity portion to the pressing cylinder portion.

  According to this configuration, in the pressed state, the pressing member moves until the pressing cylinder portion of the pressing member comes close to the holding member. Therefore, the axial length of the friction engagement device is shortened while ensuring the stroke range of the pressing member. Thus, the friction engagement device can be reduced in size. Accordingly, the entire starting device can be reduced in size. Moreover, by setting it as the structure which provides a through-hole in the position adjacent to a radial direction outer side with respect to the proximity | contact part with a press cylinder part among holding members, the diameter of 2nd space from the 1st space side via the said through-hole. Oil can be appropriately supplied to the inner end in the direction.

  Further, it is preferable to have an oil guide portion that protrudes from the holding member to the first space side and guides oil from the first oil supply portion to the through hole on the radially outer side of the through hole. is there.

  According to this configuration, the oil from the first oil supply unit can be guided to the through hole by the oil guide unit, and the oil can be efficiently guided from the first space to the second space through the through hole. . Therefore, the controllability of the friction engagement device can be maintained better.

  In addition, the pressing member has a cylindrical pressing tube portion extending in the axial direction at the radially inner end portion, and in the pressed state, the pressing tube portion and the holding member are arranged close to each other, It is preferable that a gap is formed between the pressing cylinder part and the holding member, and the second oil supply part is provided on the radially inner side of the gap.

  According to this configuration, in the pressed state, the pressing member moves until the pressing cylinder portion of the pressing member comes close to the holding member. Therefore, the axial length of the friction engagement device is shortened while ensuring the stroke range of the pressing member. Thus, the friction engagement device can be reduced in size. Accordingly, the entire starting device can be reduced in size. In addition, a second oil supply portion is provided on the radially inner side of the gap between the holding member and the pressing cylinder portion, and oil can be appropriately supplied to the radially inner end portion of the second space via the gap. .

  Further, the housing has a cylindrical portion extending in the axial direction on the radially inner side of the pressing cylinder portion, and the first oil supply portion is an axial oil passage extending in the axial direction in the cylindrical portion. The second oil supply portion is branched from the axial oil passage on the side opposite to the pressing direction than the holding member, and is formed on the cylindrical portion. A configuration having a radially outer opening of a radial oil passage extending in the radial direction is preferable.

  According to this configuration, the axial oil passage extending in the axial direction is provided in the cylindrical portion provided on the radially inner side of the pressing cylinder portion of the pressing member, and the pressing direction side is more than the holding member of the axial oil passage. Oil can be appropriately supplied to the radially inner end of the first space from the opening. Further, a radial oil passage that branches off from the axial oil passage and extends in the radial direction in the cylindrical portion is opened at a position of a gap between the pressing cylinder portion and the holding member in the axially pressed state. By providing, oil can be appropriately supplied to the radially inner end of the second space from the radially outer opening of the radial oil passage. Further, in this configuration, by forming both the axial oil passage and the radial oil passage in the cylindrical portion, both the supply port of the first oil supply unit and the supply port of the second oil supply unit can be simplified. There is an advantage that it can be configured.

It is a schematic diagram which shows schematic structure of the hybrid drive device provided with the starting apparatus which concerns on 1st embodiment. It is a fragmentary sectional view of the hybrid drive device concerning a first embodiment. It is principal part sectional drawing of the hybrid drive device which concerns on 1st embodiment. It is a perspective view of the 4th bearing with which the hybrid drive device concerning a first embodiment is equipped. It is the expanded view of the circumferential direction which looked at the 4th bearing etc. from the radial direction inner side. It is principal part sectional drawing of the hybrid drive device which concerns on 2nd embodiment.

1. First Embodiment A first embodiment of the present invention will be described with reference to the drawings. In the present embodiment, a case where the starting device according to the present invention is incorporated and applied to a hybrid drive device will be described as an example. FIG. 1 is a schematic diagram showing a schematic configuration of a hybrid drive apparatus H according to the present embodiment. The hybrid drive device H is a drive device for a hybrid vehicle that uses one or both of the internal combustion engine E and the rotating electrical machine MG as a drive force source of the vehicle. The hybrid drive device H is configured as a so-called 1-motor parallel type hybrid drive device. Below, the hybrid drive device H which concerns on this embodiment is demonstrated in detail.

1-1. Overall Configuration of Hybrid Drive Device First, the overall configuration of the hybrid drive device H according to the present embodiment will be described. As shown in FIG. 1, the hybrid drive device H includes an input shaft I that is drivingly connected to an internal combustion engine E as a first driving force source of a vehicle, and a rotating electrical machine MG as a second driving force source of the vehicle. And a starting device SM, a transmission mechanism TM, an intermediate shaft M that is drivingly connected to the rotating electrical machine MG and that is drivingly connected to the transmission mechanism TM, and an output shaft O that is drivingly connected to the wheels W. . The clutch CL provided in the starting device SM is provided so as to be able to switch between transmission and disconnection of the driving force between the input shaft I and the intermediate shaft M. The hybrid drive device H includes a counter gear mechanism C and an output differential gear device DF. Each of these components is housed in a case (drive device case) 1.

  In the present embodiment, the “axial direction”, “radial direction”, and “circumferential direction” directions are based on the rotational axis of the input shaft I, the intermediate shaft M, and the clutch CL arranged coaxially with each other. Is stipulated.

  The internal combustion engine E is a device that extracts power by being driven by combustion of fuel inside the engine. For example, various known engines such as a gasoline engine and a diesel engine can be used. In this example, an output rotation shaft such as a crankshaft of the internal combustion engine E is drivingly connected to the input shaft I via a damper D. The input shaft I is drivingly connected to the rotating electrical machine MG and the intermediate shaft M via a clutch CL provided in the starting device SM, and the input shaft I is selectively driven to the rotating electrical machine MG and the intermediate shaft M by the clutch CL. Connected. In the engaged state of the clutch CL, the internal combustion engine E and the rotary electric machine MG are drivingly connected via the input shaft I, and in the released state of the clutch CL, the internal combustion engine E and the rotary electric machine MG are separated.

  The rotating electrical machine MG includes a stator St and a rotor Ro, and functions as a motor (electric motor) that generates power by receiving power supply, and a generator (power generation) that generates power by receiving power supply. Function). Therefore, rotating electrical machine MG is electrically connected to a power storage device (not shown). In this example, a battery is used as the power storage device. Note that it is also preferable to use a capacitor or the like as the power storage device. The rotating electrical machine MG is powered by receiving electric power from the battery, or supplies the battery with electric power generated by the torque output from the internal combustion engine E or the inertial force of the vehicle. The rotor Ro of the rotating electrical machine MG is drivingly connected so as to rotate integrally with the intermediate shaft M. The intermediate shaft M is an input shaft (transmission input shaft) of the speed change mechanism TM.

  The speed change mechanism TM is a device that changes the rotational speed of the intermediate shaft M at a predetermined speed ratio and transmits it to the speed change output gear G. In this embodiment, the transmission mechanism TM includes a single pinion type and Ravigneaux type planetary gear mechanism and a plurality of engagement devices such as a clutch, a brake, and a one-way clutch. There is used an automatic stepped transmission mechanism provided with a switchable gear. As the speed change mechanism TM, an automatic stepped speed change mechanism having other specific configurations, an automatic stepless speed change mechanism capable of changing the speed ratio steplessly, and a plurality of speed stages having different speed ratios can be switched. Alternatively, a manual stepped transmission mechanism or the like may be used. The speed change mechanism TM changes the rotational speed of the intermediate shaft M at a predetermined speed change ratio at each time point, converts torque, and transmits the torque to the speed change output gear G.

  The transmission output gear G is drivingly connected to the output differential gear device DF via the counter gear mechanism C. The output differential gear device DF is drivingly connected to the wheels W via the output shaft O, and the rotation and torque input to the output differential gear device DF are distributed and transmitted to the two left and right wheels W. To do. Thereby, the hybrid drive device H can transmit the torque of one or both of the internal combustion engine E and the rotating electrical machine MG to the wheels W to run the vehicle.

  In the hybrid drive device H according to this embodiment, the input shaft I and the intermediate shaft M are arranged coaxially, and the output shaft O is parallel to each other on an axis different from the input shaft I and the intermediate shaft M. The arrangement is a multi-axis arrangement. Such a configuration is suitable as a configuration of a hybrid drive device H mounted on, for example, an FF (Front Engine Front Drive) vehicle.

1-2. Configuration of Each Part of Hybrid Drive Device Next, the configuration of each part of the hybrid drive device H according to the present embodiment will be described. As shown in FIG. 2, the case 1 accommodates at least the rotating electrical machine MG and the starting device SM. The case 1 includes a case peripheral wall 2 that covers the outer periphery of each housing component such as the rotating electrical machine MG, the starting device SM, and the speed change mechanism TM, and an axial first direction A1 side (internal combustion engine E side) of the case peripheral wall 2. The first support wall 3 that closes the opening of the right side in FIG. 2 and the first support wall 3 in the axial second direction A2 side (the side opposite to the internal combustion engine E and the left side in FIG. 2), the second support wall 8 is provided between the rotary electric machine MG and the speed change mechanism TM in the axial direction. Further, although not shown, the case 1 includes an end support wall that closes an end of the case peripheral wall 2 on the second axial direction A2 side.

  The first support wall 3 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. An axial through hole is formed in the first support wall 3, and an input shaft I inserted through the through hole is inserted into the case 1 through the first support wall 3. The first support wall 3 is formed integrally with a cylindrical (boss-shaped) axial projecting portion 4 projecting toward the second axial direction A2. The first support wall 3 is disposed on the first axial direction A1 side with respect to the rotating electrical machine MG and the starting device SM, and more specifically, a clutch housing CH that houses the clutch CL (details will be described later). Are arranged at a predetermined interval on the first axial direction A1 side. Further, the first support wall 3 rotatably supports the clutch housing CH on the first axial direction A1 side of the rotating electrical machine MG.

  The second support wall 8 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. A through hole in the axial direction is formed in the second support wall 8, and an intermediate shaft M inserted through the through hole passes through the second support wall 8. The second support wall 8 is formed integrally with a cylindrical (boss-shaped) axial protrusion 9 that protrudes toward the first axial direction A1. The second support wall 8 is disposed on the second axial direction A2 side with respect to the rotating electrical machine MG and the starting device SM, and more specifically, at a predetermined interval on the second axial direction A2 side with respect to the clutch housing CH. It is arranged in the space. Further, the second support wall 8 rotatably supports the clutch housing CH on the second axial direction A2 side of the rotating electrical machine MG.

  An oil pump 18 is accommodated in a pump chamber formed inside the second support wall 8. In the present embodiment, the oil pump 18 is an inscribed gear pump having an inner rotor and an outer rotor. The inner rotor of the oil pump 18 is splined so as to rotate integrally with the clutch housing CH at the center in the radial direction. The oil pump 18 sucks oil from an oil pan (not shown) as the clutch housing CH rotates, discharges the sucked oil, and supplies the oil to the clutch CL, the speed change mechanism TM, the rotating electrical machine MG, and the like. To do. Note that oil passages are respectively formed inside the second support wall 8 and the intermediate shaft M, and the oil discharged by the oil pump 18 passes through a hydraulic control device (not shown) and those oil passages. Supplied to each part to be supplied with oil. The oil supplied to each part performs one or both of lubrication and cooling of the part. The oil in the present embodiment functions as a “lubricating coolant” that can perform both functions of “lubricating fluid” and “cooling fluid”.

  The input shaft I is a shaft member for inputting the torque of the internal combustion engine E to the hybrid drive device H. The input shaft I is disposed in a state of penetrating the first support wall 3, and as shown in FIG. 2, the input shaft I of the internal combustion engine E is disposed via the damper D on the first support wall 3 side in the first axial direction A 1. Drive connected so as to rotate integrally with the output rotation shaft. In addition, over the outer peripheral surface of the input shaft I and the inner peripheral surface of the through hole provided in the first support wall 3, the space between them is set in a liquid-tight state toward the first axial direction A1 side (damper D side). A seal member 77 for suppressing oil leakage is provided. In the present embodiment, the input shaft I corresponds to the “input member” in the present invention.

  In the present embodiment, an axial hole is formed at the radial center of the end of the input shaft I on the second axial direction A2 side. An end of the intermediate shaft M arranged on the same axis as the input shaft I on the first axial direction A1 side is inserted into the hole.

  The intermediate shaft M is a shaft member for inputting one or both of the torque of the rotating electrical machine MG and the torque of the internal combustion engine E via the clutch CL to the speed change mechanism TM. In the present embodiment, the intermediate shaft M corresponds to the “output member” in the present invention. The intermediate shaft M is splined to the clutch housing CH. As shown in FIG. 2, the intermediate shaft M is disposed so as to penetrate the second support wall 8. The intermediate shaft M is supported in the radial direction so as to be rotatable with respect to the second support wall 8. In the present embodiment, the intermediate shaft M has a plurality of oil passages including a supply oil passage 15 and a discharge oil passage 16 therein. The supply oil passage 15 extends in the axial direction, extends in the radial direction at a predetermined position in the axial direction so as to communicate with the hydraulic oil chamber H1 of the clutch CL, and opens to the outer peripheral surface of the intermediate shaft M. The drain oil passage 16 extends in the axial direction and opens on the side surface on the first axial direction A1 side.

  The clutch CL is a friction engagement device that is provided so as to be able to switch between transmission and disconnection of the driving force between the input shaft I and the intermediate shaft M and selectively drive-couples the internal combustion engine E and the rotating electrical machine MG. In the present embodiment, the clutch CL is configured as a wet multi-plate clutch mechanism. The clutch CL includes a clutch hub 21, a clutch drum 26, a piston 41, and the like, and is accommodated in the clutch housing CH. The clutch hub 21 is drivingly connected so as to rotate integrally with the input shaft I at the end of the input shaft I on the side in the second axial direction A2. The clutch drum 26 is formed integrally with the clutch housing CH, and is drive-connected so as to rotate integrally with the intermediate shaft M via the clutch housing CH.

  In the present embodiment, a fluid-tight hydraulic oil chamber H <b> 1 is formed between the clutch housing CH integrated with the clutch drum 26 and the piston 41. The hydraulic oil H1 discharged from the oil pump 18 and adjusted to a predetermined hydraulic pressure level by a hydraulic pressure control device (not shown) is supplied to the hydraulic oil chamber H1 via a supply oil passage 15 formed in the intermediate shaft M. Supplied. Engagement and release of the clutch CL are controlled according to the hydraulic pressure level of the oil supplied to the hydraulic oil chamber H1. A circulating oil chamber H2 is formed on the opposite side of the piston 41 from the hydraulic oil chamber H1. In this circulating oil chamber H2, pressure oil discharged by the oil pump 18 and adjusted to a predetermined hydraulic pressure level by a hydraulic control device (not shown) is passed through a circulating oil passage 65 formed in the clutch housing CH. Supplied.

  The clutch housing CH is formed so as to cover the periphery of the clutch CL, that is, the first axial direction A1 side, the second axial direction A2 side, and the radially outer side. Therefore, the clutch housing CH is disposed on the first axial direction A1 side of the clutch CL and extends in the radial direction, and is disposed on the second axial direction A2 side of the clutch CL in the radial direction. A second radially extending portion 61 that extends, and an axially extending portion 68 that is disposed on the radially outer side of the clutch CL and extends in the axial direction are provided. Details of the starting device SM including these clutch CL and clutch housing CH as main components will be described later.

  As shown in FIG. 2, the rotating electrical machine MG is disposed on the radially outer side of the clutch housing CH. The rotating electrical machine MG includes a stator St fixed to the case 1 and a rotor Ro that is rotatably supported via a clutch housing CH on the radially inner side of the stator St. The stator St and the rotor Ro are opposed to each other with a minute gap in the radial direction. The stator St includes a stator core that is configured as a laminated structure in which a plurality of annular plate-shaped electromagnetic steel plates are stacked and is fixed to the first support wall 3, and a coil that is wound around the stator core. The rotor Ro includes a rotor core configured as a laminated structure in which a plurality of annular plate-shaped electromagnetic steel plates are stacked, and a permanent magnet embedded in the rotor core.

  In the present embodiment, the rotating electrical machine MG is disposed so as to overlap the clutch housing CH when viewed in the radial direction. Regarding the arrangement of the two members, “overlapping when seen in a certain direction” means that the two members overlap when the viewpoint is moved in each direction perpendicular to the line-of-sight direction with the direction as the line-of-sight direction. This means that the visible viewpoint exists in at least some areas. In the present embodiment, the rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the axially extending portion 68 constituting the clutch housing CH. That is, the inner peripheral surfaces of the plurality of electromagnetic steel plates constituting the rotor core of the rotor Ro are fixed in a state where the inner peripheral surfaces are in contact with the outer peripheral surface of the axially extending portion 68. The rotor Ro is supported from the radially inner side by the first radially extending portion 51 and the second radially extending portion 61 via the axially extending portion 68. Accordingly, the clutch housing CH also functions as a rotor support member that supports the rotor Ro, and in this embodiment, the clutch housing CH and the rotor support member are formed in common. Therefore, in the following, when the term “clutch housing CH” is used, it also includes the meaning of “rotor support member”.

  In the present embodiment, the rotation sensor 11 is provided between the first support wall 3 and the first radially extending portion 51 on the first axial direction A1 side of the clutch housing CH. The rotation sensor 11 is a sensor for detecting the rotational position of the rotor Ro relative to the stator St of the rotating electrical machine MG. In the present embodiment, the rotation sensor 11 is arranged on the inner side in the radial direction of the rotor Ro so as to overlap the rotor Ro when viewed in the radial direction. In this example, the sensor stator of the rotation sensor 11 is fixed to the first support wall 3, and the sensor rotor of the rotation sensor 11 is fixed to the first radial extending portion 51 outside the sensor stator in the radial direction. As such a rotation sensor 11, a resolver etc. can be used, for example.

1-3. Configuration of Starting Device Next, the configuration of the starting device SM incorporated in the hybrid drive device H according to the present embodiment will be described. This starting device SM fulfills the function of starting the hybrid vehicle by the driving force of the rotating electrical machine MG with the internal combustion engine E disconnected. As shown in FIG. 3, the starting device SM according to the present embodiment includes a clutch housing CH and a clutch CL as main components. Hereinafter, it demonstrates in order. In the present embodiment, the clutch housing CH corresponds to the “housing” in the present invention, and the clutch CL corresponds to the “friction engagement device” in the present invention.

1-3-1. Clutch Housing The clutch housing CH is a member that accommodates the clutch CL, and includes a first radial extension 51, a second radial extension 61, and an axial extension 68.

  The first radially extending portion 51 is a plate-like member as a whole, and is disposed on the first axial direction A1 side of the clutch CL. The first radially extending portion 51 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. The first radially extending portion 51 is formed with an axial through hole, and the input shaft I inserted through the through hole passes through the first radially extending portion 51 and is inserted into the clutch housing CH. Has been. The first radially extending portion 51 is formed integrally with a cylindrical (boss-shaped) axial protruding portion 52 that protrudes toward the first axial direction A1 side. The axial projecting portion 52 is formed at the radially inner end of the first radially extending portion 51 so as to surround the periphery of the input shaft I. A third bearing 73 is disposed between the axial protrusion 52 and the input shaft I in the radial direction. A first bearing 71 is disposed between the axial protrusion 52 and the axial protrusion 4 of the first support wall 3 in the radial direction. In this example, a ball bearing is used as such a first bearing 71. Further, as the third bearing 73, a bearing with a sealing function (here, a needle bearing with a seal ring) configured to ensure a certain degree of liquid tightness is used. The first bearing 71 and the third bearing 73 are disposed so as to overlap each other when viewed in the radial direction. In this example, an oil seal or the like is not provided between the axial protruding portion 52 and the axial protruding portion 4 of the first support wall 3, and an oil-tight structure is not provided.

  The second radially extending portion 61 is a plate-like member formed in a stepped shape as a whole, and is disposed on the second axial direction A2 side of the clutch CL. The second radially extending portion 61 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. The second radial extending portion 61 is formed with an axial through hole, and the intermediate shaft M inserted through the through hole passes through the second radial extending portion 61 and is inserted into the clutch housing CH. Has been. Further, in this example, the second radially extending portion 61 has a predetermined axial range at a central portion in the radial direction (a cylindrical portion 43 (see FIG. 3) of the piston 41 described later when viewed in the radial direction). A cylindrical portion 63 is formed so as to occupy a range overlapping with a part on the second axial direction A2 side. The second radially extending portion 61 has a shape that is offset such that a portion radially inward of the cylindrical portion 63 is positioned closer to the axial first direction A1 side than a radially outer portion. The second radially extending portion 61 is formed so as to occupy a predetermined axial range (here, a range between the end of the input shaft I on the second axial direction A2 side and the oil pump 18). The second cylindrical portion 62 is integrally formed. Hereinafter, in order to clearly distinguish these, the cylindrical portion 62 disposed on the radially inner side is referred to as “inner cylindrical portion 62”, and the cylindrical portion 63 disposed on the radially outer side is referred to as “outer cylindrical portion 63”. ". In the present embodiment, the inner cylindrical portion 62 corresponds to the “cylindrical portion” in the present invention.

  The inner cylindrical portion 62 is formed integrally with the second radially extending portion 61 at the central portion in the axial direction. That is, the inner cylindrical portion 62 protrudes on both the first axial direction A1 side and the second axial direction A2 side with respect to the second radially extending portion 61. The inner cylindrical portion 62 surrounds the middle shaft M at the radially inner end of the second radially extending portion 61. The inner cylindrical part 62 is in contact with the outer peripheral surface of the intermediate shaft M over a part of the inner peripheral surface in the axial direction. A second bearing 72 is disposed between the inner cylindrical portion 62 and the axial protruding portion 9 of the second support wall 8 in the radial direction. In this example, a ball bearing is used as the second bearing 72. In this example, an oil seal or the like is not provided between the inner cylindrical portion 62 and the axial projecting portion 9 of the second support wall 8, and an oil-tight structure is not provided.

  A fourth bearing 74 is disposed between the inner cylindrical portion 62 and the input shaft I in the axial direction. In the present embodiment, a thrust washer capable of receiving an axial load (thrust force) is used as the fourth bearing 74. As shown in FIG. 4, the fourth bearing 74 is formed in an annular plate shape and includes a plurality of radial grooves 74 a and a plurality of axial grooves 74 b. The radial grooves 74a are concave groove-shaped grooves extending in the radial direction so as to communicate the inner peripheral surface and the outer peripheral surface of the fourth bearing 74. In this example, four radial grooves 74a are provided on each of both axial surfaces. It is formed evenly distributed in the circumferential direction. In this example, a total of eight radial grooves 74a, which are the four radial grooves 74a on the first axial direction A1 side and the four radial grooves 74a on the second axial direction A2 side, are even in the circumferential direction. It is formed in a dispersed manner. Further, the inner circumferential surface at the circumferential position where a total of eight radial grooves 74a are formed has eight concavely recessed shapes extending in the axial direction so as to communicate both axial surfaces of the fourth bearing 74. An axial groove 74b is formed.

  Returning to FIG. 3, the inner cylindrical portion 62 is splined to the intermediate shaft M on the inner peripheral surface of the end portion on the second axial direction A2 side so as to rotate integrally with the intermediate shaft M. Further, the inner cylindrical portion 62 is splined to the inner rotor on the outer peripheral surface of the end portion on the second axial direction A2 side so as to rotate integrally with the inner rotor constituting the oil pump 18.

  The axially extending portion 68 has a shape extending at least in the axial direction, and in the present embodiment, extends in the axial direction and the circumferential direction. The axially extending portion 68 has a cylindrical shape that surrounds the radially outer side of the clutch CL, and the first radially extending portion 51 and the second radially extending portion 61 are divided into these diameters. It is connected in the axial direction at the direction outer end. In this example, the axially extending portion 68 is formed integrally with the first radially extending portion 51 on the axial first direction A1 side. The axially extending portion 68 is connected to the second radially extending portion 61 by a fastening member such as a bolt on the axial second direction A2 side. Note that these may be connected by welding or the like. A rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the axially extending portion 68.

1-3-2. Clutch The clutch CL includes a clutch hub 21, a clutch drum 26, a friction plate 31, a piston 41, a return plate 47, and a return spring 49.

  The clutch CL has a hub-side friction plate 31a and a drum-side friction plate 31b as a pair as the friction plate 31. Here, the clutch CL has a plurality (four in this example) of hub-side friction plates 31a and a plurality (four in this example) of drum-side friction plates 31b. Both the hub side friction plate 31a and the drum side friction plate 31b are formed in an annular plate shape. The hub side friction plates 31a and the drum side friction plates 31b are alternately arranged in the axial direction. In the present embodiment, the pair of hub-side friction plates 31a and the drum-side friction plates 31b correspond to “friction members” in the present invention.

  The hub-side friction plate 31a and the drum-side friction plate 31b are formed as friction contact surfaces whose annular side surfaces are generally annular, and both friction contact surfaces are engaged with each other when the clutch CL is engaged. Are arranged so as to face each other. Further, a friction material based on, for example, paper or synthetic resin is attached to at least one axial side surface of the hub side friction plate 31a and the drum side friction plate 31b. It constitutes the contact surface. For example, the friction contact surface can be configured by arranging a plurality of segment-like friction materials having the same shape in an annular shape as a whole at regular intervals along the circumferential direction.

  The clutch hub 21 is formed in a cylindrical shape and holds a plurality of hub-side friction plates 31a from the radially inner side, and a circular plate extending in the radial direction so as to connect the cylindrical portion 22 and the input shaft I. And 24. A plurality of spline grooves extending in the axial direction are formed on the outer peripheral surface of the cylindrical portion 22 so as to be dispersed in the circumferential direction. Spline teeth that engage with the spline grooves of the cylindrical portion 22 are formed on the inner peripheral surface of the hub-side friction plate 31a. As a result, the hub-side friction plate 31a is supported by the clutch hub 21 from the inside in the radial direction, the relative rotation with respect to the clutch hub 21 is restricted, and the hub-side friction plate 31a is held slidable in the axial direction. In addition, the cylindrical portion 22 is formed with an inner through-hole 23 formed so as to communicate with the inner peripheral surface and the outer peripheral surface of the cylindrical portion 22 and penetrate in the radial direction. In this example, a plurality of inner through holes 23 are formed in a distributed manner in the circumferential direction, and are formed as slit-shaped through holes formed with a predetermined width in the axial direction and the circumferential direction, respectively. In the present embodiment, the clutch hub 21 corresponds to the “inner support member” in the present invention.

  The disk-shaped part 24 is a ring-shaped member extending in the radial direction and the circumferential direction, and is formed integrally with the cylindrical part 22. The disk-shaped part 24 is arranged so as to extend radially outward from the end of the input shaft I on the second axial direction A2 side. Further, the disc-like portion 24 is disposed so as to extend radially outward with respect to the return plate 47 through the first axial direction A1 side. The disc-like portion 24 is integrated with the end portion on the axial first direction A1 side of the cylindrical portion 22 at the radially outer end portion. Note that the radially inner end of the disk-like portion 24 is connected so as to rotate integrally with the input shaft I by welding or the like. The disk-shaped part 24 supports the cylindrical part 22 and a plurality of hub side friction plates 31a held by the cylindrical part 22 from the inside in the radial direction. A fifth bearing 75 is disposed between the disc-like portion 24 and the first radial extending portion 51 in the axial direction. In this example, a thrust washer capable of receiving an axial load (thrust force) is used as the fifth bearing 75. The fifth bearing 75 has the same shape as the fourth bearing 74, and has a plurality of radial grooves and a plurality of axial grooves.

  The clutch drum 26 is formed in a cylindrical shape. The clutch drum 26 holds a plurality of drum side friction plates 31b from the radially outer side. A plurality of spline grooves extending in the axial direction are formed on the inner peripheral surface of the clutch drum 26 so as to be dispersed in the circumferential direction. Spline teeth that engage with the spline grooves of the clutch drum 26 are formed on the outer peripheral surface of the drum-side friction plate 31b. Accordingly, the drum-side friction plate 31b is supported by the clutch drum 26 from the outside in the radial direction, the relative rotation with respect to the clutch drum 26 is restricted, and the drum-side friction plate 31b is held slidable in the axial direction. Further, the clutch drum 26 is formed with an outer through hole 27 formed so as to communicate with the inner peripheral surface and the outer peripheral surface of the clutch drum 26 and penetrate in the radial direction. In this example, a plurality of outer through holes 27 are formed in a distributed manner in the circumferential direction, and are formed as slit-shaped through holes formed with a predetermined width in the axial direction and the circumferential direction, respectively. In the present embodiment, the clutch drum 26 corresponds to the “outer support member” in the present invention.

  The clutch drum 26 is disposed on the radially inner side of the axially extending portion 68 with a predetermined gap between the clutch drum 26 and the axially extending portion 68. That is, the clutch drum 26 is disposed so that the outer peripheral surface of the clutch drum 26 and the inner peripheral surface of the axially extending portion 68 are opposed to each other with a predetermined interval in the radial direction. In other words, a radial clearance S <b> 1 is formed between the outer peripheral surface of the clutch drum 26 and the inner peripheral surface of the axially extending portion 68. A cylindrical space extending in the axial direction and the circumferential direction is formed by the radial gap S1. Further, in the present embodiment, the clutch drum 26 is disposed in a state in which the end portion on the axial first direction A1 side is separated from the first radial extending portion 51. As a result, the radial gap S1 opens toward the first axial direction A1 in the clutch housing CH.

  The piston 41 is a member that presses the plurality of friction plates 31 in the axial direction so as to engage with each other, and is formed in an annular shape as a whole. The piston 41 is inserted through the inner cylindrical portion 62 through a through hole provided in the center portion. Spline teeth that engage with the spline grooves of the clutch drum 26 are formed on the outer peripheral surface of the piston 41. As a result, the piston 41 is supported by the clutch drum 26 from the outside in the radial direction, the relative rotation with respect to the clutch drum 26 is restricted, and the piston 41 is held slidable in the axial direction. The piston 41 has a predetermined axial range (a part on the first axial direction A1 side of the outer cylindrical portion 63 as viewed in the radial direction) or the axial portion of the cylindrical portion 22 of the clutch hub 21 at the central portion in the radial direction. The cylindrical portion 43 is formed so as to occupy a range overlapping with a part on the two-direction A2 side. The cylindrical portion 43 is disposed on the outer side in the radial direction with respect to the outer cylindrical portion 63 and in contact with the outer cylindrical portion 63. In the present embodiment, the piston 41 corresponds to the “pressing member” in the present invention.

  Further, the piston 41 has an annular pressing portion 42 as a whole outside the cylindrical portion 43 in the radial direction. The pressing portion 42 is disposed opposite to the friction plate 31 so as to be able to contact the side surface of the friction plate 31 (in this example, the drum side friction plate 31b) on the second axial direction A2 side when the clutch CL is engaged. Yes. Further, the piston 41 has an annular disc-shaped portion 44 as a whole on the radially inner side of the cylindrical portion 43. The disc-shaped portion 44 is disposed on the radially inner side of the cylindrical portion 22 of the clutch hub 21 at a position overlapping the cylindrical portion 22 when viewed in the radial direction. The disk-shaped part 44 is formed integrally with a cylindrical (boss-shaped) axial projecting part 45 projecting toward the first axial direction A1 side. The axial protrusion 45 is formed at the radially inner end of the disk-like portion 44. Further, the axial projecting portion 45 is disposed on the radially outer side with respect to the inner cylindrical portion 62 in contact with a portion of the inner cylindrical portion 62 that projects toward the first axial direction A1 side. In the present embodiment, the axial projecting portion 45 corresponds to the “pressing tube portion” in the present invention.

  A concave groove that is continuous in the circumferential direction is formed on the outer peripheral surface of the outer cylindrical portion 63, and a seal member 78 such as an O-ring is disposed in the concave groove. Thereby, the space between the outer cylindrical portion 63 and the cylindrical portion 43 of the piston 41 is liquid-tight. In addition, a concave groove that is continuous in the circumferential direction is formed on the outer peripheral surface of a portion of the inner cylindrical portion 62 that protrudes toward the first axial direction A1 with respect to the second radially extending portion 61. A seal member 79 such as an O-ring is disposed in the concave groove. Thereby, the space between the inner cylindrical portion 62 and the axial protruding portion 45 of the piston 41 is liquid-tight. In this way, the liquid-tight hydraulic oil chamber H <b> 1 is formed between the second radial extending portion 61 and the inner cylindrical portion 62 and the piston 41. The hydraulic oil chamber H1 has a radially outer side defined by the inner peripheral surface of the cylindrical portion 43 of the piston 41 and a radially inner side defined by the outer peripheral surface of the inner cylindrical portion 62. The extending lengths in the axial direction of the cylindrical portion 43 and the axial projecting portion 45 are set to values larger than the length of the stroke range (movable range in the axial direction) of the piston 41, respectively.

  The return plate 47 is a plate-like member that is formed in an annular shape as a whole, and is disposed on the radially inner side of the cylindrical portion 22 of the clutch hub 21 at a position overlapping the cylindrical portion 22 when viewed in the radial direction. Has been. The return plate 47 is disposed between the piston 41 and the disc-like portion 24 of the clutch hub 21 in the axial direction. That is, the return plate 47 is disposed on the first axial direction A1 side with respect to the piston 41, and is disposed on the second axial direction A2 side with respect to the disc-like portion 24 of the clutch hub 21. Here, the space formed between the return plate 47 and the disc-like portion 24 of the clutch hub 21 in the axial direction is the first space V1, and is formed between the return plate 47 and the piston 41 in the axial direction. The second space V2 is the space. The return plate 47 is inserted into the inner cylindrical portion 62 through a through hole provided in the center portion. The return plate 47 is fixed in a state where movement in the first axial direction A1 side is restricted by a snap ring locked to the outer peripheral surface of the inner cylindrical portion 62. In the present embodiment, the return plate 47 corresponds to the “holding member” in the present invention.

  A return spring 49 is disposed between the piston 41 and the return plate 47 in the axial direction (second space V2). A plurality of such return springs 49 are provided, and in this example, twelve return springs 49 are distributed in the circumferential direction. In this example, two sets of return springs 49 are arranged in six pairs, equally distributed in the circumferential direction. The return spring 49 urges the piston 41 toward the second axial direction A2 while being held by the return plate 47 from the first axial direction A1.

  The piston 41 is urged toward the second axial direction A2 by the urging force of the return spring 49 whose reaction force is supported by the return plate 47. Therefore, when the hydraulic pressure level of the oil supplied to the hydraulic oil chamber H1 is less than a predetermined value, the pair of friction plates 31a and 31b are arranged with the friction contact surfaces separated from each other, and the clutch CL is in a released state. When oil with a hydraulic pressure level equal to or higher than a predetermined value is supplied to the hydraulic oil chamber H1 via a hydraulic control device (not shown), the piston 41 moves against the urging force of the return spring 49 in the first axial direction A1 side. And the pair of friction plates 31a and 31b are pressed so that the friction contact surfaces come into contact with each other. In the pressed state of the piston 41, the clutch CL is in an engaged state. When the hydraulic pressure level of the oil supplied to the hydraulic oil chamber H1 becomes less than a predetermined value, the piston 41 moves to the second axial direction A2 side by the urging force of the return spring 49, and the clutch CL is released again. When the piston 41 moves in the axial direction, the inner peripheral surface of the cylindrical portion 43 slides with respect to the outer peripheral surface of the outer cylindrical portion 63, and the inner peripheral surface of the axial protrusion 45 is on the inner side. It slides against the outer peripheral surface of the cylindrical portion 62.

  In the present invention, the direction in which the piston 41 applies a pressing force to the plurality of friction plates 31 is referred to as a “pressing direction” of the piston 41, and in the present embodiment, the direction coincides with the first axial direction A1. . Further, the direction opposite to the direction in which the piston 41 applies the pressing force to the plurality of friction plates 31 is referred to as the “anti-pressing direction” of the piston 41, and in this embodiment coincides with the second axial direction A2. . Therefore, in the present embodiment, the “first axial direction A1 side” is the same as the “pressing direction side” and the “second axial direction A2 side” is the same as the “counterpressing direction side” with respect to the arrangement of certain members and the like. is there.

1-4. Next, an oil distribution structure in the clutch housing CH (in the circulating oil chamber H2) of the starter SM having the above-described configuration will be described. In the present embodiment, oil adjusted to a predetermined hydraulic pressure level by a hydraulic control device (not shown) is supplied to the circulating oil chamber H <b> 2 via the circulating oil path 65. Here, in the present embodiment, as described above, the third bearing 73 disposed between the axial protrusion 52 and the input shaft I is configured to ensure a certain degree of liquid tightness. Further, a part of the inner circumferential surface of the inner cylindrical portion 62 in the axial direction is in contact with the outer circumferential surface of the intermediate shaft M over the entire circumferential direction. Therefore, the circulating oil chamber H2 in the clutch housing CH is in a liquid-tight state, and when the oil is supplied, the circulating oil chamber H2 is basically filled with oil of a predetermined pressure or higher. And the oil is circulating through the circulating oil chamber H2 while maintaining the state filled with the oil of the predetermined pressure or higher. This will be described in more detail below.

  The oil supplied through the circulating oil passage 65 formed so as to extend along the axial direction inside (inside) the inner cylindrical portion 62 is supplied to the side surface of the inner cylindrical portion 62 on the side in the first axial direction A1 side. It flows into the circulating oil chamber H2 from the formed first opening P1. In the present embodiment, the circulating oil passage 65 having the first opening P1 corresponds to the “first oil supply unit” in the present invention. Here, a plurality of circulating oil passages 65 are formed in (inside) the inner cylindrical portion 62. In this example, six circulating oil passages 65 are formed to be evenly distributed in the circumferential direction. As described above, the fourth bearing 74 is formed with eight axial grooves 74b that are evenly distributed in the circumferential direction. As described above, in the present embodiment, the six circulating oil passages 65 and the eight axial grooves 74b are uniformly distributed in the circumferential direction on the contact surface between the inner cylindrical portion 62 and the fourth bearing 74. The circulating oil passage 65 and the axial groove 74b are formed at different pitches.

  The inner diameter of the circulating oil passage 65 and the circumferential width of the axial groove 74b are set to values within a range such that at least one of the six circulating oil paths 65 and one of the eight axial grooves 74b communicate with each other. Is set. In FIG. 5, the inner cylindrical portion 62 and the fourth bearing 74 viewed from the radially inner side are shown expanded in the circumferential direction, and the two sets of the circulating oil passage 65 and the axial groove 74 b communicate with each other. (In FIG. 5, the portion is indicated by a thick line). Thereby, the oil supplied from the circulating oil path 65 can be appropriately guided to the outside in the radial direction via the radial groove 74a communicating with the axial groove 74b, regardless of the phase of the fourth bearing 74. . Here, the “phase of the fourth bearing 74” is used as a concept representing the circumferential position of the part when attention is paid to a specific part of the fourth bearing 74. Moreover, oil can be supplied to the contact surface of the 1st radial direction extension part 51 and the 4th bearing 74 via the axial direction groove | channel 74b, and lubrication between these can be performed.

  Thus, in the circulating oil chamber H2, the radially inner end of the first space V1 between the return plate 47 and the disc-shaped portion 24 of the clutch hub 21 (here, the innermost circumference of the first space V1). The oil that has flowed into the part) flows radially outward through the radial groove 74a and the axial groove 74b formed in the fourth bearing 74, and then is divided into two systems. That is, the oil that has reached the radially inner end of the first space V1 passes through the fourth bearing 74 and then flows through the first space V1 toward the radially outer side as it is, and the return plate 47. And the second system introduced into the radially inner end of the second space V2 between the piston 41 and the piston 41.

  In the present embodiment, in order to allow oil to be supplied to the radially inner end of the second space V2, the return plate 47 is formed with a through hole 47a that penetrates the return plate 47 along the axial direction. ing. Such through-holes 47a are uniformly distributed at a plurality of locations in the circumferential direction. Further, in the present embodiment, in order to reduce the axial length of the clutch CL and to reduce the size of the clutch CL while securing the movable range of the piston 41 in the axial direction, ), The shape of each member is set so that the side surface of the axial protrusion 45 on the first axial direction A1 side is positioned close to the side surface of the return plate 47 on the second axial direction A2 side. And the arrangement is adapted. Further, in this example, the side surface of the axial protrusion 45 on the first axial direction A1 side is disposed adjacent to the side surface of the return plate 47 on the second axial direction A2 side. The through hole 47 a is formed in the return plate 47 at a position adjacent to the outer side in the radial direction with respect to a portion close to the axial protrusion 45. Thereby, the through-hole 47a opens to the innermost peripheral part of the second space V2.

  Furthermore, in this embodiment, the return plate 47 has the guide part 48 which protrudes to the 1st space V1 side of the axial first direction A1 side from the said return plate 47 in the radial direction outer side of each through-hole 47a. The guide portion 48 is formed so as to incline radially inward from the return plate 47 toward the first axial direction A1 with at least the radially outer side of the through hole 47a as a base end. Thereby, the oil flowing toward the outer side in the radial direction can flow along the guide portion 48, and the oil that has reached the inner end in the radial direction of the first space V1 can be efficiently guided to the through hole 47a. ing. Therefore, oil can be efficiently supplied to the radially inner end of the second space V2 through the second opening P2 on the second axial direction A2 side of the through hole 47a. The guide 48 may be formed so as to cover at least one of the through holes 47a in the circumferential direction. In the present embodiment, the through hole 47a having the second opening P2 corresponds to the “second oil supply portion” in the present invention, and the guide portion 48 corresponds to the “oil guide portion” in the present invention.

  The oil that has reached the radially inner end of the second space V2 flows toward the radially outer side in the second space V2, and then reaches the radially outer side of the return plate 47 (the radially inner side of the cylindrical portion 22). It merges with the oil that has flowed radially outward in the space V1. The joined oil flows into the space between the cylindrical portion 22 and the clutch drum 26 via the inner through hole 23 formed in the cylindrical portion 22, and when flowing radially outward, the hub side friction plate 31a. And the drum side friction plate 31b are cooled. The oil flows through the outer through hole 27 formed in the clutch drum 26 into the radial gap S1, flows through the radial gap S1 toward the first axial direction A1, and then the circle of the clutch hub 21 in the axial direction. It flows in the third space V3 formed between the plate-like portion 24 and the first radially extending portion 51 toward the radially inner side. The oil flows further radially inward through the radial groove and the axial groove formed in the fifth bearing 75, and reaches the radially inner end of the third space V3.

  Most of the oil that has reached the radially inner end of the third space V3 is discharged from the circulating oil chamber H2 through a radial communication hole that opens to the outer peripheral surface of the input shaft I, and enters the intermediate shaft M. The oil is returned to the oil pan (not shown) through the formed drain oil passage 16. Another part of the oil that has reached the radially inner end of the third space V3 leaks little by little toward the first axial direction A1 through the third bearing 73, and the radially outer side of the third bearing 73. The first bearing 71 arranged in the is lubricated. The oil after lubricating the first bearing 71 is returned to an oil pan (not shown) after cooling the coil end portion of the stator St.

  As described above, in the starting device SM according to the present embodiment, oil is supplied from the first opening P1 of the circulating oil passage 65 to the radially inner end of the first space V1 in the clutch housing CH. In addition, a part of the oil supplied to the radially inner end of the first space V1 can be supplied from the second opening P2 of the through hole 47a to the radially inner end of the second space V2. Therefore, when circulating the oil in the circulating oil chamber H2 radially outward, the oil can be sufficiently supplied and circulated in both the first space V1 and the second space V2, and the second space V2 can be circulated. The generation of negative pressure can be suppressed.

  Here, in a pressed state of the piston 41 (engagement state of the clutch CL), in order to release the clutch CL thereafter, the hydraulic pressure supplied to the hydraulic oil chamber H1 is lowered and the piston 41 is moved by the urging force of the return spring 49. It is necessary to move to the second axial direction A2 side, which is the side opposite to the pressing direction. In this regard, in the present embodiment, the oil from the second opening P2 of the through hole 47a is configured to be supplied to the second space V2 particularly in the engaged state of the clutch CL. Therefore, even in the engaged state of the clutch CL that is required to move the piston 41 in the axial second direction A2 side, which is the side opposite to the pressing direction, in terms of control, the resistance force due to the negative pressure in the second space V2 is 41 can be effectively suppressed. Therefore, it is suppressed that the controllability of the clutch CL is affected, and the starter SM having excellent controllability is realized.

2. Second Embodiment A second embodiment of the present invention will be described with reference to FIG. Also in this embodiment, the case where the starting device according to the present invention is incorporated and applied to the hybrid drive device H will be described as an example. The overall configuration and the configuration of each part of the hybrid drive device H according to this embodiment are basically the same as those of the first embodiment. However, in the present embodiment, the specific configuration for supplying oil to the radially inner end of the second space V2 is different from that of the first embodiment. In the following, differences from the first embodiment will be mainly described. Note that points not particularly specified are the same as those in the first embodiment.

  In the present embodiment, when the piston 41 is in a pressed state (engaged state of the clutch CL), the piston 41 is disposed close to the return plate 47 with a predetermined interval in the axial direction. That is, the side surface of the axial protrusion 45 on the first axial direction A1 side is disposed close to the side surface of the return plate 47 on the second axial direction A2 side, and a predetermined axial clearance S2 is formed between them. It is formed. Here, “adjacent” means that they are slightly separated so as not to block a radially outer opening of a radial oil passage 65b, which will be described later, constituting a part of the circulation oil passage 65. In the present embodiment, the axial gap S2 corresponds to the “gap” in the present invention.

  And in this embodiment, from the inner cylindrical part 62 arrange | positioned at the radial inside of the axial direction protrusion part 45 of piston 41, the radial inside edge of the 1st space V1 and the radial inside edge of the 2nd space V2 A structure in which oil is directly supplied to each part is adopted. Therefore, in the present embodiment, in the inner cylindrical portion 62, there are an axial oil passage 65a extending in the axial direction and a radial oil passage 65b branching from the axial oil passage 65a and extending in the radial direction. Is formed. In this example, six axial oil passages 65a are uniformly distributed in the circumferential direction, and corresponding to this, six radial oil passages 65b are uniformly dispersed in the circumferential direction. . In the present embodiment, the circulating oil passage 65 is constituted by the axial oil passage 65a and the radial oil passage 65b.

  The axial oil passage 65a extends along the axial direction in the inner cylindrical portion 62, and is closer to the axial first direction A1 side than the return plate 47, and on the side surface in the first axial direction A1 side of the inner cylindrical portion 62. Is open. Further, the radial oil passage 65b extends in the radial direction in the inner cylindrical portion 62 on the second axial direction A2 side from the return plate 47, and opens to the outer peripheral surface of the inner cylindrical portion 62. Yes. The opening position of the radial oil passage 65b coincides with the axial position of the axial gap S2. Thereby, the radial oil passage 65b is opened on the radially inner side of the axial gap S2 so as to overlap the axial gap S2 when viewed in the radial direction.

  In the present embodiment, the return plate 47 is formed substantially flat without having the through hole 47a and the guide portion 48.

  In the present embodiment, a part of the oil supplied through the circulating oil passage 65 formed in the inner cylindrical portion 62 passes through the axial oil passage 65 a constituting a part of the circulating oil passage 65. From the first opening P1 formed on the side surface of the inner cylindrical portion 62 on the first axial direction A1 side to the radially inner end of the first space V1 (here, the innermost peripheral portion of the first space V1). Inflow. In the present embodiment, the axial oil passage 65a having the first opening P1 corresponds to the “first oil supply section” in the present invention. Further, the other part of the oil supplied via the circulating oil path 65 passes through the radial oil path 65 b constituting the other part of the circulating oil path 65, and the outer peripheral surface of the inner cylindrical portion 62. Flows into the radially inner end of the second space V2 (in this case, the innermost peripheral portion of the second space V2) from the third opening P3 formed in the inner space. In the present embodiment, the radial oil passage 65b having the third opening P3 corresponds to the “second oil supply portion” in the present invention.

  In the starting device SM according to the present embodiment, oil is supplied from the first opening P1 of the axial oil passage 65a to the radially inner end of the first space V1 in the clutch housing CH (circulation oil chamber H2). In addition, oil can be supplied from the third opening P3 of the radial oil passage 65b to the radially inner end of the second space V2. Therefore, when circulating the oil in the circulating oil chamber H2 radially outward, the oil can be sufficiently supplied and circulated in both the first space V1 and the second space V2, and the second space V2 can be circulated. The generation of negative pressure can be suppressed. Therefore, also in this embodiment, it is possible to effectively suppress the resistance force caused by the negative pressure in the second space V2 from acting on the piston 41 and affecting the controllability of the clutch CL. Thereby, the starter SM having excellent controllability is realized.

3. Other Embodiments Finally, other embodiments of the starting device according to the present invention will be described. Note that the feature configurations disclosed in each of the following embodiments are not applied only in that embodiment, and should be applied in combination with the feature configurations disclosed in the other embodiments unless a contradiction arises. Is also possible.

(1) In said 1st embodiment, the case where the through-hole 47a penetrated the return plate 47 along the axial direction was demonstrated as an example. However, the embodiment of the present invention is not limited to this. That is, it suffices if it penetrates in the axial direction so as to communicate at least both sides of the return plate 47 in the axial direction. For example, the through hole 47a penetrates the return plate 47 along the direction inclined with respect to the axial direction. This is also a preferred embodiment of the present invention.

(2) In the first embodiment, the case where the through hole 47a is formed at a position adjacent to the outer side in the radial direction with respect to the proximity portion of the return plate 47 with the axial protrusion 45 is exemplified. As explained. However, the embodiment of the present invention is not limited to this. That is, if it is formed so as to open at least at the radially inner end of the second space V2, for example, the through hole 47a is in the radial direction with respect to the proximity portion of the return plate 47 with the axial protrusion 45. It is also one of preferred embodiments of the present invention that the structure is formed at a position slightly apart from the outside. Alternatively, a configuration in which a part of the through hole 47a is formed at a position in the return plate 47 that overlaps the axial protrusion 45 when viewed in the axial direction is one of the preferred embodiments of the present invention. It is.

(3) In the first embodiment, the case where the return plate 47 has the guide portion 48 that protrudes from the return plate 47 toward the first space V1 on the radially outer side of the through hole 47a has been described as an example. . However, the embodiment of the present invention is not limited to this. That is, it is also one of the preferred embodiments of the present invention that the return plate 47 is simply provided with the through hole 47a without providing such a guide portion 48.

(4) In the second embodiment, the inner cylindrical portion 62 is formed such that the axial oil passage 65a extends along the axial direction, and the radial oil passage 65b extends along the radial direction. The case where it is formed to extend is described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, the axial oil passage 65a may be configured to extend in the inner cylindrical portion 62 along a direction inclined with respect to the axial direction. One. Alternatively, the configuration in which the radial oil passage 65b is formed so as to extend in the inner cylindrical portion 62 along a direction inclined with respect to the radial direction is also one preferred embodiment of the present invention. It is.

(5) In each of the above embodiments, the oil passage (the circulating oil passage 65 in the first embodiment, the axial oil passage 65a in the second embodiment) extending in the inner cylindrical portion 62 in the axial direction. ) Has been described as an example in which the inner cylindrical portion 62 is opened in the first opening P1 on the side surface in the first axial direction A1 side. However, the embodiment of the present invention is not limited to this. That is, the first opening P1 only needs to be provided at least on the axial first direction A1 side with respect to the return plate 47. For example, an oil passage extending in the radial direction is separately provided in the inner cylindrical portion 62, and the oil passage It is also one of preferred embodiments of the present invention to have a configuration in which the opening opens on the outer peripheral surface of the inner cylindrical portion 62 on the first axial direction A1 side with respect to the return plate 47.

(6) In the first embodiment, the through hole 47a having the second opening P2 alone constitutes a “second oil supply part”, and in the second embodiment, the third opening P3. The case where the radial oil passage 65b having a single structure constitutes a “second oil supply unit” has been described as an example. However, the embodiment of the present invention is not limited to this. That is, by combining the configuration of the first embodiment and the configuration of the second embodiment, both the through hole 47a having the second opening P2 and the radial oil passage 65b having the third opening P3. The “second oil supply unit” is also one of the preferred embodiments of the present invention.

(7) In each of the above embodiments, the clutch hub 21 is drivingly connected so as to rotate integrally with the input shaft I, and the clutch drum 26 is driven and connected so as to rotate integrally with the intermediate shaft M. Described as an example. However, the embodiment of the present invention is not limited to this. That is, the drive connection relationship between them is switched, and the clutch hub 21 is drive-connected so as to rotate integrally with the intermediate shaft M, and the clutch drum 26 is drive-connected so as to rotate integrally with the input shaft I. This is also a preferred embodiment of the present invention.

(8) In each of the above-described embodiments, the case where the hybrid drive device H has a multi-axis configuration suitable for mounting on an FF (Front Engine Front Drive) vehicle has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, the output shaft of the speed change mechanism TM is arranged coaxially with the input shaft I and the intermediate shaft M and is directly driven and connected to the output differential gear device DF. This is also one of the preferred embodiments of the present invention. The hybrid drive device H having such a configuration is suitable when mounted on an FR (Front Engine Rear Drive) vehicle.

(9) In each of the embodiments described above, the starting device according to the present invention is incorporated and applied to a hybrid drive device H for a hybrid vehicle that includes both the internal combustion engine E and the rotating electrical machine MG as a drive power source for the vehicle. The case has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, the present invention can be incorporated and applied to a so-called drive device for an engine vehicle that includes only the internal combustion engine E as a drive power source of the vehicle. In this case, the starting device according to the present invention absorbs the differential rotational speed between the input shaft I drivingly connected to the internal combustion engine E and the intermediate shaft M drivingly connected to the wheels W when the vehicle starts. It fulfills the function of transmitting the driving force between the two.

(10) Regarding other configurations as well, the embodiments disclosed herein are illustrative in all respects, and embodiments of the present invention are not limited thereto. That is, as long as the configuration described in the claims of the present application and a configuration equivalent thereto are provided, a configuration obtained by appropriately modifying a part of the configuration not described in the claims is naturally also included in the present invention. Belongs to the technical scope.

  INDUSTRIAL APPLICABILITY The present invention is suitable for a starting device provided with a friction engagement device that can be switched between transmission and interruption of driving force between an input member drivingly connected to an internal combustion engine and an output member drivingly connected to a wheel. Can be used.

SM Starting device E Internal combustion engine I Input shaft (input member)
M Intermediate shaft (output member)
W Wheel CH Clutch housing (housing)
CL clutch (friction engagement device)
21 Clutch hub (inner support member)
26 Clutch drum (outer support member)
31 Friction plate (friction member)
31a Hub side friction plate 31b Drum side friction plate 41 Piston (pressing member)
45 Axial protrusion (pressing cylinder)
47 Return plate (holding member)
47a Through hole 48 Guide part (oil guide part)
49 Return spring 62 Inner cylindrical part (cylindrical part)
65 Circulating oil passage 65a Axial oil passage 65b Radial oil passage V1 First space V2 Second space P1 First opening P2 Second opening P3 Third opening S2 Axial clearance (gap)

Claims (6)

A starting device comprising a friction engagement device provided to be able to switch between transmission and interruption of driving force between an input member drivingly connected to an internal combustion engine and an output member drivingly connected to a wheel,
The friction engagement device includes a pair of friction members, an inner support member that supports one of the pair of friction members from a radially inner side, and an outer support member that supports the other of the pair of friction members from a radially outer side. A pressing member that axially presses the pair of friction members to engage each other, a return spring that biases the pressing member in a counter-pressing direction that is opposite to the pressing direction of the pressing member, A holding member for holding the return spring;
The inner support member is arranged to extend radially outward on the pressing direction side with respect to the holding member,
The housing containing the friction engagement device is filled with oil of a predetermined pressure or more,
A first oil supply portion that supplies oil to the first space is provided at a radially inner end portion of the first space formed between the holding member and the inner support member in the axial direction in the housing. ,
In the pressing state of the pressing member, oil is supplied to the second space at the radially inner end of the second space formed between the holding member and the pressing member in the axial direction in the housing. A starting device having a dual oil supply unit.   2. The starting device according to claim 1, wherein the second oil supply unit includes an opening portion on a side opposite to the pressing direction of a through hole provided so as to penetrate the holding member in the axial direction. The pressing member has a cylindrical pressing tube portion extending in the axial direction at the radially inner end,
In the pressed state, the pressing cylinder portion is disposed close to the holding member,
The starting device according to claim 2, wherein the through hole is provided at a position adjacent to the outer side in the radial direction with respect to a proximity portion of the holding member to the pressing cylinder portion.   The oil guide part which protrudes to the said 1st space side from the said holding member on the radial direction outer side of the said through-hole, and has an oil guide part which guides the oil from said 1st oil supply part to the said through-hole. Starting device. The pressing member has a cylindrical pressing tube portion extending in the axial direction at the radially inner end,
In the pressed state, the pressing tube portion and the holding member are disposed close to each other, and a gap is formed between the pressing tube portion and the holding member,
The starting device according to claim 1, wherein the second oil supply unit is provided on a radially inner side of the gap. The housing has a cylindrical part extending in the axial direction on the radially inner side of the pressing cylinder part,
The first oil supply part has an opening on the pressing direction side than the holding member of an axial oil passage extending in the axial direction in the cylindrical part,
The second oil supply portion is a radially outer opening of a radial oil passage that branches from the axial oil passage on the side opposite to the holding member than the holding member and extends radially in the cylindrical portion. The starting device according to claim 5, further comprising a portion.

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