JP2011214595A - Friction engaging device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve a wet friction engaging device suited to a driving device for a hybrid vehicle.SOLUTION: A groove-like part 30 extending in a radial direction of a rotary shaft is formed on at least one of a friction contact face of a first rotary plate 11 or a friction contact face of a second rotary plate, and rotating directions of the first rotary plate and the second rotary plate during normal rotation of an output member in an engaged state is considered as a forward direction F. The groove-like part 30 is formed asymmetrically in a circumferential one side and a circumferential other side of the rotary shaft such that, in a separated state, resistance of the first rotary plate 11 and the second rotary plate received from a lubricating cooling liquid when the second rotary plate is relatively rotated in the forward direction F with respect to the first rotary plate 11 is smaller than resistance of the first rotary plate 11 and the second rotary plate received from the lubricating cooling liquid when the first rotary plate 11 is relatively rotated in the forward direction F with respect to the second rotary plate.

Description

  The present invention is provided in a drive device for a hybrid vehicle having an input member that is drivingly connected to an internal combustion engine and an output member that is drivingly connected to both the rotating electrical machine and the wheels, and is a space to which lubricating coolant is supplied. The present invention relates to a wet type frictional engagement device that operates in the inside.

  As a conventional example of the above-described wet friction engagement device provided in a drive device for a hybrid vehicle, for example, there is a technique described in Patent Document 1 below. In the configuration described in Patent Document 1, as shown in FIGS. 1 and 2 of the document, both an input member (input side member 15) that is drivingly connected to the internal combustion engine via a damper, both the rotating electrical machine and the wheel. A wet friction engagement device (wet multi-plate clutch 2) for connecting and disconnecting a driving force to and from an output member (output-side member 16) that is drivingly connected to each other. In such a configuration, when the vehicle travels with only the driving force of the rotating electrical machine, the friction engagement device is in a separated state, and only the driving force of the internal combustion engine or the driving force of the internal combustion engine and the driving force of the rotating electrical machine are detected. When the vehicle travels with both driving forces, the friction engagement device is engaged.

JP 2006-298272 A

  By the way, in the wet friction engagement device, in the separated state, drag torque is generated by the resistance caused by the viscosity of the lubricating coolant (hereinafter simply referred to as “viscous resistance”), and the friction engagement device is provided. There is a problem that the energy efficiency of the driving device is lowered. However, the drag torque is not considered at all in the configuration described in Patent Document 1. Therefore, the problem peculiar to the wet friction engagement device used in the drive device for a hybrid vehicle has not yet been clarified, and the above-mentioned Patent Document 1 naturally shows means for solving the problem. Absent.

  Therefore, it is desired to realize a wet friction engagement device suitable for a drive device for a hybrid vehicle.

  According to the present invention, a drive device for a hybrid vehicle having an input member that is drivingly connected to an internal combustion engine and an output member that is drivingly connected to both the rotating electrical machine and the wheels is provided and supplied with a lubricating coolant. A characteristic configuration of a wet friction engagement device that operates in a space includes a first rotating plate that is drivingly connected to the input member, and a second rotating plate that is drivingly connected to the output member. The plate and the second rotating plate are arranged so that their rotational axes coincide with each other, and each has a friction contact surface that is formed into an annular shape as a whole, and both friction contact surfaces are opposed to each other so that they can contact each other. The friction contact surface of the first rotary plate and the friction contact surface of the second rotary plate are in contact with each other and can be switched between an engaged state and a separated state in which they are separated. The friction contact surface of the first rotating plate and the second rotating plate A groove-like portion extending in the radial direction of the rotation shaft is formed on at least one of the friction contact surface, and the first rotation plate and the second rotation at the time of forward rotation of the output member in the engaged state When the rotation direction of the plate is the forward direction, the first rotation plate and the second rotation plate are in the separated state when the second rotation plate rotates relative to the first rotation plate in the forward direction. The resistance received from the lubricating coolant is the resistance that the first rotating plate and the second rotating plate receive from the lubricating coolant when the first rotating plate rotates relative to the second rotating plate in the forward direction. The groove-shaped portion has an asymmetric shape on one side in the circumferential direction and the other side in the circumferential direction of the rotating shaft so as to be smaller.

In the present application, the “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that functions as both a motor and a generator as necessary.
In the present application, “driving connection” refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or the two This is used as a concept including a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like.
Furthermore, in the present application, “extending in a certain direction (hereinafter referred to as“ target direction ”)” with respect to the shape of the member is used as a concept including a shape in which a vector pointing in the extending direction has even a component in the target direction. Yes. That is, not only the shape in which the extending direction is parallel to the target direction but also the shape in which the extending direction is a direction intersecting the target direction and the crossing angle is not a right angle is included. In addition, the extending direction in each part of the extending part may not be uniform, and each part that satisfies the above requirements is combined in such a way that the extending direction is continuous (for example, an arc shape, A shape in which the extending direction is in a direction different from the target direction as it goes in the target direction).
In the present application, “when the output member is rotating forward” refers to when the wheel connected to the output member is rotated in the forward direction.

In the hybrid vehicle drive device configured as described above, for example, in a state in which the vehicle is started by the driving force of the internal combustion engine, the internal combustion engine is operated while the rotation of the output member is stopped. . In this state, the friction engagement device is in the separated state, and the first rotating plate that is drivingly connected to the internal combustion engine via the input member is forward with respect to the second rotating plate that is drivingly connected to the output member. (Hereinafter, this state is referred to as “first rotation state”). For example, when the internal combustion engine is not started and the vehicle is traveling forward only by the driving force of the rotating electrical machine, the output member rotates while the rotation of the input member drivingly connected to the internal combustion engine is stopped. It becomes a state. In this state, the friction engagement device is in a separated state, and the second rotating plate that is drivingly connected to the output member rotates relative to the first rotating plate that is drivingly connected to the input member in the forward direction. (Hereinafter, this state is referred to as “second rotation state”).
The inventors of the present application have obtained the following findings (issues) specific to the hybrid vehicle configured as described above. That is, in the first rotation state, it is desirable that the friction engagement device for starting the vehicle by the driving force of the internal combustion engine can be quickly switched from the separated state to the engaged state while suppressing the engagement shock. For this purpose, in this first rotation state, the viscous resistance of the lubricating coolant is ensured to some extent, so that the driving force (torque) is transmitted from the first rotating plate to the second rotating plate via the lubricating coolant to some extent. Desirably, the state is such that creep torque is transmitted to the output member. On the other hand, in the second rotation state, transmission of driving force (torque) from the second rotating plate to the first rotating plate via the lubricating cooling liquid is performed by making the viscosity resistance of the lubricating cooling liquid smaller than that in the first rotating state. It is desirable to suppress the decrease in energy efficiency.
The present invention has been made on the basis of the above knowledge (problem), and according to the above characteristic configuration, the viscous resistance of the lubricating coolant is ensured to some extent in the first rotation state, while in the second rotation state. The viscous resistance of the lubricating coolant can be kept low. As a result, creep torque can be transmitted to the output member when the vehicle is started by the driving force of the internal combustion engine, and the engagement shock can be suppressed quickly when the friction engagement device is switched from the separated state to the engaged state. It is possible to achieve both control. Further, when the vehicle is driven only by the driving force of the rotating electrical machine, the transmission of the driving force (torque) from the second rotating plate to the first rotating plate via the lubricating coolant can be suppressed. A reduction in the energy efficiency of the drive device due to drag torque in the combined device can be suppressed. As described above, the friction engagement device according to the present invention is suitable for a drive device for a hybrid vehicle.

  Here, the groove-shaped portion has at least one of a cross-sectional shape cut along a cylindrical surface about the rotation axis and a cross-sectional shape cut along a surface orthogonal to the rotation axis, It is preferable that the rotation shaft has an asymmetric shape on one side in the circumferential direction and the other side in the circumferential direction.

The viscous resistance of the lubricating coolant between the first rotating plate and the second rotating plate is the resistance that the grooved portion receives when the lubricating coolant relatively crosses the grooved portion in the circumferential direction, that is, the groove shape The resistance resulting from the agitation of the lubricating cooling liquid in the part (hereinafter simply referred to as “agitation resistance”) and the lubricating cooling liquid between the first rotating plate and the second rotating plate, which are relatively narrow in distance, On the other hand, when the first rotating plate and the second rotating plate are rotated at different speeds, resistance due to shearing of the lubricating coolant (hereinafter simply referred to as “shear resistance”) is included. . The agitation resistance is changed by a drag acting between the lubricating coolant and the groove-like portion when the lubricating coolant and the groove-like portion collide. On the other hand, the shear resistance changes according to the separation distance between the first rotating plate and the second rotating plate.
According to this configuration, the asymmetry of the shape in the circumferential direction in the cross section (first cross section) cut along the cylindrical surface with the rotation axis of the groove portion as the axis, and the surface orthogonal to the rotation axis of the groove portion The resistance that the first rotating plate and the second rotating plate receive from the lubricating coolant in the second rotation state is utilized using at least one of the asymmetry in the circumferential direction of the shape in the section (second section) cut along In the first rotation state, it is possible to appropriately set the shape of the groove portion so that the first rotation plate and the second rotation plate are smaller than the resistance received from the lubricating coolant.
That is, by controlling the shape of at least one of the first cross-section and the second cross-section of the groove-like portion on one side in the circumferential direction and the other side in the circumferential direction, both the stirring resistance and shear resistance of the lubricating coolant are controlled. be able to. Note that the shear resistance of the lubricating coolant can be controlled by the shape of the groove portion between the friction contact surface of the first rotary plate and the friction contact surface of the second rotary plate. This is because the entering force (that is, the force for separating the first rotating plate and the second rotating plate) changes.

  In addition, with respect to the groove sidewalls, which are sidewalls on both sides in the circumferential direction of the groove-shaped portion, the first rotating plate faces the flow of the lubricating coolant when rotating relative to the second rotating plate in the forward direction. The groove side wall which is opposite to the flow of the lubricating coolant when the second rotating plate rotates relative to the first rotating plate in the forward direction is the groove side wall which is the first groove side wall. The first side wall is a direction from the bottom to the top of the first groove side wall in a first cross section that is a cross section obtained by cutting the groove-shaped portion along a cylindrical surface having the rotation axis as an axis as the second groove side wall. The direction from the bottom to the top of the second groove side wall is the second side wall standing direction, and the first side wall rising direction is toward the top with respect to the direction perpendicular to the friction contact surface. The first upright angle inclined to the direction away from the second groove side wall A second inclination direction inclination angle, and an inclination angle of the second side wall standing direction toward the top with respect to a direction perpendicular to the friction contact surface is a second rising direction inclination angle. It is preferable that the second standing direction inclination angle is set larger than the first standing direction inclination angle.

  According to this configuration, since the second standing direction inclination angle is set to be larger than the first standing direction inclination angle, the groove shape is generated when the lubricating coolant relatively crosses the groove portion in the second rotation state. The stirring resistance received by the part can be made smaller than the stirring resistance in the first rotation state. In addition, compared with the first rotation state, in the second rotation state, when the lubricating cooling liquid crosses the groove-shaped portion relatively in the circumferential direction, it becomes easier for the lubricating cooling liquid to ride on the top of the groove-shaped portion. It is possible to generate a greater force for separating the rotating plate and the second rotating plate. Therefore, the shear resistance in the second rotation state can be made smaller than the shear resistance in the first rotation state. Therefore, with a simple configuration, the resistance that the first rotating plate and the second rotating plate receive from the lubricating coolant in the second rotation state, and the first rotating plate and the second rotating plate that receive from the lubricating coolant in the first rotation state. It can be made smaller than the resistance.

  In addition, with respect to the groove sidewalls, which are sidewalls on both sides in the circumferential direction of the groove-shaped portion, the first rotating plate faces the flow of the lubricating coolant when rotating relative to the second rotating plate in the forward direction. The groove side wall which is opposite to the flow of the lubricating coolant when the second rotating plate rotates relative to the first rotating plate in the forward direction is the groove side wall which is the first groove side wall. In the second cross section, which is a cross section cut along a plane orthogonal to the rotation axis, as the second groove side wall, the circumference extends toward the first groove side wall from the one radial direction side to the other radial direction side of the rotation shaft. When there is a first displacement portion whose direction position changes, the sum of the total displacement amount in the radial direction and the total displacement amount in the circumferential direction of the first displacement portion is defined as a first displacement amount. The second groove side wall is directed from one radial side of the rotating shaft to the other radial side. When there is a second displacement portion whose circumferential position changes according to the above, the sum of the total displacement amount in the radial direction and the total displacement amount in the circumferential direction of the second displacement portion is defined as the second displacement amount, and the first displacement Only the second displacement part is formed, or both the first displacement part and the second displacement part are formed, and the second displacement amount is It is preferable if the configuration is set to be larger than the first displacement amount.

  In addition, with respect to the groove sidewalls, which are sidewalls on both sides in the circumferential direction of the groove-shaped portion, the first rotating plate faces the flow of the lubricating coolant when rotating relative to the second rotating plate in the forward direction. The groove side wall which is opposite to the flow of the lubricating coolant when the second rotating plate rotates relative to the first rotating plate in the forward direction is the groove side wall which is the first groove side wall. In the second cross section, which is a cross section cut along a plane orthogonal to the rotation axis, as the second groove side wall, one end in the radial direction of the first groove side wall or one end in the both sides and one radial direction of the second groove side wall An arcuate part formed in an arcuate shape or a chamfered part formed in a straight line is provided in at least one of the side or both ends, and when the arcuate part is provided, the second The arc-shaped portion is provided only on the groove side wall, or the first groove side wall and The arc-shaped portion is provided on both the second groove side walls, and the radius of curvature of the arc-shaped portion of the second groove side wall is set larger than the radius of curvature of the arc-shaped portion of the first groove side wall. When the chamfered portion is provided, the chamfered portion is provided only on the second groove side wall, or the chamfer is provided on both the first groove side wall and the second groove side wall. It is also preferable that the length of the chamfered portion of the second groove side wall is set larger than the length of the chamfered portion of the first groove side wall.

  According to these configurations, in the second rotation state, the drag acting between the lubrication coolant and the groove-like portion at the time of the collision between the lubricating coolant and the groove-like portion is greater than the drag force in the first rotation state. Can be small. That is, the stirring resistance that the groove portion receives when the lubricating coolant relatively crosses the groove portion in the second rotation state can be made smaller than the stirring resistance in the first rotation state. Furthermore, depending on the shape of the first groove side wall and the second groove side wall in the second cross section, which is a cross section cut along a plane perpendicular to the rotation axis, the lubricating coolant in the second rotation state is less than the first rotation state. When the groove-shaped portion is relatively traversed in the circumferential direction, the lubricating cooling liquid can easily ride on the top of the groove-shaped portion. In this case, it is possible to generate a greater force for separating the first rotating plate and the second rotating plate, and to reduce the shear resistance in the second rotation state than the shear resistance in the first rotation state. Therefore, with a simple configuration, the resistance that the first rotating plate and the second rotating plate receive from the lubricating coolant in the second rotation state, and the first rotating plate and the second rotating plate that receive from the lubricating coolant in the first rotation state. It can be made smaller than the resistance.

  Further, as described above, in the configuration in which the second standing direction inclination angle is set larger than the first standing direction inclination angle, each of the first groove side wall and the second groove side wall includes It is preferable that the shape in one cross section is formed in a linear shape, a curved shape, or a staircase shape from the bottom to the top of the groove-shaped portion.

  According to this configuration, it is possible to adopt an appropriate configuration for the groove-shaped portion according to the method for forming the groove-shaped portion, the desired magnitude of the viscous resistance, and the like.

  Further, as described above, only the second displacement portion of the first displacement portion and the second displacement portion is formed, or both the first displacement portion and the second displacement portion are formed. In addition, in the configuration in which the second displacement amount is set to be larger than the first displacement amount, each of the first displacement portion and the second displacement portion has a shape in the second cross section that is the rotation shaft. It is preferable to form in a straight line shape, a curved line shape, or a staircase shape toward one of the circumferential directions as it goes from one radial direction side to the other radial direction side.

  According to this configuration, it is possible to adopt an appropriate configuration for the groove-shaped portion according to the method for forming the groove-shaped portion, the desired magnitude of the viscous resistance, and the like.

  As described above, in the configuration in which the second standing direction inclination angle is set larger than the first standing direction inclination angle, the second section is a cross section cut along a plane orthogonal to the rotation axis. In the cross section, arc-shaped portions formed in an arc shape are provided on both ends of the first groove side wall in the radial direction and both ends of the second groove side wall in the radial direction, and the first standing direction An inclination angle is set to 0 degrees, the second standing direction inclination angle is set to an acute angle larger than 0 degrees, and the arc-shaped portion formed at both ends in the radial direction of the first groove side wall It is preferable that the radius of curvature coincides with the radius of curvature of the arcuate portion formed at both ends of the second groove side wall in the radial direction.

  According to this configuration, the resistance that the first rotating plate and the second rotating plate receive from the lubricating coolant in the second rotation state is obtained using the asymmetry of the shape in the first cross section of the groove-shaped portion in the second rotation state. The resistance that the first rotating plate and the second rotating plate receive from the lubricating coolant in one rotation state can be made smaller. In addition, since such a configuration can be realized only by changing the first standing direction inclination angle of the first groove side wall and the second standing direction inclination angle of the second groove side wall, the structure of the apparatus and the manufacturing process can be simplified. It becomes easy to plan.

  In addition, as described above, in the second cross section, at least one of the end on one side or both sides in the radial direction of the first groove side wall and the end on one side or both sides in the radial direction of the second groove side wall. When the arcuate part or the chamfered part is provided and the arcuate part is provided, the arcuate part is provided only on the second groove side wall, or the first groove side wall and The arc-shaped portion is provided on both the second groove side walls, and the radius of curvature of the arc-shaped portion of the second groove side wall is set larger than the radius of curvature of the arc-shaped portion of the first groove side wall. In the configuration, in the second cross section that is a cross section cut along a plane orthogonal to the rotation axis, both ends in the radial direction of the first groove side wall and ends in the radial direction on the second groove side wall Are provided with an arc-shaped portion formed in an arc shape on both sides. In the second cross section where the axial position coincides with the top of the groove-shaped portion, the radius of curvature of the arc-shaped portion provided at the radially outer end of the second groove sidewall is the second groove sidewall. Is set to be larger than the radius of curvature of the arc-shaped portion provided at the radially inner end portion and the radius of curvature of the arc-shaped portion provided at the end portions on both radial sides of the first groove side wall. It is preferable to adopt a configuration.

  According to this configuration, the resistance that the first rotating plate and the second rotating plate receive from the lubricating coolant in the second rotation state is obtained using the asymmetry of the shape in the second cross section of the groove-shaped portion in the second rotation state. The resistance that the first rotating plate and the second rotating plate receive from the lubricating coolant in one rotation state can be made smaller. According to this configuration, in the second rotation state, the lubricating coolant is positively pushed outward in the radial direction. Therefore, this configuration is applied to the first rotary plate and the second rotary plate from the radially inner side. It is particularly suitable for a configuration in which a lubricating coolant flows toward the outside in the radial direction.

  Further, it is preferable that a friction material is fixed to at least one of the friction contact surfaces of the first rotation plate and the second rotation plate, and the groove-shaped portion is formed by molding the friction material. .

  According to this configuration, the groove-shaped portion can be formed by molding the friction material that is relatively easy to process without processing the base material of the first rotating plate or the second rotating plate. Therefore, the manufacturing process of the friction engagement device can be simplified and the manufacturing cost can be kept low.

It is a schematic diagram which shows schematic structure of the drive device which concerns on 1st embodiment of this invention. It is a fragmentary sectional view of the drive device concerning a first embodiment of the present invention. It is a partial schematic diagram of the inner friction plate according to the first embodiment of the present invention. It is IV-IV sectional drawing (1st sectional drawing) in FIG. FIG. 5 is a VV sectional view (second sectional view) in FIG. 4. It is a figure which shows typically the flow of the oil in the state (1st rotation state) in which an inner friction board rotates relative to an outer friction board in the forward direction. It is a figure which shows typically the flow of the oil in the state (2nd rotation state) in which an outer friction plate rotates relative to an inner friction plate in the forward direction. It is a partial schematic diagram of the inner friction plate according to the second embodiment of the present invention. It is IX-IX sectional drawing (1st sectional drawing) in FIG. It is XX sectional drawing (2nd sectional drawing) in FIG. It is XI-XI sectional drawing in FIG. 9 (2nd sectional drawing). It is a partial schematic diagram of an inner friction plate according to another embodiment of the present invention. It is a partial schematic diagram of an inner friction plate according to another embodiment of the present invention. It is a partial schematic diagram of an inner friction plate according to another embodiment of the present invention. It is a partial schematic diagram of an inner friction plate according to another embodiment of the present invention. It is XVI-XVI sectional drawing in FIG. It is a 1st sectional view of a slot part concerning another embodiment of the present invention. It is a 1st sectional view of a slot part concerning another embodiment of the present invention. It is a second sectional view of a part of a groove-shaped part according to another embodiment of the present invention. It is a second sectional view of a part of a groove-shaped part according to another embodiment of the present invention. It is a partial schematic diagram of an external friction plate according to another embodiment of the present invention.

1. First Embodiment A first embodiment of the present invention will be described in detail with reference to the drawings. Here, a case where the present invention is applied to a starting clutch provided in a drive device for a parallel hybrid vehicle will be described as an example. In the starting clutch C according to the present embodiment, the groove-like portion 30 formed on the friction contact surface of the inner friction plate 11 has an asymmetric shape between the one circumferential side and the other circumferential side of the rotation axis X. It is characterized in that Thereby, the starting clutch C of the form suitable for the drive device for parallel type hybrid vehicles is implement | achieved. Hereinafter, the configuration of the starting clutch C according to the present embodiment will be described in detail.

  In the following description, unless otherwise specified, the “axial direction”, “circumferential direction”, “diameter” are based on the rotational axis X (see FIG. 2) that is the rotational axis of the inner friction plate 11 and the outer friction plate 12. "Direction" is defined. In the following description, unless otherwise specified, the right side in FIG. 2 is referred to as “one axial direction”, and the left side in FIG. 2 is referred to as “the other axial direction”. Further, in the present embodiment, the starting clutch C, the inner friction plate 11, the outer friction plate 12, and the oil are respectively “friction engagement device”, “first rotation plate”, “second rotation plate” in the present invention, And “lubricating coolant”.

1-1. Overall Configuration of Drive Device As shown in FIG. 1, a drive device 1 according to this embodiment includes an input shaft I that is drivingly connected to an engine E as a first driving force source, and an output that is drivingly connected to wheels W. For a hybrid hybrid vehicle having a shaft O, a rotating electrical machine MG as a second driving force source, and a transmission TM, and in which the engine E and the rotating electrical machine MG are connected in series via a start clutch C It is comprised as a drive device. In the present embodiment, the input shaft I, the intermediate shaft M, and the output shaft O are uniaxially arranged coaxially. In the present embodiment, the engine E, the input shaft I, and the output shaft O correspond to the “internal combustion engine”, “input member”, and “output member” in the present invention, respectively.

  The engine E is an internal combustion engine that is driven by the combustion of fuel. For example, various known engines such as a gasoline engine and a diesel engine can be used. In this example, an engine output shaft such as a crankshaft of the engine E is drivingly connected to the input shaft I.

  The input shaft I is a shaft for inputting the driving force of the engine E into the driving device 1. In this example, the input shaft I is drivingly coupled so as to rotate integrally with the engine output shaft of the engine E. A damper or the like may be interposed between the input shaft I and the engine output shaft. The input shaft I is disposed so as to penetrate the case 2.

  The starting clutch C is provided so that the engine E and the input shaft I can be selectively connected to the rotating electrical machine MG. That is, the starting clutch C is a clutch that connects and disconnects the driving force between the engine E and the rotating electrical machine MG. In the engaged state of the starting clutch C, the engine E and the rotating electrical machine MG are drivingly connected via the input shaft I, and the vehicle (FIG. 5) is driven only by the driving force of the engine E or the driving force of both the engine E and the rotating electrical machine MG. (Not shown) is driven. Further, when the starting clutch C is separated (disengaged), the engine E and the rotating electrical machine MG are separated, and the vehicle is driven only by the driving force of the rotating electrical machine MG. The configuration of the starting clutch C will be described later in detail.

  The rotating electrical machine MG includes a stator 21 and a rotor 22 (see FIG. 2). The stator 21 is configured by winding a coil around a stator core made of a laminated plate. The rotor 22 is formed of a laminated plate in which permanent magnets are embedded, and the outer peripheral surface thereof faces the inner peripheral surface of the stator 21 with a predetermined gap. The rotating electrical machine MG can perform a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. It is said that. Therefore, the rotating electrical machine MG is electrically connected to a power storage device (battery, capacitor, etc.) (not shown). The rotating electrical machine MG receives power supplied from the power storage device and performs powering, or supplies power generated by the driving force transmitted from the wheels W to the power storage device to store the power. The rotor 22 of the rotating electrical machine MG is drivingly connected so as to rotate integrally with the intermediate shaft M.

  The intermediate shaft M is a shaft for inputting torque output from the engine E and the rotating electrical machine MG to the transmission apparatus TM. As shown in FIG. 2, a plurality of oil passages (first oil passage L1, second oil passage L2) extending in the axial direction are formed inside the intermediate shaft M. The first oil passage L1 is a supply passage for oil supplied to a hydraulic chamber (details will be described later) provided in the starting clutch C. Specifically, the oil flowing through the first oil passage L1 is supplied to the hydraulic chamber via the first oil hole Lh1.

  The transmission device TM is a device that changes the rotational speed of the intermediate shaft M at a predetermined speed ratio and transmits it to the output shaft O. Examples of such a transmission TM include an automatic or manual stepped transmission that can switch between a plurality of shift stages having different transmission ratios, an automatic continuously variable transmission that can change the transmission ratio steplessly, and the like. Can be used. The transmission TM shifts the rotational speed of the intermediate shaft M at a predetermined gear ratio at each time point, converts torque, and transmits the torque to the output shaft O. The torque transmitted from the transmission device TM to the output shaft O is distributed and transmitted to the two left and right wheels W via the output differential gear device D. The output shaft O is drivably coupled to the wheel W via the output differential gear device D and is drivably coupled to the rotating electrical machine MG via the transmission TM and the intermediate shaft M. That is, the output shaft O is drivingly connected to both the rotating electrical machine MG and the wheels W.

  And each said component which comprises the drive device 1 is accommodated in the inside of case 2 (refer FIG. 2) as a non-rotating member fixed to a chassis. The case 2 supports the rotating members such as the input shaft I, the intermediate shaft M, and the rotor 22 of the rotating electrical machine MG on the engine E side (one axial side) and the transmission TM side (the other axial side) of the case 2. It is supported so as to be rotatable at the part.

  An oil pump 3 is provided inside the case 2. In this example, the oil pump 3 is an inscribed gear pump having an inner rotor and an outer rotor. The oil pump 3 is disposed coaxially with the input shaft I and the intermediate shaft M, and is configured to rotate integrally with the intermediate shaft M. As the intermediate shaft M rotates, the oil pump 3 discharges oil (hydraulic oil) and generates hydraulic pressure for supplying oil to the transmission TM, the starting clutch C, and the like. In addition, oil passages are formed inside the wall portion of the case 2 and the intermediate shaft M, and the oil discharged by the oil pump 3 flows through a hydraulic control device (not shown) and these oil passages. Then, it is supplied to each part to be hydraulically supplied.

1-2. Next, the configuration of the starting clutch C will be described in detail with reference to FIG. The starting clutch C is arranged on the inner side in the radial direction of the rotating electrical machine MG, and includes a clutch housing 50 and a clutch mechanism 10 arranged inside the clutch housing 50. The clutch housing 50 has a flange-shaped member 51 having a boss hole through which the input shaft I passes, a disk member 52 connected to the flange-shaped member 51, and a boss hole through which the intermediate shaft M passes. And a boss member 53. The disc member 52 includes a peripheral wall portion 52 a extending from the main body portion of the disc member 52 to one side in the axial direction. A spline groove for holding the outer friction plate 12 described later is formed on the inner peripheral surface of the peripheral wall portion 52a of the disc member 52. In order to create a space for accommodating the clutch mechanism 10, the hook-shaped member 51 forms an outer peripheral wall (radially outer peripheral wall) of the clutch housing 50 and a first side wall (one axial side wall) of the clutch housing 50. The disc member 52 and the boss member 53 form a second side wall (side wall on the other side in the axial direction) of the clutch housing 50.

  A first bearing 61 (ball bearing in this example) is provided between the outer peripheral surface of the boss portion 51a protruding to one side in the axial direction of the bowl-shaped member 51 and the boss-shaped axial projection portion 2a formed in the partition wall of the case 2. Is arranged to support the flange-shaped member 51, and the second bearing 62 (seal in this example) is provided between the inner peripheral surface of the boss 51a formed at the radially inner end of the flange-shaped member 51 and the input shaft I. A needle bearing with a ring) is arranged to rotatably support the input shaft I. Thereby, the bowl-shaped member 51 can rotate relative to the partition wall of the case 2 and the input shaft I. Further, the boss member 53 connected to the disk member 52 at the tip end of the radial protrusion flange portion is splined to the intermediate shaft M on the inner peripheral surface of the boss, and rotates integrally with the intermediate shaft M. A third bearing 63 (ball bearing in this example) is disposed between the boss outer peripheral surface of the boss member 53 and the boss-shaped axial protrusion 2 b formed on the partition wall of the case 2.

  The stator 21 of the rotating electrical machine MG is fixed to the inner peripheral wall of the case 2, and the rotor 22 is supported by being externally fitted to the clutch housing 50, more precisely, the outer peripheral surface of the peripheral wall portion 51 b of the bowl-shaped member 51. Therefore, the clutch housing 50 (saddle-shaped member 51) functions as a rotor support member that supports the rotor 22.

  The clutch mechanism 10 includes an input-side member 71 fixed to the input shaft I and rotating integrally with the input shaft I, a plurality (five in this example) of internal friction plates 11, and a plurality (five in this example) of external friction. This is a multi-plate clutch mechanism including a plate 12 and a piston 72. The output side member of the clutch mechanism 10 includes a disc member 52 and a boss member 53 that form the clutch housing 50.

  The input side member 71 has a peripheral wall portion 71a that extends from the main body portion of the input side member 71 disposed on one side in the axial direction in the clutch housing 50 to the other side in the axial direction and has a spline groove formed on the outer peripheral surface. Yes. And the spline groove | channel 14 (refer FIG. 3) is formed in the internal peripheral surface of the internal friction board 11, and when the said spline groove | channel 14 and the spline groove | channel of the input side member 71 engage, the internal friction board 11 is carried out. Is held to be slidable in the axial direction while restricting relative rotation with respect to the input side member 71. Thus, the inner friction plate 11 is configured to rotate integrally with the input side member 71 and the input shaft I, and is drivingly connected to the engine E via the input shaft I.

  Spline grooves are formed on the outer peripheral surface of the outer friction plate 12, and the spline grooves are engaged with the spline grooves provided on the inner peripheral surface of the peripheral wall portion 52a of the disc member 52. 12 is held so that relative rotation with respect to the disk member 52 is restricted and is slidable in the axial direction. As described above, the outer friction plate 12 is configured to rotate integrally with the output side member (the disk member 52 and the boss member 53) and the intermediate shaft M, and the output shaft via the intermediate shaft M and the transmission device TM. O is drivingly connected to O. The piston 72 is provided inside the clutch housing 50 so as to be slidable in the axial direction, and is urged toward the other side in the axial direction by a spring.

  A third oil passage L <b> 3 is formed inside the boss member 53. The third oil path L3 is an oil supply path that is supplied to the clutch mechanism 10 for lubrication and cooling. Specifically, the oil flowing through the third oil passage L3 is a space formed between the input side member 71 and the piston 72 after lubricating and cooling the fourth bearing 64 (in this example, the thrust bearing). And at least a part of the oil flows from the radially inner side toward the radially outer side through the oil supply hole (not shown) formed in the peripheral wall portion 71a of the input side member 71 and the outer friction plate 11 and the outer side. It is supplied to the friction plate 12 to perform lubrication and cooling. Thus, the clutch mechanism 10 is a wet clutch mechanism that operates in a space to which oil is supplied.

  Then, at least a part of the oil flowing through the gap between the inner friction plate 11 and the outer friction plate 12 is circled through an oil drain hole (not shown) formed in the peripheral wall portion 52a of the disc member 52. The fifth bearing 65 is discharged to the space between the peripheral wall portion 52a of the plate member 52 and the peripheral wall portion 51b of the flange-shaped member 51 and flows through the space formed between the input side member 71 and the flange-shaped member 51. (In this example, thrust bearing). A part of the oil after lubricating and cooling the fifth bearing 65 passes through the radial communication hole opened on the outer peripheral surface of the input shaft I and the second oil passage L2 formed in the inner diameter portion of the intermediate shaft M. Is discharged through. Part of the oil after lubricating and cooling the fifth bearing 65 leaks in the axial direction from the second bearing 62 and flows into the fourth oil passage L4 through the first bearing 61 and the second oil hole Lh2. . The oil discharged through the fourth oil passage L4 is returned to an oil pan (not shown). That is, in the present embodiment, both the second oil passage L2 and the fourth oil passage L4 serve as discharge passages for the oil supplied to the inner friction plate 11 and the outer friction plate 12 of the start clutch C. That is, the discharge path of the oil supplied to the inner friction plate 11 and the outer friction plate 12 of the starting clutch C is divided into two systems.

  A hydraulic chamber is formed between the piston 72 and the disk member 52. The hydraulic chamber is configured so that oil flowing through the first oil passage L <b> 1 is supplied via an oil passage formed in the first oil hole Lh <b> 1 and the boss member 53. When pressure oil is supplied to the hydraulic chamber, the piston 72 moves to one side in the axial direction, the clutch mechanism 10 is engaged, and the start clutch C is engaged. In this state, the torque of the engine E transmitted to the input side member 71 via the input shaft I is transmitted to the intermediate shaft M via the output side members (the disk member 52 and the boss member 53). At this time, in order to regulate the axial position of the inner friction plate 11 and the outer friction plate 12 that are pressed to the one side in the axial direction by the piston 72, the end on the one side in the axial direction in the peripheral wall portion 52a of the disk member 52. The part is provided with a backing plate 54 and a snap ring 55 that regulates the axial position of the backing plate. When the pressure oil is discharged from the hydraulic chamber, the piston 72 is returned to the other side in the axial direction by the spring, the clutch mechanism 10 is released, and the starting clutch C is separated.

  Incidentally, the inner friction plate 11 and the outer friction plate 12 are annular plate-like members, and are alternately arranged in the axial direction so that the rotation axes X coincide with each other. That is, the outer friction plate 12 incorporated in the disc member 52 (circumferential wall portion 52a) so as to be movable in the axial direction is the inner friction plate 11 incorporated in the input side member 71 (peripheral wall portion 71a) so as to be movable in the axial direction. It arrange | positions so that it may interpose between. The rotation axis X coincides with the rotation axis of the input shaft I and the intermediate shaft M as shown in FIG.

  The inner friction plate 11 and the outer friction plate 12 have axial end surfaces facing each other as a friction contact surface that is generally annular, and are disposed opposite to each other so that both friction contact surfaces can contact each other. ing. On at least one friction contact surface of the inner friction plate 11 and the outer friction plate 12, a friction material 13 made of, for example, paper or synthetic resin as a base material is attached. In this example, as shown in FIG. 3, the friction material 13 is fixed to the friction contact surface of the inner friction plate 11.

  A groove-like portion 30 extending along the radial direction is formed on the friction contact surface of the inner friction plate 11. Specifically, the groove-shaped portion 30 is formed by molding the friction material 13 fixed to the axial end surface of the inner friction plate 11. In the present embodiment, the inner friction plate 11 is configured by a plurality of segment-like friction materials 13 being fixed along the circumferential direction on an axial end surface of a core plate 11a formed of metal (steel plate or the like). The end surface of the friction material 13 opposite to the core plate 11a in the axial direction constitutes a friction contact surface. And the clearance gap between the friction materials 13 adjacent to the circumferential direction forms the groove-shaped part 30. FIG. Therefore, in the present embodiment, the bottom surface portion of the groove portion 30 is formed by the axial end surface of the core plate 11 a, and the side wall portion of the groove portion 30 is formed by the circumferential end surface of the friction material 13. On the other hand, the outer friction plate 12 is constituted by a core plate 12a formed of metal (steel plate or the like), and the axial end surface of the core plate 12a constitutes a friction contact surface.

  In the engaged state of the starting clutch C, the friction contact surface of the inner friction plate 11 and the friction contact surface of the outer friction plate 12 come into contact with each other and are frictionally engaged. Here, the rotation direction of the inner friction plate 11 and the outer friction plate 12 during the forward rotation of the output shaft O in this engaged state is defined as a forward direction F. In the separated state of the starting clutch C, the friction contact surface of the inner friction plate 11 and the friction contact surface of the outer friction plate 12 are separated.

  In the separated state of the starting clutch C, the resistance that the inner friction plate 11 and the outer friction plate 12 receive from oil when the outer friction plate 12 rotates relative to the inner friction body 11 in the forward direction F is the inner friction plate. When the groove 11 is rotated in the forward direction F relative to the outer friction plate 12, the groove portion 30 is arranged in the circumferential direction of the rotation axis X so that the inner friction plate 11 and the outer friction plate 12 are less than the resistance received from the oil. The shape is asymmetric between one side and the other circumferential side. Thereby, the starting clutch C of the form suitable for the drive device for parallel type hybrid vehicles is implement | achieved. Hereinafter, the configuration of the groove-shaped portion 30 which is a main part of the present invention will be described in detail.

1-3. Configuration of Groove Part The configuration of the groove part 30 according to the present embodiment will be described in detail with reference to FIGS. 3 to 7. As shown in FIG. 3, a plurality of segment-shaped friction materials 13 having the same shape are annularly formed on the end surface in the axial direction of the core plate 11 a of the inner friction plate 11 at regular intervals along the circumferential direction. Is arranged. And the groove-shaped part 30 extended along the radial direction of the mutually same shape by the clearance gap between the friction materials 13 adjacent to the circumferential direction is formed at regular intervals along the circumferential direction. In the present embodiment, both the radially inner end surface and the radially outer end surface of the friction material 13 are formed perpendicular to the friction contact surface. In the present embodiment, the inner friction plate 11 has a plurality of friction materials 13 fixed to each of the end surfaces on both sides in the axial direction of the core plate 11a to form the groove-shaped portion 30. It is symmetrically formed on the other side in the axial direction. Therefore, in the following description, only the configuration on one side in the axial direction of the inner friction plate 11 will be described, but the configuration on the other side in the axial direction is the same as that on the one side.

  4 is a cross-sectional view taken along the line IV-IV in FIG. 3, and is a cross section (hereinafter simply referred to as “first cross section”) obtained by cutting the groove-shaped portion 30 shown in FIG. It is a schematic diagram showing the shape. 5 is a cross-sectional view taken along the line VV in FIG. 4, and is a cross section (hereinafter simply referred to as “second cross section”) obtained by cutting the groove-shaped portion 30 shown in FIG. 3 along a plane orthogonal to the rotation axis X. It is a schematic diagram which shows the shape of). The resistance that the inner friction plate 11 and the outer friction plate 12 receive from the oil when the outer friction plate 12 rotates relative to the inner friction plate 11 in the forward direction F, the inner friction plate 11 against the outer friction plate 12. In order to make the inner friction plate 11 and the outer friction plate 12 less than the resistance received from the oil when they rotate relative to each other in the forward direction F, the groove-shaped portion 30 has a first cross-sectional shape and a second cross-sectional shape. At least one of the shapes is formed in an asymmetric shape between the one circumferential side and the other circumferential side. In addition, the cross-sectional shape of the groove-shaped part 30 may differ with the radial direction position of a 1st cross section, and the axial direction position of a 2nd cross section. In the present invention, if the shape of the groove-like portion 30 is asymmetrical between the one circumferential side and the other circumferential side in the first cross section at least in any radial position, the groove-like portion 30 is Is formed in an asymmetric shape on one side in the circumferential direction and the other side in the circumferential direction. Similarly, in the present invention, if the shape of the groove-shaped portion 30 is asymmetric between the one circumferential side and the other circumferential side in the second cross section at least in any axial position, It is assumed that the shape of the second cross section is formed in an asymmetric shape between the one circumferential side and the other circumferential side.

  In the present embodiment, as shown in FIG. 4, the shape of the first cross section of the groove-like portion 30 is asymmetric between the one circumferential side and the other circumferential side. On the other hand, as shown in FIG. 5, the shape of the second cross section of the groove-shaped portion 30 may be slightly asymmetric depending on the axial position in the groove-shaped portion 30 where the second cross section is located. It is almost symmetrical with the other side in the circumferential direction. Therefore, in the present embodiment, the inner friction plate 11 and the outer friction plate 12 are made of oil by making the shape in the first cross section of the groove-like portion 30 asymmetrical between the one circumferential side and the other circumferential side. The resistance to be received is changed depending on which friction plate is rotating relative to the forward direction F.

  Here, as shown in FIG. 3, the flow of oil when the inner friction plate 11 rotates relative to the outer friction plate 12 in the forward direction F with respect to the groove side walls which are the side walls on both sides in the circumferential direction of the groove-shaped portion 30. The groove side wall that faces the first friction side wall 31 is the first groove side wall 31, and the groove side wall that faces the oil flow when the outer friction plate 12 rotates relative to the inner friction plate 11 in the forward direction F is the second groove. The side wall 32 is used.

  As shown in FIG. 4, in the first cross section, from the bottom 33 of the first groove side wall 31 (the end on the core plate 11 a side in the axial direction, the same shall apply hereinafter) to the top 34 (the core plate 11 a in the axial direction). The direction toward the opposite end, the same shall apply hereinafter) is the first side wall standing direction A1, and the first side wall standing direction A1 is the top with respect to the direction perpendicular to the frictional contact surface (the direction indicated by the broken line in FIG. 4). An angle inclined toward the direction away from the second groove side wall 32 toward the line 34 is defined as a first standing direction inclination angle θ1. In the first cross section, the direction from the bottom 33 to the top 34 of the second groove side wall 32 is defined as a second side wall standing direction A2, and the second side wall standing direction A2 is perpendicular to the friction contact surface. The angle inclined toward the direction away from the first groove side wall 31 toward the second direction is defined as a second standing direction inclination angle θ2. In the example shown in FIG. 4, the first standing direction inclination angle θ <b> 1 is 0 degree, and thus the notation of θ <b> 1 is omitted, but as shown in FIG. 18, which is a schematic diagram of another embodiment described later. The first standing direction inclination angle θ1 is defined as follows.

  Further, as shown in FIG. 5, the circumferential position of the first groove side wall 31 of the second cross section changes as it goes from one radial side to the other radial side (from one side to the other side in the radial direction). The part is defined as a first displacement portion 41, and the sum of the total displacement amount Dr in the radial direction of the first displacement portion 41 and the total displacement amount Dc in the circumferential direction is defined as a first displacement amount D1. Here, the total displacement amount Dr in the radial direction of the first displacement portion 41 is the displacement amount in the radial direction of each first displacement portion 41 when the first groove side wall 31 has a plurality of first displacement portions 41. It means the total displacement that is the sum. Similarly, the total displacement amount Dc in the circumferential direction of the first displacement portion 41 is the displacement amount in the circumferential direction of each first displacement portion 41 when the first groove side wall 31 has a plurality of first displacement portions 41. It means the total displacement that is the sum. In addition, a portion of the second groove side wall 32 of the second cross section in which the circumferential position changes from the one radial side to the other radial side is defined as a second displacement portion 42, and the second displacement portion 42 in the radial direction The sum of the total displacement amount Dr and the total displacement amount Dc in the circumferential direction is defined as a second displacement amount D2. Here, the total displacement amount Dr in the radial direction of the second displacement portion 42 is the displacement amount in the radial direction of each second displacement portion 42 when the second groove sidewall 32 has a plurality of second displacement portions 42. It means the total displacement that is the sum. Similarly, the total displacement amount Dc in the circumferential direction of the second displacement portion 42 is the displacement amount in the circumferential direction of each second displacement portion 42 when the second groove sidewall 32 has a plurality of second displacement portions 42. It means the total displacement that is the sum.

  In the present embodiment, as shown in FIG. 4, both the first groove side wall 31 and the second groove side wall 32 are formed in a straight line shape from the bottom 33 to the top 34 of the groove 30 in the first cross section. Yes. And 2nd standing direction inclination angle (theta) 2 is set larger than 1st standing direction inclination angle (theta) 1 (this example 0 degree). In this example, the second standing direction inclination angle θ2 is set to 45 degrees as an example, but the second standing direction inclination angle θ2 is an arbitrary angle greater than 0 degrees and smaller than 90 degrees (a sharp angle larger than 0 degrees). It can be. Thus, by making the second standing direction inclination angle θ2 larger than the first standing direction inclination angle θ1, the outer friction plate 12 rotates relative to the inner friction plate 11 in the forward direction F as described below. When the inner friction plate 11 and the outer friction plate 12 rotate relative to the outer friction plate 12 in the forward direction F, the inner friction plate 11 and the outer friction plate 12 receive oil from the oil. It is possible to make it smaller than the resistance received from the.

  FIG. 6 shows a state in which the inner friction plate 11 is rotating relative to the outer friction plate 12 in the forward direction F in the separated state of the starting clutch C (hereinafter, this state is referred to as “first rotation state”). It is a figure which shows the flow of oil typically. This first rotation state is, for example, when the vehicle is stopped (in a state where the rotation of the output shaft O is stopped) and the start clutch C is separated in preparation for the start of the vehicle by the driving force of the engine E. This is a state that can occur when E is started (the fuel injection device of engine E is operating). FIG. 7 shows a state in which the outer friction plate 12 rotates relative to the inner friction plate 11 in the forward direction F in the separated state of the starting clutch C (hereinafter, this state is referred to as a “second rotation state”). It is a figure which shows the flow of the oil in) typically. This second rotation state is, for example, a state in which the engine E is not started and can occur while the vehicle is traveling forward only by the driving force of the rotating electrical machine. In both cases of the first rotation state (FIG. 6) and the second rotation state (FIG. 7), the oil flows in the forward direction F. In these drawings, the arrow indicating the oil flow is a groove. The shape portion 30 is used as a reference. That is, in the first rotation state shown in FIG. 6, the oil moves relative to the groove-shaped portion 30 in the direction opposite to the forward direction F, and in the second rotation state shown in FIG. On the other hand, it moves relative to the same side as the forward direction F.

  6 and FIG. 7, it is clear that when the oil moves relative to the groove-shaped portion 30 in the same direction as the forward direction F as in the second rotation state shown in FIG. When the oil moves relative to the groove portion 30 in the direction opposite to the forward direction F as in the first rotation state shown in FIG. Less than the resistance you receive. From another viewpoint, the resistance that the inner friction plate 11 and the outer friction plate 12 receive from the oil in the second rotation state is smaller than the resistance that the inner friction plate 11 and the outer friction plate 12 receive from the oil in the first rotation state. Become. Because the second standing direction inclination angle θ2 is set larger than the first standing direction inclination angle θ1 as described above, the oil relatively crosses the groove-shaped portion 30 in the circumferential direction in the second rotation state. The resistance that the groove-shaped portion 30 receives, that is, the resistance caused by the oil being stirred in the groove-shaped portion 30 (hereinafter simply referred to as “stirring resistance”) is greater than the oil stirring resistance in the first rotation state. It is also because it becomes small.

  Furthermore, since the second standing direction inclination angle θ2 is set to be larger than the first standing direction inclination angle θ1, the oil is more frictional in the second rotation state than the first rotation state. It is positively guided between the surface facing the outer friction plate 12) and the friction contact surface of the outer friction plate 12. Thereby, the force (force shown by the code | symbol T in FIG. 7) which separates the inner friction board 11 and the outer friction board 12 becomes larger in a 2nd rotation state than a 1st rotation state. Accordingly, in the second rotation state, the separation distance between the inner friction plate 11 and the outer friction plate 12 is suppressed from being excessively shortened, and resistance (hereinafter simply referred to as “shear resistance”) caused by the oil being sheared. Is smaller than in the first rotation state.

  As described above, in the second rotation state shown in FIG. 7, both the oil stirring resistance and the shear resistance can be reduced compared to the first rotation state shown in FIG. Resistance (hereinafter simply referred to as “viscous resistance”) can be reduced. That is, the resistance that the inner friction plate 11 and the outer friction plate 12 receive from the oil in the second rotation state can be made smaller than the resistance that the inner friction plate 11 and the outer friction plate 12 receive from the oil in the first rotation state. Thus, the shape of the groove-shaped portion 30 in the first cross section affects both the oil stirring resistance and the shear resistance.

  Further, in the present embodiment, as shown in FIG. 5, the first displacement portions 41 are formed at the ends on both sides in the radial direction of the first groove side wall 31 and the ends on both sides in the radial direction of the second groove side wall 32. A second displacement part 42 is formed in the part. And both the 1st displacement part 41 and the 2nd displacement part 42 are formed in the 2nd cross section in the curve shape which goes to either one side in the circumferential direction as it goes to the other radial direction side from the radial direction one side. . The first displacement portion 41 formed on the radially outer side of the first groove side wall 31 has a radial displacement amount Dr1 and a circumferential displacement amount Dc1. The first displacement portion 41 formed on the radially inner side of the first groove sidewall 31 has a radial displacement amount Dr2 and a circumferential displacement amount Dc2. Therefore, for the first displacement portion 41, the total displacement amount Dr in the radial direction is “Dr1 + Dr2”, the total displacement amount Dc in the circumferential direction is “Dc1 + Dc2,” and as a result, the first displacement amount that is the sum of Dr and Dc. D1 is “Dr1 + Dr2 + Dc1 + Dc2.”

  On the other hand, the second displacement portion 42 formed on the radially outer side of the second groove sidewall 32 has a radial displacement amount Dr3 and a circumferential displacement amount Dc3. The second displacement portion 42 formed on the radially inner side of the second groove sidewall 32 has a radial displacement amount Dr4 and a circumferential displacement amount Dc4. Therefore, for the second displacement portion 42, the total displacement amount Dr in the radial direction is “Dr3 + Dr4”, the total displacement amount Dc in the circumferential direction is “Dc4 + Dc4”, and as a result, the second displacement amount that is the sum of Dr and Dc. D2 is “Dr3 + Dr4 + Dc3 + Dc4”.

  In the present embodiment, as shown in FIG. 5, all of the first displacement portions 41 on both sides in the radial direction of the first groove side wall 31 and the second displacement portions 42 on both sides in the radial direction of the second groove side wall 32 are curved. The arc-shaped portions have substantially the same radius. That is, in the second cross section, arc-shaped portions formed in an arc shape are provided on both ends of both sides in the radial direction of the first groove side wall 31 and ends on both sides in the radial direction of the second groove side wall 32. In addition, the radius of curvature of the arc-shaped portion formed at both ends in the radial direction of the first groove side wall 31 and the radius of curvature of the arc-shaped portion formed at the ends of both sides in the radial direction of the second groove side wall 32 are It is formed so as to almost coincide. Strictly speaking, in this example, in the second cross section in which the axial position coincides with the bottom 33 of the groove-shaped portion 30, the radius of curvature of the arc-shaped portion formed at both ends in the radial direction of the first groove sidewall 31 is The curvature radii of the arcuate portions formed at the ends of the second groove sidewall 32 on both radial sides coincide with each other (see FIG. 3). On the other hand, in the second cross section in which the axial position coincides with the top portion 34 of the groove-shaped portion 30, the radius of curvature of the arc-shaped portion formed at both ends in the radial direction of the first groove sidewall 31 is the second groove. It is slightly larger than the radius of curvature of the arc-shaped portion formed at the ends on both sides in the radial direction of the side wall 32 (see FIG. 3).

  Therefore, in this example, the radial displacement amounts Dr1 to Dr4 and the circumferential displacement amounts Dc1 to Dc4 are substantially equal to each other, and the first displacement amount D1 is approximately equal to the second displacement amount D2. Thus, in this embodiment, the shape of the 2nd cross section of the groove-shaped part 30 is substantially symmetrical by the circumferential direction one side and the circumferential direction other side. By the way, although the shape in the 2nd cross section of the groove-shaped part 30 mainly affects the stirring resistance of oil, in this example, both the 1st displacement part 41 and the 2nd displacement part 42 are formed. In addition, the first displacement amount D1 and the second displacement amount D2 are set substantially equal to each other. That is, in this embodiment, depending on the shape of the second cross section of the groove-like portion 30, the oil viscosity resistance (mainly stirring resistance) between the first rotation state shown in FIG. 6 and the second rotation state shown in FIG. It does not make a difference.

  As described above, in the present embodiment, the second standing direction inclination angle θ2 is set to be larger than the first standing direction inclination angle θ1, that is, the asymmetry in the circumferential direction in the first cross section of the shape of the groove portion 30. , The resistance that the inner friction plate 11 and the outer friction plate 12 receive from oil in the second rotation state in which the outer friction plate 12 rotates relative to the inner friction body 11 in the forward direction F is In the first rotation state in which the outer friction plate 12 rotates relative to the forward direction F, the inner friction plate 11 and the outer friction plate 12 can be made smaller than the resistance received from the oil.

2. Second Embodiment A second embodiment of the present invention will be described in detail with reference to the drawings. Here, the case where the present invention is applied to a starting clutch provided in a drive device for a parallel hybrid vehicle will be described as an example. The overall configuration of the drive device 1 according to the present embodiment and the configuration of each unit are basically the same as those of the first embodiment. In the present embodiment, the configuration of the groove-like portion 30 is different from that of the first embodiment. Below, with reference to FIGS. 8-11, the structure of the groove-shaped part 30 with which the starting clutch C which concerns on this embodiment is provided is demonstrated centering on difference with said 1st embodiment. Note that points not particularly specified are the same as those in the first embodiment.

  As shown in FIG. 8, a plurality of segment-shaped friction materials 13 having the same shape are annularly formed on the end surface in the axial direction of the core plate 11a of the inner friction plate 11 as a whole at regular intervals along the circumferential direction. Is arranged. And the groove-shaped part 30 extended in the radial direction of the mutually same shape is formed at regular intervals along the circumferential direction by the clearance gap between the friction materials 13 adjacent to the circumferential direction.

  9A is a cross-sectional view taken along the line IXa-IXa in FIG. 8, and FIG. 9B is a cross-sectional view taken along the line IXb-IXb in FIG. That is, FIGS. 9A and 9B are both shapes of a cross section (first cross section) obtained by cutting the groove-like portion 30 shown in FIG. 8 along a cylindrical surface having the rotation axis X as an axis. However, as shown in FIG. 8, the radial positions of the first section are different from each other. As shown in these drawings, in this embodiment, the shape of the first groove sidewall 31 is the same as that of the first embodiment, but the shape of the second groove sidewall 32 is different from that of the first embodiment. Is different. Specifically, in the present embodiment, the first standing direction inclination angle θ1 is set to 0 degrees, and the second standing direction inclination angle θ2 is set to 0 degrees from 0 degrees toward the radially outer side from the radially inner side. It is set so as to change toward a predetermined acute angle (45 degrees in this example) that is larger than the angle.

  In the present embodiment, as in the first embodiment, the second standing direction inclination angle θ2 is set to be larger than the first standing direction inclination angle θ1. Strictly speaking, in the first cross section shown in FIG. 9A, the second standing direction inclination angle θ2 is equal to the first standing direction inclination angle θ1 (0 degrees in this example). Therefore, in the present invention, “the second standing direction inclination angle is set larger than the first standing direction inclination angle” means that the second standing direction inclination is at least in the first cross section at any radial position. This is a concept including that the angle θ2 is set larger than the first standing direction inclination angle θ1.

  10 is a cross-sectional view taken along the line XX in FIG. 9A, and FIG. 11 is a cross-sectional view taken along the line XI-XI in FIG. As shown in FIGS. 10 and 11, in the present embodiment as well, in the same manner as in the first embodiment, the first displacement portions 41 are formed at the ends of the first groove side wall 31 on both sides in the radial direction. Second displacement portions 42 are formed at the ends of the two groove sidewalls 32 in the radial direction. And both the 1st displacement part 41 and the 2nd displacement part 42 are formed in the 2nd cross section in the curve shape which goes to either one side in the circumferential direction as it goes to the other radial direction side from the radial direction one side. . However, in the present embodiment, the shape of the second groove side wall 32 in the second cross section is also the same as the shape of the second groove side wall 32 in the second cross section. This is different from the embodiment.

  As shown in FIG. 10, in the second cross section where the axial position is close to the bottom 33 of the groove-shaped portion 30, the first groove sidewall 31 is the same as in the first embodiment (see FIG. 5). And the 2nd groove | channel side wall 32 is formed. Specifically, the first displacement portion 41 formed on the radially outer side of the first groove side wall 31 has a radial displacement amount Dr5 and a circumferential displacement amount Dc5. The first displacement portion 41 formed on the radially inner side of the first groove side wall 31 has a radial displacement amount Dr6 and a circumferential displacement amount Dc6. Therefore, for the first displacement portion 41, the total displacement amount Dr in the radial direction is “Dr5 + Dr6”, the total displacement amount Dc in the circumferential direction is “Dc5 + Dc6”, and as a result, the first displacement amount that is the sum of Dr and Dc. D1 is “Dr5 + Dr6 + Dc5 + Dc6”.

  On the other hand, the second displacement portion 42 formed on the radially outer side of the second groove side wall 32 has a radial displacement amount Dr7 and a circumferential displacement amount Dc7. The second displacement portion 42 formed on the radially inner side of the second groove side wall 32 has a displacement amount in the radial direction of Dr8 and a displacement amount in the circumferential direction of Dc8. Therefore, for the second displacement portion 42, the total displacement amount Dr in the radial direction is “Dr7 + Dr8”, the total displacement amount Dc in the circumferential direction is “Dc7 + Dc8”, and as a result, the second displacement amount that is the sum of Dr and Dc. D2 is “Dr7 + Dr8 + Dc7 + Dc8”.

  As shown in FIG. 10, in the second cross section where the axial position is close to the bottom 33 of the groove-shaped portion 30, the first displacement portions 41 on the both radial sides of the first groove sidewall 31 and the second groove All of the second displacement portions 42 on both sides in the radial direction of the side wall 32 are arc-shaped portions having substantially the same radius of curvature. That is, in the second cross section where the axial position is close to the bottom 33 of the groove-shaped portion 30, both ends in the radial direction of the first groove sidewall 31 and both ends in the radial direction of the second groove sidewall 32 Are provided with arc-shaped portions formed in an arc shape, the radius of curvature of the arc-shaped portion formed at both ends of the first groove side wall 31 in the radial direction, and the diameter of the second groove side wall 32. It is formed so that the curvature radii of the arc-shaped portions formed at the ends on both sides in the direction substantially coincide with each other. Accordingly, the radial displacement amounts Dr5 to Dr8 and the circumferential displacement amounts Dc5 to Dc8 are substantially equal to each other, and the first displacement amount D1 is approximately equal to the second displacement amount D2. Thus, the shape of the groove-like portion 30 in the second cross section in which the axial position is close to the bottom 33 of the groove-like portion 30 is substantially symmetrical between the one circumferential side and the other circumferential side. .

  On the other hand, as shown in FIG. 11, in the second cross section where the axial position is close to the top 34 of the groove-shaped portion 30, the shape of the groove-shaped portion 30 is one side in the circumferential direction and the other side in the circumferential direction. It is asymmetric. Specifically, the first displacement portion 41 formed on the radially outer side of the first groove sidewall 31 has a displacement amount in the radial direction of Dr9 and a displacement amount in the circumferential direction of Dc9. The first displacement portion 41 formed on the radially inner side of the first groove side wall 31 has a radial displacement amount Dr10 and a circumferential displacement amount Dc10. Therefore, for the first displacement portion 41, the total displacement amount Dr in the radial direction is “Dr9 + Dr10”, the total displacement amount Dc in the circumferential direction is “Dc9 + Dc10”, and as a result, the first displacement amount that is the sum of Dr and Dc. D1 is “Dr9 + Dr10 + Dc9 + Dc10”.

  On the other hand, as for the 2nd displacement part 42 formed in the radial direction outer side of the 2nd groove | channel side wall 32, the displacement amount in radial direction is Dr11, and the displacement amount in the circumferential direction is Dc11. The second displacement portion 42 formed on the radially inner side of the second groove side wall 32 has a displacement amount in the radial direction of Dr12 and a displacement amount in the circumferential direction of Dc12. Therefore, for the second displacement portion 42, the total displacement amount Dr in the radial direction is “Dr11 + Dr12”, the total displacement amount Dc in the circumferential direction is “Dc11 + Dc12”, and as a result, the second displacement amount that is the sum of Dr and Dc. D2 is “Dr11 + Dr12 + Dc11 + Dc12”.

  As shown in FIG. 11, in the second cross section in which the axial position is close to the top 34 of the groove-shaped portion 30, the first displacement portions 41 on both radial sides of the first groove side wall 31, Although the second displacement portion 42 on the radially inner side of the two-groove side wall 32 is an arc-shaped portion having substantially the same radius of curvature, the second displacement portion 42 on the radially outer side of the second groove sidewall 31 is The arcuate portion has a large radius of curvature with respect to the two displacement portions. That is, the radius of curvature of the arc-shaped portion provided at the radially outer end of the second groove sidewall 32 is equal to the radius of curvature of the arc-shaped portion provided at the radially inner end of the second groove sidewall 32 and the second radius of curvature. It is set so as to be larger than the radius of curvature of the arcuate portion provided at the ends of both sides in the radial direction of the one-groove side wall 31. In other words, the radial displacement amount Dr11 and the circumferential displacement amount Dc11 of the second displacement portion 42 provided at the radially outer end of the second groove sidewall 32 are the radial displacement amounts and circumferential directions of the other displacement portions. It is larger than the displacement.

  Therefore, the radial displacement amounts Dr9, Dr10, Dr12 and the circumferential displacement amounts Dc9, Dc10, Dc12 are substantially equal to each other, and the radial displacement amount Dr11 and the circumferential displacement amount Dc11 are approximately equal to each other. , Dr11 and Dc11 are large values for all of Dr9, Dr10, Dr12, Dc9, Dc10, and Dc12. Therefore, the second displacement amount D2 is larger than the first displacement amount D1. Thus, the shape of the groove-like portion 30 in the second cross section in which the axial position is close to the top 34 of the groove-like portion 30 is asymmetric between the one circumferential side and the other circumferential side.

  In this example, as is apparent from FIG. 8, the arc-shaped portion provided at the radially outer end of the second groove side wall 32 has the axial position of the second section in the bottom 33 of the groove-shaped portion 30. The radius of curvature, in other words, the radial displacement amount and the circumferential displacement amount are set so as to increase from the position that coincides with the top portion 34 to the position that coincides with the top portion 34.

  Thus, in the present embodiment, both the first displacement portion 41 and the second displacement portion 42 are formed, and the second displacement amount D2 is set larger than the first displacement amount D1. Strictly speaking, in the cross section shown in FIG. 10, the second displacement amount D2 is substantially equal to the first displacement amount D1. Therefore, in the present invention, “the second displacement amount is set larger than the first displacement amount” means that the second displacement amount D2 is the first displacement amount in the second cross section at least in any axial position. It is a concept that includes being set larger than D1.

  As described above, in the present embodiment, since the second standing direction inclination angle θ2 is set to be larger than the first standing direction inclination angle θ1, as in the first embodiment, the oil in the second rotation state is set. Viscosity resistance (both stirring resistance and shear resistance) can be reduced compared to the first rotation state. Furthermore, in the present embodiment, unlike the first embodiment, the second displacement amount D2 is set larger than the first displacement amount D1. Therefore, in the present embodiment, the configuration in which the viscous resistance (mainly stirring resistance) of the oil in the second rotation state is made smaller than that in the first rotation state also by the shape of the second cross section of the groove-shaped portion 30. It has become.

  Further, in the present embodiment, the radius of curvature of the arc-shaped portion provided at the radially outer end of the second groove sidewall 32 is the arc-shaped portion provided at the radially inner end of the second groove sidewall 32. And the radius of curvature of the arcuate portion provided at both ends of the first groove sidewall 31 in the radial direction are set to be larger. In other words, the radial displacement amount and the circumferential displacement amount of the second displacement portion 42 provided at the radially outer end portion of the second groove sidewall 32 are provided at the radially inner end portion of the second groove sidewall 32. The second displacement portion 42 and the first groove side wall 31 are set so as to be larger than the radial displacement amount and the circumferential displacement amount in the first displacement portion 41 provided at both ends in the radial direction of the first groove side wall 31. Thereby, in the second rotation state, the oil can be positively pushed radially outward. As described above, the oil supplied to the inner friction plate 11 and the outer friction plate 12 from the radially inner side is an oil drain hole (disc member) positioned on the radially outer side with respect to the friction plates 11 and 12. The oil is discharged outward in the radial direction through an oil drain hole (not shown) formed in the peripheral wall portion 52a of 52. Therefore, in the present embodiment, the oil is positively pushed outward in the radial direction, which is the downstream side in the oil flow. From this point as well, the oil agitation resistance in the second rotation state is compared with that in the first rotation state. It can be made smaller. That is, the configuration according to the present embodiment is particularly suitable for a configuration in which oil is supplied from the radially inner side to the inner friction plate 11 and the outer friction plate 12, and the oil is discharged from the radially outer side. Yes.

3. Other Embodiments Finally, other embodiments according to the present invention will be described. Note that the features disclosed in each of the following embodiments can be used only in that embodiment, and can be applied to other embodiments as long as no contradiction arises.

(1) In the first and second embodiments, when the second standing direction inclination angle θ2 is set to be larger than the first standing direction inclination angle θ1, that is, in the first cross section of the groove-like portion 30. The case where the shape is asymmetric between the one side in the circumferential direction and the other side in the circumferential direction has been described as an example. However, the embodiment of the present invention is not limited to this, and the first standing direction inclination angle θ1 and the second standing direction inclination angle θ2 are equal to each other, that is, the shape of the groove-shaped portion 30 in the first cross section is circumferential. It can also be made symmetrical with respect to one side in the direction and the other side in the circumferential direction. For example, as shown in FIG. 12, both the first standing direction inclination angle θ1 and the second standing direction inclination angle θ2 are set to 0 degrees, and the shape of the groove-shaped portion 30 in the second cross section is set to the circumferential one side and the circumferential side. It can be asymmetric with respect to the other side in the direction. Although a detailed description is omitted, in the configuration shown in FIG. 12, the second displacement amount D2 is larger than the first displacement amount D1, so that the oil in the second rotation state is the same as in the first and second embodiments. The viscosity resistance (mainly stirring resistance) of the oil can be made smaller than the viscosity resistance (mainly stirring resistance) of the oil in the first rotation state. Although illustration is omitted, in the configuration shown in FIG. 12, the shape of the second groove side wall 32 in the second cross section is the same as that in the second cross section in the vicinity of the top 34 of the groove portion 30 in the second embodiment. A shape similar to the shape of the double groove side wall 32 (see FIG. 11) is also suitable. Further, in the configuration shown in FIG. 12, the shape in the vicinity of the bottom of the groove-shaped portion 30 is similar to that in the second embodiment in that the shape in the second cross section is symmetrical on one side in the circumferential direction and the other side in the circumferential direction. It can also be configured.

(2) In the first and second embodiments, the case where the end surface on the radially inner side of the friction material 13 is formed perpendicular to the friction contact surface has been described as an example. However, the embodiment of the present invention is not limited to this, and as shown in FIG. 13, the radially inner end face of the friction material 13 is away from the core plate 11a in the axial direction toward the radially outer side. It can also be configured as an inclined surface that is inclined with respect to the direction perpendicular to the friction contact surface. In such a configuration, the oil supplied to the inner friction plate 11 from the radially inner side can be actively guided to the friction contact surface of the friction material 13 (the surface facing the outer friction plate 12). The resistance can be kept low.

(3) In the first and second embodiments, the case where both the first displacement portion 41 and the second displacement portion 42 are formed has been described as an example. However, the embodiment of the present invention is not limited to this, and as shown in FIG. 14, only the first displacement portion 41 and the second displacement portion 42 among the second displacement portions 42 are formed. This is also a preferred embodiment of the present invention. In such a configuration, the end portions on both sides in the radial direction of the first groove side wall 31 are the right-angle end portions 36 having a right-angle shape in the second cross section, so that the viscous resistance of oil in the first rotation state (mainly stirring) Resistance) can be increased. Therefore, the creep torque transmitted to the output shaft O when starting the vehicle by the driving force of the engine E can be ensured.

(4) In the first and second embodiments, the case where the first displacement portion 41 and the second displacement portion 42 are portions formed in an arc shape has been described as an example. However, the embodiment of the present invention is not limited to this. For example, as shown in FIG. 15, at the radial intermediate position in the second groove side wall 32, a linear portion in which the shape in the second cross section uniformly goes to the forward direction F side toward the radial outer side, and the radial direction One of the preferred embodiments of the present invention is to form a substantially V-shaped second displacement portion 42 that is combined with a linear portion that is uniformly directed to the opposite side of the forward direction F toward the outside. is there. By forming such a second displacement portion 42, when the oil crosses the groove-shaped portion 30 relatively in the circumferential direction in the second rotation state, the oil that passes through the second displacement portion 42 is allowed to pass through the friction material 13. It is possible to positively guide to the friction contact surface, and it is possible to further suppress the oil shear resistance in the second rotation state. In the example shown in FIG. 15, as shown in FIG. 16, in the first cross section passing through the second displacement portion 42 formed at the radial intermediate position in the second groove side wall 32, the second standing direction inclination angle θ <b> 2 is Since the inclination angle θ1 is set to be larger than the first standing direction inclination angle θ1, when the oil relatively crosses the groove-shaped portion 30 in the circumferential direction in the second rotation state, more oil passes through the second displacement portion 42. It is possible to reliably lead to the friction contact surface of the friction material 13.

(5) In the first and second embodiments, both the first groove side wall 31 and the second groove side wall 32 are formed in a straight line shape from the bottom 33 to the top 34 of the groove 30 in the first cross section. The case has been described as an example. However, the embodiment of the present invention is not limited to this, and the shape of the first groove sidewall 31 in the first cross section is a curved shape or a stepped shape from the bottom 33 to the top 34 of the groove 30. Can do. Similarly, the shape of the second groove sidewall 32 in the first cross section can be a curved shape or a stepped shape from the bottom 33 to the top 34 of the groove 30. In FIG. 17, the shape of the first groove sidewall 31 in the first cross section is a straight line from the bottom 33 to the top 34 of the groove 30, and the shape of the second groove sidewall 32 in the first cross section is the groove It is a schematic diagram which shows the case where it is the step shape which goes to 30 from the bottom part 33 of 30. In such a configuration, as shown in FIG. 17, the second side wall standing direction A2 can be defined as the overall inclination direction in the stepped shape. Similarly, when the shape in the first cross section of the first groove side wall 31 is stepped, the first side wall standing direction A1 can be defined. Moreover, when making the shape in the 1st cross section of the 1st groove | channel side wall 31 and the 2nd groove | channel side wall 32 into the curve shape which goes to the top part 34 from the bottom part 33 of the groove-shaped part 30, arc shape is used as the said curve-shaped shape. Things can be adopted. In this case, by setting the center point of the arc to the side away from the friction material 13 that forms the groove side wall with respect to the groove side wall, the arc shape is convex to the friction material 13 side. Alternatively, by setting the center point of the arc to the friction material 13 side that forms the groove side wall with respect to the groove side wall, the arc shape is convex toward the side away from the friction material 13. It may be good. In addition, when the shape in the 1st cross section of the 1st groove | channel side wall 31 or the 2nd groove | channel side wall 32 is curvilinear in this way, the 1st side wall standing up direction A1 and the 2nd side wall standing up direction A2 are the groove-shaped parts 30. It is good also as an average of the tangent direction of the curve in the position set for every predetermined space | interval toward the top from the bottom of this, and the specific position in a groove-like part 30 (a bottom, a top, height is half of the height of a groove side wall. May be defined as the tangential direction of the curve at the position.

(6) In the first and second embodiments described above, both the first displacement portion 41 and the second displacement portion 42 are either in the circumferential direction as they go from the one radial side to the other radial side in the second cross section. The case where it is formed in a curved shape toward one side has been described as an example. However, the embodiment of the present invention is not limited to this, and the shape of the first cross section of the first displacement portion 41 is changed to one side in the circumferential direction from the one side in the radial direction toward the other side in the radial direction. It can be a straight line or a staircase. Similarly, the shape of the second cross section of the second displacement portion 42 can be a linear shape or a stepped shape toward one side in the circumferential direction as it goes from one side in the radial direction to the other side in the radial direction.

(7) In the first and second embodiments, the case where the first standing direction inclination angle θ1 is set to 0 degrees has been described as an example. However, the embodiment of the present invention is not limited to this, and as shown in FIG. 18, the first standing direction inclination angle θ1 is set to an angle larger than 0 degree and smaller than the second standing direction inclination angle θ2. Is also one preferred embodiment of the present invention. By setting it as such a structure, the viscous resistance of the oil in a 1st rotation state can be adjusted.

(8) In the first and second embodiments, the first displacement amount D1 and the second displacement are related to the shapes of the first displacement portion 41 of the first groove sidewall 31 and the second displacement portion 42 of the second groove sidewall 32. The case where the shape of the said part is specified based on quantity D2 was demonstrated as an example. However, the embodiment of the present invention is not limited to this. That is, when the 1st displacement part 41 and the 2nd displacement part 42 are the circular-arc-shaped parts formed in circular arc shape, it is set as the structure which specifies the shape of the said site | part based on the curvature radius R of the said circular-arc-shaped part. be able to. In the example shown in FIG. 19, the first displacement portion 41 formed at the radially outer end of the first groove sidewall 31 is an arc-shaped portion, and the radius of curvature of the arc-shaped portion is represented by R1. Moreover, the 2nd displacement part 42 formed in the edge part of the radial direction outer side of the 2nd groove | channel side wall 32 is an arc-shaped part, and the curvature radius of the said arc-shaped part is represented by R2.
Moreover, when the 1st displacement part 41 and the 2nd displacement part 42 are chamfering parts, it can be set as the structure which specifies the shape of the said site | part based on the length Y of the said chamfering part. In the example shown in FIG. 20, the first displacement portion 41 formed at the radially outer end of the first groove side wall 31 is a chamfered portion, and the length of the chamfered portion is represented by Y1. Moreover, the 2nd displacement part 42 formed in the edge part of the radial direction outer side of the 2nd groove | channel side wall 32 is a chamfering part, The length of the said chamfering part is represented by Y2.
In the second cross section, the first groove side wall 31 is formed in an arc shape on at least one of one end or both ends in the radial direction and one end or both ends in the radial direction of the second groove side wall 32. When the arc-shaped part is provided, the arc-shaped part is provided only on the second groove side wall 32 or the arc-shaped part is provided on both the first groove side wall 31 and the second groove side wall 32. In addition, it is preferable that the radius of curvature R2 of the arc-shaped portion of the second groove side wall 32 is set larger than the radius of curvature R1 of the arc-shaped portion of the first groove side wall 31. Further, in the second cross section, the first groove side wall 31 is linearly formed at one end or both ends in the radial direction and at least one end of the second groove side wall 32 in the radial direction one side or both ends. When the chamfered portion is provided, the chamfered portion is provided only on the second groove side wall 32 or both the first groove side wall 31 and the second groove side wall 32 are provided with chamfered portions. The length Y2 of the chamfered portion of the second groove sidewall 32 is preferably set to be larger than the length Y1 of the chamfered portion of the first groove sidewall 31. In addition, the 1st groove | channel side wall 31 and the 2nd groove | channel side wall 32 can also be set as the structure by which an arc-shaped part is provided in the edge part of the one side in radial direction, and a chamfering part is provided in the edge part of the other side. Alternatively, the first groove side wall 31 may include one of an arc-shaped portion and a chamfered portion, and the second groove side wall 32 may include the other of the arc-shaped portion and the chamfered portion.
In addition, the indices for specifying the shapes of the first displacement portion 41 and the second displacement portion 42 are not limited to these, and for example, the corner portion on the basis of the case where the radial end of the groove side wall is a right angle. The shapes of the first displacement part 41 and the second displacement part 42 can also be specified using the notch amount (removal amount), the notch area (resection area), and the like.

(9) In the first and second embodiments, the inner friction plate 11 is configured by a plurality of segment-like friction materials 13 being fixed to the axial end surface of the core plate 11a along the circumferential direction. The case where the gap between the friction materials 13 adjacent to each other in the circumferential direction forms the groove portion 30 has been described as an example. However, the embodiment of the present invention is not limited to this. For example, the inner friction plate 11 is configured by adhering an annular plate-shaped friction material to the axial end surface of the core plate 11a, and the surface of the friction material is subjected to processing such as press processing or cutting processing. It is one of the preferred embodiments of the present invention to have a configuration in which the groove-like portion 30 is formed.

(10) In the first and second embodiments, the case where the groove-like portion 30 extending in the radial direction is formed on the friction contact surface of the inner friction plate 11 has been described as an example. However, the embodiment of the present invention is not limited to this, and a configuration in which a groove-like portion 30 extending in the radial direction is formed on the friction contact surface of the outer friction plate 12 is also possible. This is one of the preferred embodiments. In the example shown in FIG. 21, the outer friction plate 12 is illustrated as an example in which a plurality of segment-like friction materials 13 are fixed to the axial end surface of the core plate 12 a along the circumferential direction. . In such a configuration, a plurality of friction materials 13 may be fixed to each of both end surfaces of the outer friction plate 12 in the axial direction to form the groove-shaped portion 30, or the inner friction plate 11 in the axial direction may be formed. The groove portion 30 may be formed only on either one side, and the groove portion 30 may be formed only on the same side in the axial direction of the outer friction plate 12.

(11) In the first and second embodiments, the case where the groove-like portion 30 is formed so as to extend along the radial direction has been described as an example. However, the embodiment of the present invention is not limited to this, and the entire groove-shaped portion 30 is directed to one side (for example, the forward direction F side) in the circumferential direction as it goes radially outward. It is one of the preferred embodiments of the present invention to have a formed configuration.

(12) In the first and second embodiments, the first rotating plate that is drivingly connected to the input shaft I has an inner friction plate that is formed with a spline groove on the inner peripheral surface and is held by the input side member 71. 11, the second rotary plate that is drivingly connected to the output shaft O has been described as an example in which the outer friction plate 12 is formed with a spline groove formed on the outer peripheral surface and held by the disc member 52. However, the embodiment of the present invention is not limited to this, and the first rotating plate that is drivingly connected to the input shaft I is an outer friction plate, and the second rotating plate that is drivingly connected to the output shaft O is an inner. Of course, it is also possible to adopt a configuration of a friction plate.

  The present invention is provided in a drive device for a hybrid vehicle having an input member that is drivingly connected to an internal combustion engine and an output member that is drivingly connected to both the rotating electrical machine and the wheels, and is a space to which lubricating coolant is supplied. It can utilize suitably for the wet friction engagement apparatus which operate | moves within.

1: Drive device 1
11: Inner friction plate (first rotating plate)
12: Outer friction plate (second rotating plate)
13: Friction material 30: Groove-shaped part 31: First groove side wall 32: Second groove side wall 33: Bottom part 34: Top part 41: First displacement part 42: Second displacement part A1: First side wall standing direction A2: Second Side wall standing direction C: Starting clutch (friction engagement device)
D1: first displacement amount D2: second displacement amount Dr: total displacement amount in radial direction Dc: total displacement amount in circumferential direction E: engine (internal combustion engine)
F: Forward direction I: Input shaft (input member)
MG: rotating electrical machine O: output shaft (output member)
R: radius of curvature of arcuate portion W: wheel X: rotation axis Y: length of chamfered portion θ1: first standing direction tilt angle θ2: second standing direction tilt angle

Claims (10)

A drive device for a hybrid vehicle having an input member drivingly connected to the internal combustion engine and an output member drivingly connected to both the rotating electric machine and the wheels, and operates in a space to which lubricating coolant is supplied. A wet friction engagement device,
A first rotating plate drivingly connected to the input member; and a second rotating plate drivingly connected to the output member;
The first rotating plate and the second rotating plate are arranged so that their rotational axes coincide with each other, and each has a ring-shaped friction contact surface as a whole. It is oppositely arranged so that it can touch,
The friction contact surface of the first rotary plate and the friction contact surface of the second rotary plate are in contact with each other and can be switched between an engaged state and a separated state in which they are separated,
At least one of the friction contact surface of the first rotating plate and the friction contact surface of the second rotating plate is formed with a groove-like portion extending in the radial direction of the rotating shaft,
The rotation direction of the first rotating plate and the second rotating plate during normal rotation of the output member in the engaged state is defined as a forward direction.
In the separated state, when the second rotating plate rotates relative to the first rotating plate in the forward direction, the resistance that the first rotating plate and the second rotating plate receive from the lubricating coolant is, The groove so that the first rotating plate and the second rotating plate are less than the resistance received from the lubricating coolant when the first rotating plate rotates relative to the second rotating plate in the forward direction. A frictional engagement device in which the shape portion is asymmetrical between the circumferential one side and the other circumferential side of the rotating shaft.   The groove-shaped portion has at least one of a shape of a cross section cut along a cylindrical surface having the rotation axis as an axis and a shape of a cross section cut along a surface orthogonal to the rotation axis. The friction engagement device according to claim 1, wherein the friction engagement device has an asymmetric shape between one circumferential side and the other circumferential side. With respect to the groove sidewalls, which are sidewalls on both sides in the circumferential direction of the groove-shaped portion, the one facing the flow of the lubricating coolant when the first rotating plate rotates relative to the second rotating plate in the forward direction. The groove side wall is defined as a first groove side wall, and the groove side wall that faces the flow of the lubricating coolant when the second rotating plate rotates relative to the first rotating plate in the forward direction is defined as a second groove side wall. Groove side wall,
The first side wall standing direction is a direction from the bottom to the top of the first groove side wall in the first cross section, which is a cross section of the groove-shaped part cut along the cylindrical surface having the rotation axis as a center. The direction from the bottom of the two-groove side wall to the top is defined as the second side wall standing direction, and the first side wall standing direction from the second groove side wall toward the top with respect to the direction perpendicular to the friction contact surface. The angle that inclines in the direction of leaving is the first upright direction inclination angle, and the second side wall is inclined in the direction away from the first groove side wall toward the top with respect to the direction perpendicular to the friction contact surface. The angle is the second standing direction inclination angle,
The friction engagement device according to claim 2, wherein the second standing direction inclination angle is set larger than the first standing direction inclination angle. With respect to the groove sidewalls, which are sidewalls on both sides in the circumferential direction of the groove-shaped portion, the one facing the flow of the lubricating coolant when the first rotating plate rotates relative to the second rotating plate in the forward direction. The groove side wall is defined as a first groove side wall, and the groove side wall that faces the flow of the lubricating coolant when the second rotating plate rotates relative to the first rotating plate in the forward direction is defined as a second groove side wall. Groove side wall,
In a second cross-section that is a cross-section cut along a plane orthogonal to the rotation axis, a circumferential position of the first groove sidewall changes from one radial side to the other radial side of the rotation axis. When there is one displacement portion, the sum of the total displacement amount in the radial direction and the total displacement amount in the circumferential direction of the first displacement portion is the first displacement amount,
In the second cross section, when the second groove side wall has a second displacement portion whose circumferential position changes from the one radial direction side to the other radial direction side of the rotation shaft, The sum of the total displacement in the radial direction and the total displacement in the circumferential direction is the second displacement,
Only the second displacement portion of the first displacement portion and the second displacement portion is formed, or both the first displacement portion and the second displacement portion are formed, and the first displacement portion The friction engagement device according to claim 2 or 3, wherein the two displacement amounts are set larger than the first displacement amount. With respect to the groove sidewalls, which are sidewalls on both sides in the circumferential direction of the groove-shaped portion, the one facing the flow of the lubricating coolant when the first rotating plate rotates relative to the second rotating plate in the forward direction. The groove side wall is defined as a first groove side wall, and the groove side wall that faces the flow of the lubricating coolant when the second rotating plate rotates relative to the first rotating plate in the forward direction is defined as a second groove side wall. Groove side wall,
In the second cross section, which is a cross section cut along a plane orthogonal to the rotation axis, one end or both ends in the radial direction of the first groove side wall and one end or both ends in the radial direction of the second groove side wall An arcuate part formed in an arc shape or a chamfered part formed in a straight line is provided in at least one of the parts,
When the arc-shaped part is provided, the arc-shaped part is provided only on the second groove side wall, or the arc-shaped part is provided on both the first groove side wall and the second groove side wall. And the radius of curvature of the arc-shaped portion of the second groove sidewall is set larger than the radius of curvature of the arc-shaped portion of the first groove sidewall,
When the chamfered portion is provided, the chamfered portion is provided only on the second groove sidewall, or the chamfered portion is provided on both the first groove sidewall and the second groove sidewall. The friction engagement device according to claim 2 or 3, wherein a length of the chamfered portion of the second groove side wall is set to be larger than a length of the chamfered portion of the first groove side wall.   Each of said 1st groove | channel side wall and said 2nd groove | channel side wall is the shape in said 1st cross section, and is formed in the linear form, curved shape, or step shape which goes to the top part from the bottom part of the said groove part. The friction engagement device according to claim 1.   Each of the first displacement part and the second displacement part has a linear shape toward the any one side in the circumferential direction as the shape in the second cross section goes from the one radial direction side of the rotating shaft to the other radial direction side, The friction engagement device according to claim 4, wherein the friction engagement device is formed in a curved shape or a step shape. In the second cross section, which is a cross section cut along a plane orthogonal to the rotation axis, a circle is formed on both ends of the first groove side wall in the radial direction and both ends of the second groove side wall in the radial direction. An arc-shaped portion formed in an arc shape is provided,
The first standing direction inclination angle is set to 0 degrees, and the second standing direction inclination angle is set to an acute angle larger than 0 degrees,
The radius of curvature of the arc-shaped portion formed at both ends in the radial direction of the first groove sidewall matches the radius of curvature of the arc-shaped portion formed at both ends in the radial direction of the second groove sidewall. The friction engagement device according to claim 3. In the second cross section, which is a cross section cut along a plane orthogonal to the rotation axis, a circle is formed on both ends of the first groove side wall in the radial direction and both ends of the second groove side wall in the radial direction. An arc-shaped portion formed in an arc shape is provided,
In the second cross section where at least the axial position coincides with the top of the groove-shaped portion, the radius of curvature of the arc-shaped portion provided at the radially outer end of the second groove sidewall is the second groove sidewall. Is set to be larger than the radius of curvature of the arc-shaped portion provided at the radially inner end portion and the radius of curvature of the arc-shaped portion provided at the end portions on both radial sides of the first groove side wall. The friction engagement device according to claim 5.   The friction material is fixed to at least one of the friction contact surfaces of the first rotating plate and the second rotating plate, and the groove-shaped portion is formed by molding the friction material. The friction engagement device according to any one of claims.

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