JP5434514B2 - Hybrid vehicle drive device - Google Patents

Description

  The present invention relates to a drive device for a hybrid vehicle that includes an engine and an electric motor as drive sources, and transmits the driving force of the engine and the electric motor to an axle.

  2. Description of the Related Art Conventionally, a drive device for a hybrid vehicle including an engine and an electric motor has a clutch mechanism for intermittently connecting an input shaft for engine driving force and an output shaft fixed to the rotor of the electric motor and connected to the axle. Is provided. With such a configuration, the vehicle runs alone with the electric motor, or when the large driving force is required, the engine and the electric motor are used simultaneously as driving sources, and further, the electric motor is caused to generate electric power using the engine rotation. It becomes possible to do.

  For example, the one described in Patent Document 1 is configured such that the clutch mechanism 16 is intermittently connected by a diaphragm-like plate spring 17. In a normal state, the leaf spring 17 formed in a diaphragm shape urges the clutch plate in the engagement direction by the outer peripheral portion to maintain the clutch engagement state so that the engine and the electric motor rotate simultaneously. . When the vehicle is driven by driving only the electric motor, hydraulic oil is supplied to the back surface of the piston, the piston is moved, and extends from the leaf spring 17 to the inner diameter direction of the leaf spring 17 via the bearing and the second bearing. Press the tip of the lever. As a result, the outer peripheral portion of the leaf spring 17 is pushed away from the clutch plate by the lever action point by the action of the lever with the contact point with the fulcrum ring 18 on which the lever is supported as a fulcrum. The clutch is disengaged by releasing.

JP 2006-137406 A

  However, in the technique disclosed in Patent Document 1, the lever that extends from the leaf spring 17 is pressed by a piston to release the clutch, and the leaf spring 17 connected to the lever by the action of the lever of the lever. The outer peripheral part is moved. As a result, the movement distance of the outer peripheral portion of the plate spring 17 and the movement distance of the piston are difficult to be 1: 1, and the movement distance of the piston is longer. For this reason, the space for ensuring the stroke for the moving distance of a piston becomes large, and there exists a subject that a drive device will become large.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a hybrid vehicle drive device that can perform engagement and disengagement of a clutch with a small and simple configuration.

In order to solve the above problems, the invention according to claim 1 is characterized in that an input shaft that is rotatably connected to the engine and an output shaft that is arranged on the same rotational axis as the rotor of the electric motor and are integrally connected. A clutch device that releasably connects the input shaft and the output shaft, and a bearing that rotatably supports the input shaft and the output shaft via a bearing on the rotation axis, and at least the electric motor and the A case that surrounds the clutch device with a side wall portion on the input shaft side, a side wall portion on the output shaft side, and an outer peripheral wall portion, and the clutch device rotates to each large-diameter portion of the input shaft and the output shaft. A plurality of clutch plates that are movably engaged in the direction of the rotation axis, and are mounted on the input shaft so as to be movable in the direction of the rotation axis on the output shaft side. For pressing A pressure member, a coil spring that urges the pressing member toward the input shaft with a spring force to press-contact the plurality of clutch plates, and the large-diameter portion of the input shaft that is provided integrally with the pressing member. Between the operating portion extending in the direction of the rotation axis and extending to the input shaft side, and a cylinder formed on the side wall portion on the input shaft side so as to be movable, and a hydraulic chamber between the cylinder bottom portion A piston that is moved by hydraulic pressure supplied to the hydraulic chamber and moves the operating portion against the spring force via a relative rotation allowing member, and separates the plurality of clutch plates; and the input shaft side And an inflow port that communicates with the hydraulic chamber and supplies the hydraulic pressure .

In order to solve the above problem, the invention according to claim 2 is characterized in that an input shaft that is rotatably connected to the engine and an output shaft that is arranged on the same rotational axis as the rotor of the electric motor and are integrally connected. A clutch device that releasably connects the input shaft and the output shaft, and a bearing that rotatably supports the input shaft and the output shaft via a bearing on the rotation axis, and at least the electric motor and the A case that surrounds the clutch device with a side wall portion on the input shaft side, a side wall portion on the output shaft side, and an outer peripheral wall portion, and the clutch device rotates to each large-diameter portion of the input shaft and the output shaft. A plurality of clutch plates that are movably engaged in the direction of the rotation axis, and are mounted on the output shaft so as to be movable in the direction of the rotation axis on the input shaft side. For pressing A pressure member; a coil spring that urges the pressing member toward the output shaft side with a spring force to press-contact the plurality of clutch plates; and the large-diameter portion of the output shaft that is provided integrally with the pressing member. Between the operating portion extending in the direction of the rotation axis and extending to the output shaft side, and a cylinder formed on the side wall portion on the output shaft side, and is movably fitted, and a hydraulic chamber is provided between the cylinder bottom portion. A piston that is moved by hydraulic pressure supplied to the hydraulic chamber and moves the operating portion against the spring force through a relative rotation allowing member, and separates the plurality of clutch plates; and the output shaft side And an inflow port that communicates with the hydraulic chamber and supplies the hydraulic pressure .

  In order to solve the above-described problem, the invention according to claim 3 is characterized in that, in claim 1 or 2, the invention is fixed to the operating portion and extends toward the rotation axis, and the piston allows the relative rotation permission member to pass through. The contact member that is pushed in this way is provided.

  In order to solve the above-described problem, the invention according to claim 4 is characterized in that, in any one of claims 1 to 3, the pressing member is formed in an annular shape, and the operating portion is an inner peripheral portion of the pressing member. A plurality of projections in the direction of the rotation axis.

  According to the first aspect of the present invention, the clutch plate is urged by the coil spring having a linear deflection-load characteristic. Therefore, the movement amount of the piston can be moved in a proportional relationship with respect to the deflection amount of the coil spring. The clutch engagement can be released by efficiently reducing the biasing force of the coil spring. As a result, the space for moving the piston can be reduced, and the drive device can be reduced in size.

  Further, since the coil spring has a linear deflection-load characteristic, the engagement state of the clutch can be controlled relatively easily by controlling the movement amount of the piston. Thus, by controlling the hydraulic pressure supplied to the hydraulic chamber formed between the piston and the cylinder bottom, it is possible to easily obtain a half-clutch state with less impact during connection / disconnection.

  According to the second aspect of the present invention, the clutch plate is biased by the coil spring having a linear deflection-load characteristic. Therefore, the movement amount of the piston can be moved in proportion to the deflection amount of the coil spring. The clutch engagement can be released by efficiently reducing the biasing force of the coil spring. As a result, the space for moving the piston can be reduced, and the drive device can be reduced in size.

  Further, since the coil spring has a linear deflection-load characteristic, the engagement state of the clutch can be controlled relatively easily by controlling the movement amount of the piston. Thus, by controlling the hydraulic pressure supplied to the hydraulic chamber formed between the piston and the cylinder bottom, it is possible to easily obtain a half-clutch state with less impact during connection / disconnection.

  According to the third aspect of the present invention, the rotational peripheral speed of the contact member at the position where the piston and the contact member are in contact with each other via the relative rotation allowing member is greater than the rotational peripheral speed of the operating portion having a large diameter. small. As a result, the relative circumferential speed of the abutting member with respect to the piston provided on the side wall portion of the non-rotating case can be made smaller than when the piston abuts on the operating portion, so that the sliding resistance is reduced and the reliability is improved. Can be made.

  According to the invention according to claim 4, since the operating portion of the pressing member is divided into a plurality of parts and passes through the large diameter portion of the input shaft or the output shaft from the inner peripheral portion of the pressing member, and protrudes in the rotational axis direction. The space on the input shaft side and the output shaft side can be used efficiently at the same time, which can contribute to downsizing of the drive device. Moreover, since the operation part is divided into a plurality of protrusions, the weight can be reduced.

It is the schematic which shows the drive system for hybrid vehicles in this embodiment. It is sectional drawing containing the drive device for hybrid vehicles of this embodiment. It is sectional drawing of the drive device for hybrid vehicles of 1st Embodiment which concerns on this invention. It is a schematic diagram of the hybrid vehicle drive device of Modification 1 of the first embodiment. It is a schematic diagram of the hybrid vehicle drive device of the second embodiment according to the present invention. It is a schematic diagram of the hybrid vehicle drive device of Modification 2 of the second embodiment.

  A first embodiment of the present invention is embodied in a hybrid vehicle and will be described below with reference to the drawings. FIG. 1 schematically shows a hybrid vehicle drive system to which a hybrid vehicle drive device 1 according to the present invention is applied. In FIG. 1, solid arrows indicate hydraulic piping connecting the devices, and broken arrows indicate control signal lines. In the present embodiment, the engine side of the hybrid vehicle drive device is the front side, and the transmission side is the rear side.

  As shown in FIG. 1, the vehicle engine 10 and the electric motor 20 are connected in series via a clutch device 40. The clutch device 40 connects and disconnects the connection between the engine 10 and the electric motor 20 to interrupt torque transmission. The electric motor 20 is connected with an automatic transmission device 5 of the vehicle in series, and the automatic transmission device 5 is connected with driving wheels of a vehicle (not shown). The automatic transmission (A / T) 5 includes a transmission and the torque converter 2 shown in FIG. 2, and the output of the torque converter 2 is input to the input shaft 31 of the transmission.

  As shown in FIG. 2, the electric motor 20 and the torque converter 2 are rotationally coupled via an output shaft 26 and a center piece 16 that is an input shaft of the torque converter 2. The center piece 16 that is the input shaft of the torque converter 2 is arranged side by side on the same rotational axis as the input shaft 41, is connected to the front cover 14 of the torque converter 2, and is rotated integrally with the front cover 14. When the front cover 14 is rotated together with the center piece 16, a pump impeller (not shown) in the torque converter 2 connected to the front cover 14 is rotated. As a result, an oil flow is generated by the pump impeller, and a turbine runner (not shown) connected to the input shaft 31 is rotated by the generated oil flow to transmit the rotational force to the input shaft 31. The output shaft 26, the center piece 16, and the front cover 14 are disposed on the same rotational axis as the input shaft 31.

  The engine 10 is a normal internal combustion engine that generates an output from a hydrocarbon-based fuel. Although the electric motor 20 is not limited to this, it is a synchronous motor for driving a wheel, and the automatic transmission 5 is a normal planetary gear type automatic transmission. The clutch device 40 is a normally closed type clutch mechanism that normally connects the engine 10 and the electric motor 20.

  An electromagnetic valve 50 is connected to the clutch device 40. The electromagnetic valve 50 has a pressure reducing valve and a passage to the reservoir, and switches between them appropriately. A discharge port of the electric oil pump 60 is connected to the electromagnetic valve 50. When the solenoid valve 50 is used on the pressure reducing valve side, the hydraulic pressure generated by the electric oil pump 60 is regulated by the pressure reducing valve and then supplied to the clutch device 40. When the hydraulic pressure is released, the solenoid valve 50 is switched to the reservoir passage side to discharge the hydraulic oil.

  A controller 70 is electrically connected to the electromagnetic valve 50 and the electric oil pump 60. The controller 70 operates the electric oil pump 60 and the electromagnetic valve 50 to supply an appropriate hydraulic pressure to the clutch device 40 to control the clutch device 40 to a target connection state.

  The controller 70 controls the rotation of the engine 10 or the electric motor 20 to drive the vehicle. Further, the controller 70 is connected to an electromagnetic solenoid (not shown) that operates the shift valve of the automatic transmission 5, and the operation of the automatic transmission 5 is performed based on the rotational speed of the engine 10, the vehicle speed, the shift position, and the like. Is controlling.

  Next, the hybrid vehicle drive device 1 according to the present invention will be described in detail with reference to FIGS. The hybrid vehicle drive device 1 includes an input shaft 41 that is rotatably connected to the engine 10, and an output shaft 26 that is disposed on the same rotational axis as the rotor 21 of the electric motor 20 and is integrally connected thereto. doing. The hybrid vehicle drive device 1 includes a clutch device 40 that detachably connects the input shaft 41 and the output shaft 26, and a case 3 that surrounds the electric motor 20 and the clutch device 40.

  The case 3 includes an outer peripheral wall portion 3c that forms an outer shape, a rear side wall portion 3a between the electric motor 20, the clutch device 40, and the torque converter 2, and a front side wall portion 3b described later. Further, the case 3 has an outer peripheral wall portion 3 c that extends a predetermined amount from the rear side wall portion 3 a toward the automatic transmission device 5, and covers a part of the torque converter 2. The extended case 3 is fixed to the case 4 covering the remaining portion of the torque converter 2 by bolts. Further, the case 4 is fixed to a transmission case (not shown) to form a case (not shown) of the automatic transmission 5.

  A front case 6 that forms a lid of the case 3 is disposed on the engine 10 side of the case 3, and the case 3 and the front case 6 are fixed by bolts. A through hole 6 a is provided at the center of the front side wall 3 b of the front case 6 constituting the case 3 so that the input shaft 41 is supported. A ball bearing 34 is interposed between the through hole 6a and the input shaft 41, and the input shaft 41 is rotatably supported.

  As shown in FIG. 2, the input shaft 41 is rotationally connected to the output shaft 11 of the engine 10 via the flywheel 12 and a damper 68 for absorbing rotational vibration. As shown in FIGS. 2 and 3, the input shaft 41 has a fixed portion 41a for the damper 68, a connecting portion 41b rotatably supported by the through hole 6a of the front side wall portion 3b of the front case 6, and a support having a large diameter portion. It has the part 41c and the engaging part 41d which mounts the press member 44 mentioned later. Hereinafter, the side of the front side wall portion 3b on which the input shaft 41 is supported is referred to as the input shaft side. The outer peripheral side of the support portion 41c is widened in the direction of the rotation axis, and the clutch plates 42 on the plurality of rings described above are engaged.

  The output shaft 26 is rotationally connected to the center piece 16 that is an input shaft of the torque converter 2. The center piece 16 is rotatably supported in a through hole 3d formed in the rear side wall portion 3a of the case 3. Hereinafter, the side of the rear side wall portion 3a on which the center piece 16 connected to the output shaft 26 is supported is referred to as an output shaft side.

  The output shaft 26 has an inverted S-shaped cross section in the direction of the rotation axis shown in FIG. 2, an outer peripheral opening 27 opened on the engine 10 side is formed on the large diameter side, and an opening on the transmission 5 side is formed on the small diameter side. The inner peripheral opening 32 is formed. The outer peripheral opening portion 27 is surrounded and formed by a small-diameter side wall portion 27d, a large-diameter side wall portion 27c, and stepped bottom wall portions 27e and 27f. The aforementioned plurality of annular clutch plates 43 are engaged with the inner peripheral surface of the distal end portion of the large-diameter side wall portion 27c. The plurality of clutch plates 42 supported by the support portion 41c, which is the large diameter portion of the input shaft 41, and the plurality of clutch plates 43 supported by the large diameter side wall portion 27c of the output shaft 26 are alternately fitted. Yes. When the clutch plate 42 and the clutch plate 43 are pressed in the rotational axis direction, the clutch plate 42 and the clutch plate 43 are pressed and engaged with each other, whereby the input shaft 41 and the output shaft 26 are connected. Are coupled together, and the output shaft 11 of the engine 10 and the input shaft 31 of the automatic transmission 5 are integrally rotated.

  The inner peripheral opening 32 formed on the small diameter side of the output shaft 26 includes a fixed portion 32b that is spline-coupled with the center piece 16 that is an input shaft of the torque converter 2 so as to be integrally rotatable, and an input shaft side of the fixed portion 32b. It consists of the connection part 32a extended toward radial direction outward from an edge part. An annular protrusion 63 projects from the rear side wall 3a of the case 3 in a space surrounded by the inner peripheral opening 32 and the small-diameter side wall 27d of the outer peripheral opening 27 and opened to the automatic transmission 5 side. Has been. The small-diameter side wall portion 27d of the outer peripheral opening 27 is fitted to the outer peripheral surface 63b of the protrusion 63, and a ball bearing 64 is interposed between the fixed portion 32b of the inner peripheral opening 32 and the inner peripheral surface 63a of the protrusion 63. The protrusion 63 and the inner peripheral opening 32 can smoothly rotate relative to each other.

  Next, the clutch device 40 will be described with reference to FIGS. The clutch device 40 is engaged with a clutch plate 42 whose relative rotation is restricted to the input shaft 41 and slidable in the axial direction, and to the output shaft 26 whose relative rotation is restricted and slidable in the axial direction. The clutch plate 43, a pressing member 44 for pressing the plurality of clutch plates 42, 43, and a coil spring 45 that presses the plurality of clutch plates 42, 43 by urging the pressing member 44 toward the input shaft with a spring force. And a cylinder 48 formed on the front side wall 3b on the input shaft side, and a piston 46 movably fitted to the cylinder 48.

  The pressing member 44 is fitted and mounted on the output shaft side such that the relative rotation is restricted by the engaging portion 41d of the input shaft 41 so as to be movable in the rotation axis direction. The pressing member 44 is formed in an annular shape, and an outer peripheral portion of the annular ring extends to the input shaft side to form a pressing portion 44 a that presses the clutch plate 42 and the clutch plate 43. In addition, three operating portions 47 are arranged in a protruding manner in the circumferential direction from the inner peripheral portion of the ring toward the input shaft side in the rotational axis direction. The operating portion 47 is provided integrally with the pressing member 44 and passes through a support portion 41c which is a large-diameter portion of the input shaft 41 in the rotation axis direction and extends to the input shaft side.

  In the present embodiment, the three operating portions 47 are projected from the inner peripheral portion of the pressing member 44 at equal intervals. However, the number of the operating portions 47 may be two or more. May be arranged on the inner periphery of the pressing member 44.

  A contact member 52 is fixed to the inner peripheral surface of the distal end portion 47 a of the operating portion 47. The contact member 52 is formed in a disc shape, and an outer peripheral portion thereof is fitted to a step portion provided on the inner peripheral surface of the distal end portion 47 a of the operating portion 47. The contact member 52 is prevented from coming off to the input shaft side by a general C-ring fitted in a groove 47b provided in the step portion. The side surface on the input shaft side in the inner peripheral portion of the abutting member 52 is abutted and pressed through a piston 46 and an annular relative rotation allowing member 51 having good sliding property formed of resin such as PA. A contact portion 52a is formed for this purpose.

  As shown in FIGS. 2 and 3, the coil spring 45 is contracted between the pressing member 44 and the stop member 53. The stop member 53 is an annular member fixed to the outer periphery of the engaging portion 41 d of the input shaft 41. In the present embodiment, 10 coil springs 45 are arranged at equal intervals on the same radius of the rotation shaft of the pressing member 44, urge the pressing members 44 toward the input shaft, and the clutch plate 42 via the contact portion 52a. The clutch plate 43 is pressed and pressed with a predetermined load. A cylindrical hole having a diameter slightly larger than the outer diameter of the coil spring 45 is formed on the side surface on the output shaft side of the pressing member 44 where the coil spring 45 is disposed so that each of the ten coil springs 45 is disposed. Each coil spring 45 is engaged with the cylindrical hole. In the present embodiment, ten coil springs 45 are arranged. However, the present invention is not limited to this, and a predetermined urging force capable of pressing and engaging the clutch plate 42 and the clutch plate 43 can be applied, and the pressing portion 44a causes the clutch plate 42 and the clutch plate 43 to contact the entire contact portion 52a. What is necessary is just to arrange | position a some coil spring so that it can press uniformly over.

  The cylinder 48 is formed on the front side wall 3b. The cylinder 48 is surrounded by a large-diameter wall 54 formed in an annular shape around the rotation axis of the input shaft 41, an annular small-diameter wall 55 formed on the inner peripheral side of the large-diameter wall 54, and the front side wall portion 3b. It is formed by the created space.

  The piston 46 is formed in an annular shape, and is movably fitted between the inner peripheral surface 54 a of the large-diameter wall 54 of the cylinder 48 and the outer peripheral surface 55 a of the small-diameter wall 55, and between the cylinder bottom 48 a of the cylinder 48. A hydraulic chamber 49 is formed in the front. A groove 46c is formed on the outer circumferential surface 46a of the piston 46 over the entire circumference. For example, a rubber O-ring is disposed in the groove 46 c, and the hydraulic chamber 49 is liquid-tightly sealed on the outer periphery of the piston 46. A groove 46d is also formed on the inner peripheral surface 46b of the piston 46 over the entire circumference. A rubber O-ring, for example, is also provided in the groove 46d, and the hydraulic chamber 49 is liquid-tightly sealed on the inner periphery of the piston 46. Further, the piston 46 is provided with a contact portion 52 a of the contact member 52 and a protrusion 46 e that contacts with the relative rotation allowing member 51.

  The relative rotation permission member 51 absorbs a rotational difference between the contact member 52 of the pressing member 44 that rotates integrally with the input shaft 41 and the piston 46 that does not rotate, and allows the contact member 52 to rotate smoothly. It is. In this embodiment, it is formed of a resin such as PA. However, it may be formed of any material as long as it has good slidability and satisfies a predetermined durability, and may be configured by interposing a bearing or the like. .

  The hydraulic chamber 49 has an inflow port (inlet) 61 that communicates with the electric oil pump 60 and the reservoir 72 via the electromagnetic valve 50, and the inflow port 61 penetrates the front side wall portion 3b. The electric oil pump 60 and the reservoir 72 are switched by operating the electromagnetic valve 50, and by switching to the reservoir 72, the hydraulic chamber 49 is configured to communicate with the atmosphere via the inflow port 61.

  Next, the electric motor 20 will be described. The electric motor 20 composed of a brushless DC motor or the like is disposed on the outer peripheral side of the outer peripheral opening 27 of the output shaft 26. The electric motor 20 includes a cylindrical rotor 21, a stator 22 that is disposed on the outer periphery of the rotor 21 and is formed by stacking silicon steel plates (not shown), and a coil 23 that is wound around a protruding portion of the stator 22. I have.

  The outer side of the stator 22 is fixed to the inner peripheral surface of the outer peripheral wall 3 c of the case 3. The rotor 21 has a plate member 24 extending radially inward from the output shaft side end surface, and is fixed to the output shaft side surface of the bottom wall portion 27e of the output shaft 26 by bolts. Thereby, only the rotor 21 of the electric motor 20 is rotated integrally with the output shaft 26. Further, the coil 23 is electrically connected to the controller 70, and the controller 70 is based on signals from sensors (vehicle speed sensor, throttle opening sensor, shift position sensor, etc.) that are not shown for detecting various states. The energization amount to the coil 23 or the non-energization of the coil 23 is controlled.

  Next, the operation of the above-described hybrid vehicle drive device 1 will be described. Now, when the vehicle is stopped, when an unillustrated ignition switch is turned on and the driver steps on the accelerator pedal (at the time of low throttle opening), a current flows from the battery (not shown) to the electric motor 20. The electric motor 20 functions as a drive motor. The rotational driving force is transmitted to the torque converter 2 via the output shaft 26, and is increased by a predetermined torque ratio by the torque converter 2 and then transmitted to the input shaft 31.

  When the vehicle starts, the fuel injection device of the engine 10 does not operate and the engine 10 is in a stopped state. The vehicle starts by only the driving force from the electric motor 20. At this time, the clutch device 40 is disengaged, and the flywheel 12 and the like serving as a load are disconnected. Further, even in a region where engine efficiency is poor, such as when the engine is under low load or under extremely low load, the engine 10 is stopped and travels only by the electric motor 20, and the clutch device 40 is disengaged.

  Further, even when the vehicle is immediately after starting and the speed is relatively low, the engine 10 is started when accelerating or climbing. That is, when the accelerator pedal is depressed to accelerate or climb up and the throttle is opened more than a certain degree of opening, the fuel injection device is activated and the spark plug is ignited and fixed to the case 3 (see FIG. (Not shown) is driven. Then, a ring gear (not shown) on the outer periphery of the flywheel 12 that meshes with the output shaft of the starter motor is rotated together with the flywheel 12 and the output shaft 11 to start the engine 10. At this time, when the clutch device 40 is engaged, the rotational driving force of the input shaft 41 is transmitted to the input shaft 31 of the automatic transmission 5 via the output shaft 26. As a result, the driving forces of both the engine 10 and the electric motor 20 are added and the vehicle is driven with a large driving force. When the vehicle is in a steady high-speed traveling state, the electric motor 20 is operated without load (the motor output is controlled so as to cancel the torque generated by the counter electromotive force generated in the motor), and the electric motor 20 is idled. Let Thus, the vehicle travels solely by the driving force of the engine 10 while the clutch device 40 remains engaged.

  Next, the operation of the clutch device 40 in each operation state of the hybrid vehicle drive device 1 described above will be described. First, a description will be given of the traveling of only the electric motor 20 selected as the traveling mode when the vehicle starts, when the engine is in a low load state due to traffic congestion, or when the vehicle is traveling in a region where the engine efficiency is extremely low.

  When traveling only by the electric motor 20, as described above, the electric motor 20 needs an extra driving force for driving the flywheel 12 and the output shaft 11 of the engine 10 with the clutch device 40 engaged. . For this reason, the clutch device 40 is disengaged and only the electric motor 20 is driven so that an operation with high energy efficiency can be performed.

  Therefore, in order to disengage the plurality of clutch plates 42 and 43 of the normally closed clutch device 40 engaged in the normal state, first, the reservoir 72 connected to the hydraulic chamber 49 by driving the electromagnetic valve 50 is provided. Switch to electric oil pump 60. Then, the electric oil pump 60 is driven, and the controller 70 supplies a hydraulic pressure of a predetermined pressure into the hydraulic chamber 49 via the electromagnetic valve 50 and the inflow port 61. The hydraulic pressure supplied to the hydraulic chamber 49 starts to move the piston 46 toward the output shaft side. Eventually, the protrusion 46 e of the piston 46 comes into contact with the contact portion 52 a of the contact member 52 fixed to the operating portion 47 of the pressing member 44 via the relative rotation allowing member 51. Then, the piston 46 pushes the pressing member 44 urged toward the input shaft side by the coil spring 45 against the spring force of the coil spring 45 toward the output shaft side. When the pressure in the hydraulic chamber 49 further rises, the pressing member 44 further moves toward the output shaft side against the spring force of the coil spring 45, and eventually the clutch member 42 and the clutch plate 43 of the clutch device 40 move the pressing member 44. The pressing portion 44a is separated and the engagement between the clutch plate 42 and the clutch plate 43 is released. At this time, the coil spring 45 that presses the pressing member 44 in the direction in which the clutch device 40 is engaged has a linear deflection-load characteristic. Therefore, the spring force is efficiently applied in proportion to the amount of movement of the piston 46. Therefore, the piston 46 can be disengaged from the clutch device 40 with a short moving distance. When the clutch device 40 is disengaged, the input shaft 41 and the output shaft 26 are disconnected, and the vehicle is driven by driving only the electric motor 20.

  Next, the case where the vehicle is accelerated from the low load operation state and the driving force of the engine 10 is added to the driving force of the electric motor 20 will be described. At this time, it is necessary to engage the clutch device 40 and connect the input shaft 31 and the output shaft 26 again. Therefore, the electric oil pump 60 that drives the electromagnetic valve 50 and is connected to the hydraulic chamber 49 is switched to the reservoir 72. As a result, the pressure in the hydraulic chamber 49 decreases to atmospheric pressure, and the urging force of the coil spring 45 becomes larger than the force that the piston 46 pushes toward the output shaft. Then, the coil spring 45 pushes the piston 46 through the pressing member 44, the operating portion 47, the abutting member 52, and the relative rotation allowing member 51 to bring the clutch device 40 into an engaged state. As a result, the input shaft 41 and the output shaft 26 are connected, the driving forces of both the engine 10 and the electric motor 20 are added, and the vehicle travels with a large driving force.

  As is apparent from the above description, in the first embodiment, the clutch plates 42 and 43 are biased by the coil spring 45 having a linear deflection-load characteristic. The movement amount of the piston 46 can be moved in a proportional relationship, and the urging force of the coil spring 45 can be efficiently reduced to release the clutch engagement. As a result, the space for moving the piston 46 can be reduced, and the size of the hybrid vehicle drive device 1 can be reduced.

  Further, since the coil spring 45 has a linear deflection-load characteristic, the engagement state of the clutch device 40 can be controlled relatively easily by controlling the movement amount of the piston 46 by hydraulic pressure. Thus, by controlling the hydraulic pressure supplied to the hydraulic chamber 49 formed between the piston 46 and the cylinder bottom 48, it is possible to easily obtain a half-clutch state with less impact during connection / disconnection.

  In the first embodiment, the rotational peripheral speed of the contact member 52 at the position where the piston 46 and the contact member 52 are in contact with each other via the relative rotation allowing member 51 is the same as that of the operating portion 47 having a large diameter. It is smaller than the rotational peripheral speed. As a result, the relative peripheral speed of the contact member 52 with respect to the piston 46 provided on the front side wall portion 3b of the case 3 that does not rotate can be made smaller than when the piston 46 contacts with the operating portion 47, so that the sliding resistance is reduced. It becomes small and can improve reliability.

  Furthermore, in the first embodiment, the operating portion 47 of the pressing member 44 passes through the large diameter portion of the input shaft 41 from the inner peripheral portion of the pressing member 44 and protrudes toward the input shaft in the rotational axis direction. Therefore, the space on the input shaft side and the output shaft side can be utilized efficiently at the same time, and the drive device 1 can be reduced in size. Moreover, since the operation part 47 is divided into three parts and protruded, the weight can be reduced.

  In addition, it is good also as a structure shown in the schematic diagram of FIG. 4 as the modification 1 of the said 1st Embodiment. In the first modification shown in FIG. 4, the arrangement of the input shaft 41 and the output shaft 26 that are engaged with the clutch plates 42 and 43 in the first embodiment is changed. That is, the clutch plate 42 is engaged with the output shaft, and the clutch plate 43 is engaged with the input shaft.

  As shown in FIG. 4, the clutch device 110 of the hybrid vehicle drive device 1 of Modification 1 includes a plurality of clutch plates 43 that are engaged with the input shaft 111 so as to be relatively slidable in the axial direction with relative rotation restricted. The output shaft 112 has a plurality of clutch plates 42 whose relative rotation is restricted and slidably engaged in the axial direction, and a pressing member 114 for pressing the plurality of clutch plates 42 and 43. The clutch device 110 includes a coil spring 115 that presses the pressing member 114 toward the input shaft side with a spring force to press-contact the plurality of clutch plates 42 and 43, and a cylinder 118 formed on the front side wall portion 3b on the input shaft side. And a piston 116 movably fitted to the cylinder 118, a hydraulic chamber 119, and a relative rotation allowing member 101 interposed between the piston 116 and the contact member 102. The rotor 21 of the electric motor 20 is integrally connected to the output shaft 112 by a plate member 29 and is disposed on the same rotation shaft.

  In the above configuration, the pressing member 114 is mounted on the outer peripheral surface of the engaging portion 111d of the input shaft 111 on the output shaft side so that the relative rotation is restricted so as to be movable in the rotation axis direction. Further, the pressing member 114 is formed in an annular shape, and the inner peripheral portion of the annular ring extends toward the input shaft side to form a pressing portion 114 a that presses the clutch plate 42 and the clutch plate 43. Three operating portions 117 are integrally provided on the pressing member 114 from the outer peripheral portion of the pressing member 114, and the support portion 111 c that is the large-diameter portion of the input shaft 111 is disposed on the outer peripheral side of the input shaft 111 in the rotation axis direction. It passes and extends to the input shaft side. An annular contact member 102 is fixed to the inner peripheral surface of the distal end portion of the operating portion 117. The abutting portion 102a provided on the inner peripheral portion of the abutting member 102 is pushed and abutted against the protrusion 116e via the relative rotation allowing member 101 by the movement of the piston 116 toward the output shaft. The engagement between the plate 42 and the clutch plate 43 is released. Other configurations are the same as those of the first embodiment, and the same effect as that of the first embodiment can be obtained also in the modified example 1 configured as described above.

  Next, a second embodiment will be described based on the schematic diagram shown in FIG. 2nd Embodiment changes the arrangement position of a cylinder and a piston with respect to the modification 1 of 1st Embodiment. In other words, the cylinder 88 is not provided on the front side wall portion 3b of the case 3, but is arranged on the rear side wall portion 3a of the case 3. Further, the pressing member 84 is mounted on the output shaft 82 instead of the input shaft 81. In addition, description is abbreviate | omitted about the part similar to 1st Embodiment, and only a changed part is demonstrated.

  As shown in FIG. 5, the clutch device 80 of the hybrid vehicle drive device 7 according to the second embodiment is controlled to rotate relative to the input shaft 81 in the axial direction, similarly to the first modification of the first embodiment. The clutch plate 43 is slidably engaged with the output shaft 82, and the clutch plate 42 is engaged with the output shaft 82, the relative rotation of which is restricted relative to the output shaft 82 and slidable in the axial direction. The clutch device 80 includes a pressing member 84 for pressing the plurality of clutch plates 42 and 43, and a coil spring that presses the plurality of clutch plates 42 and 43 by urging the pressing member 84 toward the output shaft with a spring force. 85, a cylinder 88 formed on the rear side wall 3 a on the output shaft side, and a piston 86 movably fitted to the cylinder 88.

  The pressing member 84 is mounted on the input shaft 81 side so as to be fitted to the engaging portion 82d of the output shaft 82 so as to be movable in the rotational axis direction. The pressing member 84 is formed in an annular shape, and an outer peripheral portion of the annular ring extends to the output shaft side to form a pressing portion 84 a that presses the clutch plate 42 and the clutch plate 43. In addition, three operating portions 87 project from the inner peripheral portion of the ring toward the output shaft side in the rotation axis direction, and are evenly arranged in the circumferential direction. The operating portion 87 is provided integrally with the pressing member 84 and passes through a support portion 82c that is a large-diameter portion of the output shaft 82 in the rotational axis direction and passes through the output shaft side. A contact member 92 is fixed to the inner peripheral surface of the distal end portion 87 a of the operating portion 87. On the side surface of the contact member 92 on the output shaft side, a contact portion 92 a for contacting and pressing through the piston 86 and the relative rotation allowing member 91 is formed.

  As shown in FIG. 5, the coil spring 85 is contracted between the pressing member 84 and the stop member 93. Ten coil springs 85 are arranged at equal intervals on the same radius of the rotation shaft of the pressing member 84 and bias the pressing member 84 to the output shaft side, and the clutch plate 42 and the clutch plate 43 are loaded with a predetermined load. Press and press contact.

  As described above, the cylinder 88 is formed on the rear side wall portion 3a on the output shaft side. The cylinder 88 is formed by a space surrounded by a large-diameter wall 94 formed around the rotation axis, a small-diameter wall 95 formed on the inner peripheral side of the large-diameter wall 94, and the rear side wall portion 3a.

  The piston 86 is formed in an annular shape, and is movable between the inner peripheral surface 94a of the large-diameter wall 94 of the cylinder 88 and the outer peripheral surface 95a of the small-diameter wall 95, and the outer periphery and the inner periphery are fitted in a liquid-tight manner. A hydraulic chamber 89 is formed between the cylinder 88 and the cylinder bottom 88a. The hydraulic chamber 89 is supplied with hydraulic pressure from the electric oil pump 60 through the inflow port 100 penetrating the rear side wall 3a, and moves the piston 86 to the input shaft side.

  Further, the piston 86 is provided with a contact portion 92 a of the contact member 92 and a protrusion 86 e that contacts with the relative rotation allowing member 91.

  The relative rotation allowing member 91 absorbs a rotational difference between the abutting member 92 fixed to the pressing member 84 that rotates integrally with the output shaft 82 and the non-rotating piston 86, and can smoothly rotate the abutting member 92. It is a member. The rotor 21 of the electric motor 20 is integrally connected to the output shaft 82 by a plate member 28 and is disposed on the same rotation shaft.

  The abutting portion 92a provided on the abutting member 92 with the above-described configuration is abutted against and pushed by the protrusion 86e via the relative rotation allowing member 91 by the movement of the piston 86 toward the input shaft. And the engagement of the clutch plate 43 is released.

  In this way, the operating portion 87 of the pressing member 84 mounted on the output shaft 82 passes through the support portion 82c which is the large diameter portion of the output shaft 82 from the inner peripheral portion of the pressing member 84 and passes in the direction of the rotation axis. Thus, the space on the input shaft side and the output shaft side can be utilized efficiently at the same time, and the drive device 7 can be reduced in size. Moreover, since the operation part 87 is divided into three parts and protruded, the weight can be reduced. With the above configuration, the same effects as those of the first embodiment can be obtained.

  In addition, it is good also as a structure shown in the schematic diagram of FIG. 6 as the modification 2 of the said 2nd Embodiment. In Modification 2 shown in FIG. 6, the arrangement of the input shaft 81 and the output shaft 82 engaged with the clutch plates 42 and 43 in the second embodiment is changed. That is, as in the first embodiment, the clutch plate 42 is engaged with the input shaft, and the clutch plate 43 is engaged with the output shaft.

  As shown in FIG. 6, the clutch device 120 of the hybrid vehicle drive device 9 of Modification 2 includes a plurality of clutch plates 42 whose relative rotation is restricted by the input shaft 121 and slidably engaged in the axial direction. A plurality of clutch plates 43 that are controlled to rotate relative to the output shaft 122 and are slidable in the axial direction, a pressing member 124 for pressing the plurality of clutch plates 42, 43, and a protrusion projecting from the pressing member 124 And an actuating portion 127 to be operated. In addition, the clutch device 120 includes a contact member 132 fixed to the operating portion 127, a coil spring 125 that presses the plurality of clutch plates 42 and 43 by urging the pressing member 124 toward the output shaft with a spring force, and an output. A cylinder 128 formed on the rear side wall 3a on the shaft side, a piston 126 movably fitted to the cylinder 128, a hydraulic chamber 129, and a relative interposed between the piston 126 and the contact member 132. A rotation allowing member 131. Further, the rotor 21 of the electric motor 20 is integrally connected to the output shaft 122 by the plate member 33 and disposed on the same rotation shaft.

  In the above configuration, the pressing member 124 is mounted on the outer peripheral surface of the engaging portion 122d of the output shaft 122 on the input shaft side so as to be fitted so as to be able to move in the direction of the rotation axis with relative rotation restricted. Further, the pressing member 124 is formed in an annular shape, and an inner peripheral portion of the annular ring extends to the output shaft side to form a pressing portion 124 a that presses the clutch plate 42 and the clutch plate 43. Three operating portions 127 are integrally provided on the pressing member 124 from the outer peripheral portion of the pressing member 124, and the support portion 122 c that is the large diameter portion of the output shaft 122 is disposed on the outer peripheral side of the output shaft 122 in the rotation axis direction. It passes and extends to the output shaft side. An annular contact member 132 is fixed to the inner peripheral surface of the distal end portion of the operating portion 127. The abutting portion 132a provided on the inner peripheral portion of the abutting member 132 is abutted against the protruding portion 126e via the relative rotation allowing member 131 by the movement of the piston 126 toward the input shaft, and is pushed. The engagement between the plate 42 and the clutch plate 43 is released. Other configurations are the same as those of the second embodiment, and the same effects as those of the first embodiment and the second embodiment can be obtained also in the modified example 2 configured as described above.

  The present invention is not intended to be limited to the above-described embodiment. For example, the flywheel 12 and the input shaft 41 are directly connected without providing the damper 68 between the flywheel 12 and the input shaft 41. It may be in the form of

  The transmission according to the present invention is not only a planetary gear transmission that is generally used as a transmission, but also a continuously meshed transmission or a synchronous mesh gear transmission that is generally employed in a manual transmission. Also good.

  The hybrid vehicle driving apparatus 1 is not limited to the above-described use mode, and the engine 10 is started when the vehicle starts, and the engine driving force assists the driving force of the electric motor 20 to start. Of course, the clutch device 40 may be engaged and disengaged according to the driving situation after the vehicle starts.

  In addition, the present invention is not limited to a hybrid vehicle, and may include two drive sources, and one drive source may be applied to the engine in the present embodiment and the other drive source may be applied to the electric motor. .

DESCRIPTION OF SYMBOLS 1, 7, 8, 9 ... Hybrid vehicle drive device, 2 ... Torque converter, 3 ... Case, 5 ... Automatic transmission, 10 ... Engine, 12 ... Flywheel, 16 ... Centerpiece, 20 ... Electric motor, 21 ... Rotor, 22 ... Stator, 23 ... Coil, 26, 82 ... Output shaft, 31 ... Input shaft, 40, 80, 110, 120 ... clutch device, 41, 81, 111, 121 ... input shaft, 42 ... clutch plate, 43 ... separate plate, 44, 84, 114, 124 ... pressing member, 45, 85, 115, 125 ... coil springs, 46, 86, 116, 126 ... pistons, 47, 87, 117, 127 ... actuating parts, 48, 88, 118, 128 ... cylinders, 49, 89 ・・ Hydraulic chamber, 51, 91, 101, 131 ... Relative rotation permission member, 52, 92, 102, 132 ... Contact member, 53, 93 ... Stop member, 60 ... Electric oil pump, 61, 100: Inflow port.

Claims (4)

An input shaft rotatably connected to the engine;
An output shaft arranged on the same rotational axis as the rotor of the electric motor and integrally connected;
A clutch device for releasably connecting the input shaft and the output shaft;
The input shaft and the output shaft are rotatably supported via bearings on the rotation axis, and at least the electric motor and the clutch device are connected to the input shaft side wall portion, the output shaft side wall portion, and the outer peripheral wall portion. And a case surrounding with,
The clutch device includes a plurality of clutch plates that are engaged with the large-diameter portions of the input shaft and the output shaft so as to restrict rotation and move in the direction of the rotation axis
A pressing member mounted on the input shaft so as to be movable in the direction of the rotational axis on the output shaft side, and a pressing member for pressing the plurality of clutch plates;
A coil spring that urges the pressing member toward the input shaft with a spring force to press-contact the plurality of clutch plates;
An operating portion provided integrally with the pressing member, passing through the large diameter portion of the input shaft in the direction of the rotation axis and extending toward the input shaft;
A hydraulic chamber is formed between the cylinder formed on the side wall portion on the input shaft side so as to be movable, and a hydraulic chamber is formed between the cylinder bottom portion, and the operating portion is relatively rotated by being moved by the hydraulic pressure supplied to the hydraulic chamber. A piston that moves against the spring force through an allowable member and separates the plurality of clutch plates; and
An inflow port that is formed in the side wall portion on the input shaft side and communicates with the hydraulic chamber to supply the hydraulic pressure;
A drive device for a hybrid vehicle, comprising: An input shaft rotatably connected to the engine;
An output shaft arranged on the same rotational axis as the rotor of the electric motor and integrally connected;
A clutch device for releasably connecting the input shaft and the output shaft;
The input shaft and the output shaft are rotatably supported via bearings on the rotation axis, and at least the electric motor and the clutch device are connected to the input shaft side wall portion, the output shaft side wall portion, and the outer peripheral wall portion. And a case surrounding with,
The clutch device includes a plurality of clutch plates that are engaged with the large-diameter portions of the input shaft and the output shaft so as to restrict rotation and move in the direction of the rotation axis
A pressing member mounted on the output shaft so as to be movable in the direction of the rotation axis on the input shaft side, and a pressing member for pressing the plurality of clutch plates;
A coil spring that urges the pressing member toward the output shaft with a spring force to press-contact the plurality of clutch plates;
An operating portion provided integrally with the pressing member, passing through the large diameter portion of the output shaft in the direction of the rotation axis and extending toward the output shaft;
A hydraulic chamber is formed between the cylinder formed on the side wall portion on the output shaft side so as to be movable, and a hydraulic chamber is formed between the cylinder bottom portion and moved relative to the hydraulic chamber by the hydraulic pressure supplied to the hydraulic chamber. A piston that moves against the spring force through an allowable member and separates the plurality of clutch plates; and
An inflow port that is formed in the side wall portion on the output shaft side and communicates with the hydraulic chamber to supply the hydraulic pressure;
A drive device for a hybrid vehicle, comprising:   3. The hybrid according to claim 1, further comprising a contact member that is fixed to the operating portion and extends toward the rotation axis, and is pushed by the piston via the relative rotation permission member. Vehicle drive device.   The press member according to any one of claims 1 to 3, wherein the pressing member is formed in an annular shape, and a plurality of the operating portions project from the inner peripheral portion of the pressing member in the rotation axis direction. Drive device for hybrid vehicle.

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