JP2007315572A - Hydraulic clutch driving device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To heighten connection/disconnection responsiveness of a clutch actuating mechanism in a hydraulic clutch driving device including the clutch actuating mechanism, a clutch connection/disconnection control mechanism for exerting the control force having an oil pressure chamber and switching between disconnection and connection to the clutch actuating mechanism according to the hydraulic action to the oil pressure chamber, an actuator, an oil pressure generating mechanism for generating oil pressure according to the operation of the actuator, and an oil pressure pipeline connecting the oil pressure and the oil pressure generating mechanism. <P>SOLUTION: The oil pressure generating mechanism 86A includes: a small-diameter cylinder 91 slidably fitting a small-diameter piston 88 driven by the actuator 85A to a small-diameter cylinder bore 89 and having an output port 90 communicated with an oil pressure pipeline 87A; a large-diameter cylinder 94 slidably fitting a large-diameter piston 92 driven by the actuator 85A to a large-diameter cylinder bore 93; and a selector valve means 96 for switching between connection and disconnection of the oil pressure pipeline 87A and the large-diameter cylinder 94. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention has a clutch operating mechanism provided between a driving rotating member and a driven rotating member, and a hydraulic chamber, and exerts a control force to switch the connection / disconnection to the clutch operating mechanism according to the hydraulic action on the hydraulic chamber. The present invention relates to a hydraulic clutch drive device that includes a clutch disengagement / contact control mechanism, an actuator, a hydraulic pressure generating mechanism that generates hydraulic pressure in response to the operation of the actuator, and a hydraulic line that connects the hydraulic chamber and the hydraulic pressure generating mechanism.

A hydraulic clutch driving device is already known from Patent Document 1 in which hydraulic pressure generated in a cylinder by driving a piston by the operation of an electric motor is applied to a hydraulic chamber of a clutch disengagement / contact control mechanism.
Japanese Patent Laid-Open No. 2003-294062

  However, in the hydraulic clutch driving device disclosed in Patent Document 1, a single cylinder is driven by an electric motor, and the entire control of the hydraulic clutch is performed by the output hydraulic pressure of the single cylinder. Therefore, it takes time to fill the hydraulic line between the hydraulic chamber and the cylinder, and the disconnection / contact response of the clutch operating mechanism is lowered.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a hydraulic clutch driving device capable of enhancing the disconnection / contact response of a clutch operating mechanism.

  In order to achieve the above object, the invention according to claim 1 includes a clutch operating mechanism provided between the driving rotary member and the driven rotary member, a hydraulic chamber, and the clutch operation according to the hydraulic action on the hydraulic chamber. A clutch disengagement / disengagement control mechanism that exerts a control force to switch the disengagement / disengagement of the mechanism, an actuator, a hydraulic pressure generating mechanism that generates hydraulic pressure in response to the operation of the actuator, and the hydraulic chamber and the hydraulic pressure generating mechanism are connected In the hydraulic clutch driving device including a hydraulic line, the hydraulic pressure generating mechanism has a small diameter having an output port that allows the small diameter piston driven by the actuator to be slidably fitted into the small diameter cylinder hole and communicates with the hydraulic line. A large-diameter cylinder hole in which a large-diameter piston driven by the cylinder and the actuator is larger in diameter than the small-diameter cylinder hole A large-diameter cylinder that is slidably fitted and arranged in parallel with the small-diameter cylinder, and a switching valve means that can switch connection / cut-off of the hydraulic pipe and the output port of the large-diameter cylinder. To do.

  According to a second aspect of the invention, in addition to the configuration of the first aspect of the invention, the hydraulic pressure generating mechanism includes a reservoir capable of supplying hydraulic oil to at least the large-diameter cylinder, and the switching valve means includes the switching valve means, It is possible to selectively switch communication / blocking of the output port of the large-diameter cylinder to the hydraulic line and the reservoir.

  According to a third aspect of the present invention, in addition to the configuration of the first or second aspect of the invention, the actuator includes a drive source, a crankshaft having a crankpin and being rotationally driven by the drive source, and the small-diameter piston. And a pair of rotating members that are pivotally supported by the crank pin in contact with a rear end of a piston rod whose front ends are integrally connected to the large-diameter piston, respectively, the small-diameter piston and the large-diameter piston, The piston rods are biased toward the side where the rear ends of the piston rods come into contact with the rotating members.

  According to a fourth aspect of the invention, in addition to the configuration of the second aspect of the invention, the switching valve means connects the output port of the large-diameter cylinder and the hydraulic pipe line when the hydraulic pressure of the hydraulic chamber is released. It is characterized by communicating with a reservoir.

  According to a fifth aspect of the invention, in addition to the configuration of the fourth aspect of the invention, the amount of oil output from the hydraulic pressure generating mechanism in a state where the large-diameter cylinder is communicated with the hydraulic pipe line is a predetermined value or more. A sensor for detecting whether or not the engine has been reached is provided, wherein the switching valve means causes the large-diameter cylinder to communicate with the reservoir in response to the sensor detecting an oil amount greater than or equal to a predetermined amount.

  Further, the invention according to claim 6 is in addition to the configuration of the invention according to claim 1, and the hydraulic pressure generating mechanism side hydraulic chamber communicating with the hydraulic pressure generating mechanism, and the hydraulic pressure generating mechanism side hydraulic chamber communicating with the hydraulic pressure chamber are isolated from each other. And a separator that changes the hydraulic pressure of the clutch-side hydraulic chamber in response to a change in the hydraulic pressure of the hydraulic pressure generating mechanism-side hydraulic chamber, and is interposed in the middle of the hydraulic line. It is characterized by.

  The first main shaft 7 and the second main shaft 8 of the embodiment correspond to the “driven rotation member” of the present invention, and the electric motor 144 of the embodiment corresponds to the “drive source” of the present invention.

  According to the first aspect of the present invention, by connecting the output ports of the small-diameter cylinder and the large-diameter cylinder together with the hydraulic line at the initial driving stage of the hydraulic pressure generating mechanism by the actuator, the hydraulic oil is quickly supplied to the hydraulic line. Filling is possible, the filling time can be shortened, and the disconnection / contact response of the clutch operating mechanism can be improved. Further, after the start-up, the hydraulic pressure acting on the hydraulic chamber can be increased only by the output hydraulic pressure of the small diameter cylinder by shutting off the hydraulic line and the large diameter cylinder.

  According to the second aspect of the present invention, when the hydraulic pressure is increased only by the small-diameter cylinder, the hydraulic oil output from the large-diameter cylinder is returned to the reservoir to reduce the power loss in the actuator, and the actuator can be downsized. Can be planned.

  According to the third aspect of the present invention, the assembly of the hydraulic pressure generating mechanism can be facilitated by not connecting the piston rods of the small and large diameter cylinders directly to the actuator.

  According to the fourth aspect of the invention, when releasing the hydraulic pressure of the hydraulic clutch, the hydraulic line, the small diameter cylinder, and the large diameter cylinder are communicated with the reservoir, thereby improving the response of releasing the hydraulic pressure.

  According to the fifth aspect of the present invention, since the switching operation timing of the switching valve means is determined by the sensor, the oil amount can be appropriately controlled while considering the influence of disturbance.

  Furthermore, according to the invention described in claim 6, the type of hydraulic oil on the hydraulic pressure generating mechanism side and the hydraulic oil on the clutch disengagement / contact control mechanism side can be divided, and the hydraulic oil on the hydraulic pressure generating mechanism side has high responsiveness. As described above, the responsiveness of the clutch operating mechanism can be improved by arranging the separator in the vicinity of the clutch disengagement / contact control mechanism, and the hydraulic oil of the clutch disengagement / contact control mechanism is used for the members around the clutch disengagement / contact control mechanism By using the same kind of hydraulic oil, the seal structure around the hydraulic chamber can be simplified.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on examples of the present invention shown in the accompanying drawings.

  1 to 6 show a first embodiment of the present invention. FIG. 1 is a longitudinal sectional view showing a part of an engine, FIG. 2 is an enlarged view of a main part of FIG. 1, and FIG. 4 is an enlarged view of a main part of FIG. 3, FIG. 5 is a sectional view taken along line 5-5 in FIG. 4, and FIG. 6 is a sectional view taken along line 6-6 in FIG.

  First, in FIG. 1, for example, in a crankcase 5 provided in an engine mounted on a motorcycle, a gear train of a plurality of speed stages that can be selectively established, for example, first to fourth gear trains G1, G2, G3. A transmission 6 having G4 is housed, and a first speed gear train G1 includes a first speed drive gear 10 provided integrally with the first main shaft 7, and a countershaft parallel to the first main shaft 7. 9 is composed of a first speed driven gear 11 that is rotatably supported by the gear 9 and meshes with the first speed driving gear 10, and the second speed gear train G 2 is coaxial with the first main shaft 7. A second speed drive gear 12 provided integrally with the shaft 8 and a second speed driven gear 13 rotatably supported by the counter shaft 9 and meshing with the second speed drive gear 12; The speed gear train G3 is 1 comprises a third speed drive gear 14 fixed to the main shaft 7 and a third speed driven gear 15 rotatably supported on the counter shaft 9 and meshing with the third speed drive gear 14. The fourth-speed gear train G4 is a fourth-speed drive gear 16 fixed to the second main shaft 8 and a fourth-speed gear that is rotatably supported by the countershaft 9 and meshes with the fourth-speed drive gear 16. And a driven gear 17 for use.

  A first shifter 18 is splined to the countershaft 9 between the first and third speed driven gears 11 and 15, and the first and third speed driven gears 11, It is possible to switch between a state in which 15 is freely rotated with respect to the counter shaft 9 and a state in which one of the first and third speed driven gears 11 and 15 is coupled to the counter shaft 9 so as not to be relatively rotatable. A second shifter 19 is splined to the counter shaft 9 between the second and fourth speed driven gears 13 and 17, and the second and fourth speed driven gears are moved by the axial movement of the second shifter 19. It is possible to switch between a state in which the motors 13 and 17 are freely rotated with respect to the counter shaft 9 and a state in which one of the second and fourth speed driven gears 13 and 17 is coupled to the counter shaft 9 so as not to be relatively rotatable.

  An intermediate portion of the second main shaft 8 formed in a cylindrical shape penetrates the crank case 5 in a rotatable manner, and a ball bearing 22 is interposed between the crank case 5 and the second main shaft 8. . The cylindrical first main shaft 7 penetrates the second main shaft 8 so as to be rotatable relative to the second main shaft 8 while maintaining a constant axial relative position with respect to the second main shaft 8. A plurality of roller bearings 23 are interposed between the two main shafts 8. Moreover, one end of the first main shaft 7 passes through the cover 24 with a pair of ball bearings 75 interposed between the cover 24 coupled to the crankcase 5 and protrudes from the cover 24. A lid member 76 covering one end of the shaft 7 is attached to the cover 24 in a liquid-tight and detachable manner. The other end of the first main shaft 7 is rotatably supported by the crankcase 5 via a roller bearing 77.

  One end of the countershaft 9 is rotatably supported on the crankcase 5 via a roller bearing 78, and the other end of the countershaft 9 has a ball bearing 79 and an annular seal member 80 interposed between the crankcase 5 and the countershaft 9. The crankcase 5 is rotatably penetrated by interposing it, and is driven so that a chain 81 for transmitting power to a rear wheel (not shown) is wound around the protruding end portion of the countershaft 9 from the crankcase 5. The sprocket 82 is fixed.

  By the way, the power of the crankshaft 25 provided in the engine is input to the drive rotation member 28 via the primary reduction device 26 and the damper spring 27. The drive rotation member 28 and the first driven rotation member are the first driven rotation member. A twin clutch device 29 is provided between the 1 main shaft 7 and the second main shaft 8 which is the second driven rotating member.

  Referring also to FIG. 2, the primary reduction device 26 is a first gear that is rotatably supported by the second main shaft 8 and meshed with the drive gear 30. The drive gear 30 is provided integrally with the crankshaft 25. The driven gear 31 is supported on the first driven gear 31 so as to be capable of relative rotation in a limited range with the first driven gear 31 so as to absorb backlash between the driving gear 30 and the first driven gear 31, and the above-mentioned. The second driven gear 32 meshes with the drive gear 30.

  The drive rotation member 28 comes into contact with the first driven gear 31 from the side opposite to the second driven gear 32, and there are connecting bosses 28a projecting at a plurality of locations in the circumferential direction of the drive rotation member 28. The first and second driven gears 31 and 32 are inserted into elongated holes 33 provided so as to extend long in the circumferential direction. A holding plate 21 facing the second driven gear 32 on the side opposite to the first driven gear 31 is in contact with the end face of the connecting boss 28a, and is held by rivets 34 passing through the connecting bosses 28a. The plate 21 is brought into contact with the end face of the connecting boss 28a. In addition, a disc spring 35 is provided between the holding plate 21 and the second driven gear 32 to exert a spring force that causes the drive rotating member 28 to abut on the first driven gear 31.

  The first and second driven gears 31 and 32 are provided with holding holes 36 extending long in the circumferential direction at a plurality of positions shifted in the circumferential direction from the long holes 33. A damper spring 27 that exerts a spring force that relatively rotates the first and second driven gears 31 and 32 is provided between the drive rotating member 28 and the holding plate 21 and the first and second driven gears 31 and 32. It is accommodated so as to be inserted in

  The twin clutch device 29 has a plurality of first and second friction plates 37..., 38... Arranged alternately and overlapping each other to cut off power transmission between the drive rotating member 28 and the first main shaft 7. The first clutch operating mechanism 41 for switching the contact and the plurality of third and fourth friction plates 39, 40,... Arranged alternately and overlapping each other, and between the drive rotating member 28 and the second main shaft 8. A second clutch operating mechanism 42 for switching the power transmission / disconnection of the first clutch, and a first clutch disengaging / engaging control mechanism 43 for exerting a control force on the first clutch operating mechanism 41 for switching the connection / disconnection of the first clutch operating mechanism 41; And a second clutch disengagement / engagement control mechanism 44 that exerts a control force for switching the disengagement / disconnection of the second clutch operation mechanism 42 on the second clutch operation mechanism 42.

  The first clutch operating mechanism 41 is formed in a cylindrical shape with one end integrally connected to the drive rotating member 28 and coaxial with the first and second main shafts 7 and 8 on the opposite side to the primary reduction gear 26. A clutch outer 45 extending to the first main shaft 7, a plurality of first friction plates 37 engaged with the clutch outer 45 in a relatively non-rotatable manner, and relative to the clutch inner 46. A plurality of second friction plates 38, which are engaged with each other in a non-rotatable manner and alternately arranged with the first friction plates 37, and first and second friction plates 37, 38, which are arranged to overlap each other. A pressure receiving plate 47 engaged with the clutch inner 46 so as not to rotate relative to a friction plate (first friction plate 37 in this embodiment) disposed at an end portion on the drive rotating member 28 side, 1st And a pressing plate 48 sandwiching the second friction plates 37... 38 between the pressure receiving plates 47, and the clutch inner 46 is opposite to the first and second friction plates 37. A retaining ring 49 that contacts and engages the inner periphery of the pressure receiving plate 47 is mounted.

  The second clutch operating mechanism 42 is arranged so as to be aligned with the first clutch operating mechanism 41 in the direction along the rotational axis thereof. In this embodiment, the second clutch operating mechanism 42 is disposed between the first clutch operating mechanism 41 and the drive rotating member 28. Be placed.

  Thus, the second clutch operating mechanism 42 is incapable of relative rotation with the clutch outer 45 common to the first clutch operating mechanism 41, the clutch inner 50 fixed to the second main shaft 8, and the clutch outer 45. A plurality of engaged third friction plates 39 and a plurality of fourth friction plates 40 that are engaged with the clutch inner 50 in a relatively non-rotatable manner and are alternately arranged with the third friction plates 39. And the friction plate (the third friction plate 39 in this embodiment) disposed at the end of the drive rotating member 28 among the third and fourth friction plates 39, 40,. A pressure receiving plate 51 that is opposed to the clutch inner 50 so as to be relatively non-rotatable, a pressing plate 52 that sandwiches the third and fourth friction plates 39..., 40 between the pressure receiving plate 51, and a clutch outer. 45 slidably fitted And a transmission member 53 integrally having a plurality of arm portions 53a that abut against the pressing plate 52 from the side opposite to the third and fourth friction plates 39, 40,. A receiving plate 54 that rotates together with the clutch inner 50 contacts the pressure receiving plate 52 from the side opposite to the third and fourth friction plates 39.

  A plurality of slits 55 extending from an axially intermediate portion of the clutch outer 45 to an end opposite to the drive rotating member 28 are provided at a plurality of circumferential positions of the clutch outer 45, and the transmission member 53 is integrally formed. The provided arm portions 53a are inserted through the slits 55, respectively. Further, the reinforcing cylinder 56 is fitted on the outer periphery of the clutch outer 45 in a state where the insertion of the arm portions 53a into the slits 55 is completed.

  The first clutch disengagement / contact control mechanism 43 includes a stepped cylindrical control actuating member 60 that is supported by the cover 24 in a non-rotating state while allowing movement in the direction along the rotational axis of the first main shaft 7. The control actuating member 60 is liquid-tight on the inner periphery of the cover 24 so as to form an annular first hydraulic chamber 61 between the cover 24 covering the first and second clutch actuating mechanisms 41, 42. And it is slidably fitted.

  The control actuating member 60 is connected to the pressing plate 48 of the first clutch actuating mechanism 41 via the first clutch bearing 62, and the control actuating member 60 is first acted upon by hydraulic action on the first hydraulic chamber 61. When the hydraulic chamber 61 moves to the side of increasing the volume, the pressing plate 48 is pressed via the first clutch bearing 62, and the first and second friction plates 37, 38. The first and second friction plates 37..., 38... Are frictionally engaged between the clutch outer 45 and the clutch inner 46, that is, between the drive rotating member 28 and the first main shaft 7. The power will be transmitted.

  The first clutch disengagement / connection control mechanism 43 is interposed between the cover 24 and the control operation member 60 so as to urge the control operation member 60 in the direction of decreasing the volume of the first hydraulic chamber 61. The springs 63 are provided between the ring-shaped retainer 64 received by a retaining ring 65 attached to the inner surface of the cover 24 and the control actuating member 60. Are provided at a plurality of locations in the circumferential direction.

  Thus, in a state in which the hydraulic pressure in the first hydraulic chamber 61 is released, the control actuating member 60 moves to the side of reducing the volume of the first hydraulic chamber 61 by the spring force of the springs 63. In the state, the first and second friction plates 37, 38, ... are not frictionally engaged, and the power transmission between the drive rotating member 28 and the first main shaft 7 is cut off.

  The second clutch disengagement / engagement control mechanism 44 is provided with a stepped cylindrical control operation member 66 supported on the cover 24 in a non-rotating state while allowing movement in the direction along the rotation axis of the second main shaft 8. The control actuating member 66 is liquid-tightly and slidably fitted to the inner periphery of the cover 24 so as to form an annular second hydraulic chamber 67 between the cover 24 and the cover 24.

  The control actuating member 66 is connected to the transmission member 53 of the second clutch actuating mechanism 42 via a second clutch bearing 68, and the control actuating member 66 is secondly acted upon by hydraulic action on the second hydraulic chamber 67. When the hydraulic chamber 67 moves to the side of increasing the volume, the pressing plate 52 is pressed via the second clutch bearing 68, and the third and fourth friction plates 39... 40. The third and fourth friction plates 39, 40,... Are frictionally engaged with each other so that the clutch outer 45 and the clutch inner 50 are connected, that is, between the drive rotating member 28 and the second main shaft 8. The power will be transmitted.

  The second clutch disengagement / contact control mechanism 44 is interposed between the cover 24 and the control operation member 66 so as to urge the control operation member 66 in the direction of decreasing the volume of the second hydraulic chamber 67. The springs 69 are provided at a plurality of locations in the circumferential direction between the ring-shaped retainer 70 fixed to the cover 24 and the control actuating member 66. The

  Thus, in a state where the hydraulic pressure in the second hydraulic chamber 67 is released, the control actuating member 66 moves to the side of reducing the volume of the second hydraulic chamber 67 by the spring force of the springs 69. In the state, the third and fourth friction plates 39... 40 are not frictionally engaged, and the power transmission between the drive rotation member 28 and the second main shaft 8 is cut off.

  Incidentally, the first and second clutch operating mechanisms 41 and 42 are arranged coaxially with the first and second main shafts 7 and 8, but are orthogonal to the rotation axes of the first and second main shafts 7 and 8. In this direction, at least a part of the first and second clutch disengagement / contact control mechanisms 43, 44 are arranged to overlap the first and second clutch operation mechanisms 41, 42. In this embodiment, A part of the first and second clutch disengagement / engagement control mechanisms 43, 44 is arranged to overlap the first and second clutch operation mechanisms 41, 42.

  In addition, the first and second clutch operating mechanisms 41 and 42 are arranged in parallel in the direction along their rotational axes, whereas the first and second clutch disengagement / contact control mechanisms 43 and 44 are also in the direction along the rotational axes. Are arranged side by side.

  The cover 24 is provided with an oil passage 71 that communicates with the hydraulic chamber 61 of the first clutch disengagement / contact control mechanism 43 and an oil passage 72 that communicates with the hydraulic chamber 67 of the second clutch disengagement / contact control mechanism 44. It is done.

  According to such a twin clutch device 29, the first clutch disengagement / contact control mechanism 43 that exerts a control force for switching the disengagement / connection of the first clutch operation mechanism 41 on the first clutch operation mechanism 41 and the second clutch operation mechanism. The second clutch disengagement / contact control mechanism 44 that exerts a control force for switching the disengagement / connection of 42 on the second clutch actuating mechanism 42 can move in the direction along the rotation axis of the first and second main shafts 7, 8. However, the control actuating members 60 and 66 are supported by the cover 24 in a non-rotating state, and the control actuating members 60 and 66 are respectively connected to the first and second clutch actuating mechanisms 41 and 42 as clutch bearings 62, 68, respectively.

  Accordingly, the first and second clutch disengagement / contact control mechanisms 43 and 44 are disposed in the non-rotating part, and the inertial mass of the twin clutch device 29 is reduced by reducing the weight of the rotating part, thereby driving. Power from the rotating member 28 can be efficiently transmitted to the first and second main shafts 7 and 8 side.

  By the way, at the time of shifting the gear position, the connection / disconnection state of the first and second clutch operating mechanisms 41 and 42 is alternately switched, and the established state of the first to fourth gear trains G1 to G4 in the transmission 6 is changed to the first. The first and second shifters 18 and 19 are sequentially switched according to the movement of the first and second shifters 18 and 19. For example, at the time of shifting the first gear, the first clutch operating mechanism 41 is in the connected state, whereas the second clutch operating mechanism 42 is in the disconnected state. It is in. At this time, in order to switch from the first gear to the second gear, the second shifter 19 is moved to the side that engages with the second speed driven gear 13. The second speed driven gear 13 is in a rotating state with the rotation of the first clutch operating mechanism 41 because the second clutch operating mechanism 42 is in the disconnected state. There is a rotational speed difference between the shifter 19 and the second speed driven gear 19. For this reason, if the inertial mass of the second clutch operating mechanism 42 is large, the energy generated when the second shifter 19 is engaged with the second speed driven gear 13 is large, and a shift shock occurs. Since the inertial mass is reduced by reducing the weight of the rotating part in the twin clutch device 29, the shift shock accompanying the movement of the first and second shifters 18, 19 can be reduced.

  In addition, at least a part of the first and second clutch disengagement / contact control mechanisms 43, 44 in the direction perpendicular to the rotation axis of the first and second main shafts 7, 8 arranged on the same axis is connected to the first and second main shafts 7, 8. Since the two clutch actuating mechanisms 41 and 42 are arranged so as to overlap, the twin clutch device 29 can be configured compactly in the direction of the rotation axis. Further, the first and second clutch operating mechanisms 41 and 42 are arranged in parallel in the direction along their rotational axes, and the first and second clutch disengagement / contact control mechanisms 43 and 44 are arranged in the direction along the rotational axes. Therefore, the twin clutch device 29 can be configured compactly in the radial direction.

  The first and second clutch disengagement / contact control mechanisms 43 and 44 reduce the volumes of the control operation members 60 and 66 that form the hydraulic chambers 61 and 67 between the first and second clutches and the cover 24 and the hydraulic chambers 61 and 67. Springs 63 and 69 interposed between the cover 24 and the control operation members 60 and 66 so as to urge the control operation members 60 and 66 in the direction, respectively. Since the first and second hydraulic chambers 61 and 67 provided in the disconnection / contact control mechanisms 43 and 44 are provided in the non-rotating portion, the centrifugal force does not act on the oil in the hydraulic chambers 61 and 67. Not only is it unnecessary to provide a mechanism for canceling the hydraulic pressure generated by the force, but the springs 63 and 69 are also provided in the non-rotating part, so that the weight of the rotating part is further reduced and the inertia mass is further reduced. It can be reduced.

  Further, the first and second hydraulic chambers 61 and 67 are formed between the cover 24 and the control operating members 60 and 66 covering the first and second clutch operating mechanisms 41 and 42, so that oil is supplied to the hydraulic chambers 61 and 67. The guiding oil passages 71 and 72 can be easily formed in the cover 24, and the passage of the oil passages 71 and 72 can be simplified and shortened as compared with the case where the oil passage is formed in the rotating member. Reduction of loss and reduction of processing man-hours can be achieved.

  In FIG. 3, a hydraulic pressure generating mechanism 86A is connected to an oil passage 71 communicating with the first hydraulic chamber 61 of the first clutch disengagement / engagement control mechanism 43 via a hydraulic line 87A. A hydraulic pressure generating mechanism 86B is connected to an oil passage 72 communicating with the second hydraulic chamber 67 of 44 through a hydraulic pipe line 87B.

  4 to 6 together, the hydraulic pressure generating mechanism 86A generates hydraulic pressure in response to the operation of the actuator 85A, and slides the small diameter piston 88 driven by the actuator 85A into the small diameter cylinder hole 89. A small-diameter cylinder 91 having a first output port 90 communicating with the hydraulic pipe 87 </ b> A and a large-diameter piston 92 driven by the actuator 85 </ b> A is larger in diameter than the small-diameter cylinder hole 89. The large diameter cylinder 94 which is slidably fitted in the cylinder hole 93 and arranged in parallel with the small diameter cylinder 91, and the connection / disconnection between the second output port 95 of the large diameter cylinder 94 and the hydraulic pipe line 87A are switched. Possible switching valve means 96.

  The small-diameter cylinder 91 and the large-diameter cylinder 94 are provided in a common cylinder body 97. The small-diameter cylinder hole 89 and the large-diameter cylinder hole 93 are provided in parallel to the cylinder body 97 with a bottom, respectively. Piston rods 88a and 92a whose front ends are coaxially and integrally connected to the small-diameter piston 88 and the large-diameter piston 92, which are slidably fitted in the large-diameter cylinder hole 93, respectively. It protrudes from the opening end of the cylinder hole 93.

  A small-diameter hydraulic pressure generating chamber 98 is formed between the closed end of the small-diameter cylinder hole 89 and the small-diameter piston 88 so that the front end of the small-diameter piston 88 faces, and a large diameter is provided between the closed end of the large-diameter cylinder hole 93 and the large-diameter piston 92. A large-diameter hydraulic pressure generating chamber 99 that faces the front end of the piston 92 is formed. A first return spring 100 accommodated in the small-diameter hydraulic pressure generation chamber 98 is contracted between the closed end of the small-diameter cylinder hole 89 and the small-diameter piston 88, and a second return spring accommodated in the large-diameter hydraulic pressure generation chamber 99. The spring 101 is contracted between the closed end of the large-diameter cylinder hole 93 and the large-diameter piston 92, and the small-diameter piston 88 and the large-diameter piston 92 increase the volumes of the small-diameter hydraulic pressure generation chamber 98 and the large-diameter hydraulic pressure generation chamber 99. It is energized to the side to perform, that is, the backward side. In addition, retaining rings 102 and 103 are mounted on the inner surfaces of the opening ends of the small-diameter cylinder hole 89 and the large-diameter cylinder hole 93, respectively, and come into contact with the outer peripheral portions of the rear ends of the small-diameter piston 88 and the large-diameter piston 92. Ring-shaped stoppers 104 and 105 for restricting the retreat limit of the large-diameter piston 92 are received by the retaining rings 102 and 103, respectively.

  A reservoir 106 is provided on the cylinder body 97. The reservoir 106 includes a cylindrical portion 107 integrally connected to the upper side wall of the cylinder body 97, and a cap 108 fastened to the cylindrical portion 107 so as to close the upper end opening of the cylindrical portion 107. A gas-liquid separation bladder 109 is sandwiched between the cylindrical portion 107 and the cap 108, and a filter 110 is mounted on the inner surface of the intermediate portion of the cylindrical portion 107.

  The cylinder body 97 is provided with primary ports 111 and 112 that allow the small-diameter hydraulic pressure generation chamber 98 and the large-diameter hydraulic pressure generation chamber 99 to communicate with the reservoir 106 when the small-diameter piston 88 and the large-diameter piston 92 are retracted to the retreat limit. .

  Further, first and second cup seals 113 and 114 are attached to the outer periphery of the small diameter piston 88, and between the first and second cup seals 113 and 114, between the outer periphery of the small diameter piston 88 and the inner periphery of the small diameter cylinder hole 89. A secondary port 116 for communicating the small-diameter annular chamber 115 formed in the reservoir 106 into the reservoir 106 is provided in the cylinder body 97, and the first cup seal on the small-diameter hydraulic pressure generation chamber 98 side of the first and second cup seals 113, 114 is provided. 113 allows the hydraulic oil to flow from the small-diameter annular chamber 115 to the small-diameter hydraulic pressure generation chamber 98 side.

  Further, third and fourth cup seals 117 and 118 are mounted on the outer periphery of the large diameter piston 92, and the outer periphery of the large diameter piston 92 and the large diameter cylinder hole 93 are interposed between the third and fourth cup seals 117 and 18. A secondary port 120 through which the large-diameter annular chamber 119 formed between the inner circumferences communicates with the reservoir 106 is provided in the cylinder body 97, and the large-diameter hydraulic pressure generation chamber 99 side of the third and fourth cup seals 117, 118 is provided. The third cup seal 117 allows the hydraulic oil to flow from the large-diameter annular chamber 119 to the large-diameter hydraulic pressure generation chamber 99 side.

  The cylinder body 97 has first and second output ports 90 and 95 disposed on a plane passing through the axes of the small diameter cylinder hole 89 and the large diameter cylinder hole 93, and one end of the first output port 90 is connected to the small diameter cylinder. The small diameter hydraulic pressure generating chamber 98 is communicated with the small diameter hydraulic pressure generating chamber 98 at a position eccentric from the axis of the hole 89, and one end of the second output port 95 is communicated with the large diameter hydraulic pressure generating chamber 99 at a position eccentric from the axial line of the large diameter cylinder hole 93. The other end of the first output port 90 opens to the closed end of a bottomed connection hole 121 provided in the cylinder body 97.

  Thus, the hydraulic pipe line 87 </ b> A is connected to the connection hole 121 via a joint 122, and the joint 122 includes a banjo adapter 124 having a washer 123 interposed between the joint body 121 and the cylinder body 97. The banjo adapter 124 includes a banjo bolt 126 that has a locking head 126 a with a washer 125 interposed between the banjo adapter 124 and penetrates the banjo adapter 124 and is screwed into the connection hole 121. A hydraulic line 87A is connected. In addition, a filter 127 is mounted in the connection hole 121 between the first output port 90 and the banjo bolt 126.

  The switching valve means 96 includes a first normally-open electromagnetic valve 130 interposed between the second output port 95 and the first output port 90, and a second valve interposed between the second output port 95 and the reservoir 106. And a normally open solenoid valve 131.

  The first valve housing 132 provided in the first normally open solenoid valve 130 has a bottomed first mounting hole provided in the cylinder body 97 having an axis perpendicular to the axes of the first and second output ports 90 and 95. 133, and between the inner surface of the first mounting hole 133 and the outer surface of the first valve housing 132, an annular first inlet chamber 134 leading to the second output port 95, and the first output port 95 An annular first outlet chamber 135 communicating with the intermediate portion is formed. Thus, the first normally open solenoid valve 130 communicates between the first inlet chamber 134 and the first outlet chamber 135, that is, between the second and first output ports 95 and 90, when the solenoid 136 is not energized. When the solenoid 136 is energized, the connection between the first inlet chamber 134 and the first outlet chamber 135, that is, between the second and first output ports 95 and 90 is cut off. That is, the first output port 90 of the small-diameter cylinder 91 is always in communication with the hydraulic line 87A, whereas the second output port 95 of the large-diameter cylinder 94 is in communication / blocking with the hydraulic line 87A. Are selectively switched by the first normally open solenoid valve 130.

  The cylinder body 97 is provided with a first passage 137 that communicates with the first inlet chamber 134 that communicates with the second output port 95 so as to be orthogonal to the second output port 95. The second valve housing 138 of the electromagnetic valve 131 is mounted in a bottomed second mounting hole 139 provided in the cylinder body 97 with an axis parallel to the first mounting hole 133. Thus, an annular second inlet chamber 140 communicating with the first passage 137 and an annular second outlet chamber 141 are formed between the inner surface of the second mounting hole 139 and the outer surface of the second valve housing 138. . Thus, the cylinder body 97 is provided with a second passage 142 that allows the second outlet chamber 141 to communicate with the reservoir 106, and the second normally open solenoid valve 131 has the second passage when the solenoid 143 is not energized. The inlet chamber 140 and the second outlet chamber 141 communicate with each other, that is, the second output port 95, and the reservoir 106. When the solenoid 143 is energized, between the second inlet chamber 140 and the second outlet chamber 141, that is, the second output port. 95 and the reservoir 106 are blocked.

  The actuator 85A includes an electric motor 144 that is a drive source, first and second crank pins 148 and 149, and a crankshaft 145 that is rotationally driven by the electric motor 144, a small-diameter piston 88, and a large-diameter piston 92. The first and second rotating members 150 and 151 are rotatably supported by the first and second crank pins 148 and 149 in contact with the rear ends of the piston rods 88a and 92a that are integrally connected, and the electric motor 144 is provided. Can rotate forward and backward.

  A cover 152 that covers the open ends of the small diameter cylinder hole 89 and the large diameter cylinder hole 93 is fastened to the cylinder body 97 with a plurality of bolts 153. . The electric motor 144 has a rotation axis parallel to the axes of the small diameter cylinder hole 89 and the large diameter cylinder hole 93, and is a motor fastened to the cover 152 so as to close one end of the working chamber 154. It is supported by the support case 155.

  The crankshaft 145 includes a first rotating shaft 146 having one end protruding into the motor support case 155, and a first crankpin having one end integrally and parallel to the eccentric position of the other end of the first rotating shaft 146. 148, a second crankpin 149 arranged coaxially with one end opposed to the other end of the first crankpin 148, and one end integrally and parallel to the eccentric position of the other end of the second crankpin 149. A second rotating shaft 147 disposed coaxially with the first rotating shaft 146, and a connecting member 155 that coaxially connects the first and second crank pins 148, 149.

  The first rotating shaft 146 is rotatably supported by the cover 152 and the motor support case 155 via a first ball bearing 156. Also, a bearing support cylinder 157 is fitted and fixed to the cover 152 on the side opposite to the motor support case 155, and between the second rotating shaft 147 coaxially passing through the bearing support cylinder 157 and the bearing support cylinder 157. A second ball bearing 158 is interposed between the second ball bearing 158 and the second ball bearing 158.

  One end of the crankshaft 145, that is, one end of the first rotating shaft 146, is a worm gear 160 provided on the output shaft 159 of the electric motor 144, and a worm wheel provided on one end of the first rotating shaft 146 and meshing with the worm gear 160. 161, the rotational power of the electric motor 144 is transmitted. A sensor case 163 of a rotation angle sensor 162 for detecting the operation amount of the actuator 85A and controlling the operation of the electric motor 144 is fastened to the bearing support cylinder 157. The rotation angle sensor 162 The other end of the shaft 145, that is, the other end of the second rotating shaft 147 is coaxially connected.

  The first and second crank pins 148 and 149 of the crankshaft 145 are mounted with the first and second rotating members 150 and 151 via the first and second needle bearings 164 and 165, respectively. The member 150 contacts the rear end of the piston rod 88a whose front end is integrally connected to the small-diameter piston 88 urged in the backward direction by the first return spring 100, and the second rotating member 151 is moved backward by the second return spring 101. The large-diameter piston 92 biased in the direction abuts against the rear end of the piston rod 92a whose front end is integrally connected.

  Thus, as the crankshaft 145 is angularly displaced by the operation of the electric motor 144, the axial position of the small diameter piston 88 in the small diameter cylinder 91 and the axial position of the large diameter piston 92 in the large diameter piston 94 are determined. .

  Further, a sensor 166A is provided in the middle of the hydraulic pipe line 87A. The sensor 166A has a predetermined amount of oil output from the hydraulic pressure generating mechanism 86 in a state where the large diameter cylinder 94 is communicated with the hydraulic pipe line 87A. Detects whether the value is greater than or equal to the value.

  By the way, the first normally open type solenoid valve 130 of the switching valve means 96 can switch between connection and disconnection of the hydraulic line 87A and the second output port 95 of the large diameter cylinder 94, and a hydraulic pressure generating mechanism by the clutch actuator 85A. In the initial stage of driving 86, the first normally open solenoid valve 130 is held in the open state and the second normally open solenoid valve 131 is closed so that the output ports 90 and 95 of the small diameter cylinder 91 and the large diameter cylinder 94 are closed. Are communicated with the hydraulic line 87A. As a result, both the hydraulic pressures output from the small diameter cylinder 91 and the large diameter cylinder 94 are guided to the first hydraulic chamber 61 from the hydraulic line 87A.

  Thus, the first normally open solenoid valve 130 of the switching valve means 96 is closed in response to the sensor 166 detecting that the amount of oil output from the hydraulic pressure generating mechanism 86 has exceeded a predetermined value. The second normally-open electromagnetic valve 131 is opened, whereby the hydraulic line 87A and the large-diameter cylinder 94 are shut off, and the second output port 95 of the large-diameter cylinder 94 communicates with the reservoir 106. It will be. In this state, the first output port 90 of the small-diameter cylinder 91 remains in communication with the hydraulic pipe line 87 </ b> A, and the hydraulic pressure in the first hydraulic chamber 61 is controlled according to the operation of the small-diameter cylinder 91. The output pump 95 remains in communication with the reservoir 106.

  Further, when releasing the hydraulic pressure in the first hydraulic chamber 61, the electric motor 144 is operated in reverse to cause the small-diameter piston 88 and the large-diameter piston 92 to retreat, and the first and second normally-opening of the switching valve means 96 is also performed. The mold solenoid valves 130 and 131 are opened.

  Mount rubber 167... For mounting on a member that supports the cylinder body 97 is attached to a plurality of locations of the cylinder body 97 in the hydraulic pressure generating mechanism 86A.

  In FIG. 3 again, in the oil passage 72 communicating with the second hydraulic chamber 67 of the second clutch disengagement / engagement control mechanism 44, a hydraulic pressure generating mechanism 86B configured similarly to the hydraulic pressure generating mechanism 86A is provided via a hydraulic pipe line 87B. The hydraulic pressure generating mechanism 86B generates hydraulic pressure in response to the operation of an actuator 85B configured similarly to the actuator 85A. A sensor 166B for detecting whether or not the amount of oil output from the hydraulic pressure generation mechanism 86 has reached a predetermined value or more is provided in the middle of the hydraulic pipe line 87B.

  Next, the operation of the first embodiment will be described. The hydraulic pressure generating mechanisms 86A and 86B are configured to slidably fit the small diameter piston 88 driven by the actuators 85A and 85B into the small diameter cylinder hole 89 and the hydraulic line 87A. A small-diameter cylinder 91 having an output port 90 communicating with the small-diameter cylinder and a large-diameter piston 92 driven by actuators 85A and 85B are slidably fitted into a large-diameter cylinder hole 93 having a larger diameter than the small-diameter cylinder hole 91. A large-diameter cylinder 94 arranged in parallel with 91, and a switching valve means 96 capable of switching connection / disconnection of the hydraulic pipe line 87A and the second output port 95 of the large-diameter cylinder 94 are provided.

  Therefore, by connecting the output ports 90 and 95 of the small-diameter cylinder 91 and the large-diameter cylinder 94 to the hydraulic lines 87A and 87B at the initial driving stage of the hydraulic pressure generating mechanisms 86A and 86B by the actuators 85A and 85B, the hydraulic line 87A. , 87B can be quickly filled with hydraulic oil, the filling time can be shortened, and the disconnection / contact response of the first and second clutch operating mechanisms 41, 42 can be improved. After the start-up, the hydraulic pressure acting on the hydraulic chambers 61 and 67 can be increased only by the output hydraulic pressure of the small-diameter cylinder 91 by shutting off the hydraulic lines 87A and 87B and the large-diameter cylinder 94.

  The hydraulic pressure generating mechanisms 86A and 86B are each provided with a reservoir 106 capable of supplying hydraulic oil to at least the large diameter cylinder 94, and the switching valve means 96 is connected to the hydraulic lines 87A and 87B and the reservoir 106 with the first diameter of the large diameter cylinder 94. Since the communication between the two output ports 95 can be switched selectively, the hydraulic oil output from the large-diameter cylinder 94 is returned to the reservoir 106 when the hydraulic pressure is increased by the small-diameter cylinder 91 alone. The power loss at 85B can be reduced, and the actuators 85A and 85B can be downsized.

  The actuators 85A and 85B have an electric motor 144, first and second crank pins 148 and 149, and a crankshaft 145 that is driven to rotate by the electric motor 144, a small diameter piston 88, and a large diameter piston 92 with front ends. First and second rotating members 150 and 151 that are in contact with the rear ends of the piston rods 88a and 92a that are integrally connected to the first and second crank pins 148 and 149, respectively, are rotatably supported. Since the small-diameter piston 88 and the large-diameter piston 92 are biased to the side where the rear ends of the piston rods 88a and 92a abut against the first and second rotating members 150 and 151, the small-diameter and large-diameter Piston rods 88a and 92a of cylinders 91 and 94 are directly connected to actuators 85A and 85B. And it was not so, it is possible to oil pressure generating mechanism 86A, the assembly of 86B easily.

  The switching valve means 96 communicates the second output port 95 of the large-diameter cylinder 94 and the hydraulic lines 87A and 87B to the reservoir 106 when releasing the hydraulic pressure in the first and second hydraulic chambers 61 and 67. When releasing the oil pressure, the hydraulic lines 87A and 87B, the small diameter cylinder 91 and the large diameter cylinder 94 are communicated with the reservoir 106, so that the response of releasing the hydraulic pressure is improved.

  Further, whether or not the amount of oil output from the hydraulic pressure generating mechanisms 86A and 86B exceeds a predetermined value in a state where the large diameter cylinder 94 is communicated with the hydraulic lines 87A and 87B is detected by the sensors 166A and 166B. The means 96 allows the large-diameter cylinder 94 to communicate with the reservoir 106 in response to the sensors 166A and 166B detecting an oil amount greater than or equal to a predetermined amount, so that the switching operation timing of the switching valve means 96 is determined by the sensors 166A and 166B. In other words, the amount of oil can be appropriately controlled while considering the influence of disturbance.

  7 and 8 show a second embodiment of the present invention. FIG. 7 is a diagram showing a configuration of a hydraulic clutch driving device, and FIG. 8 is an enlarged sectional view of a separator.

  It should be noted that portions corresponding to the first embodiment in FIGS. 1 to 6 are only given the same reference numerals and are not shown in the drawings.

  The hydraulic pressure generating mechanism side hydraulic chamber 171 leading to the hydraulic pressure generating mechanism 86A is provided in the middle of the hydraulic pipe line 87A connecting the oil passage 71 leading to the first hydraulic pressure chamber 61 of the first clutch disengagement / contact control mechanism 43 and the hydraulic pressure generating mechanism 86A. And a clutch-side hydraulic chamber 172 that communicates with the first hydraulic chamber 61 and is isolated from the hydraulic pressure generating mechanism-side hydraulic chamber 171, and the clutch-side hydraulic chamber 172 responds to changes in the hydraulic pressure of the hydraulic pressure generating mechanism-side hydraulic chamber 171. A separator 170 that changes the hydraulic pressure is interposed.

  The casing 173 of the separator 170 is formed by fastening bottomed cylindrical first and second case halves 174 and 175 that are open on opposite sides, and is connected to the hydraulic pressure generating mechanism 86A. A first piston 176 that forms the side hydraulic chamber 171 between the closed end of the first case half 174 is fitted in the first case half 174 in a fluid-tight and slidable manner. A second piston 177 that forms a communicating clutch side hydraulic chamber 172 between the closed end of the second case half 175 is fitted to the second case half 175 in a fluid-tight and slidable manner. A spring 178 for biasing the second piston 177 is provided between the closed end of the second case half 175 and the second piston 177 so as to increase the volume of the clutch-side hydraulic chamber 172. A retaining ring 179 that restricts the moving end of the second piston 177 toward the side that increases the volume of the clutch-side hydraulic chamber 172 is mounted on the inner surface of the opening end of the half body 175.

  Thus, when the first and second case halves 174 and 175 are fastened to each other to form the casing 173, the first piston 176 that is slidably fitted to the first case half 174 is connected to the first piston 176. A second piston 177 slidably fitted to the two case half 175 is brought into contact. That is, the first and second pistons 176 and 177 isolate the hydraulic pressure generating mechanism side hydraulic chamber 171 and the clutch side hydraulic chamber 172 from each other, and the clutch side hydraulic chamber 172 according to the change in the hydraulic pressure of the hydraulic pressure generating mechanism side hydraulic chamber 171. It is linked and connected so as to change the hydraulic pressure.

  A release chamber 180 is formed between the first and second pistons 176 and 177 in the casing 173, and a release hole 181 for communicating the release chamber 180 to the outside is provided in the first and second case halves 174 and 175. Formed between the coupling surfaces.

  The second piston 177 is fitted with a shock-absorbing piston 182 in a liquid-tight and slidable manner. The shock-absorbing chamber 183 formed between the second piston 177 and the shock-absorbing piston 182 is connected to the clutch-side hydraulic chamber 172. The second piston 177 is provided with a plurality of communication holes 184. An impact absorbing spring 187 is contracted between a spring receiving plate 186 received by a retaining ring 185 attached to the inner surface of the second piston 177 on the first piston 176 side and the impact absorbing piston 182.

  Thus, the sudden change in the hydraulic pressure in the clutch-side hydraulic chamber 172 is avoided by changing the volume of the shock-absorbing chamber 183 communicated with the clutch-side hydraulic chamber 172 by operating the shock absorbing piston 182 in the axial direction. It is possible to suppress a rapid change in the hydraulic pressure in the first hydraulic chamber 61.

  Further, an air bleeder 188 for extracting air from the hydraulic pressure generating mechanism side hydraulic chamber 171 is attached to the first case half 174, and an air bleeder 189 for extracting air from the clutch side hydraulic chamber 172 is attached to the second case half 175. Mounted.

  According to the second embodiment, the type of hydraulic oil on the hydraulic pressure generating mechanism 86A side and the hydraulic oil on the first clutch disengagement / contact control mechanism 43 side can be divided, and the hydraulic oil on the hydraulic pressure generating mechanism 86A side can be responsive. By disposing the separator 170 in the vicinity of the first clutch disengagement / contact control mechanism 43 as a high one (for example, ATF oil or brake fluid), the responsiveness of the first clutch operating mechanism 41 can be improved. By making the hydraulic oil of the disconnection / contact control mechanism 43 the same type as the hydraulic oil used for the members around the clutch disconnection / contact control mechanism 43 (for example, engine oil), the seal structure around the first hydraulic chamber 61 is simplified. Can be

  Although not shown, a separator similar to the separator 170 is provided in the middle of the hydraulic passage 87B connecting the oil passage 72 and the hydraulic pressure generation mechanism 86B leading to the second hydraulic chamber 67 of the second clutch disengagement / contact control mechanism 44. By interposing, the type of hydraulic oil on the hydraulic pressure generating mechanism 86B side and the hydraulic oil on the second clutch disengagement / contact control mechanism 44 side can be divided as described above. The responsiveness of the second clutch operating mechanism 42 can be enhanced as a highly responsive one, and the hydraulic oil of the second clutch disengagement / contact control mechanism 44 is used as a member around the clutch disengagement / contact control mechanism 44. The seal structure around the second hydraulic chamber 67 can be simplified.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. It is.

It is a longitudinal cross-sectional view which shows a part of engine of 1st Example. It is a principal part enlarged view of FIG. It is a figure which shows the structure of a hydraulic clutch drive device. It is a principal part enlarged view of FIG. FIG. 5 is a sectional view taken along line 5-5 of FIG. FIG. 6 is a sectional view taken along line 6-6 of FIG. It is a figure which shows the structure of the hydraulic clutch drive device of 2nd Example. It is an expanded sectional view of a separator.

Explanation of symbols

7: First main shaft as a driven rotating member 8 ... Second main shaft as a driven rotating member 28 ... Drive rotating members 41, 42 ... Clutch operating mechanisms 43, 44 ... Clutch disengagement Contact control mechanisms 61, 67 ... hydraulic chambers 85A, 85B ... actuators 86A, 86B ... hydraulic pressure generation mechanisms 87A, 87B ... hydraulic pipes 88 ... small diameter pistons 88a, 92a ... pistons Rod 89 ... small diameter cylinder holes 90, 95 ... output port 91 ... small diameter cylinder 92 ... large diameter piston 93 ... large diameter cylinder hole 94 ... atmospheric cylinder 96 ... switching valve means 106 ... Reservoir 144 ... Electric motor 145 as drive source ... Crank shaft 148, 149 ... Crank pins 150, 151 ... Rotating members 166A, 166 ... sensor 170 ... separator 171 ... oil pressure generating mechanism-side hydraulic chamber 172 ... clutch fluid pressure chamber

Claims (6)

  The clutch operating mechanism (41, 42) provided between the driving rotary member (28) and the driven rotary member (7, 8) and the hydraulic chamber (61, 67) and the hydraulic pressure to the hydraulic chamber (61, 67) are provided. A clutch disengagement / disengagement control mechanism (43, 44) that exerts a control force to switch the disengagement / disengagement to the clutch actuation mechanism (41, 42) according to the action, an actuator (85A, 85B), and the actuator (85A, 85B) and hydraulic lines (87A, 87B) connecting the hydraulic pressure generating mechanism (86A, 86B) to the hydraulic chamber (61, 67) and the hydraulic pressure generating mechanism (86A, 86B). The hydraulic pressure generating mechanism (86A, 86B) has a small diameter piston (88) driven by the actuator (85A, 85B) with a small diameter. A small-diameter cylinder (91) having an output port (90) that is slidably fitted into the Linda hole (89) and communicated with the hydraulic pipes (87A, 87B) and driven by the actuator (85A, 85B). A large-diameter cylinder (92) that is slidably fitted into a large-diameter cylinder hole (93) having a larger diameter than the small-diameter cylinder hole (91) and is arranged in parallel with the small-diameter cylinder (91). 94) and switching valve means (96) capable of switching connection / disconnection of the hydraulic pipes (87A, 87B) and the output port (95) of the large-diameter cylinder (94). Clutch drive device.   The hydraulic pressure generating mechanism (86A, 86B) includes a reservoir (106) capable of supplying hydraulic oil to at least the large diameter cylinder (94), and the switching valve means (96) includes the hydraulic pipes (87A, 87B). The hydraulic clutch driving device according to claim 1, wherein the communication and blocking of the output port (95) of the large-diameter cylinder (94) to the reservoir (106) can be selectively switched.   The actuator (85A, 85B) has a drive source (144), a crankpin (148, 149) and is driven to rotate by the drive source (144), and the small diameter piston (88). And a pair of rotating members (which are rotatably supported by the crank pins (148, 149) by abutting against the rear ends of the piston rods (88a, 92a) whose front ends are integrally connected to the large-diameter piston (92). 150, 151), and the small-diameter piston (88) and the large-diameter piston (92) abut the rear ends of the piston rods (88a, 92a) against the rotating members (150, 151). 3. The hydraulic clutch driving device according to claim 1, wherein the hydraulic clutch driving device is biased to the side.   When the switching valve means (96) releases the hydraulic pressure in the hydraulic chambers (61, 67), the output port (95) of the large diameter cylinder (94) and the hydraulic pipe lines (87A, 87B) are connected to the reservoir. The hydraulic clutch driving device according to claim 2, wherein the hydraulic clutch driving device communicates with (106).   It is detected whether or not the amount of oil output from the hydraulic pressure generating mechanism (86A, 86B) is equal to or greater than a predetermined value in a state where the large diameter cylinder (94) is in communication with the hydraulic lines (87A, 87B). The switching valve means (96) includes a sensor (166A, 166B), and the switching valve means (96) moves the large-diameter cylinder (94) into the reservoir (106) in response to the sensor (166A, 166B) detecting an amount of oil greater than a predetermined amount. The hydraulic clutch driving device according to claim 4, wherein the hydraulic clutch driving device is communicated with the hydraulic clutch driving device.   The hydraulic pressure generating mechanism side hydraulic chamber (171) communicating with the hydraulic pressure generating mechanism (86A, 86B) and the hydraulic pressure generating mechanism side hydraulic chamber (171) are connected to the hydraulic pressure generating mechanism side hydraulic chamber (171) and separated from the hydraulic pressure generating mechanism side hydraulic chamber (171). And a separator (170) configured to change the hydraulic pressure of the clutch-side hydraulic chamber (172) in response to a change in the hydraulic pressure of the hydraulic pressure generating mechanism-side hydraulic chamber (171). The hydraulic clutch driving device according to claim 1, wherein the hydraulic clutch driving device is interposed in the middle of 87A, 87B).

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