JP2011179637A - Transmission with twin-clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a structure which can connect/disconnect a clutch with compact structure in a transmission with twin-clutch in which a first clutch is arranged outside and second clutch is arranged inside in such a structure that it is equipped with: a first transmission and second transmission different in gear ratio; the first clutch connecting/disconnecting between an input gear and the first transmission; the second clutch connecting/disconnecting between the input gear and the second transmission; a first driving piston operating the first clutch; a second driving piston operating the second clutch; a cam body processing in pressing drive either of the first and second driving pistons by being driven by a motor; a first passive piston connecting/disconnecting the first clutch; and second passive piston connecting/disconnecting the second clutch. <P>SOLUTION: In the transmission with twin-clutch: a pressing member transmitting a pressing force of the first passive piston to the first clutch is arranged; and the pressing member is equipped with one input section receiving the pressing force input from the first passive piston, and a plurality of output section transmitting the pressing force received by the input section to a lifter of the first clutch. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a transmission mechanism with a twin clutch provided with two clutches inside and outside in the radial direction.

  In a transmission mechanism with twin clutches having two clutches coaxially and radially in and out, a first piston for operating the first clutch and a second piston for the purpose of eliminating the need for a complicated hydraulic system including a hydraulic pump and the like, A clutch provided with a second piston for operating the clutch, and a cam body that is driven to tilt by a motor and presses the first piston when tilted to one side, and presses and drives the second piston when tilted to the other side A connection / disconnection structure is disclosed (for example, see Patent Document 1).

  In this clutch connection / disconnection structure, connection / disconnection of the second clutch disposed radially inward is performed by pressing one central point of the rod support portion with one push rod and one slave cylinder. However, the first clutch disposed on the outer periphery in the radial direction is connected and disconnected by pressing the three points of the rod support portion with the three push rods and the three slave cylinders. The number of parts and costs related to connection / disconnection increased, and the structure was enlarged accordingly.

JP 2007-24079 A

  The present invention has been made in view of the above circumstances, and in a twin clutch transmission mechanism having two clutches on the inside and outside of a coaxial radial direction, the twin clutch has a compact structure while reducing the number of parts and cost. The purpose is to provide a structure that can be connected and disconnected.

The present invention solves the above problems, and the invention according to claim 1
A first transmission 2A and a second transmission 2B having different transmission ratios;
A first clutch 3A, which is operated by the hydraulic pressure of the first master cylinder 19A and connects / disconnects between the input gear 15 and the first transmission 2A;
A second clutch 3B, which is operated by the hydraulic pressure of the second master cylinder 19B and connects / disconnects between the input gear 15 and the second transmission 2B;
A first drive piston 22A for operating the first clutch 3A by pushing out the hydraulic fluid of the first master cylinder 19A;
A second drive piston 22B for operating the second clutch 3B by pushing out the hydraulic fluid of the second master cylinder 19B;
A cam body 63 that is driven to tilt by the motor 21 and presses the first drive piston 22A when tilted to one side, and presses and drives the second drive piston 22B when tilted to the other;
The first clutch 3A is disposed between the first master cylinder 19A and the first clutch 3A, and is slid in the first slave cylinder 17A by the hydraulic pressure of the first master cylinder 19A to connect and disconnect the first clutch 3A. A first passive piston 18A;
The second clutch 3B is disposed between the second master cylinder 19B and the second clutch 3B, and is slid in the second slave cylinder 17B by the hydraulic pressure of the second master cylinder 19B to connect and disconnect the second clutch 3B. A second passive piston 18B,
In the twin clutch mechanism 3 in which the first clutch 3A is disposed on the radially outer side and the second clutch 3B is disposed on the radially inner side,
A pressing member 50 for transmitting the pressing force of the first passive piston 18A to the first clutch 3A;
The pressing member 50 includes one input portion 51 that receives a pressing input from the first passive piston 18A,
The present invention relates to a twin clutch-equipped transmission mechanism 1 including a plurality of output portions 52 that transmit the pressing force received by the input portion 51 to the first clutch 3A.

The invention according to claim 2 is the transmission mechanism 1 with a twin clutch according to claim 1,
The lifter 48A of the first clutch 3A includes a cylindrical end 48Ad,
The output portion 52 of the pressing member 50 includes a first output portion 52X and a second output portion 52Y,
The first output portion 52X and the second output portion 52Y are point-symmetric with respect to the center C of the cylindrical end portion 48Ad on the end surface of the cylindrical end portion 48Ad when viewed from the axial direction of the lifter 48A. Each is characterized by being arranged.

The invention described in claim 3 is the transmission mechanism 1 with a twin clutch according to claim 1 or 2,
The transmission mechanism with twin clutch 1 includes a cylinder block 16 that houses at least the first passive piston 18A and the first slave cylinder 17A.
The pressing member 50 is formed in a Y-shape consisting of a trunk portion 50a and a branching portion 50b as viewed in the axial direction of the first passive piston 18A.
The pressing member 50 is pivotally supported by the cylinder block 16 at the end of the basic portion 50a so as to be swingable.
The branch portion 50b extends so as to surround the pressing projection 49 of the second passive piston 18B,
The first output part 52X and the second output part 52Y are arranged so as to be aligned with the pressing point 54 of the pressing protrusion 49 of the second passive piston 18B.

According to a fourth aspect of the present invention, in the transmission mechanism with a twin clutch according to any one of the first to third aspects,
In the axial direction of the first passive piston 18A, the length from the first output part 52X to the input part 51 is equal to the length from the second output part 52Y to the input part 51, and the parts are connected. The line is formed so as to be an isosceles triangle.

According to a fifth aspect of the present invention, in the transmission mechanism with a twin clutch according to any one of the first to fourth aspects,
The input part 51 is provided on the side closer to the branch part 50b than the pivotal support part 50c in the basic part 50a.

The invention according to claim 6 is the transmission mechanism 1 with a twin clutch according to any one of claims 1 to 5,
The trunk portion 50a of the pressing member 50 is pivotally supported on the inner side from the outer periphery of the cylinder block 16, and parallel to the axis of the first slave cylinder 17A toward the inner pivot portion 50c of the cylinder block 16. It is formed by bending.

The invention according to claim 7 is the transmission mechanism with a twin clutch 1 according to any one of claims 1 to 6,
The diameter of the first slave cylinder 17A is larger than the diameter of the second slave cylinder 17B.

The invention according to claim 8 is the transmission mechanism 1 with a twin clutch according to any one of claims 1 to 7,
A hydraulic pressure sensor 89 for detecting hydraulic pressure is provided in at least one of the first master cylinder 19A in which the first drive piston 22A is accommodated and the second master cylinder 19B in which the second drive piston 22B is accommodated. It is characterized by.

In the invention of claim 1,
With the above configuration, the second clutch 3B can be connected / disconnected only by providing the pressing member 50 having one input unit and a plurality of output units, so that the number of parts and cost can be reduced, and It is possible to prevent the transmission mechanism 1 with a twin clutch from becoming large and to have a compact structure.

In the invention of claim 2,
With the above configuration, the lifter 48A of the first clutch 3A can be evenly pushed by the first output portion 52X and the second output portion 52Y, so that the first clutch 3A can be appropriately connected and disconnected.

In the invention of claim 3,
With the above configuration, the pressing member 50 can be arranged compactly while pressing the lifter 48A of the first clutch 3A evenly and avoiding the tip of the second passive piston 18B.

In the invention of claim 4,
The transmission force from the input unit 51 can be evenly transmitted to each output unit 52.

In the invention of claim 5,
With the above configuration, by providing the input portion 51 on the branching portion 50b side, that is, on the output portion 52 side, it is possible to push the pressing member 50 with less force than that provided on the shaft support portion 50c side of the trunk portion 50a.

In the invention of claim 6,
The cylinder block 16 and the pressing member 50 can be provided without increasing the size as compared with the case where the shaft support portion 50c of the pressing member 50 is provided outside the cylinder block 16.

In the invention of claim 7,
Since the pressing member 50 is interposed on the first slave cylinder 17A side, the stroke is smaller than that of the second slave cylinder 17B. However, since a large acting force is required, the diameter is increased. As a result, the required amount of oil becomes substantially equal, so the dimensions and capacities of the two master cylinders 19A and 19B can be made substantially the same.

In the invention of claim 8,
In the speed change mechanism 1, controllability can be improved.

It is a lineblock diagram of transmission mechanism 1 with a twin clutch concerning one embodiment of the present invention. It is a longitudinal cross-sectional view of the constantly meshing transmission 2 with the twin clutch. 3 is an enlarged view of a twin clutch 3 and a slave cylinder device 4. FIG. It is a figure of the pressing member 50, A figure (a) is a top view, A figure (b) is a side view. 3 is a cross-sectional front view of the clutch actuator 5. FIG. 3 is a cross-sectional side view of the clutch actuator 5. FIG.

  FIG. 1 is a configuration diagram of a transmission mechanism 1 with a twin clutch according to an embodiment of the present invention. This speed change mechanism mainly includes an always-meshing transmission 2, a twin clutch 3, a slave cylinder device 4, a clutch actuator 5, a control unit 6, and a hydraulic oil supply device 7.

  The constantly meshing transmission 2 includes a main shaft 10 composed of an outer shaft 10A and an inner shaft 10B, a counter shaft 11 parallel to the main shaft 10, and a shift fork drive device 12 having an axis parallel to these. . The outer shaft 10A includes odd-numbered transmission gears of 1, 3, and 5 speeds, the inner shaft 10B includes even-speed transmission gears of 2, 4, and 6 speeds, and gears corresponding to these gears are provided on the counter shaft 11. It is provided. The first transmission 2A is a transmission that changes gears with the outer shaft 10A and the odd-numbered transmission gears, and the second transmission 2B is a transmission that changes gears with the inner shaft and the even-numbered transmission gears.

  The twin clutch 3 includes an outer first clutch 3A and an inner second clutch 3B. The clutch outer 13A of the first clutch 3A is connected to the input gear 15.

  The slave cylinder device 4 includes two slave cylinders, a first slave cylinder 17A and a second slave cylinder 17B, in a cylinder block 16. A second slave cylinder 17B is on the extension of the center line of the main shaft 10, and a second passive piston 18B is slidably provided therein. This connects and disconnects the second clutch 3B. The first slave cylinder 17A is provided next to the second slave cylinder 17B, and the first passive piston 18A is slidably provided therein. This connects and disconnects the first clutch 3A. A driving force transmission mechanism 44 is provided between the slave cylinder device 4 and the twin clutch 3.

  The clutch actuator 5 includes two master cylinders, a first master cylinder 19A and a second master cylinder 19B, a worm gear device 20, a control motor 21 that drives the worm gear device 20, and a cam body that is tilt-driven by the worm gear device 20. 63. The first master cylinder 19A includes a first drive piston 22A that can slide inside, and the second master cylinder 19B includes a second drive piston 22B that can slide inside. These drive pistons are driven by a worm gear device 20 driven by a control motor 21 and a cam body 63. The first master cylinder 19A and the first slave cylinder 17A, and the second master cylinder 19B and the second slave cylinder 17B are connected by the first pipe line 23A and the second pipe line 23B, respectively, and are slaved according to the movement of the drive piston. One of the passive pistons 18A and 18B of the cylinder device 4 is configured to move. The stop, rotation, and rotation direction of the control motor 21 are controlled by a command from the control unit 6, and the driving piston 19 </ b> A or 19 </ b> B is driven by the worm gear device 20 to pressurize the hydraulic oil.

  FIG. 2 is a longitudinal sectional view of the constantly meshing transmission 2. In the figure, an outer shaft 10A is put on a narrow diameter portion on the right side of the central portion of the inner shaft 10B of the main shaft 10 via a needle bearing 24, and is relatively rotatable. At the left end of the main shaft 10, the inner shaft 10B is supported by the crankcase 25 via a ball bearing 26L, and at the center of the main shaft 10, the outer shaft 10A is supported by the crankcase 25 via a ball bearing 26R. . Both ends of the counter shaft are supported by the crankcase 25 via ball bearings 27L and 27R, respectively.

  The main shaft 10 is provided with six gears M1 to M6, and the counter shaft 11 is provided with six gears C1 to C6 which are always meshed with the gears M1 to M6. M is a main shaft attached gear, C is a counter shaft attached gear, and suffixes 1 to 6 are gears that determine a gear ratio of 1st to 6th gears. The odd speed gears M1, M3, M5 are provided on the outer shaft 10A, and the even speed gears M2, M4, M6 are provided on the inner shaft 10B. A transmission consisting of an odd-numbered transmission gear is the first transmission 2A, and a transmission consisting of an even-numbered transmission gear is the second transmission 2B.

  The subscript x attached to the gear symbol is a fixed gear integrally formed with the shaft, the subscript w is held by the shaft, and is an idling gear that can rotate relative to the shaft at a predetermined position on the shaft. An axially slidable slidable gear is represented. The slidable gear (subscript s) is a gear that is held on a shaft by a spline and does not rotate relative to the shaft in the circumferential direction but can slide in the axial direction. The mating gear with which the fixed gear (subscript x) meshes and the mating gear with which the slidable gear (subscript s) meshes are always idle gears (subscript w). The idling gear (subscript w) alone does not function as a gear, and in order to fulfill the function as a gear, it is engaged with a slidable gear (subscript s) provided next to and fixed to the shaft. It is necessary. The slidable gear is provided with an engagement groove G that engages with the shift fork F (FIG. 1) of the shift fork drive mechanism. Moves in the axial direction as needed. Since the operation of the constantly meshing transmission is a known technique, a description thereof will be omitted.

  FIG. 3 is an enlarged view of the twin clutch 3 and the slave cylinder device 4. In the figure, an input gear 15 that always meshes with the output gear of the crankshaft is rotatably provided via a needle bearing 28 at the right end portion of the main shaft outer shaft 10A. A clutch outer 13A of the first clutch 3A is attached to the input gear 15 via a rubber cushioning material 29. A clutch inner 14A of the first clutch 3A is provided inside the clutch outer 13A of the first clutch 3A, and its inner periphery is fixed to the main shaft outer shaft 10A by a spline 30, a washer 31 and a nut 32.

  The clutch outer 13B of the second clutch 3B is attached to the inside of the clutch outer 13A of the first clutch 3A so as to be integrally rotatable. A clutch inner 14B of the second clutch 3B is provided inside the clutch outer 13B of the second clutch 3B, and an inner peripheral portion thereof is fixed to the main shaft inner shaft 10B by a spline 33, a washer 34, and a nut 35.

  In the first clutch 3A, a plurality of driving friction plates 36A are slidably provided in the clutch outer 13A in the axial direction, and a plurality of driven friction plates 37A are alternately arranged on the clutch inner 14A with the driving friction plates 36A. It is provided so as to be slidable in the axial direction. In the drawing, the outer peripheral portion on the right end side of the clutch inner 14A is a pressure receiving plate portion 39A that comes into contact with one end portion of the friction plate group 38A composed of the friction plates. An annular pressure plate 40A is provided at the other end of the friction plate group 38A, and the friction plate group 42A is supported by a disc spring 42A whose inner end is supported by a circlip 41A provided on the clutch inner 14A. 38A is pushed toward the pressure receiving plate portion 39A, and the first clutch 3A is in a connected state.

  In the second clutch 3B, a plurality of driving friction plates 36B are slidably provided in the clutch outer 13B in the axial direction, and a plurality of driven friction plates 37B are alternately arranged on the clutch inner 14B with the driving friction plates 36B. It is provided so as to be slidable in the axial direction. In the figure, the outer peripheral portion on the right end side of the clutch inner 14B is a pressure receiving plate portion 39B that comes into contact with one end portion of the friction plate group 38B composed of the friction plates. The other end of the friction plate group 38B is provided with an annular pressure plate 40B that comes into contact with the friction plate group 38B, and the friction plate group 42B is supported by a disc spring 42B whose inner end is supported by a circlip 41B provided on the clutch inner 14B. 38B is pushed toward the pressure receiving plate portion 39B, and the second clutch 3B is in a connected state.

  One end of the first clutch 3A contacts the pressure plate 40A of the first clutch 3A, passes through the clutch inner 14A of the first clutch 3A and the clutch outer 13B of the second clutch 3B, and the other end of the first clutch 3A. A plurality of first drive rods 43A projecting outward from 3A are provided. When the first drive rod 43A is pushed by a drive force transmission mechanism 44 described later, the first clutch 3A is disengaged.

  The second clutch 3B has a plurality of second clutches having one end abutting against the pressure plate 40B of the second clutch 3B, penetrating the clutch inner 14B of the second clutch 3B, and the other end protruding outward of the second clutch 3B. Two drive rods 43B are provided. When the second driving rod 43B is pushed by a driving force transmission mechanism 44 described later, the second clutch 3B is disengaged.

  The slave cylinder device 4 and the driving force transmission mechanism 44 are provided on the open end side of the clutch. The slave cylinder device 4 includes two slave cylinders and passive pistons that are slidably inserted into the two slave cylinders, and the driving force transmission mechanism 44 transmits the movement of the passive pistons to the corresponding clutches. Then connect and disconnect the clutch.

  The cylinder block 16 of the slave cylinder device 4 includes two slave cylinders, a first slave cylinder 17A and a second slave cylinder 17B. A second slave cylinder 17B is on the extension of the main shaft center line, and a second passive piston 18B is slidably provided through an O-ring 67 therein. This connects and disconnects the second clutch 3B. Next to the second slave cylinder 17B is a first slave cylinder 17A, in which a first passive piston 18A is slidably provided via an O-ring 67. This connects and disconnects the first clutch 3A.

  The inner diameter of the first slave cylinder 17A is larger than the inner diameter of the second slave cylinder 17B. Since a pressing member 50 that presses a first lifter 48A, which will be described later, is interposed on the first slave cylinder 17A side, the stroke is smaller than that of the second slave cylinder 17B, but a large acting force is required. Therefore, the inner diameter is increased. As a result, the required amount of oil becomes substantially equal, so that the two master cylinders 19A and 19B of the clutch actuator 5 can be made substantially the same in size and capacity.

  Hydraulic oil input ports 45A and 45B are provided at the ends of the slave cylinders 17A and 17B of the cylinder block 16, respectively, and swivels for connecting pipelines 23A and 23B connected to the master cylinders 19A and 19B of the clutch actuator 5. Pipe joints 46A and 46B are provided. A cylinder block cover 47 is provided on the cylinder block 16.

  The driving force transmission mechanism 44 is provided between the twin clutch 3 and the slave cylinder device 4, and includes a first lifter 48A that transmits driving force to the first clutch 3A, and a second lifter that transmits driving force to the second clutch 3B. It consists of 48B. A pressing member 50 is interposed between the first passive piston 18A and the first lifter 48A.

  The first lifter 48A includes an inner sliding ring 48Aa provided on the cylinder block cover 47 so as to be axially slidable, and an outer rotating ring 48Ac provided on the inner sliding ring 48Aa so as to be rotatable via a ball bearing 48Ab. It consists of and. The end of the first drive rod 43A is fixed to the outer rotating ring 48Ac. An end portion of the inner sliding ring 48Aa is a cylindrical end portion 48Ad.

  The second lifter 48B is rotated by an inner sliding member 48Ba provided in the center hole of the inner sliding ring 48Aa of the first lifter 48A so as to be axially slidable, and the inner sliding member 48Ba via a ball bearing 48Bb. The outer rotation ring 48Bc is provided as possible. The end of the second drive rod 43B is fixed to the outer rotating ring 48Bc.

  The tip of the second passive piston 18B is a pressing protrusion 49 having a hemispherical tip. This portion is in contact with the end face of the inner sliding member 48Ba of the second lifter 48B. When the inner sliding member 48Ba of the second lifter 48B is pushed by the second passive piston 18B, the pressure plate 40B of the second clutch 3B is pushed via the outer rotating ring 48Bc and the second drive rod 43B, and the second clutch 3B is cut off.

  FIG. 4 is a view of the pressing member 50 interposed between the first passive piston 18A and the first lifter 48A. FIG. 4A is a plan view of the first passive piston 18A viewed from the axial direction. (B) is a side view. The planar shape is a Y-shape consisting of a trunk portion 50a and a branching portion 50b. The trunk portion 50a is straight in the plan view, but is bent substantially at a right angle in a side view, and is supported by a shaft support 50c at the end. The cylinder block 16 is swingably supported. The branch portion 50b extends so as to surround the pressing protrusion 49 at the tip of the second passive piston 18B, and contacts the end surface of the cylindrical end portion 48Ad of the inner sliding ring 48Aa of the first lifter 48A at the tip portion of the branch portion 50b. It touches.

  The pressing member 50 has one input portion 51 that receives a pressing input from the tip protrusion 53 of the first passive piston 18A, and two hemispheres that transmit the pressing force received by the input portion 51 to the first clutch 3A. Output portions 52X and 52Y. With the above configuration, the first clutch can be connected and disconnected simply by providing a pressing member having one input portion and two output portions, so that the number of parts and cost can be reduced, and the twin clutch An increase in size can be prevented and a compact structure can be achieved.

  The inner sliding ring 48Aa of the lifter 48A of the first clutch 3A has a cylindrical end portion 48Ad, and the first output portion 52X and the second output portion 52Y of the pressing member 50 are on the end face of the cylindrical end portion 48Ad. Are arranged at positions that are point-symmetric with respect to the center C of the cylindrical end 48Ad. Therefore, since the lifter 48A can be pushed evenly by the first output portion 52X and the second output portion 52Y, the first clutch 3A can be appropriately connected and disconnected.

  The pressing member 50 is pivotally supported by the cylinder block 16 at a shaft supporting portion 50c at the end of the trunk portion 50a, and the branching portion 50b is a second passive piston with respect to the end surface of the inner sliding member 48Ba of the second lifter 48B. The first output portion 52X and the second output portion 52Y are arranged so as to be in line with the pressing point 54 of the pressing protrusion 49 of the second passive piston 18B. Has been. With such a configuration, it is possible to arrange the pressing member 50 in a compact manner while avoiding the pressing protrusion 49 of the second passive piston 18B while pressing the lifter 48A of the first clutch 3A evenly.

  When viewed from the axial direction of the first passive piston 18A, the length from the first output part 52X to the input part 51 is equal to the length from the second output part 52Y to the input part 51. A line connecting the output part 52X and the second output part 52Y is formed to be an isosceles triangle. Therefore, the transmission force from the input unit 51 can be evenly transmitted to the output units 52X and 52Y.

  The input portion 51 is provided on the trunk portion 50a on the side closer to the branch portion 50b than the shaft support portion 50c. With the configuration described above, the pressing member 50 can be pushed with less force than that provided on the branch portion 50b side, that is, on the side closer to the output portion 52 than on the side closer to the shaft support portion 50c.

  The trunk portion 50a of the pressing member 50 is pivotally supported by the shaft support portion 50c on the inner side of the outer periphery of the cylinder block 16, and the shaft support portion 50c on the inner side of the cylinder block 16 is parallel to the axis of the first slave cylinder 17A. It is bent to the direction. Since it is configured in this way, the cylinder block 16 and the pressing member 50 can be provided without increasing the size as compared with the case where the backbone 50a of the pressing member 50 is attached to the outside of the cylinder block 16.

  When the input point 51 of the pressing member 50 is pushed by the tip protrusion 53 of the first passive piston 18A, the output portions 52X and 52Y at the tip of the branching portion 50b push the inner sliding ring 48Aa of the first lifter 48A, and the outer rotating ring The pressure plate 40A of the first clutch 3A is pushed through 48Ac and the first drive rod 43A, and the first clutch 3A is disconnected.

  FIG. 5 is a sectional front view of the clutch actuator 5, and FIG. 6 is a sectional side view of the clutch actuator 5. The shell of the clutch actuator 5 includes a main body case 55, two master cylinders 19A and 19B, and a motor case 56.

  A worm gear device 20 is provided in the main body case 55. The worm gear device 20 includes a worm 57 and a worm wheel 58. The worm 57 is rotatably supported by the ball bearing 59. The worm wheel 58 is fixed to a rotation shaft 61 (FIG. 6) supported by the ball bearing 60 and is rotatable. The rotation shaft 61 includes a front rotation shaft 61a and a rear rotation shaft 61b which are connected to each other. The worm wheel 58 is fixed to the front rotation shaft 61a, and the cam body 63 is attached to the rear rotation shaft 61b. Is fixed. The cam body 63 rotates with the worm wheel 58. Upward pressing protrusions 64 are provided on the ends (FIG. 5) of the left and right arms of the cam body 63, respectively. The worm 57 is coupled to and driven by the rotary shaft extension 65 of the control motor 21 provided in the motor case 56.

  A first master cylinder 19 </ b> A and a second master cylinder 19 </ b> B are fitted and inserted into the upper part of the main body case 55 via O-rings 68. At the upper part of each master cylinder 19A, 19B, hydraulic oil output ports 69A, 69B are provided respectively, and pipe lines 23A, 23B connected to slave cylinders 17A, 17B are connected via swivel fittings 70A, 70B. Yes. These master cylinders are equipped with drive pistons 22A and 22B having the same structure. Therefore, the description will be given with respect to the right first master cylinder 19A and the first drive piston 22A.

  The first drive piston 22A includes an upper flange 71, an intermediate flange 72 having a slightly smaller diameter than the upper flange 71, and a lower flange 73. A spring receiving member 74 is provided on the upper surface of the upper flange 71, and a coil spring 75 is mounted between the upper portion of the first master cylinder 19A and urges the first drive piston 22A downward. An upper seal member 76 is provided between the outer periphery of the spring receiving member 74 and the inner surface of the first master cylinder 19A to prevent oil leakage. A lower seal material 77 is provided between the intermediate flange 72 and the lower flange 73 to prevent oil leakage.

  A washer 79 is fixed to a lower end portion of the first master cylinder 19A below the lower flange 73 via a circlip 78. When the lower surface of the lower flange 73 contacts the upper surface of the washer 79, the first drive piston 22A is prevented from coming off. A rod portion 80 below the first drive piston 22A is inserted through the central hole of the washer 79. A pressing projection 64 at the end of the cam body 63 is in contact with the lower end of the rod portion 80.

  In FIG. 6, the hydraulic oil supply device 7 is connected to the side surface of the first master cylinder 19A. This includes a swivel pipe joint 84 connected to the hydraulic oil supply port 83 on the side wall of the first master cylinder 19A, a reservoir tank 85 for storing hydraulic oil, and a hose 86 for connecting the swivel pipe joint 84 and the reservoir tank 85 to each other. It is made up of. Similarly, the hydraulic oil supply device 7 is connected to the side surface of the second master cylinder 19B. In this case, a hose 86 connected to the reservoir tank 85 is branched halfway and connected to the hydraulic oil supply port 83 of the second master cylinder 19B.

  The side wall of the first master cylinder 19A is provided with a main supply hole 87 and a sub supply hole 88 that are connected to the oil passage in the swivel fitting 84. The main supply hole 87 has a small diameter, and the sub supply hole 88 has a relatively large diameter. The main supply hole 87 is provided at a position slightly above the upper seal member 76 when the first drive piston 22A is lowered to the bottom dead center, and responds to changes in the volume of hydraulic oil due to temperature changes, etc. Insufficient hydraulic fluid is supplied from the reservoir tank 85, and excess hydraulic fluid is recovered into the reservoir tank 85. Since the tip of the main supply hole 87 has a small diameter, it is possible to prevent the influence of vibration of the hose 86 from being transmitted to the first pipeline 23A. Regardless of the position of the piston 22A, the auxiliary supply hole 88 always communicates the space between the upper and lower sealing materials 76 and 77 with the reservoir tank 85.

  When the first drive piston 22A rises slightly, the main supply hole 87 is blocked by the upper seal material 76, the first pipe line 23A and the reservoir tank 85 are disconnected, and when the first drive piston 22A further rises, the first The hydraulic oil in the pipe line 23A is pressurized, and the first passive piston 18A is driven.

  A hydraulic pressure sensor 89 that detects the hydraulic pressure inside the cylinder is provided at the top of the first master cylinder 19A. The hydraulic sensor 89 is also provided in the second master cylinder 19B. This is to improve controllability in a twin clutch that requires finer control than a single clutch.

  A potentiometer 90 for detecting the tilt angle of the cam body 63 is provided on the side of the main body case 55, and the detected value is sent to the control device 6 (FIG. 1) and used for the control operation of the control motor 21. Since the structural action in the second master cylinder 19B is the same as the structural action in the first master cylinder 19A, the description thereof is omitted. A symbol is assigned to a member specific to the first master cylinder 19A, and a symbol B is attached to a symbol unique to the second master cylinder 19B.

The twin clutch transmission mechanism 1 having the above-described configuration operates as follows.
When the speed change mechanism is stopped, the twin clutches 3A and 3B are all in a connected state.
When operating the first transmission 2A, the second clutch 3B is disengaged. In response to a command from the control device 6, the control motor 21 is driven to rotate in one direction, the worm gear device 20 and the cam body 63 rotate, the second drive piston 22B is pushed upward, the second master cylinder 19B, the second pipe The hydraulic oil in the passage 23B and the second slave cylinder 17B is pressurized, and the second passive piston 18B is pushed out. The second lifter 48B is pushed by the movement of the second passive piston 18B, the pressure plate 40B of the second clutch 3B is pushed through the second drive rod 43B, the second clutch 3B is disengaged, and the first transmission 2A operation is possible.

  When operating the second transmission 2B, the first clutch 3A is disengaged. In response to a command from the control device 6, the control motor 21 is rotationally driven in the reverse direction, the worm gear device 20 and the cam body 63 are rotated in the reverse direction, and the first drive piston 22A is pushed upward, so that the hydraulic oil Is pressurized and the first passive piston 18A is pushed out. By the movement of the first passive piston 18A, the first lifter 48A is pushed through the pushing member 50, the pressure plate 40A of the first clutch 3A is pushed through the first drive rod 43A, and the first clutch 3A is disconnected. Thus, the second transmission 2B can be operated.

As described in detail above, the following effects are brought about in the above embodiment.
(1) The pressing member 50 includes one input portion 51 that receives a pressing input from the first passive piston 18A, and two output portions 52X that transmit the pressing force received by the input portion 51 to the first clutch 3A. 52Y, the first clutch can be connected / disconnected simply by providing a pressing member having one input portion and two output portions, and the number of parts and cost can be reduced. The size of the clutch can be prevented and the structure can be made compact.
(2) The lifter 48A of the first clutch 3A has a cylindrical end 48Ad, and the output part 52 of the pressing member 50 is composed of a first output part 52X and a second output part 52Y, as viewed in the axial direction of the lifter 48A. The first output portion 52X and the second output portion 52Y are respectively arranged on the end face of the cylindrical end portion 48Ad at positions that are point-symmetric with respect to the center C of the cylindrical end portion 48Ad. Therefore, since the lifter 48A can be pushed evenly by the first output portion 52X and the second output portion 52Y, the first clutch 3A can be appropriately connected and disconnected.
(3) The pressing member 50 is pivotally supported by the cylinder block 16 at the shaft supporting portion 50c at the end of the basic portion 50a, and the branching portion 50b surrounds the pressing protrusion 49 of the second passive piston 18B. The first output portion 52X and the second output portion 52Y are arranged so as to be aligned with the pressing point 54 of the pressing protrusion 49 of the second passive piston 18B. With such a configuration, it is possible to arrange the pressing member 50 in a compact manner while avoiding the pressing protrusion 49 of the second passive piston 18B while pressing the lifter 48A of the first clutch 3A evenly.
(4) When viewed in the axial direction of the first passive piston 18A, the length from the first output portion 52X to the input portion 51 is equal to the length from the second output portion 52Y to the input portion 51. Is formed so that the line connecting the two becomes an isosceles triangle. Therefore, the transmission force from the input unit 51 can be evenly transmitted to the output units 52X and 52Y.
(5) The input unit 51 is provided on the trunk portion 50a on the side closer to the branch portion 50b than to the shaft support portion 50c. With the configuration described above, the pressing member 50 can be pushed with less force than that provided on the branch portion 50b side, that is, on the side closer to the output portion 52 than on the side closer to the shaft support portion 50c.
(6) The trunk portion 50a of the pressing member 50 is supported by the shaft support portion 50c on the inner side of the outer periphery of the cylinder block 16, and the inner shaft of the cylinder block 16 is parallel to the axis of the first slave cylinder 17A. It is formed by bending toward the support 50c. Since it is configured in this way, the cylinder block 16 and the pressing member 50 can be provided without increasing the size as compared with the case where the backbone 50a of the pressing member 50 is attached to the outside of the cylinder block 16.
(7) The inner diameter of the first slave cylinder 17A is larger than the inner diameter of the second slave cylinder 17B. Since the pressing member 50 is interposed on the first slave cylinder 17A side, the stroke is smaller than that of the second slave cylinder 17B. However, since a large acting force is required, the inner diameter is increased. As a result, the required amount of oil becomes substantially equal, so the size and capacity of the two master cylinders can be made substantially the same.
(8) A hydraulic pressure sensor 89 for detecting the hydraulic pressure inside the cylinder is provided in the first master cylinder 19A and the second master cylinder 19B. This is to improve controllability.

  DESCRIPTION OF SYMBOLS 1 ... Transmission mechanism with a twin clutch, 2 ... Always meshing transmission, 2A ... 1st transmission, 2B ... 2nd transmission, 3 ... Twin clutch, 3A ... 1st clutch, 3B ... 2nd clutch, 4 ... Slave Cylinder device, 5 ... clutch actuator, 6 ... control unit, 7 ... hydraulic oil supply device, 10 ... main shaft, 10A ... main shaft outer shaft, 10B ... main shaft inner shaft, 11 ... counter shaft, 12 ... shift fork drive Device, 13A, 13B ... Clutch outer, 14A, 14B ... Clutch inner, 15 ... Input gear, 16 ... Cylinder block, 17A ... First slave cylinder, 17B ... Second slave cylinder, 18A ... First passive piston, 18B ... First 2 passive pistons, 19A ... first master cylinder, 19B ... second master cylinder, 20 ... worm gear device, 21 ... control motor, 22A ... first drive piston, 22B ... second drive piston, 23A ... first Pipe line, 23B ... 2nd pipe line, 25 ... Crankcase, 36A, 36B ... Drive friction plate, 37A, 37B ... Driven friction plate, 38A, 38B ... Friction plate group, 39A, 39B ... Pressure receiving plate part, 40A, 40B ... Pressure plate, 43A ... First drive rod, 43B ... Second drive rod, 44 ... Driving force transmission mechanism, 45A, 45B ... Input port, 46A, 46B ... Swivel fitting, 47 ... Cylinder block cover, 48A ... 1 lifter, 48Aa ... inner sliding ring, 48Ab ... ball bearing, 48Ac ... outer rotating ring, 48Ad ... cylindrical end, 48B ... second lifter, 48Ba ... inner sliding member, 48Bc ... outer rotating ring, 49 ... pressing Projection part 50 ... Pressing member 50a ... Branch part 50b ... Branch part 50c ... Spindle support part 51 ... Input part 52 ... Output part 52X ... First output part 52Y ... Second output part 53 ... The tip protrusion of the first passive piston, 54 ... the pressing point of the second passive piston, 55 ... the body case, 56 ... 57 ... Worm, 58 ... Worm wheel, 61 ... Rotating shaft, 63 ... Cam body, 64 ... Pressing protrusion, 65 ... Rotating shaft extension, 69A, 69B ... Output port, 70A, 70B ... Swivel fitting, 71 ... upper flange, 72 ... intermediate flange, 73 ... lower flange, 74 ... spring receiving member, 75 ... coil spring, 76 ... upper seal material, 77 ... lower seal material, 83 ... hydraulic oil supply port, 84 ... swivel fitting, 85 ... reservoir tank, 87 ... main supply hole, 88 ... sub supply hole, 89 ... hydraulic sensor, 90 ... potentiometer, C ... center of the cylindrical end 48Ad.

Claims (8)

A first transmission 2A and a second transmission 2B having different transmission ratios;
A first clutch 3A, which is operated by the hydraulic pressure of the first master cylinder 19A and connects / disconnects between the input gear 15 and the first transmission 2A;
A second clutch 3B, which is operated by the hydraulic pressure of the second master cylinder 19B and connects / disconnects between the input gear 15 and the second transmission 2B;
A first drive piston 22A for operating the first clutch 3A by pushing out the hydraulic fluid of the first master cylinder 19A;
A second drive piston 22B for operating the second clutch 3B by pushing out the hydraulic fluid of the second master cylinder 19B;
A cam body 63 that is driven to tilt by the motor 21 and presses the first drive piston 22A when tilted to one side, and presses and drives the second drive piston 22B when tilted to the other;
The first clutch 3A is disposed between the first master cylinder 19A and the first clutch 3A, and is slid in the first slave cylinder 17A by the hydraulic pressure of the first master cylinder 19A to connect and disconnect the first clutch 3A. A first passive piston 18A;
The second clutch 3B is disposed between the second master cylinder 19B and the second clutch 3B, and is slid in the second slave cylinder 17B by the hydraulic pressure of the second master cylinder 19B to connect and disconnect the second clutch 3B. A second passive piston 18B,
In the twin clutch-equipped transmission mechanism 1 in which the first clutch 3A is disposed on the radially outer side and the second clutch 3B is disposed on the radially inner side,
A pressing member 50 for transmitting the pressing force of the first passive piston 18A to the first clutch 3A;
The pressing member 50 includes one input portion 51 that receives a pressing input from the first passive piston 18A,
A transmission mechanism 1 with a twin clutch, comprising: a plurality of output portions 52 that transmit the pressing force received by the input portion 51 to the first clutch 3A. The lifter 48A of the first clutch 3A includes a cylindrical end 48Ad,
The output portion 52 of the pressing member 50 includes a first output portion 52X and a second output portion 52Y,
The first output portion 52X and the second output portion 52Y are respectively point-symmetric with respect to the center C of the cylindrical end portion 48Ad on the end surface of the cylindrical end portion 48Ad when viewed from the axial direction of the lifter 48A. The transmission mechanism with a twin clutch according to claim 1, wherein the transmission mechanism is disposed. The transmission mechanism with twin clutch 1 includes a cylinder block 16 that houses at least the first passive piston 18A and the first slave cylinder 17A.
The pressing member 50 is formed in a Y-shape consisting of a trunk portion 50a and a branching portion 50b as viewed in the axial direction of the first passive piston 18A.
The pressing member 50 is pivotally supported by the cylinder block 16 at the end of the basic portion 50a so as to be swingable.
The branch portion 50b extends so as to surround the pressing projection 49 of the second passive piston 18B,
The first output part 52X and the second output part 52Y are arranged so as to be aligned with the pressing point 54 of the pressing protrusion 49 of the second passive piston 18B. 2. A transmission mechanism 1 with a twin clutch according to   In the axial direction of the first passive piston 18A, the length from the first output part 52X to the input part 51 is equal to the length from the second output part 52Y to the input part 51, and the parts are connected. The speed change mechanism (1) with a twin clutch according to any one of claims 1 to 3, wherein the line is formed to be an isosceles triangle.   The transmission mechanism with a twin clutch according to any one of claims 1 to 4, wherein the input portion 51 is provided on a side closer to the branch portion 50b than the shaft support portion 50c in the trunk portion 50a. 1.   The trunk portion 50a of the pressing member 50 is pivotally supported on the inner side from the outer periphery of the cylinder block 16, and parallel to the axis of the first slave cylinder 17A toward the inner pivot portion 50c of the cylinder block 16. The transmission mechanism with a twin clutch according to any one of claims 1 to 5, wherein the transmission mechanism is bent.   The speed change mechanism 1 with a twin clutch according to any one of claims 1 to 6, wherein a diameter of the first slave cylinder 17A is larger than a diameter of the second slave cylinder 17B.   A hydraulic pressure sensor 89 for detecting hydraulic pressure is provided in at least one of the first master cylinder 19A in which the first drive piston 22A is accommodated and the second master cylinder 19B in which the second drive piston 22B is accommodated. The speed change mechanism 1 with a twin clutch according to any one of claims 1 to 7.

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