JP5612876B2 - Clutch actuator - Google Patents

Description

  The present invention relates to a clutch actuator of a transmission with a twin clutch.

  In a vehicle having one clutch, a motor is provided in a clutch actuator, a crankshaft is provided on a worm wheel shaft connected to the motor, and an output rod (piston rod for generating hydraulic pressure) is provided on a crankpin connected to the crankshaft. In a system that connects and drives the output rod by driving the motor, an assist spring is attached to the crank arm in order to reduce the load on the motor of the clutch actuator and the operating force of the clutch lever in manual operation. A structure for assisting the stroke of the output rod by assisting the rotation of the crankshaft is disclosed (for example, see Patent Document 1).

  On the other hand, a twin clutch structure in which two clutches are operated by one motor is disclosed for the purpose of eliminating a complicated hydraulic system including a hydraulic pump or the like (see, for example, Patent Document 2). Even in this structure, it was desired to use the assist mechanism for the purpose of reducing the motor load and the clutch lever operating force. However, since the twin clutch structure has two clutch operating mechanisms, one clutch operating mechanism is required. Compared to the mechanism, the number of components increased, and the layout of the assist spring was limited.

JP 2007-285453 A (FIGS. 11 to 13) JP 2007-24079 A (FIGS. 1 to 3)

  The present invention provides a compact clutch actuator of a transmission with a twin clutch that has an assist spring but does not impose layout restrictions, in a twin clutch structure in which two clutches are operated by one motor. With the goal.

The present invention solves the above problems, and the invention according to claim 1
The first transmission (2A) and the second transmission (2B) having different transmission ratios are operated by the hydraulic pressure of the first master cylinder (19A), the input gear (15) and the first transmission (2A). The first clutch (3A) for connecting / disconnecting between the second gear and the second master cylinder (19B) is operated by the hydraulic pressure to connect / disconnect between the input gear (15) and the second transmission (2B). The clutch (3B), the first drive piston (22A) for operating the first clutch (3A) by pushing out the hydraulic fluid of the first master cylinder (19A), and the hydraulic fluid of the second master cylinder (19B) a second drive piston for operating the second clutch (3B) extruding the (22B), a cam body driven tilting by a motor (21) (63), when tilted in one, the first When the drive piston (22A) is driven to push the hydraulic fluid of the first master cylinder (19A) and tilts to the other , The second drive piston (22B), the cam member that presses the drive to push the hydraulic fluid in the second master cylinder (19B) and (63), in the clutch actuator of the twin clutch with transmission comprising,
A rotation shaft (61) that rotatably supports the cam body (63) for the tilting, and an assist that assists the tilting of the cam body (63) as the rotation shaft (61) rotates. A mechanism (91) and a load application point (B) at which a load applied by the assist mechanism (91) is transmitted to the rotating shaft (61), and at the neutral position of the cam body (63), the assist mechanism The load application point (B) and the center (C) of the rotation shaft (61) are arranged on the load application direction line of (91), and the assist mechanism (91) is a single mechanism, rotation shaft assisting the tilting of the with the rotation of (61) a first driving piston (22A) or the cam member or to perform one of the press drive of the second drive piston (22B) (63) Arranged such that the axis (D) of the first master cylinder (19A) and the second master cylinder (19B) and the axis (E) of the assist mechanism (91) are parallel, Times The assist mechanism (91) is disposed on the same side as the side on which the first and second master cylinders (19A, 19B) are located with respect to the rotation shaft (61) when viewed in the direction of the dynamic shaft (61). The clutch actuator is formed so as to be sandwiched between the first master cylinder (19A) and the second master cylinder (19B).

According to a second aspect of the present invention, in the clutch actuator according to the first aspect, a worm gear mechanism (20) is interposed between the motor (21) and the cam body (63), and the worm gear mechanism (20) Includes a worm wheel (58) on the rotation shaft (61), and the cam body (63) is stretched outside the outer diameter of the worm wheel (58) when viewed in the direction of the rotation shaft (61). It is formed so that it may come out.

According to a third aspect of the present invention, in the clutch actuator according to the first or second aspect, the assist mechanism (91) includes an assist spring (96) for assisting tilting of the cam body (63) and an assist spring support shaft ( 95), and the assist spring support shaft (95) has a telescopic structure that can be expanded and contracted.

According to a fourth aspect of the present invention, in the clutch actuator according to any one of the first to third aspects, the length from the rotating shaft (61) to the longitudinal end of the assist mechanism (91) is The first and second master cylinders (19A, 19B) are shorter than the length to the end in the longitudinal direction.

The invention according to claim 5 is the clutch actuator according to claim 1 , wherein a gear mechanism (20) is provided between the motor (21) and the cam body (63), and the assist mechanism (91) is provided. Is arranged on the opposite side of the gear mechanism (20) and the motor (21) across the cam body (63).

According to a sixth aspect of the present invention, in the clutch actuator according to any one of the first to fifth aspects, the reservoir tank is provided in the first and second master cylinders (19A, 19B) via a hose (86). A hydraulic oil supply port (83) coupled to (85), wherein the assist mechanism (91) and the hydraulic oil supply port (83) are orthogonal to the rotating shaft (61) and the first and first The side where the first and second master cylinders (19A, 19B) are provided with respect to the rotating shaft (61) in a side view in a direction perpendicular to the axis (D) of the two master cylinders (19A, 19B) The assist mechanism (91) and the hydraulic oil supply port (83) are formed on opposite sides of the first and second master cylinders (19A, 19B) in the side view. It is characterized by being.

According to the invention of claim 1,
With the above configuration, since the load application point and the center of the rotation shaft are arranged on the load application direction line of the assist mechanism at the neutral position of the cam body, it is possible to adopt the assist mechanism even in the twin clutch, The assist mechanism does not generate a rotational force with respect to the rotation shaft at the neutral position of the cam body, and evenly assists the first drive piston and the second drive piston when the rotation shaft rotates from the neutral position. Can do. An overall compact arrangement is obtained.

According to invention of Claim 2, a compact structure is obtained.

According to the invention of claim 3, it is possible to always assist in a stable direction.

According to the fourth aspect of the present invention, the assist mechanism can be prevented from projecting outward from the longitudinal ends of the first and second master cylinders, so that the assist mechanism can be operated without increasing the size of the clutch actuator. It can be provided compactly.

According to the fifth aspect of the present invention , since the surroundings of the gear mechanism and the mutual interference can be avoided as compared with the case where the gear mechanism and the motor are provided, the maintainability of the assist mechanism, the motor, etc. is improved.

According to the sixth aspect of the present invention, the assist mechanism and the hydraulic oil supply port are provided on the same side as the side on which the first and second master cylinders are provided with respect to the rotating shaft in a side view. Since the two master cylinders are formed on opposite sides of each other, the assist mechanism and the hydraulic oil supply port can be arranged compactly.

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. 3 is a cross-sectional side view of an assist mechanism 91. FIG. 3 is a cross-sectional front view of an assist mechanism 91. 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 mechanism 20, a control motor 21 that drives the worm gear mechanism 20, and a cam body that is tilt-driven by the worm gear mechanism 20. 63, and an assist mechanism 91 that assists the movement of the cam body 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 mechanism 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 drive piston 19A, 19B is driven by the worm gear mechanism 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 engaging groove G that engages with the shift fork F (FIG. 1) of the shift fork drive mechanism, and the slidable gear (subscript s) is provided by the shift fork F that engages with the groove. 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. 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.

  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 arranged on the end face of the cylindrical end portion 48Ad. The cylindrical end portions 48Ad are arranged at positions that are point-symmetric with respect to the center O of the cylindrical end portion 48Ad.

  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 mechanism 20 is provided in the main body case 55. The worm gear mechanism 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.

  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.

In FIG. 5, the appearance of the assist mechanism 91 is visible between the master cylinders 19A and 19B. The assist mechanism 91 is provided behind the master cylinders 19A and 19B.
In FIG. 6, the main body case 55 of the clutch actuator 5 includes a front case 55F and a rear case 55R. A crank arm 93 is fixed to the rear rotating shaft 61.

  FIG. 7 is a cross-sectional side view including the rotation shaft 61 and the axis E of the assist mechanism 91. The appearance of the first master cylinder 19A is visible beyond the assist mechanism 91. An assist mechanism case 92 is formed at the boundary between the front case 55F and the rear case 55R of the main body case 55 of the clutch actuator 5, and extends upward. A crank arm 93 and a crank pin 94 are provided on the rear rotating shaft 61. A spring support shaft 95 is provided in the assist mechanism case 92 between the arcuate recess 92 a on the ceiling of the assist mechanism case 92 and the crank pin 94. The spring support shaft 95 is a telescopic structure shaft that includes an upper member 95U and a lower member 95L. An assist spring 96 is mounted on the outer periphery of the spring support shaft 95 to urge the spring support shaft 95 in the extending direction.

  FIG. 8 is a front view of the assist mechanism 91. An arcuate portion 95Ua at the top of the upper member 95U of the spring support shaft 95 is inserted into an arcuate recess 92a on the ceiling of the assist mechanism case 92 and is rotatable. The crank pin 94 is inserted into the lower member 95L, and is prevented from coming off by a washer 97 and a split pin 98. The lower member 95L and the crank pin 94 are rotatable relative to each other.

  The center A of the arc portion 95Ua of the upper member 95U is a base point of the urging force of the assist spring 96. The center B of the crank pin 94 is the point of application of the urging force of the assist spring 96. The crank arm 93 is provided between the point B of the urging force of the assist spring 96 and the center C of the rotating shaft.

  In FIG. 8, at the neutral position of the cam body 63, the center A of the cylindrical portion of the upper member 95U, the urging force action point B of the assist spring 96, and the center C of the rotating shaft 61 are set to be in a straight line. This state is the neutral position of the assist mechanism. At this time, since the cam body 63 is also in the neutral position, no pressing force is applied to any of the drive pistons 22A and 22B. At this time, the urging force of the assist spring 96 does not act in the rotating direction of the rotating shaft 61.

  When the rotation shaft 61 starts to rotate in either the left or right direction, the urging force of the assist spring 96 acts in a direction to assist the rotation in response to this, and the driving force of the motor 21 and the cam body 63 are The pressing force applied to either of the drive pistons 22A and 22B is assisted. Since the cam body 63 and the assist mechanism 91 are in a neutral state at the same time, the first drive piston 22A and the second drive piston 22B can be equally assisted.

  The assist mechanism 91 is a single assist mechanism, and the cam body 63 is configured to press and drive either the first drive piston 22A or the second drive piston 22B as the rotation shaft 61 rotates. Since it assists, compared with the case where the assist mechanism for assisting the 1st drive piston 22A and the 2nd drive piston 22B is provided separately, it can assist a plurality of drive pistons with a single assist mechanism, and the number of parts Can be reduced.

  5 and 7, the axis D of the first master cylinder 19A and the second master cylinder 19B and the axis E of the assist mechanism 91 are arranged in parallel. Thereby, the assist mechanism 91 can be disposed without interfering with the master cylinders 19A and 19B.

  In FIG. 5, an assist mechanism 91 is arranged on the same side as the first and second master cylinders 19B with respect to the rotation shaft 61. Therefore, the clutch actuator mechanism is compactly formed.

  5 and 7, the assist mechanism 91 is formed so as to be sandwiched between the first master cylinder 19A and the second master cylinder 19B. An empty space between the first master cylinder 19A and the second master cylinder 19B is effectively utilized, and the assist mechanism 91 is arranged in a compact manner.

  In FIG. 5, the length from the rotating shaft 61 to the longitudinal end of the assist mechanism 91 is shorter than the length from the longitudinal end of the first and second master cylinders 19B. Therefore, the assist mechanism 91 can be prevented from projecting outward from the longitudinal ends of the first and second master cylinders 19B, and the assist mechanism 91 can be provided in a compact manner without increasing the size of the clutch actuator 5.

  In FIG. 7, the assist mechanism 91 is disposed on the opposite side of the worm gear mechanism 20 and the motor 21 with the cam body 63 interposed therebetween. Compared with the case where the assist mechanism 91 is provided on the worm gear mechanism 20 or the motor 21 side, the surroundings of the worm gear mechanism 20 and the mutual interference can be avoided, so that the maintenance of the assist mechanism 91, the motor 21 and the like can be avoided. Improves.

  6 and 7, the assist mechanism 91 and the hydraulic oil supply port 83 are provided in the same direction with respect to the rotating shaft 61, and the assist mechanism 91 and the hydraulic oil supply port 83 are provided in the first and second master cylinders. 19A and 19B are formed on opposite sides of each other. Therefore, the assist mechanism 91 and the hydraulic oil supply port 83 can be arranged in a compact manner.

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 rotationally driven in one direction, the worm gear mechanism 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. When the cam body 63 is rotated, the assist mechanism 91 assists the rotation of the rotation shaft 61 and the pressing force of the cam body 63. 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 mechanism 20 and the cam body 63 are rotated in the reverse direction, and the first drive piston 22A is pushed upward, and the hydraulic oil Is pressurized and the first passive piston 18A is pushed out. When the cam body 63 is rotated, the assist mechanism 91 assists the rotation of the rotation shaft 61 and the pressing force of the cam body 63. 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 neutral position of the assist mechanism 91 is such that when the cam body 63 is in the neutral state, the center A of the arc portion 95Ua at the top of the upper member 95U, the biasing action point B of the assist spring 96, and the rotation shaft 61 The center C is a position that is in a straight line. At this time, the urging force of the assist spring 96 does not act in the rotating direction of the rotating shaft 61. Therefore, this mechanism can equally assist the first drive piston 22A and the second drive piston 22B (FIGS. 7 and 8).
(2) The assist mechanism 91 is a single mechanism, and assists the cam body 63 so as to press and drive either the first drive piston 22A or the second drive piston 22B as the rotation shaft 61 rotates. Therefore, the number of parts can be reduced as compared with the case where the assist mechanism 91 is provided separately for the first drive piston 22A and the second drive piston 22B.
(3) The axis D of the first master cylinder 19A and the second master cylinder 19B and the axis E of the assist mechanism 91 are arranged in parallel. As a result, the assist mechanism 91 is disposed in these mechanisms without interfering with each other (FIGS. 5 and 7).
(4) Since the assist mechanism 91 is disposed on the same side as the first and second master cylinders 19A and 19B with respect to the rotation shaft 61, the clutch actuator 5 can be formed compactly (FIG. 5). ).
(5) The assist mechanism 91 is formed so as to be sandwiched between the first master cylinder 19A and the second master cylinder 19B. The vacant space between the master cylinders 19A and 19B is effectively utilized, and the assist mechanism is compactly arranged (FIGS. 5 and 7).
(6) The length from the rotating shaft 61 to the longitudinal end of the assist mechanism 91 is shorter than the length from the longitudinal end of the first and second master cylinders 19A and 19B. Therefore, the assist mechanism 91 can be prevented from projecting outward from the longitudinal ends of the master cylinders 19A and 19B, and the assist mechanism 91 can be provided in a compact manner without increasing the size of the clutch actuator 5 (FIG. 5). .
(7) The assist mechanism 91 is disposed on the opposite side of the worm gear mechanism 20 and the motor 21 with the cam body 63 interposed therebetween. Compared with the case where the assist mechanism 91 is provided on the worm gear mechanism 20 or the motor 21 side, it is possible to avoid complications around the worm gear mechanism 20 and mutual interference. Is improved (FIG. 7).
(8) The assist mechanism 91 and the hydraulic oil supply port 83 are provided in the same direction with respect to the rotation shaft 61, and the assist mechanism 91 and the hydraulic oil supply port 83 connect the first and second master cylinders 19A and 19B. They are formed on opposite sides of each other. Therefore, the assist mechanism 91 and the hydraulic oil supply port 83 can be arranged in a compact manner (FIGS. 6 and 7).

  2A ... 1st transmission, 2B ... 2nd transmission, 3A ... 1st clutch, 3B ... 2nd clutch, 5 ... Clutch actuator, 15 ... Input gear, 19A ... 1st master cylinder, 19B ... 2nd master cylinder, 20 ... Worm gear mechanism, 21 ... Control motor, 22A ... First drive piston, 22B ... Second drive piston, 61 ... Rotating shaft, 63 ... Cam body, 83 ... Hydraulic oil supply port, 85 ... Reservoir tank, 86 ... Hose 91: Assist mechanism, A: Base point, B: Action point, C: Center of rotation axis, D: Master cylinder axis, E: Assist mechanism axis.

Claims (6)

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) to connect and disconnect between the input gear (15) and the first transmission (2A);
A second clutch (3B) that is operated by the hydraulic pressure of the second master cylinder (19B) to connect and disconnect between the input gear (15) and the second transmission (2B);
A first drive piston (22A) that pushes out the hydraulic fluid of the first master cylinder (19A) and operates the first clutch (3A);
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 tilted by a motor (21) so that when it tilts to one side , the first drive piston (22A) pushes out the hydraulic fluid of the first master cylinder (19A). when you press drive, tilts in the other, a twin clutch including a second driving piston (22B), the cam member that presses the drive to push the hydraulic fluid in the second master cylinder (19B) and (63), the In the clutch actuator of the transmission with
A rotating shaft (61) that rotatably supports the cam body (63) for the tilting;
An assist mechanism (91) for assisting the tilting of the cam body (63) with the rotation of the rotation shaft (61);
A load application point (B) at which a load by the assist mechanism (91) is transmitted to the rotating shaft (61),
At the neutral position of the cam body (63), the load application point (B) and the center (C) of the rotation shaft (61) are arranged on the load application direction line of the assist mechanism (91),
The assist mechanism (91) is a single mechanism, one of said first driving piston in accordance with the rotation of the pivot shaft (61) (22A) or said second driving piston (22B) It is configured to assist the tilting of the cam body (63) to perform a pressing drive,
The axis (D) of the first master cylinder (19A) and the second master cylinder (19B) and the axis (E) of the assist mechanism (91) are arranged in parallel,
When viewed in the direction of the rotation axis (61), the assist mechanism (91) moves to the same side as the side where the first and second master cylinders (19A, 19B) are located with respect to the rotation axis (61). A clutch actuator characterized in that it is disposed and is sandwiched between the first master cylinder (19A) and the second master cylinder (19B). A worm gear mechanism (20) is interposed between the motor (21) and the cam body (63), and the worm gear mechanism (20) includes a worm wheel (58) on the rotating shaft (61). ,
The clutch actuator according to claim 1, wherein the cam body (63) is formed so as to project outward from the outer diameter of the worm wheel (58) when viewed in the direction of the rotation shaft (61).   The assist mechanism (91) includes an assist spring (96) for assisting tilting of the cam body (63) and an assist spring support shaft (95), and the assist spring support shaft (95) is a telescopic structure that can be expanded and contracted. The clutch actuator according to claim 1 or 2, wherein:   The length from the rotating shaft (61) to the longitudinal end of the assist mechanism (91) is shorter than the length from the longitudinal end of the first and second master cylinders (19A, 19B). The clutch actuator according to any one of claims 1 to 3, wherein A gear mechanism (20) is provided between the motor (21) and the cam body (63),
The clutch actuator according to claim 1, wherein the assist mechanism (91) is disposed on the opposite side of the gear mechanism (20) and the motor (21) across the cam body (63). . A hydraulic oil supply port (83) provided in the first and second master cylinders (19A, 19B) and connected to a reservoir tank (85) via a hose (86);
The assist mechanism (91) and the hydraulic oil supply port (83) are orthogonal to the rotating shaft (61) and are orthogonal to the axis (D) of the first and second master cylinders (19A, 19B). As viewed from the side, the assist shaft (91) and hydraulic fluid are provided on the same side as the first and second master cylinders (19A, 19B) with respect to the pivot shaft (61). The supply port (83) is formed on the opposite side of the first and second master cylinders (19A, 19B) in the side view, respectively. Clutch actuator.

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