JP4805754B2 - Clutch device - Google Patents

Description

  The present invention relates to a clutch device suitable for motorcycles (motorcycles) and the like, and more specifically, the clutch mechanism is disengaged using clutch operating hydraulic pressure generated in response to manual operation of a clutch lever by a rider (driver). The present invention relates to a clutch device configured to perform a contact operation.

  2. Description of the Related Art In a motorcycle or the like, a configuration in which a clutch lever that is manually operated is provided on the left side of an operation handle and a rider grips the clutch lever with the left hand to perform connection / disconnection operation of the clutch mechanism is generally used. In such a clutch device, the clutch mechanism is normally connected by receiving a spring force or the like, and the rider holds and operates the clutch lever with a hand at the start and at the time of shifting to release and connect the clutch mechanism. The operation to let you do. For this reason, it is necessary to have the gripping force necessary to release the spring against the spring force that connects the clutch mechanism, and it is difficult for female riders who have a small gripping force to operate. There is a problem that the left hand performing the clutch operation tends to get tired. This problem tends to be prominent in large motorcycles that require a large clutch capacity and a large clutch connection force.

  For this reason, for example, Patent Document 1 discloses a configuration in which a device for assisting operation of a clutch lever for releasing a clutch mechanism is provided. In this assist device, pressure oil that forcibly lubricates the inside of the engine is applied to the plunger, and a pusher rod for releasing the clutch mechanism is pressed to the release side by this plunger, and the assist force to the release side (i.e., The assisting force to the side where the clutch lever is gripped is obtained.

JP-A-8-133169

  Although the above-described problem can be reduced by using the assist device in this way, the assist device disclosed in Patent Document 1 is configured to obtain the assist force using the lubricating pressure of the engine, and the engine rotation, oil temperature Since the assist force fluctuates under the influence of the above, there are problems that it is difficult to obtain a stable assist force and that it is difficult to stably supply the assist force requested by the rider.

  In view of such problems, an object of the present invention is to provide a clutch device including an assist device having a configuration capable of always providing a stable assist force without being affected by external conditions or the like.

The clutch device according to the present invention includes a clutch mechanism that is provided in a power transmission path that transmits the rotational driving force of the engine to the wheels, and that connects and disconnects the transmission of the rotational driving force. A clutch actuator that is connected to the clutch, a clutch lever that is provided on the operating handle and is operated by a driver, and the clutch operating hydraulic pressure that is operated in response to the operation of the clutch lever and is supplied to the clutch actuator. An assist hydraulic pressure generated by the assist pressure generating device is configured to include a clutch operating hydraulic pressure generating device that is generated and an assist pressure generating device that is electrically driven according to the operation of the clutch lever to generate an assist hydraulic pressure. was supplied to the clutch hydraulic oil pressure generating device, the assist hydraulic and assist force Used by the clutch hydraulic pressure generating device in response to the operation of the clutch lever is adapted to generate the clutch hydraulic pressure.

The assist pressure generator includes an electric motor, an assist crankshaft that is rotationally driven by the electric motor, and an assist master cylinder, and the crank of the assist crankshaft that is rotationally driven by the electric motor. A lever rotation sensor that detects the amount of rotation of the clutch lever by rotating the piston member of the assist master cylinder when the piston member of the assist master cylinder is reciprocated in the cylinder chamber. A crank rotation sensor for detecting the amount of rotation, and receiving the rotation amount information of the assist crankshaft detected by the crank rotation sensor as feedback information, while adjusting the operation amount of the clutch lever detected by the lever rotation sensor. Based on Drive control of the electric motor is performed, and the clutch operating oil pressure generator is connected to the clutch lever and is connected to the clutch master cylinder that generates the clutch operating oil pressure in conjunction with the clutch lever. A clutch operating hydraulic path that separately connects an assist slave cylinder that applies the assist force to the operation of the clutch lever, and that connects a hydraulic chamber of the clutch master cylinder and a hydraulic chamber of the clutch actuator; An assist hydraulic path connecting the hydraulic chamber of the assist slave cylinder and the hydraulic chamber of the assist master cylinder is configured as an independent hydraulic path.

  In this case, the assist pressure generating device is configured to receive a rotational driving force by the electric motor on one end side of the assist crankshaft and to detect rotation by the crank rotation sensor on the other end side. Is preferred.

In the clutch device of the present invention, a gain adjusting device that adjusts the driving force generation gain characteristic of the electric motor and a gain setting unit that variably sets the driving force generation gain characteristic by an external operation are provided. The adjustment device is preferably configured to perform drive control of the electric motor in accordance with the operation of the clutch lever using a gain characteristic set by an external operation of the gain setting means.
Furthermore, it is preferable that the clutch master cylinder and the assist slave cylinder are arranged in parallel with each other on the facing side of the clutch lever.
In addition, a knocker member that is rotated by receiving an operation of the clutch lever is provided, a first connecting rod connected to a piston of the assist slave cylinder is provided at one end of the knocker member, and the other end is provided with the first connecting rod. It is preferable that a second connecting rod connected to the piston of the clutch master cylinder is provided.
Furthermore, it is preferable that the lever rotation sensor for detecting the rotation operation amount of the clutch lever is provided on the rotation shaft of the knocker member.
Moreover, it is preferable to comprise a reservoir tank provided in the assist master cylinder and supplying hydraulic oil to the hydraulic chamber of the assist master cylinder.

  According to the clutch device of the present invention configured as described above, the assist pressure generating device is electrically driven according to the operation of the clutch lever to generate assist hydraulic pressure, and this assist hydraulic pressure is supplied to the clutch pressure generating device. Since the clutch operating oil pressure is generated by the clutch operating oil pressure generator in response to the operation of the clutch lever, the clutch lever operating force is first generated by using the assist force by the assist oil pressure. This makes it possible to reduce the fatigue of the left hand that performs the clutch operation even in a driving operation that requires frequent clutch operation. In particular, since the assist hydraulic pressure is generated by being electrically driven according to the operation of the clutch lever, a stable assist force can be supplied without being affected by external conditions such as engine rotation and oil temperature. The assist power required by the rider can be supplied stably.

Further, the piston member of the assist master cylinder is reciprocated in the cylinder chamber by driving the electric motor to generate assist hydraulic pressure, and the rotation amount information of the assist crankshaft detected by the crank rotation sensor is used as feedback information. In this configuration , the drive control of the electric motor is performed based on the operation amount of the clutch lever detected by the lever rotation sensor , so that the assist hydraulic pressure (that is, the assist force) that accurately corresponds to the operation of the clutch lever is generated. It is possible to control the clutch operating force with high accuracy.

  In this case, if one end side of the assist crankshaft is rotationally driven by the electric motor and the rotation detection by the crank rotation sensor is performed on the other end side, the rotation detection of the crank rotation sensor is affected by the twist of the crankshaft. It is difficult to detect the rotation accurately, and control to set the clutch operating force with higher accuracy is possible.

  In this clutch device, if the gain adjusting device is configured to control the drive of the electric motor in accordance with the operation of the clutch lever using the gain characteristic set by the external operation of the gain setting means, the rider can It becomes possible to set operating force characteristics according to preference.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. FIG. 2 shows the overall appearance of a motorcycle including the clutch device according to the embodiment of the present invention. The motorcycle includes a main frame MF, a front fork FF attached to a front end portion of the main frame MF so as to be rotatable (steerable) about an axis extending obliquely up and down, and rotatable to a lower end of the front fork FF. The attached front wheel FW, the steering handle SH attached to the upper end of the front fork FF to the left and right, and the upper part of the front fork FF are covered from the front side and the left and right sides to the front of the main frame MF. The attached front cover FC, the swing arm SA pivoted to the rear of the main frame MF and extending rearward and swingable up and down, the rear wheel RW rotatably attached to the rear end of the swing arm SA, etc. It is configured with. A fuel tank FT, a rider's seat RS, an exhaust muffler EM, and the like are provided on the main frame MF as shown in the figure.

  Furthermore, a power unit (not shown) that is located in the internal space covered by the front cover FC and is integrated with the engine and the transmission is attached. FIG. 3 shows a part of the transmission TM constituting the power unit (the part on the input shaft side where the engine rotation is input via the clutch CL). In the transmission TM, a plurality of drive gears 4 are disposed on an input shaft 2 rotatably supported by a housing HG via bearings 3a and 3b, and these drive gears 4 are rotatably supported by the housing HG. The gear train is configured to mesh with a plurality of driven gears (not shown) disposed on an output shaft (not shown), and to transmit power by a transmission mechanism (not shown). An engine drive gear 1 which is coaxially connected to the input shaft 2 and meshes with a gear provided on the crankshaft of the engine to transmit the rotation of the engine and is driven to rotate, and a clutch which connects and disconnects the engine drive gear 1 and the input shaft 2. A mechanism CL is arranged.

  The clutch mechanism CL is coupled to the engine drive gear 1 and rotates integrally therewith, the driven member 12 that is spline coupled to the input shaft 2 and integrally rotated, and moves in the axial direction along the inner periphery of the drive material 11. A plurality of separator plates 13 that are attached so as to rotate integrally and are movable in the axial direction along the outer periphery of the driven member 12 and are attached so as to rotate integrally, and are sandwiched between the separator plates 13. The friction plate 14 is configured to have a pressing member 15 which is attached to the side end of the driven member 12 by being pressed to the left in FIG. 3 by a pressing spring 16 held by a bolt 16a.

  On the outer peripheral side, the pressing member 15 is opposed to the separator plate 13 and the friction plate 14 in the axial direction, receives the urging force of the pressing spring 16 and presses both the plates 13 and 14 to the left in the axial direction, and frictionally engages them. Combine. As a result, the engine rotational driving force transmitted to the engine drive gear 1 is transmitted from the drive member 11 to the driven member 12 via both plates 13 and 14 frictionally engaged, and the input shaft 2 is rotationally driven. The rotation of the input shaft 2 is shifted by the above-described transmission TM, transmitted to the rear wheel RW via a chain mechanism (not shown), etc., the rear wheel RW is driven to rotate, and the motorcycle is driven to travel.

  Thus, the clutch mechanism CL is normally configured to be connected using the urging force of the pressing spring 16. Then, the clutch mechanism CL is released by the rider performing an operation of gripping and pulling the clutch lever 5 with the left hand applied to the left hand grip 6 of the steering handle SH, and the rotation from the engine drive gear 1 to the input shaft 2. It is comprised so that driving force transmission may be interrupted | blocked. The configuration of the clutch device for causing the clutch mechanism CL to be connected and disconnected in this way will be described below.

  To release the clutch mechanism CL, the pressing member 15 is moved in a direction opposite to the urging direction of the pressing spring 16 (right direction in FIG. 3) to release the force that presses the separator plate 13 and the friction plate 14. The frictional engagement may be released. As a configuration for performing this operation, a receiving member 17 is disposed on the inner peripheral portion of the pressing member 15 via a bearing 17a, and extends in the communication hole 2a penetrating along the central axis of the input shaft 2. The tip of the push rod 18 disposed in contact with the receiving member 17 is in contact with the receiving member 17. Note that the proximal end of the push rod 18 is in contact with a clutch slave piston 23 constituting the clutch slave cylinder 21. A configuration including the clutch slave cylinder 21, the push rod 18 and the receiving member 17 is referred to as a clutch actuator 20.

  The clutch slave cylinder 21 is formed by being surrounded by a clutch slave cylinder case 22, a clutch slave piston 23 fitted and disposed in a cylinder hole of the clutch slave cylinder case 22, and the clutch slave piston 23 in the cylinder hole. And a spring 25 disposed in the clutch slave hydraulic chamber 24. The clutch slave cylinder case 22 is provided with an inlet port 24a communicating with the clutch slave hydraulic chamber 24. The clutch slave cylinder 21 receives the clutch operating oil pressure supplied from the inlet port 24a via the clutch operating oil pressure line 27 as a clutch slave. It is received in the hydraulic chamber 24. When the clutch operating hydraulic pressure is thus supplied into the clutch slave hydraulic chamber 24, the clutch slave piston 23 is pressed and moved in the axial direction, and the push rod 18 is pressed and moved in the right direction in FIG. As a result, the push rod 18 can press and move the receiving member 17 in the right direction to release the clutch mechanism CL as described above. The spring 25 is for eliminating play of the push rod 18 in a state where the clutch operating hydraulic pressure is not supplied.

  Next, an apparatus configuration for supplying clutch operating oil pressure to the clutch operating oil pressure line 27 will be described with reference to FIG. This device includes a clutch operating oil pressure generating device 50 that generates a clutch operating oil pressure in response to an operation of the clutch lever 5, and this clutch operating oil pressure generating device 50 operates in conjunction with the operation of the clutch lever 5 to operate the clutch. A clutch master cylinder 70 that generates hydraulic pressure and an assist slave cylinder 60 that applies assist force to the operation of the clutch lever 5 are provided. Further, the assist slave cylinder 60 is provided with an assist pressure generating device 30 that generates assist hydraulic pressure for operating the assist slave cylinder 60. As shown in FIG. 2, the assist pressure generating device 30 is located on the inner side of the front cover FC and is attached to the main frame MF, and the clutch operating oil pressure generating device 50 is in the vicinity of the hand grip 6 on the left side of the steering handle SH. It is arranged.

  First, the configuration and operation of the assist pressure generator 30 will be described with reference to FIGS. The assist pressure generator 30 includes an electric motor 31, a gear box 32 that transmits the rotational driving force of the electric motor 31, and a crankshaft 34 that is rotationally driven by receiving the rotational driving force of the electric motor 31 via the gear box 32. A crankcase 33 having a crankcase 33, a first rotation angle sensor 39 attached to the crankcase 33 opposite to the gear box 32, and an assist master cylinder 40 extending upward from the center of the crankcase 33. And a reservoir tank 45 connected to the assist master cylinder 40 via a pipe 45a.

  As shown in FIG. 1, a worm pinion 32 a that is rotationally driven by an electric motor 31 and a worm wheel 32 b that meshes with the worm pinion 32 are disposed inside the gear box 32. A crankshaft 34 is rotatably supported in the crankcase 33 by bearings 36a and 36b, and a worm wheel 32b is attached to one end of the crankshaft 34. For this reason, if the electric motor 31 is rotationally driven, the crankshaft 34 is rotationally driven via the worm pinion 32a and the worm wheel 32b. However, in practice, the electric motor 31 is driven forward and backward, and the crankshaft 34 is driven to reciprocate. A first rotation angle sensor 39 is attached to the other end side of the crankshaft 34 (on the side opposite to the attachment portion of the worm wheel 32b), and the rotation angle of the crankshaft 34 is detected. Since the rotation angle of the crankshaft 34 is detected in the portion of the crankshaft 34 that does not receive the rotational driving torque of the electric motor 31 by being attached to the opposite side of the attachment portion of the worm wheel 32b in this way, the crankshaft 34 can be accurately detected. The rotation angle can be detected.

  The crankshaft 34 includes a crank portion 35 having an eccentric shaft portion 35a straddling a pair of left and right eccentric arms 35b, 35b, and a cylindrical abutting member rotatably on the eccentric shaft portion 35a via a bearing. 35c is attached (see FIG. 7). Furthermore, as shown in FIGS. 6 and 8, the eccentric rubber 35b on one side is surrounded obliquely from the left and right, and a stopper rubber base 37 having a letter "" "in a side view made of an elastic material (for example, made of rubber) is a crankcase. 33. The stopper rubber base 37 is provided with a downward movement restricting stopper 38a and an upward movement restricting stopper 38b made of an elastic material (for example, made of rubber) as shown in the figure, and the eccentric shaft 35b of the crankshaft 34 is moved downward. A reciprocating rotational movement can be performed between a position in contact with the stopper 38a and a position in contact with the upward movement stopper 38b.

  The assist master cylinder 40 is integrally coupled with the crankcase 33 and extends upward, an assist master piston 42 fitted and disposed in a cylinder hole of the assist master cylinder case 41, a cylinder A push-down spring 44 disposed in an assist master hydraulic chamber 43 formed by being surrounded by the assist master piston 42 in the hole is configured. As shown in FIGS. 6 and 7, the lower end of the piston rod 42a that is integrally connected to the assist master piston 42 and extends downward is in contact with a cylindrical contact member 35c that is rotatably attached to the eccentric shaft 35a. . The reservoir tank 45 is connected to an intermediate portion of the assist master cylinder case 41 at the opening ports 45b and 45c through a pipe 45a. Therefore, the hydraulic oil in the reservoir tank 45 can be supplied into the cylinder hole via the opening ports 45b and 45c.

  In the assist master cylinder 40 configured in this manner, when the crankshaft 34 is rotationally driven by the electric motor 31 to a position where it comes into contact with the downward movement restricting stopper 38 a, the assist master piston 42 is cylindrical due to the urging of the push-down spring 44. The assist master piston 42 is moved downward while in contact with the contact member 35c, the upper end of the assist master piston 42 is positioned below the opening ports 45b and 45c of the pipe 45a, and the assist master hydraulic chamber 43 is connected to the reservoir tank 45 via the pipe 45a. Communicate with. As a result, the hydraulic oil in the reservoir tank 45 is supplied into the assist master hydraulic chamber 43.

  When the electric motor 31 is driven in reverse from this state and the crankshaft 34 is driven to rotate in the reverse direction, the cylindrical contact member 35c pushes up the assist master piston 42 and resists the bias of the spring 44. 42 is moved up. Due to this upward movement, since the upper end of the piston 42 is only in communication from the position where the upper end of the piston 42 is blocked to the opening port 45b through the opening port 45c made of a small hole, the hydraulic oil in the assist master hydraulic chamber 43 is gently It is compressed and begins to be boosted. Then, the hydraulic oil in the assist master hydraulic chamber 43 is compressed in response to the upward movement of the piston 42 from a state where the upper end of the piston 42 is positioned so as to block the opening port 45c.

  When the hydraulic oil in the assist master hydraulic chamber 43 is compressed in this way, the hydraulic oil in the assist master hydraulic chamber 43 is supplied to the assist slave cylinder 60 via the assist hydraulic line 47. Therefore, the configuration of the clutch hydraulic pressure generator 50 having the assist slave cylinder 60 and the clutch master cylinder 70 will be described below with reference to FIGS. 9 to 12 in addition to FIG.

  The assist slave cylinder 60 includes an assist slave cylinder case 61 fixed to the left side of the steering handle SH, an assist slave piston 62 fitted and disposed in a cylinder hole of the assist slave cylinder case 61, and an assist slave piston. 62 is configured to include a first spring 64 that biases rightward in FIGS. 1, 10, and 11. In the cylinder hole, an assist slave hydraulic chamber 63 is formed surrounded by the assist slave piston 62, and this is connected to the assist hydraulic line 47 via the connection port 63a. It is adapted to be received in the assist slave hydraulic chamber 63.

  The clutch master cylinder 70 includes a clutch master cylinder case 71 fixed to the left side of the steering handle SH, a clutch master piston 72 fitted and disposed in a cylinder hole of the clutch master cylinder case 71, and a clutch master piston. 72 is configured to include a second spring 74 that urges leftward in FIGS. 1, 10, and 11. A clutch master hydraulic chamber 73 is formed in the cylinder hole and surrounded by the clutch master piston 72, and is connected to the clutch operating hydraulic line 27 via a connection port 73a.

  The assist slave cylinder case 61 and the clutch master cylinder case 71 are integrally formed and fixed to the steering handle SH, and the clutch lever 5 and the knocker 51 are rotatably attached thereto by pins 51a. The clutch lever 5 is operated so that the rider holds it with his left hand, and is rotated in the direction indicated by the arrow A in the figure. 10 shows a non-operating state (clutch engaged state) of the clutch lever 5, and FIG. 11 shows a state where the clutch lever is operated in the arrow A direction (clutch releasing operation state). As shown in FIG. 12, the knocker 51 is rotatably attached to the lower side of the clutch lever 5 independently of the knocker 51. However, the knocker 51 is provided with an engaging projection 51b protruding upward, and as shown in FIGS. 10 and 11, when the clutch lever 5 is rotated in the direction of arrow A, the clutch lever 5 is The knocker 51 is also rotated together in contact with the engaging protrusion 51b.

  A first connecting rod 65 is connected to one end portion 52 and a second connecting rod 75 is connected to the other end portion 53 with the knocker 51 centered on a pivoting portion formed by a pin 51 a. The first connecting rod 65 has a distal end portion 65 a that enters into the proximal end side recessed portion 62 a of the assist slave piston 62 and comes into contact therewith, and the proximal end portion 65 b is connected to one end portion 52 of the knocker 51. A connection structure between the one end portion 52 of the knocker 51 and the base end portion 65b of the first connecting rod 65 will be described with reference to FIGS.

  A through hole 52a penetrating vertically is formed in one end portion 52 of the knocker 51, and a mounting hole 52b and a mounting slot 52c extending through the through hole 52a from the side surface side are integrally formed. On the other hand, a retaining ring 66 is attached to the outer periphery of the base end portion 65b of the first connecting rod 65, and its outer diameter d is slightly smaller than the inner diameter of the mounting hole 52b, but larger than the width W of the mounting slot 52c. Yes. Therefore, if the base end portion 65b of the first connecting rod 65 is inserted into the mounting hole 52b, the retaining ring 66 can be inserted together as shown in FIG. 15, and the end surface of the base end portion 65b is inserted into the through hole 52a. If it is inserted until it abuts, the retaining ring 66 enters the through hole 52a. In this state, if the first connecting rod 65 is rotated about the base end portion 65b as shown by the arrow B, the retaining ring 66 is rotated while being in the through hole 52a, and is placed inside the mounting slot 52c. It is positioned and cannot be pulled out, and is engaged with one end 52 of the knocker 51. However, the first connecting rod 65 can be rotated within a predetermined angle range in a state in which the first connecting rod 65 is positioned in the mounting slot 52c while being engaged in this manner.

  The second connecting rod 75 has a distal end portion 75 a that enters the proximal end side concave portion 72 a of the clutch master piston 72 and comes into contact therewith, and a proximal end portion 75 b is connected to the other end portion 53 of the knocker 51. . However, the other end portion 53 of the knocker is only formed with a through hole 53a penetrating vertically and a mounting slot 53b extending from the side surface to the through hole 53a, and the base end portion 75b of the second connecting rod 75 is formed. Is configured to be inserted from the mounting slot 53b and to be in contact with the through hole 53a.

  As can be seen from FIG. 12, the second rotation angle sensor 57 is attached concentrically to the lower end of the pin 51a. A rotating arm 57b is integrally attached to the rotating portion 57a, and this is engaged with an engaging rod 55 protruding downward from the lower surface of the clutch lever 5. For this reason, when the clutch lever 5 is operated and rotated around the pin 51 a, the rotating portion 57 a rotates in the same manner via the engagement rod 55, and the operation angle of the clutch lever 5 is detected by the second rotation angle sensor 57. It can be done.

  In the above configuration, as shown in FIG. 1, the drive of the electric motor 31 is controlled based on a control signal sent from the control unit 90 via the drive control line 95. The rotation angle detection signal of the crankshaft 34 from the first rotation angle sensor 39 and the clutch lever operation angle signal from the second rotation angle sensor 57 are input via signal lines 90a and 90b. Further, an assist force setting knob (gain adjustment knob) 91 is provided at a position where the rider can operate in the motorcycle, and the assist force can be set in four stages of 0 to 3 by manual operation. The assist force setting signal is also sent to the control unit 90 via the signal line 90c. The assist force setting is such that no assist force is applied at “0 level”, and the assist force is gradually increased from “1 level” to “3 level”.

  In the clutch device configured as described above, an operation associated with the operation of the clutch lever 5 will be described with reference to FIG. FIG. 16 is a graph showing the time change of the values indicated by A to E. The value A shows the time change of the operation amount of the clutch lever 5 detected by the second rotation angle sensor 57, and the value B shows the assist force. The time change of the hydraulic pressure generated in the clutch slave hydraulic chamber 24 of the clutch slave cylinder 21 (that is, the hydraulic pressure supplied via the clutch operating hydraulic pressure line 27) when there is no noise (that is, when the electric motor 31 is not driven). The value C indicates the time change of the rotation amount of the crankshaft 34 detected by the first rotation angle sensor 39 when the electric motor 31 is driven, and the value D indicates the assist slave hydraulic chamber 63 of the assist slave cylinder 60. The time change of the internal hydraulic pressure (that is, the hydraulic pressure supplied via the assist hydraulic pressure line 47), and the value E indicates the assist slave series. Shows the time change of the hydraulic pressure of the clutch slave hydraulic chamber 24 of the clutch slave cylinder 21 (i.e., the hydraulic pressure supplied through the clutch hydraulic pressure line 27) at the time when receiving the assisting force from da 60.

  First, the operation when the assist force setting knob 91 is set to “0 level”, that is, the setting not to apply the assist force will be described. When the clutch lever 5 is operated at this set level and rotated in the direction of arrow A, it abuts on the engaging protrusion 51b and the knocker 51 is also rotated together. The rotation angle of the clutch lever 5 is detected by the second rotation angle sensor 57, and the detected signal information is input to the control unit CU via the signal line 90b. Therefore, for example, when the clutch lever 5 changes as indicated by a value A in FIG. 16, that is, the operation is started from time t0, the operation is slightly returned from time t4 to t5, and the time t5 to t6 is constant. In the following, a case where an operation that is held and is released gradually from time t6 to t10 will be described.

  In this case, since the “0 level” signal from the assist force setting knob 91 is also input via the signal line 90 c, the control unit CU ignores the rotation angle signal of the clutch lever 5. This is held stationary without sending a drive signal to the electric motor 31. Therefore, no assist hydraulic pressure is supplied from the assist master cylinder 40 to the assist slave cylinder 60, and the assist slave piston 62 is moved to the right by the bias of the first spring 64 as shown in FIG. Held in. As a result, the values C and D shown in FIG. 16 do not occur, and the value E corresponds to the value B as it is.

  Since the “0 level” is set as described above, when the knocker 51 rotates in accordance with the operation of the clutch lever 5, the first connecting rod 65 moves together with it as shown in FIG. No assist force from 60 is received. On the other hand, the second connecting rod 75 presses and moves the clutch master piston 72 in the right direction against the bias of the second spring 74 in accordance with the rotation of the knocker 51. As a result, the hydraulic oil in the clutch master hydraulic chamber 73 is compressed and pushed out to the clutch hydraulic pressure line 27, and the hydraulic oil is supplied into the clutch slave hydraulic chamber 24 of the clutch slave cylinder 21. At this time, since an operation delay (time t0 to t3) is generated by an invalid stroke (play) in the clutch master cylinder 70 and the clutch slave cylinder 21, the hydraulic pressure in the clutch slave hydraulic chamber 24 is as indicated by a value B in FIG. The change starts at time t3 and ends at time t7. As a result, as described above, the push rod 18 is pushed by the clutch slave piston 23 to release the clutch mechanism CL. Thus, in a state where “0 level” is set by the assist force setting knob 91, the clutch mechanism CL is released only by the operating force of the clutch lever 5.

  Next, an operation when any one of “1 to 3 levels” is set by the assist force setting knob 91 will be described. When the clutch lever 5 is operated at this set level and rotated in the direction of arrow A, the rotation angle is detected by the second rotation angle sensor 57, and changes as indicated by the value A in FIG. The detection signal information is input to the control unit CU via the signal line 90b. At this time, the control unit CU sends a drive signal to the electric motor 31 in accordance with the rotation angle signal of the clutch lever 5 input in this way, and rotationally drives it. As a result, the crankshaft 34 is rotated as indicated by a value C in FIG. At this time, a slight time delay occurs between times t0 and t1. In accordance with the rotational drive of the crankshaft 34, the assist master piston 42 of the assist master cylinder 40 is moved up and down, and the assist hydraulic pressure indicated by the value D in FIG. At this time, a time delay (time t0 to t2) corresponding to the invalid stroke (play) from the electric motor 31 to the assist master piston 42 occurs.

  The rotation angle of the crankshaft 34 at this time is detected by the first rotation angle sensor 39, and the detection signal is sent to the control unit CU via the signal line 90a. Receiving this, the control unit CU calculates the actual rotational angle position of the crankshaft 34 and corrects the drive of the electric motor 31. That is, using the signal from the first angle sensor 39 as feedback information, drive control of the electric motor 31 is performed so that an accurate assist force according to the operation of the clutch lever 5 is obtained.

  When the electric motor 31 is driven in this way and assist hydraulic pressure is supplied from the assist master cylinder 40 to the assist slave cylinder 60, the assist slave piston 62 is moved to the left in FIG. One end 52 of the knocker 51 is pressed in the left direction through the rod 65. This pressing force becomes a force assisting the operation of the clutch lever 5, and as a result, a value corresponding to the assist hydraulic pressure indicated by the value D is added to the clutch lever operating force when there is no assist force indicated by the value B in FIG. The hydraulic pressure indicated by E is supplied into the clutch slave hydraulic chamber 24, and the operation of the clutch lever 5 is reduced. In the value E, the hatched portion corresponds to the value B.

  In this case, the control unit CU changes the drive control content of the electric motor 31 according to the set level, and performs gain adjustment of the assist force corresponding to the operation of the clutch lever 5. Specifically, the drive control of the electric motor 31 is performed so that the gain is reduced at the setting level 1 to keep the assist force relatively small, and the gain is increased at the setting level 3 to increase the assist force.

1 is a schematic diagram illustrating an overall configuration of a clutch device according to an embodiment of the present invention. It is a side view which shows the whole external appearance of the motorcycle provided with the said clutch apparatus. It is sectional drawing which shows a part of structure of the power unit with which the said motorcycle is provided. It is a front view which shows the external appearance of the assist pressure generator which comprises the said clutch apparatus. It is a perspective view which shows the external appearance of the said assist pressure generator. It is a perspective view which shows the internal structure of the said assist pressure generator. It is sectional drawing which shows the internal structure of the said assist pressure generator. It is sectional drawing which shows the internal structure of the said assist pressure generator. It is a top view which shows the external appearance of the clutch hydraulic pressure generator which comprises the said clutch apparatus. It is sectional drawing which shows the internal structure of the said clutch action hydraulic pressure generator. It is sectional drawing which shows the internal structure of the said clutch action hydraulic pressure generator. It is a perspective view which shows the internal structure of the said clutch action hydraulic pressure generator. It is sectional drawing explaining the connection structure of the knocker and connection rod which comprise the said clutch action hydraulic pressure generator. It is a side view which shows the shape of the attachment hole and attachment slot which were formed in the said knocker. It is sectional drawing explaining the connection structure of the knocker and connection rod which comprise the said clutch action hydraulic pressure generator. It is a graph which shows the time change of value AE.

Explanation of symbols

CL clutch mechanism 2 input shaft 5 clutch lever 6 grip 18 push rod 20 clutch actuator 21 clutch slave cylinder 27 clutch operating hydraulic line 30 assist pressure generator 31 electric motor 34 crankshaft 39 first rotation angle sensor 40 assist master cylinder 45 Reservoir tank 47 Assist hydraulic line 50 Clutch operating hydraulic pressure generator 51 Knocker 57 Second rotation angle sensor 60 Assist slave cylinder 65 First connecting rod 70 Clutch master cylinder 75 Second connecting rod 90 Control unit 91 Assist force setting knob

Claims (7)

A clutch mechanism (CL) which is provided in a power transmission path for transmitting the rotational driving force of the engine to the wheels (RW) and which connects and disconnects the transmission of the rotational driving force;
A clutch actuator (20) for receiving and supplying a clutch operating hydraulic pressure to cause the clutch mechanism (CL) to be connected and disconnected;
A clutch lever (5) provided on the operation handle (SH) and operated by the driver;
A clutch operating oil pressure generator (50) that is operated in response to an operation of the clutch lever (5) and generates the clutch operating oil pressure supplied to the clutch actuator (20) ;
An assist pressure generator (30) that is electrically driven in response to an operation of the clutch lever (5) to generate assist hydraulic pressure;
The assist pressure generator (30) includes an electric motor (31), an assist crankshaft (34) rotated by the electric motor (31), and an assist master cylinder (40). The piston member (42) of the assist master cylinder (40) is reciprocated in the cylinder chamber (41) by being driven by a crank portion (35) of the assist crankshaft (34) that is rotationally driven by a motor (31). The assist hydraulic pressure is generated,
A lever rotation sensor (57) for detecting the amount of rotation of the clutch lever (5); and a crank rotation sensor (39) for detecting the amount of rotation of the assist crankshaft (34). Based on the operation amount of the clutch lever (5) detected by the lever rotation sensor (57) while receiving the rotation amount information of the assist crankshaft (34) detected by (39) as feedback information. Drive control of the electric motor (31) is performed,
The clutch operating oil pressure generator (50) is connected to the clutch lever (5) and is linked to the clutch master cylinder (70) that generates the clutch operating oil pressure, and is connected to the clutch lever (5). And an assist slave cylinder (60) for applying the assist force to the operation of the clutch lever (5) separately.
A clutch operating hydraulic path (27) connecting the hydraulic chamber (73) of the clutch master cylinder (70) and the hydraulic chamber (24) of the clutch actuator (20), and the hydraulic pressure of the assist slave cylinder (60) An assist hydraulic path (47) connecting the chamber (63) and the hydraulic chamber (43) of the assist master cylinder (40) is configured as an independent hydraulic path,
The generation has been assisted hydraulic by the assist pressure generator (30) is supplied to the clutch hydraulic oil pressure generating device (50), wherein in response to the operation of the clutch lever (5) using the assist hydraulic as assist force A clutch device configured to generate the clutch operating oil pressure by a clutch operating oil pressure generator (50) . In the assist pressure generator (30) , one end of the assist crankshaft (34) receives a rotational driving force by the electric motor (31) , and the other end detects rotation by the crank rotation sensor (39). The clutch device according to claim 1 , wherein the clutch device is configured to be performed. A gain adjusting unit (CU) for adjusting the driving force generation gain characteristic of the electric motor (31) and a gain setting means (91) for variably setting the driving force generation gain characteristic by an external operation;
The gain adjusting unit (CU) performs drive control of the electric motor (31) according to the operation of the clutch lever (5) using the gain characteristic set by the external operation of the gain setting means (91). The clutch device according to claim 1 or 2 , characterized in that The clutch master cylinder (70) and the assist slave cylinder (60) are arranged in parallel to each other on the facing side of the clutch lever (5). The clutch device as described. A knocker member (51) that is rotated in response to the operation of the clutch lever (5) is provided, and a piston member (62) of the assist slave cylinder (60) is provided at one end (52) of the knocker member (51). A first connecting rod (65) connected to the piston master member (72) and a second connecting rod (75) connected to the piston member (72) of the clutch master cylinder (70). The clutch device according to any one of claims 1 to 4, wherein the clutch device is provided. The said lever rotation sensor (57) which detects the amount of rotation operations of the said clutch lever (5) was provided on the rotating shaft (51a) of the said knocker member (51), The Claim 5 characterized by the above-mentioned. Clutch device. The reservoir tank (45) provided in the said assist master cylinder (40) and supplying a hydraulic fluid to the hydraulic chamber (43) of the said assist master cylinder (40) is provided, The any one of Claims 1-6 characterized by the above-mentioned. A clutch device according to claim 1.

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