WO2018124270A1 - クラッチ駆動装置及び車両 - Google Patents
クラッチ駆動装置及び車両 Download PDFInfo
- Publication number
- WO2018124270A1 WO2018124270A1 PCT/JP2017/047197 JP2017047197W WO2018124270A1 WO 2018124270 A1 WO2018124270 A1 WO 2018124270A1 JP 2017047197 W JP2017047197 W JP 2017047197W WO 2018124270 A1 WO2018124270 A1 WO 2018124270A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- spring
- clutch
- pin
- axis
- output gear
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D28/00—Electrically-actuated clutches
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62K—CYCLES; CYCLE FRAMES; CYCLE STEERING DEVICES; RIDER-OPERATED TERMINAL CONTROLS SPECIALLY ADAPTED FOR CYCLES; CYCLE AXLE SUSPENSIONS; CYCLE SIDE-CARS, FORECARS, OR THE LIKE
- B62K23/00—Rider-operated controls specially adapted for cycles, i.e. means for initiating control operations, e.g. levers, grips
Definitions
- the present invention relates to a clutch drive device that supplies assist force for assisting each operation of disconnection and connection of a clutch.
- a clutch driving device that supplies assist force for assisting each operation of disconnection and connection of the clutch is known.
- a clutch drive device for example, a configuration disclosed in Patent Document 1 is known.
- connection and disconnection of the clutch are controlled by operating a push rod using a hydraulic mechanism including a master cylinder and a clutch release cylinder.
- Patent Document 1 discloses a mechanism for generating an assist force for assisting the operation of the push rod.
- a piston pressing rod that presses a piston in the master cylinder is rotatably supported by a rotating member by a rotating shaft (hereinafter referred to as a first rotating shaft).
- An auxiliary spring portion is attached to the rotating member by a rotating shaft (hereinafter referred to as a second rotating shaft) different from the first rotating shaft.
- the rotating member rotates about a rotation axis (hereinafter referred to as a third rotation axis) different from the first rotation axis and the second rotation axis.
- a worm wheel that meshes with a worm gear connected to the rotation shaft of the motor is attached to the third rotation shaft. Thereby, the rotating member is rotated by the motor.
- auxiliary spring part One end of the auxiliary spring part is supported by the inner wall of the actuator case.
- the other end of the auxiliary spring portion presses the second rotating shaft for attaching the auxiliary spring portion to the rotating member.
- the auxiliary spring portion can swing at the other end about the one end.
- the auxiliary spring portion has a built-in spring that is compressed to a state shorter than the natural length and acts to extend independently. Due to the elastic force of the spring, a pressing force acts on the second rotation shaft, so that an auxiliary torque (rotation torque) is applied to the third rotation shaft.
- auxiliary torque rotation torque
- the first rotating shaft, the third rotating shaft, and the second rotating shaft are provided in this order in the radial direction on the rotating member.
- the rotation position of the said rotation member is a rotation position corresponding to the connection state of the said clutch, the torque input into the said rotation member from the said piston pressing rod via the said 1st rotating shaft, The said 2nd
- the combined torque with the torque input from the spring to the rotating member via the rotating shaft is a torque for rotating the rotating member in the direction in which the clutch is connected. Therefore, the clutch can be stabilized in the connected state.
- Patent Document 1 can reduce the size of the motor used for the clutch actuator. Therefore, the clutch actuator can be reduced in size.
- the spring in order to make it possible to change the direction of the torque applied from the spring to the rotating member according to the rotational position of the rotating member, the spring is connected to the actuator casing at one end. It is attached so that it can swing around. Therefore, it is necessary to provide a space in the actuator casing where the spring can swing.
- the present invention provides a clutch drive device that supplies a clutch disengagement and engagement assist force to a clutch so as to obtain a desired assist characteristic while further reducing the size of the device compared to a conventional device. With the goal.
- the present inventors can change the force obtained from the torsion spring without moving the torsion spring if the torsion spring can obtain an elastic restoring force against deformation in the circumferential direction. Noticed.
- the inventors have deformed the torsion spring in the circumferential direction in a state in which the radial displacement of the torsion spring is restricted, and received the elastic restoring force of the torsion spring and the center of the torsion spring. It has been found that the direction of the force obtained from the torsion spring can be changed while further miniaturizing the apparatus by changing the distance from the axis line.
- a clutch drive device is a clutch drive device that supplies assist force for assisting each operation of disconnection and connection of a clutch by a clutch.
- the clutch driving device is provided at a spring extending in a spiral shape around an axis and generating elastic restoring force in the circumferential direction by deformation in the circumferential direction when viewed from the axial direction, and one end of the spring.
- the output portion that outputs the elastic restoring force from the spring, the movement restricting portion that restricts the radial movement of the spring when the spring is deformed in the circumferential direction, and the axis of the spring are different.
- Rotating body that rotates in the cutting direction when disconnecting the clutch and rotates in the connecting direction when connecting the clutch, with the rotating shaft extending parallel to the axis at the position as the rotation center, and the rotation And a transmission unit that is provided on the rotating body so as to be rotatable integrally with the body and that transmits the elastic restoring force to the rotating body by contacting the output unit.
- a reaction force generated by each of the clutch disengagement and connection operations in the clutch is input as torque to the rotating body, and the elastic restoring force generated by the deformation of the spring in the circumferential direction is The assist force is input through the output unit and the transmission unit.
- the contact point between the output unit and the transmission unit is at a position different from the rotation axis of the rotating body and the axis of the spring, and the rotating body rotates in a direction in which the elastic restoring force of the spring is reduced. In doing so, it moves so as to approach the axis at least once when viewed from the axial direction of the spring.
- the clutch drive device By restricting the movement of the spring in the radial direction by the movement restricting portion, the spring that extends spirally around the axis and generates elastic restoring force in the circumferential direction by deformation in the circumferential direction when viewed from the axial direction, The elastic restoring force of the spring can be applied to the rotating body as an assisting force, and a space for moving the spring is not required in the apparatus. Therefore, the clutch drive device can be reduced in size.
- the contact point between the output portion provided at one end of the spring and the transmission portion provided at the rotating body is defined as the rotation axis of the rotating body and the axis of the spring.
- the clutch driving device of the present invention preferably includes the following configuration.
- the rotating shaft of the rotating body is located outside the spring as viewed from the axial direction.
- the spring When the rotating shaft of the rotating body is located inside the spring as viewed from the axial direction of the spring, the spring needs to have a diameter that includes the output portion and the transmission portion. On the other hand, as described above, the diameter of the spring can be reduced by disposing the rotating shaft outside the spring as viewed from the axial direction. Therefore, the size of the spring can be reduced.
- the clutch driving device of the present invention preferably includes the following configuration.
- the contact point is located outside the spring as viewed from the axial direction.
- the clutch driving device of the present invention preferably includes the following configuration.
- the distance between the rotating shaft of the rotating body and the contact point is smaller than the distance between the rotating shaft of the rotating body and the axis of the spring.
- the contact point where the output part provided on the spring contacts the transmission part provided on the rotating body moves within the range in which the rotating point of the rotating body moves around the rotating shaft of the rotating body and the spring. It can be formed between the two axes. Therefore, the moving range of the contact point can be made smaller than when the distance between the rotation axis and the contact point is equal to or greater than the distance between the rotation axis and the axis. Therefore, the size of the clutch drive device can be reduced.
- the clutch driving device of the present invention preferably includes the following configuration.
- the contact point is located on an imaginary line connecting the axis of the spring and the rotation axis of the rotating body, the distance between the axis of the spring and the contact point is the rotation of the rotating body It is smaller than the distance between the shaft and the axis of the spring.
- the distance between the axis of the spring and the contact point between the output part and the transmission part, and the distance between the contact point and the rotation axis can be made smaller than the distance between the rotation axis and the axis, respectively. Therefore, the rotating body and the spring can be arranged in a compact manner. Therefore, the clutch drive device can be reduced in size.
- the clutch driving device of the present invention preferably includes the following configuration.
- the output part is provided integrally with the spring.
- the clutch driving device of the present invention preferably includes the following configuration.
- the transmission unit moves relative to the output unit while contacting the output unit due to the rotation of the rotating body and the deformation of the spring in the circumferential direction accompanying the rotation.
- the distance between the contact point where the output part provided on the spring contacts the transmission part provided on the rotating body and the axis of the spring can be changed according to the rotation of the rotating body. Therefore, when the rotating body rotates, a configuration in which the contact point moves so as to approach the axis of the spring at least once when viewed from the axial direction of the spring can be realized with a simple configuration.
- the clutch driving device of the present invention preferably includes the following configuration.
- the output unit includes a link that rotates relative to the rotation of the rotating body and the deformation of the spring in the circumferential direction.
- the clutch driving device of the present invention preferably includes the following configuration.
- An actuator for applying a rotational torque to the rotating body is further provided.
- the clutch driving device of the present invention preferably includes the following configuration.
- the transmission mechanism further includes a transmission mechanism that transmits the rotational torque from the actuator to the rotating body, and the transmission mechanism includes an input shaft to which the rotational torque is input from the actuator. It is arranged so as to extend inwardly in parallel to the axis.
- the clutch drive device 14 including the motor 50 can be made compact.
- the clutch driving device of the present invention preferably includes the following configuration.
- the actuator is a motor.
- the clutch driving device of the present invention preferably includes the following configuration.
- the contact point between the output unit and the transmission unit moves so as to pass an imaginary line connecting the axis of the spring and the rotating shaft of the rotating body.
- the elastic restoring force generated by the deformation in the circumferential direction of the spring can be obtained in a wider range in the circumferential direction. Therefore, in the driving range of the clutch, the range that can be driven with a relatively low load by the assist force can be expanded. Therefore, the degree of freedom in driving the clutch can be improved.
- the force acting on the transmission unit causes the rotating body to rotate, and the contact point between the output unit and the transmission unit passes through an imaginary line connecting the axis of the spring and the rotation axis of the rotating body. It becomes the maximum when you do. As a result, a desired assist force can be obtained even when the shaft torque generated by the clutch reaction force is maximum at a predetermined rotational position of the rotating body.
- a vehicle according to an embodiment of the present invention includes a clutch unit having any one of the above-described configurations.
- attachment As used herein, “attached”, “connected”, “coupled”, and / or their equivalents are used in a broad sense, and include “direct and indirect” attachment, Includes both connections and couplings. Further, “connected” and “coupled” are not limited to physical or mechanical connections or couplings, and can include direct or indirect connections or couplings.
- the clutch drive device it is possible to further reduce the size of the device as compared with the conventional device while obtaining desired assist characteristics.
- FIG. 1 is a side view of a vehicle including a clutch drive device according to Embodiment 1 of the present invention.
- FIG. 2 is a partial cross-sectional view showing a schematic configuration of the clutch unit.
- FIG. 3 is an enlarged partial cross-sectional view of the clutch drive device.
- FIG. 4 is an exploded perspective view of the assist mechanism and the friction mechanism in the clutch drive device.
- FIG. 5 is a view of the assist mechanism as viewed from the axial direction of the output shaft.
- FIG. 6 is a view corresponding to FIG. 5 showing the regions X and Y in the assist mechanism.
- FIG. 7 is a diagram schematically illustrating an example of the operation of the assist mechanism.
- FIG. 8 is a diagram schematically showing an example of the relationship between the actuator rotation angle and the axial torque.
- FIG. 9 is a view of the engine and the clutch unit as viewed from above the vehicle.
- FIG. 10 is a view of the engine and the clutch unit as viewed from the side of the vehicle.
- FIG. 11 is an enlarged sectional view showing the friction mechanism.
- FIG. 12 is a perspective view illustrating the configuration of the rotation transmitting unit and the rotating plate.
- FIG. 13 is a view corresponding to FIG. 7 of the clutch drive device according to the second embodiment.
- FIG. 14 is a view corresponding to FIG. 7 of the clutch drive device according to the third embodiment.
- FIG. 15 is a view corresponding to FIG. 7 of the clutch drive device according to the fourth embodiment.
- FIG. 16 is a view corresponding to FIG. 7 of the clutch drive device according to the fifth embodiment.
- FIG. 17 is a view corresponding to FIG.
- FIG. 18 is a view corresponding to FIG. 7 of the clutch drive device according to the seventh embodiment.
- FIG. 19 is a view corresponding to FIG. 8 in the clutch drive device according to the seventh embodiment.
- FIG. 20 is a view corresponding to FIG. 7 of a clutch drive device according to another embodiment.
- FIG. 21 is a view corresponding to FIG. 8 of a clutch drive device according to another embodiment.
- FIG. 1 shows a schematic diagram of a vehicle 1 provided with a clutch drive device 14 according to Embodiment 1 of the present invention.
- the vehicle 1 is, for example, a motorcycle and includes a vehicle body 2, a front wheel 3, and a rear wheel 4.
- the vehicle body 2 has a frame (not shown).
- An engine unit 10 for supplying rotational driving force to the rear wheels 4 is attached to the frame of the vehicle body 2.
- the engine unit 10 includes an engine 11, a transmission 12, and a clutch unit 17.
- the clutch unit 17 includes a clutch 13 and a clutch driving device 14.
- the clutch 13 is configured to be able to transmit the rotation of a crankshaft (not shown) of the engine 11 to the transmission 12. That is, the clutch 13 is configured to be able to switch between transmission and non-transmission of rotation of the crankshaft with respect to the transmission 12.
- FIG. 2 is a partial cross-sectional view showing a schematic configuration of the clutch unit 17.
- the clutch 13 is provided on the main shaft 15.
- the main shaft 15 is an input shaft of the transmission 12, for example.
- the clutch 13 includes a clutch housing 21 and a clutch inner 25 disposed inside the clutch housing 21.
- the clutch housing 21 has a bottomed cylindrical shape having a bottom portion 21a through which the main shaft 15 passes and a cylindrical peripheral wall portion 21b provided on the outer periphery of the bottom portion 21a.
- the bottom part 21a and the peripheral wall part 21b are integrally formed.
- the clutch housing 21 is disposed concentrically with the main shaft 15.
- a clutch inner 25 is disposed inside the peripheral wall portion 21 b of the clutch housing 21.
- the clutch housing 21 has a bottom 21 a connected to the reduction gear 22.
- the reduction gear 22 rotates integrally with the gear by engaging with a gear (not shown) of the crankshaft.
- the clutch housing 21 and the reduction gear 22 rotate according to the rotation of the crankshaft and can rotate relative to the main shaft 15.
- the clutch inner 25 has a clutch boss 26, a pressure member 27, and a clutch spring 28.
- the clutch boss 26 has a cylindrical shape, and the main shaft 15 passes through the center thereof.
- the clutch boss 26 is splined on the outer peripheral surface of the main shaft 15. As a result, the clutch boss 26 rotates integrally with the main shaft 15.
- the clutch housing 21, the clutch boss 26 and the pressure member 27 are arranged with respect to the main shaft 15 in order from one side in the axial direction of the main shaft 15.
- the pressure member 27 is disposed outward of the main shaft 15 in the axial direction so as to face the clutch boss 26 in the axial direction.
- a plurality of clutch plates 23 and a plurality of friction plates 24 are arranged alternately in the axial direction between the clutch boss 26 and the pressure member 27.
- the friction plate 24 is rotatably provided integrally with the clutch housing 21 on the inner peripheral surface of the clutch housing 21.
- the friction plate 24 is rotatable with respect to the clutch boss 26 and the pressure member 27.
- the clutch plate 23 is rotatably provided integrally with the clutch boss 26 on the outer peripheral surface of the clutch boss 26.
- the pressure member 27 can rotate integrally with the clutch boss 26. Therefore, the clutch plate 23 can rotate integrally with the pressure member 27.
- the clutch plate 23 is rotatable with respect to the clutch housing 21.
- the pressure member 27 is movable in the axial direction with respect to the clutch boss 26.
- the clutch spring 28 is provided so as to push the pressure member 27 toward the clutch boss 26 in the axial direction.
- the clutch plate 23 and the friction plate 24 disposed between the clutch boss 26 and the pressure member 27 are pressed against each other. That is, the clutch plate 23 and the friction plate 24 are connected to each other by the clutch spring 28.
- the clutch boss 26 and the clutch housing 21 rotate integrally by friction between the clutch plate 23 and the friction plate 24. This state is the connection state of the clutch 13.
- the push rod 29 penetrates through the pressure member 27 in the central portion when viewed from the axial direction.
- the push rod 29 is disposed so as to extend in the axial direction.
- a flange portion 29 a is provided on one side of the push rod 29.
- the other end of the push rod 29 is connected to the clutch drive device 14 via a link mechanism 16 described later.
- the push rod 29 is configured to be movable in the axial direction by the output of the clutch drive device 14.
- the push rod 29 moves in the axial direction away from the main shaft 15 (rightward in FIG. 3)
- the pressure member 27 is separated from the clutch boss 26 in the axial direction by the flange portion 29a of the push rod 29. Receive force in the direction.
- the clutch spring 28 is deformed in the compressing direction, so that the force with which the pressure member 27 pushes the clutch plate 23 and the friction plate 24 decreases.
- the clutch 13 is switched between the connected state and the disconnected state when the push rod 29 moves in the axial direction.
- the pressure member 27 can rotate with respect to the push rod 29 via a bearing 27a. Thereby, when the clutch 13 is in the connected state, the pressure member 27 rotates integrally with the clutch housing 21 and the clutch boss 26.
- the link mechanism 16 includes a rotation shaft 31 and an arm portion 32.
- the link mechanism 16 transmits the output of the clutch drive device 14 described later to the push rod 29 of the clutch 13.
- the rotary shaft 31 has one axial direction connected to the other push rod 29 in the axial direction. Specifically, a rack portion 29b having a plurality of teeth arranged in the axial direction is provided on the other side of the push rod 29 in the axial direction.
- the rotating shaft 31 is provided with a gear 31a that meshes with the rack portion 29b.
- the push rod 29 moves in the axial direction by the rotation of the rotating shaft 31. That is, the push rod 29 reciprocates in the axial direction according to the rotation direction of the rotary shaft 31.
- the rotating shaft 31 is rotatably supported by the casing 20 in which the clutch 13, the transmission 12, and the like are housed.
- the arm portion 32 includes a first arm 33, a second arm 34, and an adjustment mechanism 35.
- the first arm 33 and the second arm 34 are each formed in a plate shape that is long in one direction.
- the first arm 33 is connected to the rotary shaft 31 so as to be rotatable integrally with the rotary shaft 31.
- the second arm 34 is connected to the output shaft 63 of the clutch driving device 14 so as to be rotatable integrally with the output shaft 63.
- the first arm 33 and the second arm 34 are connected via an adjustment mechanism 35.
- the arm unit 32 transmits the rotation of the output shaft 63 of the clutch driving device 14 to the rotating shaft 31.
- the arm portion 32 transmits a driving force output from the output shaft 63 of the clutch driving device 14 to the clutch 13 and also generates a reaction force (hereinafter referred to as a clutch reaction force) generated in the clutch 13 by the clutch spring 28 or the like.
- 14 output shafts 63 In other words, the output of the clutch driving device 14 and the clutch reaction force generated in the clutch 13 are input to the output shaft 63.
- the adjusting mechanism 35 connects the first arm 33 and the second arm 34 so that the distance between them can be adjusted.
- the adjustment mechanism 35 includes a first adjustment member 91, a second adjustment member 92, and an adjustment bolt 93.
- the first adjustment member 91 is rotatably connected to the first arm 33.
- the second adjustment member 92 is rotatably connected to the second arm 34. That is, the first adjustment member 91 and the second adjustment member 92 are connected to the first arm 33 and the second arm 34 in a rotatable manner by rod-like connection members 94 and 95 each having a spherical portion at one end. Has been.
- the connecting members 94 and 95 have the spherical portions located inside the first adjusting member 91 and the second adjusting member 92, respectively.
- the connection member 94 extends from the first adjustment member 91 toward the first arm 33 and is fixed to the first arm 33 while penetrating the first arm 33.
- the connection member 95 extends from the second adjustment member 92 toward the second arm 34 and is fixed to the second arm 34 while penetrating the second arm 34.
- the adjusting bolt 93 has a long column shape in the axial direction.
- the adjustment bolt 93 is provided with screw portions 93a and 93b having spiral grooves at both ends in the axial direction.
- the direction in which the screw groove extends from the screw tip is opposite to the direction in which the screw groove extends from the screw tip in the screw portion 93a.
- the adjustment bolt 93 has a large-diameter portion 93c having a larger diameter than other portions in the central portion in the axial direction. The large diameter portion 93c functions as a grip portion when the adjusting bolt 93 is rotated as will be described later.
- Screw holes 91a and 92a are formed in the first adjustment member 91 and the second adjustment member 92, respectively.
- the screw hole 92a When viewed from the opening end side of the screw hole 92a, the screw hole 92a has a direction in which the screw groove extends from the open end opposite to the direction in which the screw groove extends from the opening end in the screw hole 91a.
- a screw portion 93a provided at one end of the adjustment bolt 93 in the axial direction is fastened to the screw hole 91a.
- a screw portion 93b provided at the other end portion of the adjustment bolt 93 in the axial direction is fastened to the screw hole 92a. Therefore, the first adjustment member 91 and the second adjustment member 92 are connected by the adjustment bolt 93.
- the screw portion 93b and the screw hole 92a are opposite to the screw portion 93a and the screw hole 91a in the direction in which the screw groove extends. Therefore, by rotating the adjustment bolt 93 in one direction with respect to the first adjustment member 91 and the second adjustment member 92, the adjustment bolt 93 has a fitting length with respect to the first adjustment member 91 and the second adjustment member 92. Increase.
- the adjustment bolt 93 is fitted to the first adjustment member 91 and the second adjustment member 92 by rotating the adjustment bolt 93 in the direction opposite to the one direction with respect to the first adjustment member 91 and the second adjustment member 92. The length decreases.
- the nuts 96 and 97 are fastened with respect to the thread part 93a, 93b of the adjustment bolt 93, and 1st.
- the adjustment member 91 and the second adjustment member 92 can be fixed to the adjustment bolt 93.
- the distance between the first adjustment member 91 and the second adjustment member 92 that is, the distance between the first arm 33 and the second arm 34 can be adjusted.
- the clutch drive device 14 outputs to the clutch 13 a driving force obtained by applying an assist force by the assist mechanism 70 to the output of the motor 50 (actuator).
- FIG. 3 shows an enlarged schematic configuration of the clutch drive device 14.
- the clutch drive device 14 includes a casing 40, a motor 50, a transmission mechanism 60, an assist mechanism 70, and a friction mechanism 80.
- the casing 40 includes a casing body 41, a cover 42, and a motor storage unit 45.
- FIG. 4 is an exploded perspective view showing a part of the clutch driving device 14 in an exploded manner.
- the casing body 41 has a bottomed cylindrical shape extending in the cylinder axis direction. That is, the casing body 41 has an opening 41a.
- a transmission mechanism 60 and an assist mechanism 70 are accommodated in the casing body 41.
- a convex portion 46 is integrally formed at the bottom of the casing body 41.
- the cover 42 covers the opening 41 a of the casing body 41.
- the cover 42 has a storage space V inside.
- a friction mechanism 80 is arranged in the storage space V.
- the cover 42 includes a cover main body 43 and a storage cover portion 44.
- the cover main body 43 is formed with a first recess 43 a that constitutes a part of the storage space V.
- the storage cover portion 44 is formed with a second recess 44 a that constitutes a part of the storage space V. In a state where the storage cover portion 44 is combined with the cover body 43, the storage space V is configured by the first recess 43a and the second recess 44a.
- an output shaft 63 described later of the transmission mechanism 60 passes through a portion different from the portion where the storage space V is provided.
- the output shaft 63 extends in the cylinder axis direction of the casing body 41 and toward the outside of the casing 40. That is, the axial direction of the output shaft 63 coincides with the cylindrical axis direction of the casing body 41.
- the motor housing 45 is connected to the bottom of the casing body 41. Specifically, the motor storage unit 45 is attached to the casing body 41 at a position that does not overlap the output shaft 63 when viewed from the axial direction of the output shaft 63.
- the motor 50 generates an operation driving force for operating the clutch 13.
- the motor 50 is disposed in the motor housing 45 such that a rotating shaft (not shown) extends along the axial direction of the output shaft.
- the transmission mechanism 60 includes an input shaft 61, an intermediate shaft 62, and an output shaft 63.
- the input shaft 61, the intermediate shaft 62, and the output shaft 63 are arranged in parallel to each other.
- the input shaft 61 is an output shaft of the motor 50. Therefore, the intermediate shaft 62 and the output shaft 63 are arranged in parallel to the output shaft of the motor 50. That is, the input shaft 61 and the intermediate shaft 62 extend along the axial direction of the output shaft 63.
- One end of the input shaft 61 in the axial direction is positioned in the motor storage unit 45 in which the motor 50 is stored.
- the other axial direction of the input shaft 61 is positioned in a space formed by the casing body 41 and the cover 42.
- a gear 61a having a plurality of teeth arranged in the circumferential direction is provided on the other side in the axial direction of the input shaft 61.
- the gear 61a is a spur gear.
- the intermediate shaft 62 is rotatably supported at one end in the axial direction by the casing body 41.
- An intermediate gear 64 that is a spur gear is provided on the intermediate shaft 62 so as to be rotatable integrally with the intermediate shaft 62.
- the intermediate gear 64 meshes with the gear 61 a of the input shaft 61. Thereby, the rotation of the input shaft 61 is transmitted to the intermediate shaft 62 via the intermediate gear 64. That is, the intermediate shaft 62 rotates according to the rotation of the input shaft 61.
- the intermediate shaft 62 is provided with a gear 62a having a plurality of teeth arranged in the circumferential direction at a position closer to the center in the axial direction than the one end portion rotatably supported by the casing body 41.
- the gear 62 a is a spur gear provided on one side of the intermediate gear 64 in the axial direction of the intermediate shaft 62.
- the other side of the intermediate shaft 62 in the axial direction is rotatably supported by the cover 42.
- a rotation transmission portion 83 of a friction mechanism 80 described later is provided at the other end portion of the intermediate shaft 62 in the axial direction.
- a rotation transmission portion 83 having a rectangular cross section is provided at the other end in the axial direction of the intermediate shaft 62 (see FIG. 12).
- a part of the intermediate shaft 62 including the rotation transmission portion 83 protrudes outward of the casing body 41.
- the rotation transmitting portion 83 is inserted into a through hole 81a of a rotating plate 81 (described later) of the friction mechanism 80 (see FIGS. 11 and 12).
- the friction mechanism 80 when the friction mechanism 80 is assembled to the intermediate shaft 62 by projecting a part of the intermediate shaft 62 including the rotation transmission portion 83 to the outside of the casing body 41, the friction mechanism 80 is positioned. It can be done easily. Therefore, the assembly operation of the clutch drive device 14 is facilitated.
- the friction mechanism 80 suppresses the rotation of the intermediate shaft 62 by the frictional force when the rotational torque acting on the intermediate shaft 62 is a predetermined value or less (for example, when the output of the motor 50 is stopped). .
- one of the output shafts 63 in the axial direction is rotatably supported by the casing body 41, and the central portion in the axial direction is rotatably supported by the cover 42. .
- the other of the output shaft 63 protrudes outward from the cover 42 in the axial direction.
- the second arm 34 of the link mechanism 16 is connected to the other of the output shafts 63 in the axial direction so as to be integrally rotatable.
- the output shaft 63 is provided with a fan-shaped output gear 65 (rotary body) in plan view so as to be rotatable integrally with the output shaft 63.
- the output gear 65 is a spur gear and meshes with the gear 62 a of the intermediate shaft 62. Thereby, the rotation of the intermediate shaft 62 is transmitted to the output shaft 63 via the output gear 65. That is, the output shaft 63 rotates according to the rotation of the intermediate shaft 62.
- the output gear 65 is a rotating body that rotates about the axis center (rotary axis) of the output shaft 63 in the cutting direction when the clutch 13 is disconnected and rotates in the connecting direction when the clutch 13 is connected. Function.
- the rotation of the intermediate shaft 62 of the clutch driving device 14 is input to the output shaft 63 and the clutch reaction force generated by the clutch 13 is input to the output shaft 63.
- the output gear 65 is provided with a cylindrical pin 72 (transmission portion) protruding in the thickness direction on one side in the thickness direction. That is, the pin 72 extends along the axial direction of the output shaft 63. Further, in the present embodiment, as shown in FIGS. 3 and 4, the pin 72 is provided on a surface located on one side in the axial direction of the output shaft 63 out of both surfaces in the thickness direction of the output gear 65. . That is, the pin 72 is provided on the output gear 65 so as to extend toward the bottom of the casing body 41 in a state where the output shaft 63 and the output gear 65 are disposed in the casing 40. Accordingly, the pin 72 rotates around the output shaft 63 as the output gear 65 rotates integrally with the output shaft 63.
- the pin 72 is counterclockwise from the center of the output gear 65 in the circumferential direction of the output gear 65 when the output shaft 63 is viewed from the opening side of the casing main body 41 (hereinafter, simply referred to as the axial direction of the output shaft 63). It is provided at a position in the direction (see FIG. 5).
- the pin 72 is in contact with a first protrusion 71b of a spring 71 of an assist mechanism 70 described later.
- the pin 72 is rotatable with respect to the output gear 65. Therefore, when the pin 72 moves while contacting the first protrusion 71b of the spring 71 as described later, the pin 72 moves relative to the first protrusion 71b while rotating.
- the assist mechanism 70 includes a coiled spring 71 and the pin 72 described above.
- the spring 71 includes a wire that extends in a spiral shape around the axis.
- the spring 71 has a cylindrical shape extending in the axial direction.
- the spring 71 is a so-called torsion spring that generates an elastic restoring force in the circumferential direction by twisting one end of the wire in the circumferential direction with respect to the other end.
- the wire rod of the spring 71 is wound clockwise from the winding start side (first projecting portion 71b) which is one end side of the wire rod.
- the spring 71 is disposed in the casing main body 41 so as to surround the input shaft 61 and the intermediate shaft 62 when viewed from the axial direction of the output shaft 63.
- the input shaft 61 is inserted through the inside of the spring 71.
- One end portion of the intermediate shaft 62 in the axial direction is rotatably supported by a part of the casing body 41 (a convex portion 46 described later) positioned inward of the spring 71.
- the axis of the spring 71 is arranged in parallel with the output shaft 63.
- One end of the wire constituting the spring 71 extends toward the output shaft 63.
- FIG. 5 shows a schematic configuration of the assist mechanism 70 when viewed from the axial direction of the output shaft 63.
- a cylindrical convex portion 46 (movement restricting portion) provided on the inner surface of the casing body 41 is positioned inside the spring 71.
- the convex portion 46 has an outer diameter smaller than the inner diameter of the spring 71.
- the convex portion 46 functions as a movement restricting portion that restricts the movement of the spring 71 in the radial direction when the spring 71 is deformed as will be described later.
- the convex portion 46 is provided with a through hole 46 a through which the input shaft 61 is inserted and a hole portion 46 b into which one end portion in the axial direction of the intermediate shaft 62 is inserted.
- the spring 71 is in contact with a portion close to the output shaft 63 in the convex portion 46 with respect to the convex portion 46.
- An arc-shaped metal contact plate 47 is provided in a part of the convex portion 46 including a contact portion with the spring 71 when viewed from the axial direction of the output shaft 63. Both end portions of the contact plate 47 are fixed to a protruding portion 46 c provided on the convex portion 46.
- a spring 71 contacts the contact plate 47.
- the spring 71 has one end of the wire extending toward the output shaft 63. That is, one end of the wire extends toward the radially outer side of the spring 71. The other end of the wire rod of the spring 71 also extends outward in the radial direction of the spring 71. That is, the spring 71 includes a cylindrical coil portion 71a, a first protrusion 71b (output portion) that includes one end of the wire, and extends radially outward from the coil portion 71a, and the other end of the wire. And a second projecting portion 71c extending radially outward from the coil portion 71a. In the present embodiment, the first protrusion 71 b and the second protrusion 71 c extend toward the output shaft 63 when viewed from the axial direction of the output shaft 63.
- the first protrusion 71 b is in contact with a pin 72 provided on the output gear 65 of the output shaft 63.
- the second projecting portion 71 c is in contact with the inner surface of the casing body 41. As shown in FIG. 6, the first projecting portion 71b and the second projecting portion 71c are viewed from the axial direction of the output shaft 63 in a state where the output gear 65 is positioned at the clutch disengaged state as will be described later.
- FIG. 6 is a diagram schematically showing the ranges of the regions X and Y in FIG.
- the spring 71 when the one end of the wire rod in the first projecting portion 71b rotates in the circumferential direction of the spring 71 in a state where the second projecting portion 71c is in contact with the inner surface of the casing body 41, the spring 71 has the first projecting portion 71b. Produces an elastic restoring force in a direction away from the second protrusion 71c. That is, when the pin 72 rotates around the axis of the output shaft 63 in accordance with the rotation of the output shaft 63 so that the clutch 13 changes from the clutch disengaged state to the connected state, the first projecting portion 71b of the spring 71 moves to the pin 72. Is pushed in the circumferential direction of the spring 71.
- one end of the wire rod of the spring 71 rotates around the axis Q of the spring 71 so as to approach the other end of the wire rod in the second protrusion 71c. Due to the deformation of the spring 71, an elastic restoring force is generated in the spring 71 in the circumferential direction of the spring 71 in the direction in which the first protrusion 71b is separated from the second protrusion 71c. Since the pin 72 provided on the output gear 65 is in contact with the first protrusion 71 b of the spring 71, the elastic restoring force generated by the spring 71 is output via the first protrusion 71 b and the pin 72 to the output gear. 65.
- the first protrusion 71 b functions as an output unit that outputs an elastic restoring force from the spring 71.
- the pin 72 functions as a transmission unit that transmits the elastic restoring force to the output gear 65 by contacting the first protrusion 71 b.
- FIG. 7A to 7C schematically show the relationship between the rotation position of the output gear 65 and the deformation of the spring 71.
- FIG. In this figure, for the sake of explanation, the output shaft 63 and the output gear 65 are indicated by a two-dot chain line, and only the pin 72 and the spring 71 are indicated by a solid line. Further, in this figure, as in FIG. 6, the ranges of the regions X and Y are indicated by hatching for the sake of explanation. 7A to 7C schematically show the regions X and Y separated by the virtual line M in order to simplify the drawing.
- FIG. 7A shows the rotational position of the output gear 65 when the clutch 13 is in a disconnected state.
- FIG. 7B shows the output gear 65 when the clutch 13 is in a half-clutch state (slip occurs between the clutch plate 23 and the friction plate 24 but a force in the rotational direction is transmitted). Indicates the rotational position.
- FIG. 7C shows the rotational position of the output gear 65 when the clutch 13 is in the connected state.
- the pin 72 provided on the output gear 65 is connected to the output shaft 65.
- the region is located in the region X.
- the pin 72 is in contact with the first protrusion 71b of the spring 71 at a position close to the tip.
- the force that the pin 72 receives by the elastic restoring force of the spring 71 is a predetermined direction (hereinafter referred to as the rotational direction of the clutch disengagement) so that the output gear 65 disengages the clutch 13. That is, the force to rotate in the direction of the two-dot chain line arrow in FIG. That is, torque is applied to the output gear 65 in the rotational direction of clutch disengagement by the spring 71 via the pin 72.
- the first protrusion 71 b of the spring 71 is not significantly displaced by the pin 72 in the circumferential direction of the spring 71. Therefore, the force which the pin 72 receives by the elastic restoring force of the spring 71 is smaller than the case of FIG.7 (b) mentioned later and (c). For example, the pin 72 receives a force having a direction and magnitude indicated by a solid arrow in FIG. 7A from the first protrusion 71 b of the spring 71.
- the spring 71 is twisted in the circumferential direction. Therefore, the spring 71 generates an elastic restoring force in a direction in which the first protrusion 71b is separated from the second protrusion 71c.
- the elastic restoring force of the spring 71 acts on the pin 72 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 71 is transmitted to the output gear 65 through the pin 72 as torque in the rotational direction of clutch disengagement (the rotational direction indicated by the two-dot chain line arrow in FIG. 7B). .
- a force assisting in the direction of clutch disengagement is transmitted from the spring 71 to the output gear 65 via the pin 72.
- the force which the pin 72 receives from the 1st protrusion part 71b of the spring 71 is large compared with the case of Fig.7 (a).
- the pin 72 When the output gear 65 is positioned at the rotational position shown in FIG. 7C, that is, when the pin 72 is positioned in the region Y of the two regions X and Y, the pin 72 causes the spring 71 to move.
- the first protrusion 71b is displaced so as to be closer to the other end of the wire in the second protrusion 71c.
- the pin 72 is positioned closer to one end of the wire than the position shown in FIG. 7B with respect to the first protrusion 71b of the spring 71.
- the spring 71 is further twisted in the circumferential direction.
- the elastic restoring force of the spring 71 acts on the pin 72 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 71 is rotated in the direction in which the clutch 13 is connected to the output gear 65 via the pin 72 (hereinafter referred to as the rotation direction of the clutch connection in two points in FIG. 7C). Acting in the direction of the rotation of the dashed arrow. As a result, a force assisting in the rotational direction of the clutch connection is transmitted from the spring 71 to the output gear 65 via the pin 72.
- the contact point T between the pin 72 and the first projecting portion 71 b of the spring 71 corresponds to the axial center P of the output shaft 63 and the axis Q of the spring 71 as viewed from the axial direction of the output shaft 63 according to the rotation of the output gear 65.
- the virtual line M connecting The contact point T between the pin 72 and the first projecting portion 71b is at a position different from the axial center P of the output shaft 63 and the axis Q of the spring 71, and in the direction in which the elastic restoring force of the spring 71 decreases. Is rotated (in the example of FIG. 7, when the output gear 65 is rotated in the order of FIGS.
- the axis Q of the spring 71 is viewed from the axial direction of the spring 71. Move to approach at least once. Accordingly, the elastic restoring force generated by the spring 71 can be transmitted to the output gear 65 as an assist force in a direction in which the first protrusion 71b is separated from the second protrusion 71c. At this time, the elastic restoring force of the spring 71 is transmitted as torque to the output gear 65 via the first protrusion 71 b and the pin 72.
- the distance D between the contact point T and the axis Q of the spring 71 changes according to the rotation of the output gear 65. That is, the interval D is the smallest when the contact point T crosses the virtual line M when viewed from the axial direction of the output shaft 63, and the distance D is larger as the contact point T is farther from the virtual line M.
- the distance between the shaft center P of the output shaft 63 and the contact point T between the first protrusion 71 b and the pin 72 is smaller than the distance between the shaft center P and the axis Q of the spring 71.
- the clutch drive device 14 can be reduced in size.
- the distance between the axis Q of the spring 71 and the contact point T is smaller than the distance between the axis P of the output shaft 63 and the axis Q of the spring 71.
- FIG. 8 shows the rotational angle of the output gear 65 (actuator rotational angle), the rotational torque acting on the output shaft 63 (hereinafter referred to as shaft torque) due to the load when operating the clutch 13 (clutch load), and the assist.
- the relationship between the shaft torque generated in the output shaft 63 by the assist force by the mechanism 70 and the sum of the shaft torque generated in the output shaft 63 by the clutch load (clutch reaction force) and the assist force is shown.
- the actuator rotation angle is the initial rotation when the output gear 65 rotates counterclockwise from the initial rotation position (position of FIG. 7C) as viewed from the axial direction of the output shaft 63. It means the rotation angle of the output gear 65 with respect to the position.
- the rotation range of the output gear 65 is defined by the inner surface of the casing body 41. That is, the position where the output gear 65 contacts the inner surface of the casing main body 41 when the output gear 65 rotates in the rotation direction of the clutch connection is the limit rotation position of the output gear 65 in the rotation direction of the clutch connection. The position where the output gear 65 contacts the inner surface of the casing body 41 when the output gear 65 rotates in the clutch disengagement rotation direction is the limit rotation position of the output gear 65 in the clutch disengagement rotation direction.
- the actuator rotation angle is determined when the output gear 65 rotates in the order of FIG. 7C, FIG. 7B, and FIG. 7A when viewed from the axial direction of the output shaft 63. Increase.
- the clutch load is equal to the reaction force (clutch reaction force) that the clutch drive device 14 receives from the clutch spring 28 of the clutch 13 when the clutch 13 operates.
- the clutch reaction force increases with an increase in the actuator rotation angle when the clutch 13 is switched from the connected state to the disconnected state.
- the shaft torque acting on the output shaft 63 by the clutch reaction force is shown by a solid line in FIG. 8 according to the lever ratio determined based on the relationship between the position and length of the first arm 33 and the second arm 34 in the link mechanism 16. It changes so as to become maximum at a predetermined actuator rotation angle as indicated by a solid line (indicated by a solid line “generated by clutch reaction force” in the figure).
- the lever ratio means the ratio of the shaft torque acting on the output shaft 63 of the clutch drive device 14 and the shaft torque acting on the rotating shaft 31.
- the clutch driving device 14 is arranged with respect to the engine 11 and the clutch 13 as shown in FIGS. 9 and 10.
- FIG. 9 is a diagram schematically showing the engine 11, the clutch 13, and the clutch driving device 14 as viewed from above the vehicle 1.
- FIG. 10 is a diagram schematically showing the engine 11, the clutch 13, and the clutch driving device 14 as viewed from the side of the vehicle 1. 9 and 10, in order to explain the arrangement relationship of the engine 11, the clutch 13, and the clutch drive device 14, other components are not shown, and the engine 11, the clutch 13, and the clutch drive device 14 are Simplified and illustrated.
- the arrow L in the figure indicates the left direction of the vehicle 1.
- An arrow R in the figure indicates the right direction of the vehicle 1.
- An arrow RR in the figure indicates the backward direction of the vehicle 1.
- An arrow U in the figure indicates the upward direction of the vehicle 1.
- the front-rear and left-right directions mean front-rear and left-right directions as viewed from the occupant driving the vehicle 1.
- the clutch drive device 14 is disposed above the clutch 13 and behind the engine 11.
- the clutch driving device 14 is disposed above the clutch 13 and on the right side when viewed from above the vehicle 1.
- the clutch drive device 14 is arranged so that the axial direction of the output shaft 63 is along the left-right direction of the vehicle 1.
- the clutch 13 is arranged so that the axial direction of the rotary shaft 31 is along the vertical direction of the vehicle 1.
- the clutch drive device 14 is connected to the clutch 13 via the link mechanism 16. Specifically, one end of the first arm 33 of the link mechanism 16 is connected to the rotating shaft 31 and extends in the left direction of the vehicle 1. One end of the second arm 34 of the link mechanism 16 is connected to the output shaft 63 of the clutch driving device 14 and extends downward in the vehicle 1.
- the adjustment mechanism 35 of the link mechanism 16 connects the first arm 33 and the second arm 34 rotatably.
- the first adjustment member 91 and the second adjustment member 92 of the adjustment mechanism 35 are connected to the plate-like first arm 33 and the second arm 34 in the thickness direction, respectively.
- the 1st adjustment member 91 and the 2nd adjustment member 92 are arrange
- the configuration of the link mechanism 16 is simplified.
- the lever ratio rt which is the ratio of the shaft torque acting on the output shaft 63 of the clutch drive device 14 and the shaft torque acting on the rotating shaft 31, is obtained by the following equation.
- the following equation is an equation for determining the lever ratio rt on the assumption that the inclination of the adjustment mechanism 35 does not change when the link mechanism 16 operates.
- ⁇ 1 is an angle formed by the second arm 34 with respect to a reference line parallel to the axis of the rotating shaft 31 when the link mechanism 16 is viewed from the side of the vehicle 1 (see FIG. 10).
- ⁇ 2 is an angle formed by the first arm 33 with respect to a reference line parallel to the axis of the output shaft 63 when the link mechanism 16 is viewed from above the vehicle 1 (see FIG. 9).
- L1 is the length of the second arm 34
- L2 is the length of the first arm 33.
- the clutch reaction force increases as the actuator rotation angle increases.
- the increase amount of the clutch reaction force with respect to the increase amount of the actuator rotation angle is smaller than when the actuator rotation angle is small.
- the shaft torque generated in the output shaft 63 when the clutch reaction force acts on the output shaft 63 decreases as the lever ratio rt increases. Therefore, the shaft torque decreases as the actuator rotation angle increases.
- the shaft torque generated in the output shaft 63 by the clutch reaction force increases with an increase in the actuator rotation angle when the actuator rotation angle is small.
- the actuator rotation angle increases and decreases. That is, the shaft torque changes so as to become maximum at the predetermined actuator rotation angle.
- the axial torque acting on the output shaft 63 is a positive range (range larger than 0 in FIG. 8) as the axial torque range to which the clutch 13 is connected, and the axial torque acting on the output shaft 63 is A negative range (a range smaller than 0 in FIG. 8) is set as a range of shaft torque for disengaging the clutch 13.
- the rotation position of the output gear 65 changes according to the rotation (operation driving force) of the motor 50 so that the actuator rotation angle becomes large, that is, FIG. 7C, FIG. 7B, and FIG.
- the force acting on the pin 72 of the output gear 65 from the spring 71 changes in a parabolic shape that becomes maximum at a predetermined actuator rotation angle.
- the shaft torque acting on the output shaft 63 by the assist force of the clutch drive device 14 (the solid line described as “generated by the assist force” in FIG. 8) also becomes a parabolic shape that becomes maximum at the predetermined actuator rotation angle. Change.
- the elastic restoring force of the spring 71 acting on the pin 72 of the output gear 65 is the magnitude of the force acting on the pin 72 as an assisting force in the direction of clutch disengagement according to the rotational position of the output gear 65. Changes. This is because the contact point T between the first projecting portion 71b of the spring 71 and the pin 72 changes along the first projecting portion 71b according to the rotational position of the output gear 65. This is because the direction of the force applied to the pin 72 changes and the distance D between the contact point T between the pin 72 and the first protrusion 71b of the spring 71 and the axis Q of the spring 71 changes.
- the shaft torque acting on the output shaft 63 by the drive and assist mechanism 70 of the motor 50, that is, by the assist force of the clutch drive device 14, is mainly applied to the clutch 13 as shown in FIG. This is the shaft torque to be cut (the shaft torque in the negative region in FIG. 8).
- the shaft torque acting on the output shaft 63 by the clutch reaction force generated when the clutch 13 is operated is the actuator rotation angle at which the clutch 13 starts to shift from the connected state to the disconnected state when the actuator rotation angle increases. (S in FIG. 8).
- the shaft torque that acts on the output shaft 63 by the clutch reaction force is generated by a force that rotates the output shaft 63 in a predetermined direction (hereinafter referred to as a rotational direction of clutch connection) so as to connect the clutch 13.
- the clutch reaction force is generated by an elastic restoring force of the clutch spring 28 of the clutch 13 or the like.
- the shaft torque acting on the output shaft 63 due to the clutch reaction force also changes in a parabolic shape that becomes maximum at a desired actuator rotation angle, as shown in FIG.
- the sum of the shaft torque acting on the output shaft 63 by the assist mechanism 70 and the shaft torque acting on the output shaft 63 by the clutch reaction force generated in the clutch 13 is shown in FIG.
- the value is relatively small. That is, the total shaft torque becomes a value within a certain range in the half-clutch region (range of the actuator rotation angle in the half-clutch state) shown in FIG. Thereby, the half-clutch state of the clutch 13 can be realized with relatively small and stable shaft torque in the output shaft 63.
- the total shaft torque is an operation driving force of the motor 50 required when the clutch 13 is operated.
- the clutch 13 can be easily switched from the connected state to the disconnected state, and a stable half-clutch state can be realized.
- FIG. 11 is an enlarged view showing the friction mechanism 80.
- FIG. 12 is a perspective view illustrating the configuration of the rotation transmitting unit and the rotating plate.
- the friction mechanism 80 holds the intermediate shaft 62 in a stationary state by the friction of the rotating plate 81 and the pair of friction plates 82 when the torque in the rotational direction acting on the intermediate shaft 62 of the transmission mechanism 60 is a predetermined value or less. .
- the disengaged state of the clutch 13 can be maintained by the friction mechanism 80.
- the friction mechanism 80 includes a rotating plate 81, a pair of friction plates 82, a rotation transmitting portion 83 provided on one of the intermediate shafts 62, and a spring 84.
- the friction mechanism 80 is disposed in a storage space V formed in the cover 42 of the clutch drive device 14.
- the friction mechanism 80 is disposed between the cover main body 43 and the storage cover portion 44. Therefore, in the present embodiment, as shown in FIGS. 2 and 3, the friction mechanism 80 is arranged such that the transmission mechanism 60 is positioned between the friction mechanism 80 and the motor 50 in the axial direction of the output shaft 63. ing. Thereby, the friction mechanism 80 can be arranged compactly without interfering with the motor 50.
- the pair of friction plates 82 are arranged on one side and the other side in the thickness direction with respect to the rotating plate 81. That is, the pair of friction plates 82 and the rotating plate 81 are laminated in the thickness direction of the friction plate 82 in the order of the friction plate 82, the rotating plate 81 and the friction plate 82.
- Each of the pair of friction plates 82 has a hollow disk shape in which at least a surface in contact with the rotating plate 81 out of both surfaces in the thickness direction has a friction coefficient such that a predetermined frictional force can be obtained by contacting the rotating plate 81. It is a member.
- the friction plate 82 is made of, for example, a plate member made of stainless steel whose surface is polished.
- the pair of friction plates 82 and the rotating plate 81 are disposed in a first recess 43 a provided in the cover main body 43.
- One friction plate 82 of the pair of friction plates 82 is in contact with the inner surface of the first recess 43 a of the cover body 43.
- each of the pair of friction plates 82 has a plurality of positioning protrusions 82a on the outer peripheral portion.
- the positioning convex portion 82 a is positioned in the positioning concave portion 43 b formed on the inner surface of the first concave portion 43 a in a state where the pair of friction plates 82 are disposed in the first concave portion 43 a of the cover main body 43. Thereby, it can suppress that a pair of friction board 82 rotates with the rotation board 81.
- the rotating plate 81 is a disk-shaped metal member. As shown in FIG. 12, the rotation plate 81 has a through hole 81 a (hole) that penetrates in the thickness direction of the rotation plate 81 at the center (rotation center).
- the through hole 81a has a rectangular shape when the rotary plate 81 is viewed from the thickness direction.
- a rotation transmitting portion 83 provided on one side of the intermediate shaft 62 passes through the through hole 81a.
- the rotating plate 81 is provided with a contact portion 81b that contacts the pair of friction plates 82 on the outer peripheral portion of the disc-shaped rotating plate 81 when viewed from the thickness direction.
- the contact part 81 b has a thickness larger than the thickness of the central part of the rotating plate 81. That is, the contact portion 81 b protrudes in the thickness direction of the rotating plate 81 from the center portion of the rotating plate 81. Thereby, the contact portion 81 b of the rotating plate 81 contacts the pair of friction plates 82 in a state where the rotating plate 81 is disposed between the pair of friction plates 82.
- the rotation transmission part 83 is provided in the axial direction end part of the intermediate shaft 62 as described above.
- the rotation transmission unit 83 has a columnar shape with a rectangular cross section.
- the rotation transmitting portion 83 is formed so as to be insertable into the through hole 81 a of the rotating plate 81.
- the symbol Z is the axis of the intermediate shaft 62.
- the axial direction in which the axis Z extends is the same direction as the axial direction of the output shaft 63.
- the direction in which the axial direction (axial direction) of the intermediate shaft 62 and the axial direction of the output shaft 63 are the same is the same direction as long as rotation can be transmitted between the intermediate shaft 62 and the output shaft 63. Including other directions.
- the friction transmission mechanism 80 moves from the input shaft 61 to the output shaft 63 in the transmission mechanism 60 by inserting the rotation transmission portion 83 provided in the intermediate shaft 62 into the through hole 81 a of the rotation plate 81.
- the power transmission path is separated. That is, the friction mechanism 80 is not included in the transmission mechanism 60 but is provided separately from the transmission mechanism 60.
- the rotation plate 81 is allowed to move in the axial direction of the intermediate shaft 62 with respect to the rotation transmission unit 83 while transmitting the rotation of the intermediate shaft 62 to the rotation plate 81 via the rotation transmission unit 83. be able to. Thereby, even when the rotating plate 81 is inclined or displaced in the axial direction of the intermediate shaft 62, the rotating plate 81 can be relatively displaced with respect to the rotation transmitting portion 83.
- the spring 84 includes a wire extending spirally around the axis.
- the spring 84 has a cylindrical shape extending in the axial direction.
- the spring 84 is a compression spring that generates an elastic restoring force by being compressed in the axial direction.
- the spring 84 is disposed in the storage cover portion 44 so that the axial direction coincides with the axial direction of the intermediate shaft 62. That is, the axis of the spring 84 extends in the same direction as the axial direction of the output shaft 63.
- the spring 84 is disposed with respect to the pair of friction plates 82 and the rotating plate 81 so that the axis thereof coincides with the thickness direction of the pair of friction plates 82 and the rotating plate 81.
- One of the springs 84 in the axial direction of the spring 84 is in contact with the other friction plate 82 of the pair of friction plates 82. That is, the pair of friction plates 82 and the rotating plate 81 are closer to the rotation transmitting unit 83 than the spring 84.
- one of the pair of friction plates 82 is in contact with the inner surface of the first recess 43 a of the cover body 43. Thereby, a force is applied to the pair of friction plates 82 and the rotating plate 81 in the thickness direction by the springs 84. Accordingly, the pair of friction plates 82 and the rotating plate 81 are pressed in the thickness direction between the spring 84 and the inner surface of the first recess 43 a of the cover main body 43.
- the sum of the shaft torque generated by the assist force of the clutch drive device 14 and the shaft torque generated by the clutch reaction force of the clutch 13 is the clutch drive device 14. Is the shaft torque acting on the output shaft 63.
- the range of the axial torque in which the rotation of the rotating plate 81 and the intermediate shaft 62 stops by the frictional force between the rotating plate 81 and the pair of friction plates 82 is indicated by a two-dot chain line.
- the rotating plate 81 and the intermediate shaft 62 are rotated by the frictional force between the rotating plate 81 and the pair of friction plates 82 in the range between the two-dot chain line (below a predetermined value). Is suppressed.
- the clutch reaction force and the assist force input to the output shaft 63 of the clutch drive device 14 are set so that the sum of the shaft torques generated in the output shaft 63 is not more than a predetermined value as shown in FIG.
- the self-locking mechanism as described above can be realized. That is, when the clutch 13 is switched from the connected state to the disconnected state, the assist force input from the spring 71 to the output shaft 63 becomes the maximum after the clutch reaction force is input from the clutch 13 to the output shaft 63. Thus, or when the clutch 13 is switched from the disconnected state to the connected state, the assist force input from the spring 71 to the output shaft 63 is the clutch reaction force input from the clutch 13 to the output shaft 63. By reaching the maximum before reaching zero, the total shaft torque generated in the output shaft 63 can be made equal to or less than the predetermined value, and the above-described self-locking mechanism can be realized.
- the rotation transmitting portion 83 of the intermediate shaft 62 into the through hole 81a of the rotating plate 81, a displacement other than the rotating direction of the rotating plate 81 with respect to the intermediate shaft 62 can be allowed. Therefore, for example, even when the intermediate shaft 62 is inclined, the rotation of the intermediate shaft 62 can be transmitted to the rotating plate 81 while preventing the rotating plate 81 from being inclined. Accordingly, the rotating plate 81 can be rotated by the intermediate shaft 62 while the rotating plate 81 is more reliably brought into contact with the pair of friction plates 82.
- the rotating plate 81, the friction plate 82, and the spring 84 of the friction mechanism 80 can be mounted in the cover main body 41 in the cover 42 in an assembled state. Therefore, the assembly workability of the friction mechanism 80 can be improved.
- the casing in which the friction mechanism 80 is accommodated is constituted by a part of the cover 42 of the clutch drive device 14.
- the whole structure of the clutch drive device 14 can be made into a compact structure.
- the clutch drive device 14 is a clutch drive device that supplies assist force for assisting each operation of disconnection and connection of the clutch 13.
- the clutch driving device 14 is provided at one end of the spring 71 and a spring 71 that extends spirally around the axis Q and generates an elastic restoring force in the circumferential direction by deformation in the circumferential direction when viewed from the axial direction.
- a first projecting portion 71b that outputs the elastic restoring force from the spring 71; a convex portion 46 that restricts the radial movement of the spring 71 when the spring 71 is deformed in the circumferential direction;
- the output shaft 63 that extends parallel to the axis Q at a position different from the axis Q rotates about the axis center P of the output shaft 63 in the cutting direction when the clutch is disconnected, and is connected when the clutch is connected.
- An output gear 65 that rotates in the direction, and is provided in the output gear 65 so as to be rotatable integrally with the output gear 65, and by contacting the first protrusion 71b, the elastic restoring force is supplied to the output gear 65.
- a pin 72 for transmitting.
- the output gear 65 receives the reaction force generated by the disconnection and connection operations of the clutch 13 as torque, and the elastic restoring force generated by the deformation of the spring 71 in the circumferential direction causes the first protruding portion.
- the assist force is input via 71b and pin 72.
- the contact point T between the first projecting portion 71b and the pin 72 is at a position different from the axial center P of the output shaft 63 and the axis Q of the spring 71, and in the direction in which the elastic restoring force of the spring 71 decreases. , When viewed from the axial direction of the spring 71, it moves so as to approach the axis Q at least once.
- a spring 71 that spirally extends around the axis Q and generates an elastic restoring force in the circumferential direction when deformed in the circumferential direction when viewed from the direction of the axis Q is moved in the radial direction by the protrusion 46.
- the elastic restoring force of the spring 71 can be applied to the output gear 65 as an assist force, and a space for moving the spring 71 is not required in the apparatus. Therefore, the clutch drive device can be reduced in size.
- the contact point T between the first protrusion 71 b provided at one end of the spring 71 and the pin 72 provided at the output gear 65 is defined as the axial center P of the output shaft 63.
- the output gear 65 rotates at a position different from the axis Q of the spring 71 and in a direction in which the elastic restoring force of the spring 71 decreases, the output gear 65 approaches the axis Q at least once when viewed from the axis direction of the spring 71. Move. Accordingly, the elastic restoring force generated by the spring 71 can be transmitted to the output gear 65 as an assist force in a direction in which the first protrusion 71b is separated from the second protrusion 71c. At this time, the elastic restoring force of the spring 71 is transmitted as torque to the output gear 65 via the first protrusion 71 b and the pin 72.
- the shaft center P of the output shaft 63 is located outside the spring 71 when viewed from the axial direction of the spring 71.
- the spring 71 has a diameter that includes the output shaft, the first protrusion, and the pin. It is necessary to.
- the diameter of the spring 71 can be reduced by arranging the shaft center P of the output shaft 63 outside the spring 71 as viewed from the axial direction. Therefore, the size of the spring 71 can be reduced.
- the contact point T between the first protrusion 71b of the spring 71 and the pin 72 is located radially outward from the spring 71 when viewed from the axial direction.
- the spring 71 can be downsized as compared with the case where the contact point T is located radially inward of the spring 71 when viewed from the axial direction of the spring 71.
- the distance between the shaft center P of the output shaft 63 and the contact point T of the first protrusion 71b and the pin 72 is smaller than the distance between the shaft center P and the axis Q of the spring 71.
- the contact point T where the first protrusion 71 b provided on the spring 71 and the pin 72 provided on the output gear 65 come into contact with each other is within the range in which the contact point T moves around the axis center P of the output shaft 63. It can be formed between P and the axis Q of the spring 71. Therefore, the moving range of the contact point T can be made smaller than when the distance between the axis center P of the output shaft 63 and the contact point T is equal to or greater than the distance between the axis center P and the axis Q. Therefore, the size of the clutch drive device 14 can be reduced.
- the distance between the axis Q of the spring 71 and the contact point T is the distance between the axis center P of the output shaft 63 and the axis Q of the spring 71 when the contact point T is located on the virtual line M. Less than distance.
- the distance between the axis Q of the spring 71 and the contact point T of the first projecting portion 71b and the pin 72, and the distance between the contact point T and the axis center P of the output shaft 63 are respectively set to the axis center P and the axis line. It can be made smaller than the distance from Q. Therefore, the output gear 65 and the spring 71 can be arranged in a compact manner. Therefore, the size of the clutch drive device 14 can be reduced.
- the first protrusion 71b is provided integrally with the spring 71. Thereby, the number of parts of the clutch drive device 14 can be reduced.
- the pin 72 moves relative to the first protrusion 71b while contacting the first protrusion 71b by the rotation of the output gear 65 and the deformation of the spring 71 in the circumferential direction accompanying the rotation.
- the distance between the contact point T where the first protrusion 71 b provided on the spring 71 and the pin 72 provided on the output gear 65 are in contact with the axis Q of the spring 71 is determined according to the rotation of the output gear 65. Can be changed. Therefore, when the output gear 65 rotates, a configuration in which the contact point T moves so as to approach the axis Q of the spring 71 at least once when viewed from the axial direction of the spring 71 can be realized with a simple configuration.
- the clutch drive device 14 further includes a transmission mechanism 60 that transmits rotational torque from the motor 50 to the output gear 65.
- the transmission mechanism 60 has an input shaft 61 to which the rotational torque is input from the motor 50.
- the input shaft 61 is disposed inward of the spring 71 so as to extend parallel to the axis Q.
- the input shaft 61 can be arranged by effectively utilizing the space inside the spring 71. Therefore, the clutch drive device 14 including the motor 50 can be made compact.
- the contact point T between the first protrusion 71 b of the spring 71 and the pin 72 is an imaginary line that connects the axis Q of the spring 71 and the axis center P of the output shaft 63 when the output gear 65 rotates. Move to pass M.
- the elastic restoring force generated by the deformation in the circumferential direction of the spring 71 can be obtained in a wider range in the circumferential direction. Therefore, in the driving range of the clutch 13, the range that can be driven with a relatively low load by the assist force can be expanded. Therefore, the degree of freedom in driving the clutch 13 can be improved.
- the force acting on the pin 72 causes the output gear 65 to rotate, so that the contact point T between the first protrusion 71 b and the pin 72 is the axis Q of the spring 71 and the axis center P of the output shaft 63. Is maximized when passing through an imaginary line M. Thereby, even if the shaft torque generated by the clutch reaction force becomes the maximum value at the predetermined rotational position of the output gear 65, a desired assist force can be obtained.
- (Embodiment 2) 13A to 13C show a schematic configuration of the spring 171 in the assist mechanism 170 of the clutch drive device according to the second embodiment.
- the spring 171 is different from the configuration of the first embodiment in that the first projecting portion 171b is located radially inward of the coil portion 171a.
- symbol is attached
- the spring 171 has a first projecting portion 171b coiled from the coil portion 171a so that one end of the wire is positioned radially inward of the cylindrical coil portion 171a.
- the portion 171a extends inward in the radial direction. That is, the first protrusion 171b is formed by bending so that one end of the wire of the spring 171 is positioned inward of the coil 171a.
- one end of the wire constituting the spring 171, that is, the tip of the first projecting portion 171 b is the coil portion. It is located at the center of 171a.
- the pin 172 is provided at the center position of the output gear 65 in the circumferential direction of the output gear 65 when viewed from the axial direction of the output shaft 63.
- the output gear 65 is disposed such that the pin 172 is positioned between the first projecting portion 171b and the coil portion 171a and is in contact with the first projecting portion 171b when viewed from the axial direction of the spring 171. . That is, the pin 172 of the output gear 65 is disposed so as to be caught by the first protrusion 171b. As a result, when the output gear 65 rotates so that the clutch 13 changes from the clutch disengaged state to the connected state, the pin 172 deforms the spring 171 so that the first projecting portion 171b approaches the second projecting portion 171c. Cause it to occur.
- the spring 171 has a first protrusion 171b that contacts the pin 172 when the pin 172 rotates around the axis of the output shaft 63 as the output gear 65 rotates.
- the bent portion 171 d is displaced in the circumferential direction of the spring 171 around the axis Q of the spring 171.
- the contact point T between the pin 172 and the first protrusion 171b of the spring 171 reciprocates with respect to the first protrusion 171b along the first protrusion 171b.
- the contact point T is located radially inward from the spring 171 when viewed from the axial direction of the spring 171.
- FIG. 13A shows the rotational position of the output gear 65 when the clutch 13 is in a disconnected state.
- FIG. 13B shows the rotational position of the output gear 65 when the clutch 13 is in the half-clutch state.
- FIG. 13C shows the rotational position of the output gear 65 when the clutch 13 is in the connected state.
- the pin 172 provided on the output gear 65 is connected to the output shaft 65.
- the region is located in the region X.
- the pin 172 is in contact with the first projecting portion 171b of the spring 171 at a position close to the base end portion (connection portion with the coil portion 171a).
- the first protrusion 171 b of the spring 171 is not significantly displaced by the pin 172 in the circumferential direction of the spring 171. Therefore, the force which the pin 172 receives by the elastic restoring force of the spring 171 is smaller than the case of FIG.13 (b) mentioned later and (c).
- the pin 172 receives a force having a direction and a size indicated by a solid arrow in FIG. 13A from the first protrusion 171 b of the spring 171.
- the first projecting portion 171b of the spring 171 When the output gear 65 is positioned at the rotational position shown in FIG. 13B, that is, when the pin 172 is positioned on the imaginary line M, the first projecting portion 171b of the spring 171 has a base end portion. It is displaced so as to be located in the region Y, that is, the proximal end portion of the first projecting portion 171b approaches the other end of the wire in the second projecting portion 171c.
- the pin 172 contacts the first projecting portion 171b of the spring 171 toward the tip.
- the spring 171 is twisted in the circumferential direction. Therefore, the spring 171 generates an elastic restoring force in a direction in which the first protrusion 171b is separated from the second protrusion 171c.
- the elastic restoring force of the spring 171 acts on the pin 172 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 171 is transmitted to the output gear 65 via the pin 172 as torque in the clutch disengagement rotation direction (rotation direction indicated by the two-dot chain line arrow in FIG. 13B). .
- a force assisting in the direction of clutch disengagement is transmitted from the spring 171 to the output gear 65 via the pin 172.
- the force which the pin 172 receives from the 1st protrusion part 171b of the spring 171 is large compared with the case of Fig.13 (a).
- the spring 171 is further twisted in the circumferential direction.
- the elastic restoring force of the spring 171 acts on the pin 172 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 171 acts on the output gear 65 via the pin 172 in the rotation direction of the clutch connection (the rotation direction of the two-dot chain line arrow in FIG. 13C).
- a force assisting in the rotational direction of the clutch connection is transmitted from the spring 171 to the output gear 65 via the pin 172.
- the contact point T between the pin 172 and the first projecting portion 171b of the spring 171 corresponds to the axial center P of the output shaft 63 and the axis Q of the spring 171 when viewed from the axial direction of the output shaft 63 according to the rotation of the output gear 65.
- the virtual line M connecting The contact point T between the pin 172 and the first projecting portion 171b is at a position different from the axial center P of the output shaft 63 and the axis Q of the spring 171 and in the direction in which the elastic restoring force of the spring 171 decreases. Is rotated (in the example of FIG. 13, when the output gear 65 is rotated in the order of FIGS.
- the axis Q of the spring 171 is viewed from the axial direction of the spring 171. Move to approach at least once.
- the elastic restoring force generated by the spring 171 can be transmitted to the output gear 65 as an assist force in the direction in which the first protrusion 171b is separated from the second protrusion 171c.
- the elastic restoring force of the spring 171 is transmitted as torque to the output gear 65 via the first protrusion 171b and the pin 172.
- the distance D between the contact point T and the axis Q of the spring 171 changes according to the rotation of the output gear 65. That is, the interval D is the smallest when the contact point T crosses the virtual line M when viewed from the axial direction of the output shaft 63, and the distance D is larger as the contact point T is farther from the virtual line M.
- the distance between the shaft center P of the output shaft 63 and the contact point T between the first protrusion 171b and the pin 72 is smaller than the distance between the shaft center P and the axis Q of the spring 171. Further, the distance between the axis Q of the spring 171 and the contact point T is smaller than the distance between the axis P of the output shaft 63 and the axis Q of the spring 171.
- the assist mechanism 170 changes the rotational position of the output gear 65 by the rotation of the motor 50 (operation driving force) so that the actuator rotation angle becomes large, that is, FIG. 13 (c), FIG. 13 (b), and FIG. 13 (a), the force acting on the pin 172 of the output gear 65 from the spring 171 becomes a parabolic shape that maximizes at a predetermined actuator rotation angle. Change. As a result, the shaft torque acting on the output shaft 63 by the assist force of the assist mechanism 170 also changes in a parabolic shape that becomes maximum at the predetermined actuator rotation angle.
- (Embodiment 3) 14A to 14C show a schematic configuration of the spring 271 in the assist mechanism 270 of the clutch drive device according to the third embodiment.
- the output shaft 63 is different from the configuration of the second embodiment in that the output shaft 63 is positioned inward of the spring 271 when viewed from the axial direction of the spring 271.
- symbol is attached
- the spring 271 has a first projecting portion 271b coiled from the coil portion 271a so that one end of the wire is positioned radially inward of the cylindrical coil portion 271a.
- the portion 271a extends inward in the radial direction. That is, the first protruding portion 271b is formed by bending so that one end of the wire of the spring 271 is positioned inward of the coil portion 271a.
- a bent portion 271d is formed between the first projecting portion 271b and the coil portion 271a continuous to the first projecting portion 271b when the spring 271 is viewed from the axial direction. It is formed.
- one end of the wire constituting the spring 271, that is, the tip of the first protruding portion 271 b is located at the center of the coil portion 271 a. Yes.
- the output shaft 63 is located inside the spring 271 when viewed from the axial direction of the spring 271.
- the pin 272 is provided in a clockwise direction from the center of the output gear 65 in the circumferential direction of the output gear 65 when viewed from the axial direction of the output shaft 63.
- the output gear 65 is disposed such that the pin 272 is positioned between the first projecting portion 271b and the coil portion 271a and is in contact with the first projecting portion 271b when viewed from the axial direction of the spring 271. . That is, the pin 272 of the output gear 65 is disposed so as to be hooked on the first protrusion 271b. Thereby, when the output gear 65 rotates, the pin 272 causes the spring 271 to be deformed so that the first projecting portion 271b approaches the second projecting portion 271c.
- the spring 271 includes a first protrusion 271b that contacts the pin 272 when the pin 272 rotates around the axis of the output shaft 63 as the output gear 65 rotates.
- the bent portion 271d is displaced in the circumferential direction of the spring 271 around the axis Q of the spring 271.
- the contact point T between the pin 272 and the first protrusion 271b of the spring 271 reciprocates with respect to the first protrusion 271b along the first protrusion 271b.
- the contact point T is located radially inward from the spring 271 when viewed from the axial direction of the spring 271.
- FIG. 14A shows the rotational position of the output gear 65 when the clutch 13 is in a disconnected state.
- FIG. 14B shows the rotational position of the output gear 65 when the clutch 13 is in the half-clutch state.
- FIG. 14C shows the rotational position of the output gear 65 when the clutch 13 is in the connected state.
- the pin 272 provided on the output gear 65 is connected to the output shaft 65.
- the pin 272 is located in the region X.
- the pin 272 is in contact with the first protrusion 271b of the spring 271 at a position close to the tip.
- the first projecting portion 271 b of the spring 271 is not significantly displaced by the pin 272 in the circumferential direction of the spring 271. Therefore, the force which the pin 272 receives by the elastic restoring force of the spring 271 is smaller than the case of FIG.14 (b), (c) mentioned later.
- the pin 272 receives a force having a direction and a size indicated by a solid arrow in FIG. 14A from the first protrusion 271 b of the spring 271.
- the bent portion 271d of the first protrusion 271b is the second protrusion. It moves so that it may approach the other end of the wire in part 271c.
- the pin 272 contacts the first projecting portion 271b of the spring 271 and contacts the bent portion 271d. Move towards.
- the spring 271 is twisted in the circumferential direction. Therefore, the spring 271 generates an elastic restoring force in a direction in which the first projecting portion 271b is separated from the second projecting portion 271c.
- the elastic restoring force of the spring 271 acts on the pin 272 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 271 is transmitted to the output gear 65 through the pin 272 as torque in the clutch disengagement rotation direction (rotation direction indicated by a two-dot chain line arrow in FIG. 14B). .
- a force assisting in the rotational direction of clutch disengagement is transmitted from the spring 271 to the output gear 65 via the pin 272.
- the force that the pin 272 receives from the first protrusion 271b of the spring 271 is larger than that in the case of FIG.
- the spring 271 is further twisted in the circumferential direction.
- the elastic restoring force of the spring 271 acts on the pin 272 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 271 acts on the output gear 65 via the pin 272 in the rotation direction of the clutch connection (the rotation direction of the two-dot chain line arrow in FIG. 14C).
- a force assisting in the rotational direction of the clutch connection is transmitted from the spring 271 to the output gear 65 via the pin 272.
- the contact point T between the pin 272 and the first projecting portion 271b of the spring 271 corresponds to the shaft center P of the output shaft 63 and the axis Q of the spring 271 when viewed from the axial direction of the output shaft 63 according to the rotation of the output gear 65.
- the virtual line M connecting The contact point T between the pin 272 and the first projecting portion 271b is at a position different from the axial center P of the output shaft 63 and the axis Q of the spring 271 and in the direction in which the elastic restoring force of the spring 271 is reduced. Is rotated (in the example of FIG. 14, when the output gear 65 is rotated in the order of FIGS.
- the axis Q of the spring 271 is viewed from the axial direction of the spring 271. Move to approach at least once. Accordingly, the elastic restoring force generated by the spring 271 can be transmitted to the output gear 65 as an assist force in a direction in which the first projecting portion 271b is separated from the second projecting portion 271c. At this time, the elastic restoring force of the spring 271 is transmitted as torque to the output gear 65 via the first protrusion 271b and the pin 272.
- the distance D between the contact point T and the axis Q of the spring 271 changes according to the rotation of the output gear 65. That is, the interval D is the smallest when the contact point T crosses the virtual line M when viewed from the axial direction of the output shaft 63, and the distance D is larger as the contact point T is farther from the virtual line M.
- the distance between the shaft center P of the output shaft 63 and the contact point T between the first protrusion 271b and the pin 272 is smaller than the distance between the shaft center P and the axis Q of the spring 271.
- the distance between the axis Q of the spring 271 and the contact point T is greater than the distance between the axis center P of the output shaft 63 and the axis Q of the spring 271 when the contact point T is located on the imaginary line M. small.
- the assist mechanism 270 changes the rotational position of the output gear 65 so that the rotation angle of the actuator becomes large, that is, the rotation angle of the motor 50 (operation driving force). 14 (c), FIG. 14 (b), and FIG. 14 (a), the force acting on the pin 272 of the output gear 65 from the spring 271 becomes a parabolic shape that maximizes at a predetermined actuator rotation angle. Change. Thereby, the shaft torque acting on the output shaft 63 by the assist force of the assist mechanism 270 also changes in a parabolic shape that becomes maximum at the predetermined actuator rotation angle.
- FIGS. 15A to 15C show a schematic configuration of the assist mechanism 370 of the clutch drive device according to the fourth embodiment. It differs from the configuration of the first embodiment in that a link 375 is provided between the pin 372 provided on the output gear 65 and the spring 371.
- a link 375 is provided between the pin 372 provided on the output gear 65 and the spring 371.
- the assist mechanism 370 includes a pin 372 provided in the output gear 65, a spring 371, and a link 375 that connects the pin 372 and the spring 371.
- the spring 371 has one end of a wire bent in a U shape when viewed from the axial direction. That is, the first projecting portion 371b is formed in a U shape when viewed from the axial direction.
- the pin 372 is provided at a position counterclockwise from the center of the output gear 65 in the circumferential direction of the output gear 65 when the output shaft 63 is viewed from above in the axial direction.
- the link 375 is a flat member formed in an L shape in plan view. That is, the link 375 has a bent portion 375a. One end of the link 375 is rotatably connected to the center of the convex portion 46. In the link 375, a long oval slide hole 375b extending from the bent portion 375a toward the other end portion is provided between the bent portion 375a and the other end portion. A pin 372 provided on the output gear 65 is slidably disposed in the slide hole 375b of the link 375. Thereby, the link 375 is connected to the pin 372 provided in the output gear 65 so as to be slidable in one direction. In FIGS. 15A to 15C, the convex portion 46 is illustrated in a simplified manner.
- a connecting pin 378 projecting in the thickness direction of the link 375 is provided at the bent portion 375a of the link 375.
- the connection pin 378 is connected to the first protrusion 371b by being positioned inward of the first protrusion 371b of the spring 371.
- the spring 371 is deformed so that the first protrusion 371b moves in the circumferential direction with respect to the second protrusion 371c in accordance with the rotation of the pin 372 around the output shaft 63 as described above. Such deformation in the spring 371 causes elastic deformation in the spring 371.
- the elastic restoring force generated by the spring 371 acts on the pin 372 via the link 375.
- the link 375 and the first projecting portion 371 b of the spring 371 are included in the output portion 379 that outputs an elastic restoring force from the spring 371.
- FIG. 15A shows the rotational position of the output gear 65 when the clutch 13 is in a disconnected state.
- FIG. 15B shows the rotational position of the output gear 65 when the clutch 13 is in the half-clutch state.
- FIG. 15C shows the rotational position of the output gear 65 when the clutch 13 is in the connected state.
- the pin 372 provided on the output gear 65 is connected to the output shaft 65.
- the region X is located in the region X.
- the first protrusion 371b is also located in the region X.
- the position of the pin 372 with respect to the slide hole 375b of the link 375 is a position close to the other end of the link 375 in the slide hole 375b. Therefore, the contact point T between the pin 372 and the peripheral edge of the slide hole 375b of the link 375 is also a position close to the other end of the link 375 in the slide hole 375b.
- the first projecting portion 371 b of the spring 371 is not significantly displaced by the pin 372 in the circumferential direction of the spring 371. Therefore, the force which the pin 372 receives by the elastic restoring force of the spring 371 is smaller than the case of FIG.15 (b) mentioned later and (c).
- the pin 372 receives a force having a direction and magnitude indicated by a solid arrow in FIG. 15A from the first protrusion 371 b of the spring 371 via the link 375.
- the first protrusion 371b is also in the position shown in FIG. Is closer to the imaginary line M.
- the position of the pin 372 with respect to the slide hole 375b of the link 375 is a position close to the bent portion 375a in the slide hole 375b. Therefore, the contact point T between the pin 372 and the peripheral edge of the slide hole 375b of the link 375 is also a position close to the bent portion 375a in the slide hole 375b.
- the spring 371 is twisted in the circumferential direction so that the first protrusion 371b approaches the second protrusion 371c. Therefore, the spring 371 generates an elastic restoring force in a direction in which the first protrusion 371b is separated from the second protrusion 371c.
- the elastic restoring force of the spring 371 acts on the pin 372 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 371 is transmitted to the output gear 65 through the pin 372 as torque in the clutch disconnection rotation direction (rotation direction indicated by a two-dot chain line arrow in FIG. 15B). .
- the output gear 65 When the output gear 65 is positioned at the rotational position shown in FIG. 15C, that is, when the pin 372 is positioned in the region Y of the two regions X and Y, the first protrusion 371b is , Closer to the second protrusion 371c than in the case of FIG. At this time, the position of the pin 372 with respect to the slide hole 375b of the link 375 is a position near the center in the longitudinal direction in the slide hole 375b. Therefore, the contact point T between the pin 372 and the peripheral edge of the slide hole 375b of the link 375 is also a position near the center in the longitudinal direction of the slide hole 375b.
- the elastic restoring force generated by the spring 371 acts on the pin 372 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 371 acts on the output gear 65 via the pin 372 in the rotation direction of the clutch connection (the rotation direction of the two-dot chain line arrow in FIG. 15C). As a result, a force assisting in the rotational direction of the clutch connection is transmitted from the spring 371 to the output gear 65 via the pin 372.
- the pin 372 straddles an imaginary line M connecting the axis center P of the output shaft 63 and the axis Q of the spring 371 as viewed from the axial direction of the output shaft 63 according to the rotation of the output gear 65.
- the contact point T between the pin 372 and the peripheral edge of the slide hole 375b is at a position different from the axial center P of the output shaft 63 and the axis Q of the spring 371, and in the direction in which the elastic restoring force of the spring 371 is reduced.
- the elastic restoring force generated by the spring 371 can be transmitted to the output gear 65 as an assist force in a direction in which the first projecting portion 371b is separated from the second projecting portion 371c. At this time, the elastic restoring force of the spring 371 is transmitted as torque to the output gear 65 via the first protrusion 371b and the pin 372.
- the distance D between the contact point T and the axis Q of the spring 371 changes according to the rotation of the output gear 65. That is, the interval D is the smallest when the contact point T crosses the virtual line M when viewed from the axial direction of the output shaft 63, and the distance D is larger as the contact point T is farther from the virtual line M.
- the distance between the shaft center P of the output shaft 63 and the contact point T between the first protrusion 371b and the pin 72 is smaller than the distance between the shaft center P and the axis Q of the spring 371. Further, the distance between the axis Q of the spring 371 and the contact point T is larger than the distance between the axis center P of the output shaft 63 and the axis Q of the spring 371 when the contact point T is located on the imaginary line M. small.
- the assist mechanism 370 changes the rotational position of the output gear 65 so that the rotation angle of the actuator becomes large, that is, the rotation angle of the motor 50 (operation driving force). 15 (c), FIG. 15 (b), and FIG. 15 (a), the force acting on the pin 372 of the output gear 65 from the spring 371 becomes a parabolic shape that becomes maximum at a predetermined actuator rotation angle. Change. As a result, the shaft torque acting on the output shaft 63 by the assist force of the assist mechanism 370 also changes in a parabolic shape that becomes maximum at the predetermined actuator rotation angle.
- the output unit 379 includes a link 375 that rotates relative to the rotation of the output gear 65 and the deformation of the spring 371 in the circumferential direction.
- FIGS. 16A to 16C show a schematic configuration of the assist mechanism 470 of the clutch driving device according to the fifth embodiment.
- the configuration of the link 475 provided between the pin 472 provided on the output gear 65 and the spring 371 is different from the configuration of the link 375 in the fourth embodiment.
- symbol is attached
- the assist mechanism 470 includes a pin 472 provided on the output gear 65, a spring 371, and a link 475 that connects the pin 472 and the spring 371.
- the pin 472 is provided at a position in the clockwise direction from the center of the output gear 65 in the circumferential direction of the output gear 65 when the output shaft 63 is viewed from above in the axial direction.
- the link 475 has a first link part 476 and a second link part 477.
- the first link portion 476 and the second link portion 477 are each formed in a flat plate shape that is long in one direction.
- the first link portion 476 is bent in the width direction (short direction) at the center portion in the longitudinal direction, and is formed in a V shape in plan view.
- a connection pin 478 projecting in the thickness direction is provided at the center portion in the longitudinal direction of the first link portion 476.
- the connection pin 478 is connected to the first protrusion 371b by being positioned inward of the first protrusion 371b of the spring 371.
- the first link portion 476 is rotatably supported at one center in the longitudinal direction at the center of the convex portion 46.
- the other one of the first link portions 476 in the longitudinal direction is rotatably connected to one of the second link portions 477 in the longitudinal direction.
- the other end of the second link portion 477 in the longitudinal direction is rotatably connected to the pin 472 of the output gear 65.
- FIG. 16A shows the rotational position of the output gear 65 when the clutch 13 is in a disconnected state.
- FIG. 16B shows the rotational position of the output gear 65 when the clutch 13 is in the half-clutch state.
- FIG. 16C shows the rotational position of the output gear 65 when the clutch 13 is in the connected state.
- the pin 472 provided on the output gear 65 is connected to the output shaft 63.
- the region X and Y obtained by dividing the internal space of the casing main body 41 into two by a virtual line M connecting the shaft center P and the axis Q of the spring 371, it is located in the region X.
- the force that the pin 472 receives by the elastic restoring force of the spring 371 is applied to the output gear 65 in the direction of clutch disengagement (the two-dot chain line arrow in FIG. 16A). (Rotation direction). That is, torque is applied to the output gear 65 in the rotational direction of clutch disengagement by the spring 371 via the pin 472.
- the force received by the pin 472 by the elastic restoring force of the spring 371 coincides with the longitudinal direction of the second link portion 477.
- the first projecting portion 371b of the spring 371 is not significantly displaced by the pin 472 in the circumferential direction of the spring 371. Therefore, the force that the pin 472 receives by the elastic restoring force of the spring 371 via the link 475 is smaller than in the case of FIGS. 16B and 16C described later.
- the pin 472 receives a force having a direction and magnitude indicated by a solid arrow in FIG. 16A from the first protrusion 371 b of the spring 371.
- the first protrusion 371b is It is closer to the virtual line M than the position shown in FIG. Therefore, the spring 371 is twisted in the circumferential direction so that the first protrusion 371b approaches the second protrusion 371c. Accordingly, the spring 371 generates a larger elastic restoring force in the direction in which the first protrusion 371b is separated from the second protrusion 371c.
- the elastic restoring force of the spring 371 acts on the pin 472 as shown by the solid line arrow in FIG.
- the elastic restoring force of the spring 371 is transmitted to the output gear 65 through the pin 472 as torque in the clutch disengagement rotation direction (rotation direction indicated by a two-dot chain line arrow in FIG. 16B). .
- a force assisting in the direction of clutch disengagement is transmitted from the spring 371 to the output gear 65 via the pin 472.
- the force that the pin 472 receives from the first protrusion 371b of the spring 371 is larger than that in the case of FIG.
- the second link portion 477 When the output gear 65 is positioned at the rotational position shown in FIG. 16C, that is, when the pin 472 is positioned in the region Y of the two regions X and Y, the second link portion 477 is It rotates with respect to the first link portion 476 about one side in the longitudinal direction. At this time, the second link portion 477 rotates together with the output gear 65.
- the elastic restoring force generated by the spring 371 acts on the pin 472 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 371 acts on the output gear 65 via the pin 472 in the rotation direction of the clutch connection (the rotation direction of the two-dot chain line arrow in FIG. 16C). As a result, a force assisting in the rotational direction of the clutch connection is transmitted from the spring 371 to the output gear 65 via the pin 472.
- the pin 472 straddles an imaginary line M connecting the shaft center P of the output shaft 63 and the axis Q of the spring 371 as viewed from the axial direction of the output shaft 63 according to the rotation of the output gear 65.
- the assist mechanism 470 changes the rotational position of the output gear 65 so that the rotation angle of the actuator increases by the rotation of the motor 50 (operation driving force), that is, FIG.
- the force acting on the pin 472 of the output gear 65 from the spring 371 becomes a parabolic shape that becomes maximum at a predetermined actuator rotation angle. Change.
- the shaft torque acting on the output shaft 63 by the assist force of the assist mechanism 470 also changes in a parabolic shape that becomes maximum at the predetermined actuator rotation angle.
- the contact point between the pin 472 and the second link part 477 of the link 475 corresponds to the contact point between the transmission part and the output part.
- FIG. 6 shows a schematic configuration of the assist mechanism 570 of the clutch drive device according to the sixth embodiment.
- the configuration of the pin 572 that contacts the first protrusion 71 b of the spring 71 is different from that of the first embodiment.
- symbol is attached
- the pin 572 provided in the output gear 65 has a protruding portion 572a protruding in the radial direction.
- the protruding portion 572a is formed with an acute angle at the tip as viewed from the axial direction of the output shaft 63.
- the pin 572 has a semicircular cylindrical portion 572b on the side opposite to the protruding portion 572a when viewed from the axial direction. That is, the pin 572 has a shape in which a protruding portion 572a is integrally provided on a columnar member.
- the pin 572 is provided at a position in the clockwise direction from the center of the output gear 65 in the circumferential direction of the output gear 65 when the output shaft 63 is viewed from above in the axial direction.
- the pin 572 is in contact with the first protrusion 71b of the spring 71. Therefore, when the output gear 65 rotates, the pin 572 moves relative to the first protrusion 71b while being in contact with the first protrusion 71b. At this time, the position where the pin 572 contacts the first protrusion 71 b moves in the circumferential direction of the pin 572 according to the rotation of the output gear 65. As described above, since the pin 572 is a member in which the protruding portion 572a is provided on the cylindrical member, the protruding portion 572a of the pin 572 or the cylindrical portion 572b is the first protruding portion according to the rotation of the output gear 65. 71b is contacted.
- the spring 71 includes a first protrusion 71b that contacts the pin 572 when the pin 572 rotates around the axis of the output shaft 63 as the output gear 65 rotates. However, it is displaced in the circumferential direction of the spring 71 with respect to the second protrusion 71c. At this time, the contact point T between the pin 572 and the first protrusion 71b of the spring 71 reciprocates with respect to the first protrusion 71b along the first protrusion 71b. The contact point T is located radially outward from the spring 71 when viewed from the axial direction of the spring 71.
- FIG. 17A shows the rotational position of the output gear 65 when the clutch 13 is in a disconnected state.
- FIG. 17B shows the rotational position of the output gear 65 when the clutch 13 is in the half-clutch state.
- FIG. 17C shows the rotational position of the output gear 65 when the clutch 13 is in the connected state.
- the pin 572 when the output gear 65 is positioned at the rotational position shown in FIG. 17A when viewed from the axial direction of the output shaft 63, that is, the pin 572 and the spring 71 provided on the output gear 65.
- the contact point T with the first projecting portion 71 b is located in the vicinity of an imaginary line M connecting the axis center P of the output shaft 63 and the axis Q of the spring 71, the pin 572 is One projecting portion 71b is in contact with the vicinity of the center in the projecting direction. At this time, the pin 572 is in contact with the first protrusion 71b at the tip of the protrusion 572a.
- the contact point T between the pin 572 and the first protrusion 71b is divided into two regions X and X obtained by dividing the internal space of the casing body 41 into two by the virtual line M. Of Y, it is located in region Y.
- the protrusion 572a of the pin 572 is in contact with the first protrusion 71b of the spring 71, the cylindrical portion 572b of the pin 572 is located in the region X of the two regions X and Y.
- the pin 572 receives a force having a direction and magnitude indicated by a solid arrow in FIG. 17A from the first protrusion 71 b of the spring 71.
- the output gear 65 When the output gear 65 is positioned at the rotational position shown in FIG. 17B, that is, when the cylindrical portion 572 b of the pin 572 is positioned on the imaginary line M, the protruding portion 572 a and the cylindrical portion 572 b of the pin 572.
- the connecting portion contacts with the first protrusion 71 b of the spring 71.
- the contact point T between the pin 572 and the first projecting portion 71b of the spring 71 is a position close to the base end portion (connecting portion with the coil portion 71a) of the first projecting portion 71b.
- the contact point T moves so as to approach the proximal end portion of the first protrusion 71 b of the spring 71.
- the first protrusion 71b is displaced so as to approach the second protrusion 71c.
- the spring 71 is twisted in the circumferential direction. Therefore, the spring 71 generates an elastic restoring force in a direction in which the first protrusion 71b is separated from the second protrusion 71c.
- the elastic restoring force of the spring 71 acts on the pin 572 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 71 is transmitted to the output gear 65 through the pin 572 as torque in the clutch disengagement rotation direction (rotation direction indicated by a two-dot chain line arrow in FIG. 17B). .
- a force assisting in the rotational direction of the clutch disengagement is transmitted from the spring 71 to the output gear 65 via the pin 572.
- the force that the pin 572 receives from the first protrusion 71b of the spring 71 is larger than that in the case of FIG.
- the spring 71 is further twisted in the circumferential direction.
- the elastic restoring force of the spring 71 acts on the pin 572 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 71 acts on the output gear 65 via the pin 572 in the rotation direction of the clutch connection (the rotation direction of the two-dot chain line arrow in FIG. 17C).
- a force assisting in the rotational direction of the clutch connection is transmitted from the spring 71 to the output gear 65 via the pin 572.
- the contact point T between the pin 572 and the first protrusion 71 b of the spring 71 is output as viewed from the axial direction of the output shaft 63 according to the rotation of the output gear 65.
- An imaginary line M connecting the axis center P of the shaft 63 and the axis Q of the spring 71 does not straddle. That is, according to the rotation of the output gear 65, the contact point T moves only in the region Y of the two regions X and Y.
- the contact point T between the pin 572 and the first projecting portion 71b is a position different from the axis center P of the output shaft 63 and the axis Q of the spring 71.
- the output gear 65 rotates in a direction in which the elastic restoring force of the spring 71 decreases (in the example of FIG. 17, the output gear 65 rotates in the order of FIGS. 17C, 17B, and 17A).
- it moves so as to approach the axial line Q of the spring 71 at least once.
- the elastic restoring force generated by the spring 71 can be transmitted to the output gear 65 as an assist force in a direction in which the first protrusion 71b is separated from the second protrusion 71c. At this time, the elastic restoring force of the spring 71 is transmitted as torque to the output gear 65 via the first protrusion 71 b and the pin 572.
- the distance D between the contact point T and the axis Q of the spring 71 changes according to the rotation of the output gear 65.
- the distance D is such that the contact point T between the pin 572 and the first protrusion 71b of the spring 71 is on the imaginary line M as viewed from the axial direction of the output shaft 63.
- it is the smallest when it is located at the position of the contact point T, and the contact point T is larger as it is farther from the virtual line M.
- the distance D can be changed by changing the shape of the pin 572. Therefore, the assist force obtained by the assist mechanism 570 can be changed depending on the shape of the pin 572. Thereby, a desired assist force can be obtained.
- the distance between the shaft center P of the output shaft 63 and the contact point T between the first protrusion 71 b and the pin 572 is smaller than the distance between the shaft center P and the axis Q of the spring 71.
- the distance between the axis Q of the spring 71 and the contact point T is greater than the distance between the axis center P of the output shaft 63 and the axis Q of the spring 71 when the contact point T is located on the virtual line M. small.
- the assist mechanism 570 changes the rotational position of the output gear 65 so that the rotation angle of the actuator becomes larger, that is, the diagram of FIG.
- the force acting on the pin 572 provided on the output gear 65 from the spring 71 becomes maximum at a predetermined actuator rotation angle. It changes into a parabolic shape.
- the shaft torque acting on the output shaft 63 by the assist force of the assist mechanism 570 also changes in a parabolic shape that becomes maximum at the predetermined actuator rotation angle.
- FIG. 7 shows a schematic configuration of the assist mechanism 670 of the clutch driving device according to the seventh embodiment.
- the position of the pin 672 in the output gear 65 is different from that of the first embodiment.
- symbol is attached
- the pin 672 is a cylindrical member like the pin 72 in the first embodiment, and is provided on the output gear 65 so as to protrude in the thickness direction of the output gear 65.
- the pin 672 is positioned more clockwise than the center of the output gear 65 in the circumferential direction of the output gear 65 when the output gear 65 is viewed from above in the axial direction. is doing. As a result, when the output gear 65 is rotated in the clockwise direction when the output gear 65 is viewed from above in the axial direction, the pin 672 comes into contact with the first protrusion 71 b of the spring 71.
- the spring 71 when the pin 672 rotates around the axis of the output shaft 63 as the output gear 65 rotates, the spring 71 has one end of the wire that contacts the pin 672, The spring 71 is displaced in the circumferential direction with respect to the other end of the wire. At this time, the contact point T between the pin 672 and the first protrusion 71b including one end of the wire rod of the spring 71 moves relative to the first protrusion 71b along the first protrusion 71b. The contact point T is located radially outward from the spring 71 when viewed from the axial direction of the spring 71.
- FIG. 18A shows the rotational position of the output gear 65 when the clutch 13 is in a disconnected state.
- FIG. 18B shows the rotational position of the output gear 65 when the clutch 13 is in the half-clutch state.
- FIG. 18C shows the rotational position of the output gear 65 when the clutch 13 is in the connected state.
- the pin 672 provided on the output gear 65 is connected to the output shaft 65.
- the pin 672 is positioned on an imaginary line M that connects the axial center P of 63 and the axis Q of the spring 71, the pin 672 is positioned near the base end with respect to the first protrusion 71 b of the spring 71. ing.
- the contact point T between the pin 672 and the first projecting portion 71b is obtained by dividing the internal space of the casing body 41 into two regions X, Of Y, it is located in region Y.
- the pin 672 receives a force having a direction and magnitude indicated by a solid arrow in FIG. 18A from the first protrusion 71 b of the spring 71.
- the pin 672 When the output gear 65 is positioned at the rotational position shown in FIG. 18B, that is, the pin 672 is located in the region Y of the two regions X and Y, and the center in the circumferential direction of the output gear 65 is an imaginary line. When positioned on M, the pin 672 contacts the first protrusion 71b of the spring 71 near the center in the protrusion direction.
- the spring 71 is twisted in the circumferential direction. Therefore, the spring 71 generates an elastic restoring force in a direction in which the first protrusion 71b is separated from the second protrusion 71c.
- the elastic restoring force of the spring 71 acts on the pin 672 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 71 is transmitted to the output gear 65 through the pin 672 as torque in the clutch disengagement rotation direction (rotation direction indicated by a two-dot chain line arrow in FIG. 18B). .
- a force assisting in the direction of clutch disengagement is transmitted from the spring 71 to the output gear 65 via the pin 672.
- the pin 672 When the output gear 65 is positioned at the rotational position shown in FIG. 18C, that is, the pin 672 is located in the region Y of the two regions X and Y, and more than half of the output gear 65 is in the region Y. When positioned, the pin 672 is positioned closer to the tip than the position shown in FIG. 18B with respect to the first protrusion 71 b of the spring 71.
- the elastic restoring force of the spring 71 acts on the pin 672 as shown by the solid line arrow in FIG.
- the elastic restoring force of the spring 71 acts on the output gear 65 via the pin 672 in the rotation direction of the clutch connection (the rotation direction of the two-dot chain line arrow in FIG. 18C).
- a force assisting in the rotational direction of the clutch connection is transmitted from the spring 71 to the output gear 65 via the pin 672.
- the contact point T between the pin 672 and the first protrusion 71 b of the spring 71 is output as viewed from the axial direction of the output shaft 63 according to the rotation of the output gear 65.
- An imaginary line M connecting the axis center P of the shaft 63 and the axis Q of the spring 71 does not straddle. That is, according to the rotation of the output gear 65, the contact point T moves only in the region Y of the two regions X and Y.
- the contact point T between the pin 672 and the first projecting portion 71b is at a position different from the axial center P of the output shaft 63 and the axis Q of the spring 71, and in the direction in which the elastic restoring force of the spring 71 decreases.
- the elastic restoring force generated by the spring 71 can be transmitted to the output gear 65 as an assist force in a direction in which the first protrusion 71b is separated from the second protrusion 71c.
- the elastic restoring force of the spring 71 is transmitted as torque to the output gear 65 via the first protrusion 71 b and the pin 672.
- the distance D between the contact point T and the axis Q of the spring 71 changes according to the rotation of the output gear 65.
- the interval D is the smallest when the contact point T between the pin 672 and the first protrusion 71b is located on the imaginary line M when viewed from the axial direction of the output shaft 63, while the contact point T is the imaginary line M. The farther it is, the bigger it is.
- the interval D is the smallest when the clutch 13 is in the disengaged state (FIG. 18A). Therefore, when the clutch 13 is switched from the disconnected state to the connected state, the interval D increases.
- the distance between the shaft center P of the output shaft 63 and the contact point T between the first protrusion 71 b and the pin 672 is smaller than the distance between the shaft center P and the axis Q of the spring 71.
- the distance between the axis Q of the spring 71 and the contact point T is greater than the distance between the axis center P of the output shaft 63 and the axis Q of the spring 71 when the contact point T is located on the virtual line M. small.
- the assist mechanism 670 changes the rotation position of the output gear 65 so that the rotation angle of the actuator becomes large, that is, FIG. 18C and FIG. 18), the force acting on the pin 672 provided on the output gear 65 from the spring 71 gradually increases in the direction in which the clutch 13 is disengaged.
- the torque acting on the output shaft 63 by the assist force of the assist mechanism 670 also increases so that the torque acting in the rotational direction of disengagement of the clutch 13 increases as the actuator rotation angle increases. Change.
- the shaft torque generated in the output shaft 63 increases due to the reaction force of the clutch when the actuator rotation angle increases.
- the assist force of the assist mechanism 670 can reduce the drive force when the clutch 13 is driven. Therefore, the operation driving force of the motor 50 can be reduced.
- S is an actuator rotation angle at which the clutch 13 starts to be disengaged when the actuator rotation angle increases, and when the actuator rotation angle decreases, the friction with the clutch plate 23 of the clutch 13 occurs. This is the actuator rotation angle at which the connection with the plate 24 is completed.
- the first protrusions 71b, 171b, 271b, 371b are displaced so as to approach the second protrusions 71c, 171c, 271c, 371c in the circumferential direction of the springs 71, 171, 271 and 371.
- the elastic restoring force obtained by the above is transmitted to the pins 72, 572, 672 and used as an assist force.
- the elastic restoring force obtained by separating the first protrusion 771b from the second protrusion 771c in the circumferential direction of the spring 771 is transmitted to the pin 772. By doing so, it may be used as an assist force.
- the spring 771 includes a coil portion 771a, a first projecting portion 771b, and a second projecting portion 771c.
- the first protrusion 771 b is provided in a counterclockwise position in the circumferential direction of the spring 771 with respect to the second protrusion 771 c when viewed from above in the axial direction of the output shaft 63.
- the wire 77 is wound counterclockwise when the spring 771 is viewed from the first protrusion 771b in the axial direction.
- the spring 771 is a reverse-wound spring with respect to the springs 71, 171, 271, and 371 in the above embodiments.
- the 2nd protrusion part 771c is being fixed to the casing main body 41 etc. so that it may not move with respect to the casing main body 41, for example.
- the elastic restoring force is generated in the spring 771 by deforming the first protruding portion 771b so as to be separated from the second protruding portion 771c in the circumferential direction of the spring 771.
- the spring 771 is deformed so as to increase in diameter.
- the pin 772 is provided at a position in the clockwise direction from the center of the output gear 65 in the circumferential direction of the output gear 65 when the output shaft 63 is viewed from above in the axial direction.
- the spring 771 includes a first protrusion 771b that contacts the pin 772 when the pin 772 rotates around the axis of the output shaft 63 as the output gear 65 rotates. However, the spring 771 is displaced in the circumferential direction. At this time, the contact point T between the pin 772 and the first protrusion 771b of the spring 771 reciprocates with respect to the first protrusion 771b along the first protrusion 771b.
- FIG. 20A shows the rotational position of the output gear 65 when the clutch 13 is in a disconnected state.
- FIG. 20B shows the rotational position of the output gear 65 when the clutch 13 is in the half-clutch state.
- FIG. 20C shows the rotational position of the output gear 65 when the clutch 13 is in the connected state.
- the pin 772 provided on the output gear 65 is connected to the output shaft 65.
- the pin 772 is located in the region X.
- the pin 772 is in contact with the first projecting portion 771b of the spring 771 at a position between the center in the projecting direction and the base end portion (connecting portion with the coil portion 771a).
- the first protrusion 771b of the spring 771 is not significantly displaced by the pin 772 in the circumferential direction of the spring 771. Therefore, the force that the pin 772 receives by the elastic restoring force of the spring 771 is smaller than in the case of FIGS. 20B and 20C described later.
- the pin 772 receives a force having a direction and a size indicated by a solid arrow in FIG. 20A from the first protrusion 771 b of the spring 771.
- the pin 772 When the output gear 65 is positioned at the rotational position shown in FIG. 20B, that is, when the pin 772 is positioned on the imaginary line M, the pin 772 is proximal to the first protrusion 771b. Touch at the position of the part. At this time, the first protrusion 771b of the spring 771 is displaced so that the base end is located in the region Y, that is, the base end of the first protrusion 771b is separated from the second protrusion 771c. To do. For example, when the output gear 65 is changed from the position shown in FIG. 20A to the position shown in FIG. 20B, the pin 772 is in contact with the first projecting portion 771b of the spring 771 at the proximal end portion. Move towards.
- the spring 771 is twisted in the circumferential direction. Therefore, the spring 771 generates an elastic restoring force in a direction in which the first protrusion 771b approaches the second protrusion 771c.
- the elastic restoring force of the spring 771 acts on the pin 772 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 771 is transmitted to the output gear 65 through the pin 772 as torque in the clutch disengagement rotation direction (rotation direction indicated by the two-dot chain line arrow in FIG. 20B). .
- a force assisting in the rotational direction of the clutch disengagement is transmitted from the spring 771 to the output gear 65 via the pin 772.
- the force that the pin 772 receives from the first protrusion 771b of the spring 771 is larger than that in the case of FIG.
- the spring 771 is further twisted in the circumferential direction.
- the elastic restoring force of the spring 771 acts on the pin 772 as shown by the solid line arrow in FIG. That is, the elastic restoring force of the spring 771 acts on the output gear 65 via the pin 772 in the rotation direction of the clutch connection (the rotation direction of the two-dot chain line arrow in FIG. 20C).
- a force assisting in the rotational direction of the clutch connection is transmitted from the spring 771 to the output gear 65 via the pin 772.
- the contact point T between the pin 772 and the first projecting portion 771 b of the spring 771 corresponds to the axial center P of the output shaft 63 and the axis Q of the spring 771 when viewed from the axial direction of the output shaft 63 according to the rotation of the output gear 65.
- the virtual line M connecting The contact point T between the pin 772 and the first projecting portion 771b is at a position different from the axis center P of the output shaft 63 and the axis Q of the spring 771, and in the direction in which the elastic restoring force of the spring 771 is reduced. Is rotated (in the example of FIG. 20, when the output gear 65 is rotated in the order of FIGS.
- the axis Q of the spring 771 is viewed from the axial direction of the spring 771. Move to approach at least once. Thereby, the elastic restoring force generated by the spring 771 can be transmitted to the output gear 65 as an assist force in a direction in which the first protrusion 771b approaches the second protrusion 771c. At this time, the elastic restoring force of the spring 771 is transmitted as torque to the output gear 65 via the first protrusion 771b and the pin 772.
- the distance D between the contact point T and the axis Q of the spring 771 changes according to the rotation of the output gear 65. That is, the interval D is the smallest when the contact point T crosses the virtual line M when viewed from the axial direction of the output shaft 63, and the distance D is larger as the contact point T is farther from the virtual line M.
- the distance between the shaft center P of the output shaft 63 and the contact point T between the first protrusion 771b and the pin 772 is smaller than the distance between the shaft center P and the axis Q of the spring 771. Further, the distance between the axis Q of the spring 771 and the contact point T is larger than the distance between the axis center P of the output shaft 63 and the axis Q of the spring 771 when the contact point T is located on the imaginary line M. small.
- the assist mechanism changes the rotational position of the output gear 65 so that the rotation angle of the actuator becomes large, that is, the diagram of FIG. 20 (c), FIG. 20 (b), and FIG. 20 (a) change in order, so that the force acting on the pin 772 of the output gear 65 from the spring 771 becomes a parabolic shape that becomes maximum at a predetermined actuator rotation angle. Change.
- the shaft torque acting on the output shaft 63 by the driving force of the clutch drive device also changes in a parabolic shape that becomes maximum at the predetermined actuator rotation angle.
- the clutch 13 has a so-called normal close type configuration in which the clutch 13 is in a connected state when the assist force output from the clutch driving device is zero.
- the clutch 13 may have a so-called normal open type configuration that is in a disconnected state when the assist force output from the clutch driving device is zero.
- the clutch 13 and the clutch drive device are configured such that when the actuator rotation angle is increased, the clutch reaction force is reduced by the clutch 13 and the assist force generated by the clutch drive device is also reduced. May be. That is, in the case of FIG. 21, when the actuator rotation angle is large, the clutch 13 is in a disconnected state, and when the actuator rotation angle is small, the clutch 13 is switched from the disconnected state to the connected state. In FIG. 21, the clutch 13 is in a connected state when the actuator rotation angle is zero.
- S is an actuator rotation angle at which the clutch 13 starts to be connected when the actuator rotation angle is small, and when the actuator rotation angle is large, the clutch 13 is an actuator that has been disconnected. It is a rotation angle.
- the pins 72, 172, 272, 372, 472, and 672 provided on the output gear 65 are cylindrical.
- the shape of the pin can be any It may be a shape.
- the shape of the springs 71, 171, 271, and 371 in each of the embodiments can be any configuration as long as it can generate an elastic restoring force that can reduce the actuation driving force necessary for the switching operation of the clutch 13. It may be a shape.
- the pins 72, 172, 272, 572, 672 are in direct contact with the first protrusions 71b, 171b, 271b, 371b of the springs 71, 171, 271, 371.
- another member may be provided on the first protrusions 71b, 171b, 271b, and 371b of the springs 71, 171, 271, and 371, and the pins 72, 172, 272, 572, and 672 may be brought into contact with the other members. .
- the link 475 includes the first link portion 476 and the second link portion 477.
- the link may be configured by three or more link members as long as the link can transmit the elastic restoring force of the spring 371 to the output gear 65.
- the push rod 29 of the clutch 13 moves in the axial direction of the main shaft 15 by the rotating shaft 31 connected to the link mechanism 16.
- the output of the clutch driving device 14 may be directly transmitted to the rotating shaft 31 without using the link mechanism 16.
- the output shaft 63 is cited as an example of a transmission member to which the output of the clutch driving device 14 and the clutch reaction force generated in the clutch 13 are input.
- the transmission member is a component to which the output of the motor 50 and the assist mechanism 70 and the clutch reaction force generated by the clutch 13 are input, such as the output gear 65 and the rotary shaft 31, the output shaft Components other than 63 may be used.
- the clutch driving device 14 transmits the rotation from the input shaft 61 to the output shaft 63 via the intermediate shaft 62.
- the input shaft 61 and the output shaft 63 may be configured to transmit rotation directly by a gear.
- the clutch driving device 14 includes the friction mechanism 80 as an example of a self-locking mechanism.
- the self-locking function may be realized by other configurations.
- the clutch drive device 14 may not include a self-locking mechanism such as the friction mechanism 80.
- the clutch driving device 14 includes the motor 50 that generates an operation driving force for operating the clutch 13.
- the clutch drive device 14 may have another drive source capable of generating the operation drive force.
- the gears 61a and 62a, the intermediate gear 64, and the output gear 65 that transmit the rotation of the input shaft 61 to the output shaft 63 are spur gears.
- these gears may be spur gears and the rest may be gears of other shapes.
- all of the gears described above may be gears having shapes other than spur gears.
- the input shaft 61 is provided with the gear 61a, and the intermediate shaft 62 is also provided with the gear 62a.
- the gear 61a may be provided integrally with the input shaft 61 or may be configured by another component.
- the gear 62a may be provided integrally with the intermediate shaft 62 or may be configured by another component.
- the cylinder axis direction of the casing 40, the axial directions of the input shaft 61, the intermediate shaft 62 and the output shaft 63, and the axial direction of the spring 71 are the same direction.
- the cylinder axis direction of the casing 40, the axial directions of the input shaft 61 and the output shaft 63, and the axial direction of the spring 71 may be different from each other.
- the clutch drive device includes springs 71, 171, 271 and 371 that are torsion springs.
- the clutch driving device may include a configuration other than a spring that is a torsion spring, such as a spring configured by a leaf spring.
- the vehicle 1 may be any configuration as long as the vehicle 1 includes a clutch driving device that drives a clutch, such as a three-wheeled vehicle or a four-wheeled vehicle. It may be.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
<全体構成>
図1に、本発明の実施形態1に係るクラッチ駆動装置14を備えた車両1の模式図を示す。車両1は、例えば、自動2輪車であり、車体2と、前輪3と、後輪4とを備える。車体2は、図示しないフレームを有する。車体2のフレームには、後輪4に対して回転駆動力を供給するためのエンジンユニット10が取り付けられている。
図2に示すように、リンク機構16は、回転軸31と、アーム部32とを備える。リンク機構16は、後述するクラッチ駆動装置14の出力を、クラッチ13のプッシュロッド29に伝達する。
以下で、図2から図12を用いて、クラッチ駆動装置14の構成について説明する。本実施形態におけるクラッチ駆動装置14は、モータ50(アクチュエータ)の出力に、アシスト機構70によるアシスト力を加えることによって得られる駆動力を、クラッチ13に出力する。
次に、摩擦機構80の構成を、図2から図4、図11及び図12を用いて説明する。図11は、摩擦機構80を拡大して示す図である。図12は、回転伝達部及び回転板の構成を示す斜視図である。摩擦機構80は、伝達機構60の中間軸62に作用する回転方向のトルクが所定値以下の場合に、中間軸62を、回転板81及び一対の摩擦板82の摩擦によって静止した状態で保持する。これにより、例えば車両が停止している際にモータ50の駆動を停止した場合でも、摩擦機構80によって、クラッチ13の切断状態を保持することが可能である。
図13(a)~(c)に、実施形態2に係るクラッチ駆動装置のアシスト機構170におけるスプリング171の概略構成を示す。スプリング171は、第1突出部171bがコイル部171aの径方向内方に位置している点で、実施形態1の構成とは異なる。以下では、実施形態1と同様の構成には同一の符号を付して説明を省略し、実施形態1と異なる部分についてのみ説明する。
図14(a)~(c)に、実施形態3に係るクラッチ駆動装置のアシスト機構270におけるスプリング271の概略構成を示す。出力軸63が、スプリング271の軸線方向から見て、スプリング271の内方に位置している点で、実施形態2の構成とは異なる。以下では、実施形態2と同様の構成には同一の符号を付して説明を省略し、実施形態2と異なる部分についてのみ説明する。
図15(a)~(c)に、実施形態4に係るクラッチ駆動装置のアシスト機構370の概略構成を示す。出力ギア65に設けられたピン372とスプリング371との間に、リンク375が設けられている点で、実施形態1の構成とは異なる。以下では、実施形態1と同様の構成には同一の符号を付して説明を省略し、実施形態1と異なる部分についてのみ説明する。
図16(a)~(c)に、実施形態5に係るクラッチ駆動装置のアシスト機構470の概略構成を示す。この実施形態は、出力ギア65に設けられたピン472とスプリング371との間に設けられたリンク475の構成が、実施形態4におけるリンク375の構成とは異なる。以下では、実施形態4と同様の構成には同一の符号を付して説明を省略し、実施形態4と異なる部分についてのみ説明する。
図17(a)~(c)に、実施形態6に係るクラッチ駆動装置のアシスト機構570の概略構成を示す。この実施形態に係るアシスト機構570では、スプリング71の第1突出部71bに接触するピン572の構成が、実施形態1の構成とは異なる。以下では、実施形態1と同様の構成には同一の符号を付して説明を省略し、実施形態1と異なる部分についてのみ説明する。
図18(a)~(c)に、実施形態7に係るクラッチ駆動装置のアシスト機構670の概略構成を示す。この実施形態に係るアシスト機構670では、出力ギア65におけるピン672の位置が、実施形態1の構成とは異なる。以下では、実施形態1と同様の構成には同一の符号を付して説明を省略し、実施形態1と異なる部分についてのみ説明する。
以上、本発明の実施の形態を説明したが、上述した実施の形態は本発明を実施するための例示に過ぎない。よって、上述した実施の形態に限定されることなく、その趣旨を逸脱しない範囲内で上述した実施の形態を適宜変形して実施することが可能である。
13 クラッチ
14 クラッチ駆動装置
16 リンク機構
50 モータ(アクチュエータ)
63 出力軸
65 出力ギア(回転体)
70、170、270、370、470、570、670 アシスト機構
71、171、271、371、771 スプリング
71b、171b、271b、371b、771b 第1突出部(出力部)
71c、171c、271c、371c、771c 第2突出部
72、172、272、372、472、572、672、772 ピン(伝達部)
375、475 リンク
379、479 出力部
476 第1リンク部
477 第2リンク部
P 出力軸の軸中心(回転軸)
Q スプリングの軸線
D 接触点とスプリングの軸線との間隔
T 接触点
Claims (13)
- クラッチの切断及び接続の各動作を補助するためのアシスト力を供給するクラッチ駆動装置であって、
軸線を中心に螺旋状に延び、且つ、軸線方向から見て周方向の変形によって該周方向に弾性復元力を生じるスプリングと、
前記スプリングの一方の端部に設けられ、前記スプリングから前記弾性復元力を出力する出力部と、
前記スプリングが前記周方向に変形を生じる際に前記スプリングの径方向への移動を規制する移動規制部と、
前記スプリングの前記軸線とは異なる位置で前記軸線に対して平行に延びる回転軸を回転中心として、前記クラッチを切断する際には切断方向に回転し、前記クラッチを接続する際には接続方向に回転する回転体と、
前記回転体と一体で回転可能に前記回転体に設けられ、前記出力部に接触することにより、前記弾性復元力を前記回転体に伝達する伝達部とを備え、
前記回転体には、前記クラッチの切断及び接続の各動作によって生じた反力がトルクとして入力されるとともに、前記スプリングの前記周方向への変形によって生じた前記弾性復元力が、前記出力部及び前記伝達部を介して前記アシスト力として入力され、
前記出力部と前記伝達部との接触点は、前記回転体の前記回転軸及び前記スプリングの前記軸線とは異なる位置で、且つ、前記スプリングの弾性復元力が小さくなる方向に前記回転体が回転する際に、前記スプリングの軸線方向から見て、前記軸線に少なくとも一度近づくように移動する、クラッチ駆動装置。 - 請求項1に記載のクラッチ駆動装置において、
前記回転体の前記回転軸は、前記軸線方向から見て、前記スプリングの外方に位置する、クラッチ駆動装置。 - 請求項1または2に記載のクラッチ駆動装置において、
前記接触点は、前記軸線方向から見て、前記スプリングの外方に位置する、クラッチ駆動装置。 - 請求項1から3のいずれか一つに記載のクラッチ駆動装置において、
前記回転体の前記回転軸と前記接触点との距離は、前記回転体の前記回転軸と前記スプリングの前記軸線との距離よりも小さい、クラッチ駆動装置。 - 請求項4に記載のクラッチ駆動装置において、
前記接触点が前記スプリングの前記軸線と前記回転体の前記回転軸とを結ぶ仮想線上に位置している場合に、前記スプリングの前記軸線と前記接触点との距離は、前記回転体の前記回転軸と前記スプリングの前記軸線との距離よりも小さい、クラッチ駆動装置。 - 請求項1から5のいずれか一つに記載のクラッチ駆動装置において、
前記出力部は、前記スプリングに一体で設けられている、クラッチ駆動装置。 - 請求項1から6のいずれか一つに記載のクラッチ駆動装置において、
前記伝達部は、前記回転体の回転と該回転に伴う前記スプリングの前記周方向への変形とによって、前記出力部と接触しつつ該出力部に相対移動する、クラッチ駆動装置。 - 請求項1から6のいずれか一つに記載のクラッチ駆動装置において、
前記出力部は、前記回転体の回転及び前記スプリングの前記周方向への変形に応じて相対回転するリンクを含む、クラッチ駆動装置。 - 請求項1から8のいずか一つに記載のクラッチ駆動装置において、
前記回転体に対して回転トルクを付与するアクチュエータをさらに備える、クラッチ駆動装置。 - 請求項9に記載のクラッチ駆動装置において、
前記アクチュエータから前記回転体に対して前記回転トルクを伝達する伝達機構をさらに備え、
前記伝達機構は、前記アクチュエータから前記回転トルクが入力される入力軸を有し、
前記入力軸は、前記スプリングの内方に前記軸線に対して平行に延びるように配置されている、クラッチ駆動装置。 - 請求項9または10に記載のクラッチ駆動装置において、
前記アクチュエータは、モータである、クラッチ駆動装置。 - 請求項1から11のいずれか一つに記載のクラッチ駆動装置において、
前記出力部と前記伝達部との接触点は、前記回転体が回転する際に、前記スプリングの前記軸線と前記回転体の前記回転軸とを結ぶ仮想線を通過するように移動する、クラッチ駆動装置。 - 請求項1から12のいずれか一つに記載のクラッチ駆動装置を備えた車両。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2018559630A JP6812458B2 (ja) | 2016-12-29 | 2017-12-28 | クラッチ駆動装置及び車両 |
CN201780081589.4A CN110139994B (zh) | 2016-12-29 | 2017-12-28 | 离合器驱动装置和车辆 |
CA3047906A CA3047906C (en) | 2016-12-29 | 2017-12-28 | Clutch drive device and vehicle |
EP17885966.6A EP3546783B1 (en) | 2016-12-29 | 2017-12-28 | Clutch drive device and vehicle |
US16/445,998 US10844910B2 (en) | 2016-12-29 | 2019-06-19 | Clutch drive device and vehicle |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016257437 | 2016-12-29 | ||
JP2016-257437 | 2016-12-29 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/445,998 Continuation-In-Part US10844910B2 (en) | 2016-12-29 | 2019-06-19 | Clutch drive device and vehicle |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2018124270A1 true WO2018124270A1 (ja) | 2018-07-05 |
Family
ID=62709458
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2017/047197 WO2018124270A1 (ja) | 2016-12-29 | 2017-12-28 | クラッチ駆動装置及び車両 |
Country Status (6)
Country | Link |
---|---|
US (1) | US10844910B2 (ja) |
EP (1) | EP3546783B1 (ja) |
JP (1) | JP6812458B2 (ja) |
CN (1) | CN110139994B (ja) |
CA (1) | CA3047906C (ja) |
WO (1) | WO2018124270A1 (ja) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2019120964A (ja) * | 2017-12-28 | 2019-07-22 | 本田技研工業株式会社 | レバー装置 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60241526A (ja) * | 1984-02-13 | 1985-11-30 | ヴァレオ | クラッチ作動装置 |
JPS6363225U (ja) * | 1986-10-14 | 1988-04-26 | ||
JP2006170227A (ja) | 2004-12-10 | 2006-06-29 | Yamaha Motor Co Ltd | クラッチアクチュエータ及び鞍乗型車両 |
JP2006214478A (ja) * | 2005-02-02 | 2006-08-17 | Hino Motors Ltd | クラッチ操作装置 |
JP2012062966A (ja) * | 2010-09-16 | 2012-03-29 | Univance Corp | クラッチ制御装置 |
Family Cites Families (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ES8606588A1 (es) | 1984-02-13 | 1986-04-16 | Valeo | Un recuperador de desgaste para el mando de un dispositivo de acoplamiento,tal como un embrague |
FR2588629B1 (fr) | 1985-10-11 | 1990-01-12 | Valeo | Dispositif de commande d'un moyen d'accouplement tel que par exemple un embrayage ou un variateur de vitesse ou un frein ou analogue |
DE19503137C1 (de) * | 1995-02-01 | 1996-09-26 | Fichtel & Sachs Ag | Betätigungsvorrichtung, insbesondere für ein Fahrzeug |
DE19723393B4 (de) | 1996-06-05 | 2016-02-18 | Schaeffler Technologies AG & Co. KG | Kraftfahrzeug |
FR2749636B1 (fr) | 1996-06-05 | 2000-12-29 | Luk Getriebe Systeme Gmbh | Dispositif d'actionnement |
FR2753660B1 (fr) | 1996-09-25 | 1999-03-05 | Embrayage a friction a actionneur electromecanique, notamment pour vehicule automobile | |
JP2000201826A (ja) | 1999-01-11 | 2000-07-25 | Joy Tec Kk | 無煙ロ―スタ― |
DE10014225A1 (de) | 2000-03-22 | 2001-09-27 | Bosch Gmbh Robert | Elektromotorischer Kupplungssteller |
JP3666584B2 (ja) | 2001-04-13 | 2005-06-29 | 株式会社タグチ工業 | 建設機械のアタッチメント用旋回装置 |
US7669275B2 (en) * | 2004-11-16 | 2010-03-02 | Asmo Co., Ltd. | Clutch device and motor apparatus having the same |
JP4405464B2 (ja) | 2005-12-28 | 2010-01-27 | 本田技研工業株式会社 | ツインクラッチ装置 |
FR2954429B1 (fr) | 2009-12-21 | 2012-03-09 | Valeo Embrayages | Dispositif d'actionnement a came pour un systeme d'embrayage a friction. |
JP5510195B2 (ja) | 2010-08-31 | 2014-06-04 | 日産自動車株式会社 | 駆動力伝達装置 |
WO2012045151A1 (en) * | 2010-10-04 | 2012-04-12 | Litens Automotive Partnership | Driven component with clutch for selective operation of component |
US8678159B2 (en) * | 2011-01-18 | 2014-03-25 | Tai-Her Yang | Compelling-type centrifugal clutch device with C-shaped joint structure |
JP2013133887A (ja) | 2011-12-27 | 2013-07-08 | Aisin Seiki Co Ltd | クラッチレリーズ装置 |
JP5995439B2 (ja) | 2011-12-28 | 2016-09-21 | 株式会社エフ・シー・シー | 動力伝達装置 |
KR101304193B1 (ko) * | 2012-03-15 | 2013-09-05 | 주식회사평화발레오 | 클러치 액추에이터 |
DE112013005134A5 (de) | 2012-10-24 | 2015-07-16 | Schaeffler Technologies AG & Co. KG | Antriebsklinke für eine verschleißnachstellende Reibkupplung |
KR101417417B1 (ko) | 2012-11-20 | 2014-07-08 | 현대자동차주식회사 | 차량용 클러치 액추에이터 |
JP6200263B2 (ja) | 2013-10-01 | 2017-09-20 | ヤマハ発動機株式会社 | クラッチ装置及びそれを備える鞍乗型車両 |
JP6295690B2 (ja) | 2014-02-04 | 2018-03-20 | スズキ株式会社 | バックトルクリミッターを有するクラッチ |
JP6221793B2 (ja) | 2014-02-05 | 2017-11-01 | アイシン精機株式会社 | 運動変換装置およびクラッチアクチュエータ |
DE112015001413A5 (de) | 2014-03-25 | 2016-12-08 | Schaeffler Technologies AG & Co. KG | Nachstelleinrichtung für eine Reibkupplung |
WO2016024557A1 (ja) | 2014-08-12 | 2016-02-18 | 株式会社エフ・シ-・シ- | 動力伝達装置 |
KR101862471B1 (ko) * | 2016-10-21 | 2018-05-29 | 현대다이모스(주) | 듀얼클러치 액츄에이터 |
-
2017
- 2017-12-28 WO PCT/JP2017/047197 patent/WO2018124270A1/ja unknown
- 2017-12-28 EP EP17885966.6A patent/EP3546783B1/en active Active
- 2017-12-28 CA CA3047906A patent/CA3047906C/en active Active
- 2017-12-28 CN CN201780081589.4A patent/CN110139994B/zh active Active
- 2017-12-28 JP JP2018559630A patent/JP6812458B2/ja active Active
-
2019
- 2019-06-19 US US16/445,998 patent/US10844910B2/en active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60241526A (ja) * | 1984-02-13 | 1985-11-30 | ヴァレオ | クラッチ作動装置 |
JPS6363225U (ja) * | 1986-10-14 | 1988-04-26 | ||
JP2006170227A (ja) | 2004-12-10 | 2006-06-29 | Yamaha Motor Co Ltd | クラッチアクチュエータ及び鞍乗型車両 |
JP2006214478A (ja) * | 2005-02-02 | 2006-08-17 | Hino Motors Ltd | クラッチ操作装置 |
JP2012062966A (ja) * | 2010-09-16 | 2012-03-29 | Univance Corp | クラッチ制御装置 |
Also Published As
Publication number | Publication date |
---|---|
US10844910B2 (en) | 2020-11-24 |
EP3546783A1 (en) | 2019-10-02 |
CA3047906C (en) | 2021-03-30 |
CA3047906A1 (en) | 2018-07-05 |
CN110139994B (zh) | 2021-01-26 |
JP6812458B2 (ja) | 2021-01-13 |
EP3546783B1 (en) | 2021-11-24 |
JPWO2018124270A1 (ja) | 2019-10-31 |
EP3546783A4 (en) | 2019-12-11 |
CN110139994A (zh) | 2019-08-16 |
US20190301541A1 (en) | 2019-10-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5124648B2 (ja) | デュアルマスフライホイール | |
CN102858618B (zh) | 电动动力转向装置 | |
JP5520945B2 (ja) | 調節装置、特に、車両シートの調節装置 | |
JP6210334B2 (ja) | セレクタブルワンウェイクラッチ | |
WO2016038927A1 (ja) | 電動式パワーステアリング装置 | |
CN110094503B (zh) | 车辆的驻车机构 | |
JP4957530B2 (ja) | スタータ | |
WO2018124270A1 (ja) | クラッチ駆動装置及び車両 | |
JP6808756B2 (ja) | クラッチ駆動装置及び車両 | |
JP2021017930A (ja) | ウォーム減速機および電動アシスト装置 | |
JP2013238260A (ja) | セラシ歯車装置 | |
JP4438768B2 (ja) | バルブタイミング調整装置 | |
WO2018124269A1 (ja) | クラッチユニット及び車両 | |
JP7050950B2 (ja) | ギアシフトアクチュエータ | |
JP4793176B2 (ja) | クラッチ用アクチュエータ | |
JP4513450B2 (ja) | アクチュエータ | |
JP2023517721A (ja) | クラッチ | |
JP4539306B2 (ja) | トルクリミット機構およびトルクリミット機構を備えた伝達比可変機構 | |
JP2011236877A (ja) | バルブタイミング調整装置 | |
JP7477016B1 (ja) | シザーズギア及び伝達機構 | |
JP4432344B2 (ja) | クラッチ用アクチュエータ | |
JP4856220B2 (ja) | 自動車用エンジンにおける位相可変装置 | |
JP5896736B2 (ja) | シフト操作装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 17885966 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2018559630 Country of ref document: JP Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 3047906 Country of ref document: CA |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 2017885966 Country of ref document: EP Effective date: 20190625 |